COMPRESSOR ASSEMBLY HAVING DYNAMIC DIFFUSER RING RETENTION
A compressor assembly is disclosed. The compressor assembly may have a compressor housing, which may have an inner wall inclined at a first angle relative to a plane disposed generally orthogonal to a rotational axis of the compressor assembly. The compressor assembly may also have a compressor impeller disposed within the compressor housing. Further, the compressor assembly may have a bearing housing attached to the compressor housing. The bearing housing may have a body portion and a web that may extend outward from the body portion to a web end. The web may be inclined at a second angle relative to the plane. The compressor assembly may have a diffuser ring disposed between the inner wall and the web. The compressor assembly may also have a spring disposed between the web and the diffuser ring. The spring may be configured to apply a generally axial load on the diffuser ring.
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The present disclosure relates generally to a compressor assembly and, more particularly, to a compressor assembly having dynamic diffuser ring retention.
BACKGROUNDInternal combustion engines, for example, diesel engines, gasoline engines, or natural gas engines employ turbochargers to deliver compressed air for combustion in the engine. A turbocharger compresses air flowing into the engine, helping to force more air into combustion chambers of the engine. The increased supply of air allows for increased fuel combustion in the combustion chambers, resulting in increased power output from the engine.
A typical turbocharger includes a shaft, a turbine wheel connected to one end of the shaft, a compressor wheel connected to the other end of the shaft, and bearings to support the shaft. Separate housings connected to each other enclose the compressor wheel, the turbine wheel, and the bearings. Exhaust from the engine expands over the turbine wheel and rotates the turbine wheel. The turbine wheel in turn rotates the compressor wheel via the shaft. The compressor wheel receives cool air from the ambient and forces compressed air into combustion chambers of the engine.
The compressor stage of a turbocharger often includes a diffuser configured to reduce the speed of the air leaving the compressor wheel. Reducing the air speed causes the air pressure within the compressor stage to increase, which in turn helps to deliver compressed air to the combustion chambers of the engine. The compressor diffuser usually includes vanes extending between the bearing housing and the compressor housing. These vanes direct the spinning air from the compressor impeller into the compressor housing volute. Because the compressor housing, the compressor diffuser, and the bearing housing are subject to different and varying temperatures, these components expand and contract to different extents, causing gaps to develop between the tips of the vanes and the compressor housing inner walls. Leakage of air through these gaps can significantly reduce compressor performance.
One attempt to address some of the problems described above is disclosed in U.S. Pat. No. 6,168,375 of LaRue et al. that issued on Jan. 2, 2001 (“the '375 patent”). In particular, the '375 patent discloses a turbocharger with a radial flow compressor having an annular vane diffuser disposed within the compressor housing. The vane diffuser of the '375 patent is positioned within a channel in an axially-facing surface of a compressor housing back plate. The vane diffuser of the '375 patent is also supported at one end by a lip on the back plate and on the other end by a portion of the compressor housing. The '375 patent further discloses a wave-type compression spring interposed between the vane diffuser and the axially-facing back plate to urge the vanes against the wall of the compressor housing forming one side of the diffuser. The '375 patent also discloses that during turbocharger operation, static pressure within the compressor housing volute bleeds back behind the vane diffuser to urge the vane diffuser axially away from the back plate, helping to keep the vanes in contact with the housing. In addition, the '375 patent discloses that the wave spring imposes a pressure load onto the vane diffuser to urge it axially away from the back plate regardless of static pressure conditions. Further, the '375 patent discloses an annular seal disposed within a seal groove formed in the axially-facing back plate surface. The seal of the '375 patent is interposed between the vane diffuser and the back plate and reduces recirculation of air around the backside surface of the vane diffuser.
Although the '375 patent discloses a spring-loaded diffuser, the disclosed diffuser may still not be optimal. For example, the disclosed spring-loaded diffuser design may not be useable in a mixed flow turbocharger that does not have a back plate having axially facing portions. The disclosed diffuser also may not have sufficient room for radial expansion during operation of the turbocharger because the diffuser of the '375 patent is radially constrained by the back plate lip and the compressor housing. Additionally, because the wave spring and the seal of the '375 patent are disposed on the same axially-facing back plate surface, the wave spring may push the diffuser axially away from the back plate surface, reducing the effectiveness of the seal and allowing recirculation of air around the back plate. Further still, the diffuser of the '375 patent requires machining of a channel to accommodate the spring on the axially-facing back plate surface. The need for a machined channel for the spring may increase the manufacturing cost of the compressor assembly of the '375 patent.
The compressor assembly of the present disclosure solves one or more of the problems set forth above and/or other problems of the prior art.
SUMMARYIn one aspect, the present disclosure is directed to a compressor assembly. The compressor assembly may include a compressor housing. The compressor housing may include an inner wall inclined at a first angle relative to a plane disposed generally orthogonal to a rotational axis of the compressor assembly. The compressor assembly may also include a compressor impeller disposed within the compressor housing. Further, the compressor assembly may include a bearing housing attached to the compressor housing. The bearing housing may include a body portion and a web. The web may extend outward from the body portion to a web end. The web may be inclined at a second angle relative to the plane. The compressor assembly may also include a diffuser ring disposed between the inner wall and the web. In addition, the compressor assembly may include a spring disposed between the web and the diffuser ring. The spring may be configured to apply a generally axial load on the diffuser ring.
In another aspect, the present disclosure is directed to a diffuser ring. The diffuser ring may include a back plate. The back plate may include a front face inclined at a first angle relative to a plane disposed generally orthogonal to a rotational axis. The back plate may also include a rear face inclined at a second angle relative to the plane. Further the back plate may include a top face extending axially from the front face towards the rear face. In addition, the back plate may include a bottom face extending axially from the front face towards the rear face. The diffuser ring may also include a vane extending outward from the front face.
In yet another aspect, the present disclosure is directed to a turbocharger. The turbocharger may include a turbine housing. The turbocharger may also include a turbine wheel disposed within the turbine housing and configured to be driven by exhaust received from an engine. Further, the turbocharger may include a compressor housing. The compressor housing may include an inner wall inclined at a first angle relative to a plane disposed generally orthogonal to a rotational axis of the turbocharger. The turbocharger may also include a compressor impeller disposed within the compressor housing. The turbocharger may include a shaft connecting the turbine wheel and the compressor impeller. In addition, the turbocharger may include a bearing housing attached to the compressor housing and the turbine housing. The bearing housing may include a body portion and a web. The web may extend outward from the body portion to a web end. The web end may be inclined at a second angle relative to the plane. The turbocharger may further include a diffuser ring disposed between the inner wall and the web. The turbocharger may also include a spring disposed between the web and the diffuser ring, the spring being configured to apply a generally axial load on the diffuser ring.
Compressor stage 12 may be enclosed by compressor housing 40. Turbine stage 14 may be enclosed by turbine housing 42. Bearing housing 44 may enclose bearings (not shown) that may support shaft 18. Bearing housing 44 may be attached to compressor housing 40 via bolts 46. Likewise, bearing housing 44 may be attached to turbine housing 42 via bolts 48. Compressor impeller 16, shaft 18, turbine wheel 34, compressor housing 40, turbine housing 42, and bearing housing 44 may be disposed around rotational axis 50 of turbocharger 10.
Exhaust gases exiting the engine (not shown) may enter turbine housing 42 via turbine inlet 52 and exit turbine housing 42 via turbine outlet 54. The hot exhaust gases may move through turbine housing 42, expanding against turbine blades 38, rotating turbine wheel 34. Rotation of turbine wheel 34 may rotate shaft 18, which in turn may rotate compressor impeller 16. Air may enter compressor housing 40 via compressor inlet 56 and exit compressor housing 40 via compressor outlet 58. As air moves through compressor stage 12, compressor impeller 16 may spin and accelerate the air. Compressor stage 12 may include diffuser ring 60, which may help slow down the air, causing an increase in the pressure of the air within compressor stage 12. Compressed air from compressor stage 12 may be directed into the engine.
As further illustrated in
As also illustrated in
Bearing housing flange 106 may extend radially outward from web end 108 to bearing housing flange end 110. In one exemplary embodiment as illustrated in
Bearing housing flange 106 may also include a flange recess 120, which may extend axially inwards from flange front face 112 towards flange rear face 114. Flange recess 120 may extend radially from adjacent web end 108 to recess outer edge 122. In one exemplary embodiment as illustrated in
Web 104 may include a first web face 126, ledge 128, and second web face 130. First web face 126 may extend outward from adjacent outer edge 78 of third row 32 to ledge 128 disposed between outer edge 78 and web end 108. First web face 126 may be inclined at an angle “θ2” relative to an axial plane disposed generally orthogonal to rotational axis 50. First web face 126 may be disposed opposite to and axially spaced apart from inner wall 132 of diffuser portion 70 of compressor housing 40. Inner wall 132 may be inclined at an angle “θ3” relative to an axial plane disposed generally orthogonal to rotational axis 50. First web face 126 and inner wall 132 may form passageway 134. First web face 126 and inner wall 132 may have a smooth shape that may help ensure that air can travel from outer edges 78 of compressor blades 26 through passageway 134 without significantly altering a velocity or direction of the air. In one exemplary embodiment, first web face 126 may have a smooth curvilinear shape that may conform to a shape of compressor blades 26. Likewise, inner wall 132 may have a smooth curvilinear shape that may conform to a surface defined by outer edges 78 of compressor blades 26 in first, second, and third rows 28, 30, 32.
Ledge 128 may have a generally cylindrical ledge outer surface 136, which may have a radius “R5” relative to rotational axis 50. Ledge outer surface 136 may extend axially from first web face 126 to ledge end 138 disposed between first web face 126 and compressor rear end 64. Radius R5 of ledge outer surface 136 may be larger than a radius “R2” of outer edges 78 of compressor blades 26 in third row 32. Ledge outer surface 136 may also include a generally annular groove 140. Ledge 128 may include ledge axial face 142 that may be axially spaced apart from first web face 126. Ledge axial face 142 may be disposed at ledge end 138. Ledge axial face 142 may extend radially outward from ledge outer surface 136 to second web face 130. In one exemplary embodiment as illustrated in
Diffuser ring 60 may be disposed between inner wall 132 of compressor housing 40 and second web face 130 of bearing housing 44. Diffuser ring 60 may include back plate 146 and one or more vanes 148. In one exemplary embodiment as illustrated in
Top face 156 of back plate 146 may extend axially from front face 154 to axial rear face 162 disposed adjacent recess seating surface 124. Top face 156 may have a generally cylindrical shape. Top face 156 may be disposed adjacent inner face 166 of volute rear wall 100. Inner face 166 of volute rear wall 100 may also have a generally cylindrical shape. Top face 156 of back plate 146 may be radially separated from inner face 166 by a radial gap 168. Bottom face 158 of back plate 146 may extend axially from front face 154 towards inclined rear face 160 disposed adjacent second web face 130. Bottom face 158 may abut on ledge outer surface 136. Bottom face 158 may have a generally cylindrical shape. It is contemplated, however, that bottom face 158 may have a non-cylindrical shape. Seal member 170 may be disposed in groove 140 between ledge outer surface 136 and bottom face 158. In one exemplary embodiment as illustrated in
Axial rear face 162 of back plate 146 may be axially separated from front face 154 of back plate 146. Axial rear face 162 may extend radially inward from top face 156 to adjacent web end 108. Axial rear face 162 may connect top face 156 with inclined rear face 160. In one exemplary embodiment as shown in
Recess 164 may be disposed adjacent bottom face 158 and between bottom face 158 and inclined rear face 160. Recess 164 may include recess upper face 174 and recess side face 176. Recess upper face 174 may have a generally cylindrical shape and may extend axially from inclined rear face 160 towards front face 154. Recess upper face 174 may be radially separated from ledge outer surface 136. In one exemplary embodiment as illustrated in
Vane 148 may extend radially and axially outward from front face 154 of back plate 146 to vane tip 178. In one exemplary embodiment as illustrated in
Wave spring 184 may be disposed in recess 164 between ledge axial face 142 and recess side face 176 of recess 164 in back plate 146. Wave spring 184 may have a generally annular shape having an inner radius, which may be larger than a radius R5 of ledge outer surface 136. Wave spring 184 may include a plurality of waves on axial face 186 of wave spring 184. In one exemplary embodiment, wave spring 184 may have about 11 waves. Wave spring 184 may have an axial thickness ranging from 2 mm to 4 mm. In an assembled configuration as illustrated in the exemplary embodiment of
As also illustrated in
Vaneless space 200 may be inclined at an angle “θ6” relative to an axial plane disposed generally orthogonal to rotational axis 50. Angle θ6 may be measured between an axis 206 of vaneless space 200 and an axial plane disposed generally orthogonal to rotational axis 50. For example, axis 206 of vaneless space 200 may be defined as a line connecting midpoints 202 and 204 of passageway 134. Midpoint 202 may be disposed adjacent an outer edge 78 of compressor blades 26. Midpoint 204 may be disposed adjacent a vane leading edge 180. As used in this disclosure midpoint 202 may be disposed within passageway 134 halfway between inner wall 132 and second web face 130. Similarly, midpoint 204 may be disposed within passageway 134 halfway between inner wall 132 and front face 154 of back plate 146. One of ordinary skill in the art would recognize that axis 206 may not always be disposed parallel to inner wall 132 and/or second web face 130. As also illustrated in
The above description refers to angles θ1, θ2, θ3, θ4, θ5, and θ6. It is contemplated that angles θ1, θ2, θ3, θ4, θ5, and θ6 may be equal or unequal. In one exemplary embodiment, each of angles θ1, θ2, θ3, θ4, θ5, or θ6 may range from about 0° to about 45°.
As illustrated in
As further illustrated in
Returning to
An axial distance “B” (see
Compressor housing 40 may have a compressor housing flange 270 attached to volute top wall 98 and volute rear wall 100. Compressor housing flange 270 may have a generally cylindrical flange outer surface 272. Flange outer surface 272 may have a radius “R7” relative to rotational axis 50. Compressor housing flange 270 may also include flange inner surface 274, which may have a radius “R8” relative to rotational axis 50. Radius R8 may be larger than or about equal to radius R3 of flange outer surface 116 of bearing housing flange 106. Radius R8 may also be smaller than radius R7. Flange inner surface 274 may be disposed adjacent to and may abut on flange outer surface 116 of bearing housing flange 106 of bearing housing 44. Compressor housing flange 270 may include a clamping face 276, which may extend radially from flange inner surface 274 at radius R8 to flange outer surface 272 at radius R7. Clamping face 276 may have a radial width “W2,” which may be smaller than a width W1 of clamping plate 262.
Clamping face 276 of compressor housing flange 270 may include compressor flange recess 278 and compressor flange lip 280. Compressor flange recess 278 may extend axially inwards from clamping face 276 towards compressor front end 62 forming compressor flange lip 280 on clamping face 276. Compressor flange recess 278 may extend radially outward from flange inner surface 274 to recess outer edge 282 disposed between flange inner surface 274 and flange outer surface 272. Compressor flange recess 278 may have a radial width “W3,” which may be smaller than a radial width W2 of clamping face 276. In one exemplary embodiment width W3 may range from about 70% to about 90% of width W2. As illustrated in
Recess surface 284 of compressor housing flange 270 may include a plurality of holes 286. Like holes 268, holes 286 may be circumferentially spaced from each other. A circumferential spacing between holes 286 may be uniform or non-uniform. Holes 286 may be arranged so as to align with holes 268. Holes 286 may also be threaded. Bolts 46 may pass through holes 268 and may be threadingly received in holes 286 to help connect clamping plate 262 with compressor housing flange 270. In some exemplary embodiments, bolts 46 may be also threadingly received in holes 268. Although
Clamping plate 262 may include clamping plate overhang portion 288, which may extend radially inward from adjacent flange inner surface 274. Overhang portion 288 may include a front face portion 290 that may abut on flange rear surface 114 of bearing housing flange 106. As illustrated in
Turbine housing 42 may have a turbine housing wall 320. Turbine housing wall 320 may include a notch 322. Notch 322 may have a notch inner surface 324 and a notch rear wall 326. Notch inner surface 324 may have a generally cylindrical shape disposed around rotational axis 50. Notch rear wall 326 may extend radially inward from notch inner surface 324 and may be disposed generally orthogonal to rotational axis 50. Turbine housing wall 320 may also include turbine inner surface 328, which may enclose turbine wheel 34 (see
Clamping face 330 of turbine housing wall 320 may include turbine flange recess 334 and turbine wall lip 336. Turbine flange recess 334 may extend axially inwards from clamping face 330 towards turbine inner surface 328 forming turbine wall lip 336. Turbine flange recess 334 may extend radially outward from notch inner surface 324 to recess outer edge 338 disposed between notch inner surface 324 and turbine wall outer end 332. Turbine flange recess 334 may have a radial width “W5,” which may be smaller than a radial width W4 of clamping plate 312. In one exemplary embodiment radial width W5 may range from about 70% to about 90% of width W4. As illustrated in
Bearing housing 44 may include a bearing housing flange 344. Bearing housing flange 344 may have front face 346, rear face 348 disposed opposite front face 346, and bearing flange outer surface 350. Bearing housing flange 344 may abut on notch rear wall 326 of turbine housing wall 320 such that bearing flange outer surface 350 may be disposed adjacent to and may abut on notch inner surface 324. Clamping plate 312 may include an overhang portion 352, which may extend radially inward from holes 318. Overhang portion 352 may include a rear face portion 354 that may abut on front face 346 of bearing housing flange 344. As illustrated in
Bolts 48 may pass through holes 318 and may be threadingly received in holes 342 to help connect clamping plate 312 with turbine housing wall 320 and bearing housing flange 344. In some exemplary embodiments, bolts 48 may be also threadingly received in holes 318. Although
The disclosed compressor assembly 90 may be implemented to help reduce or eliminate leakage of air through gaps between vane tips 178 of compressor diffuser ring 60 and inner wall 132 of compressor housing 40. Compressor assembly 90 may also be implemented to help improve an efficiency of compressor stage 12 by using shim 246 dimensionally matched to turbocharger cartridge 256 to help reduce or eliminate gaps between vane tips 178 and inner wall 132. Additionally, compressor assembly 90 may be implemented to reduce or eliminate failure of compressor blades induced by excitation of compressor blades 26 caused by pressure wakes generated by vanes 148 in diffuser ring 60. Further, compressor assembly 90 may be implemented to help ensure that compressor housing 40, bearing housing 44, and turbine housing 42 may be assembled without inducing bending loads on bolts 46, 48. The disclosed compressor assembly 90 may also be implemented help reduce wear on internal components of compressor assembly 90 caused by thermally induced relative movement between the components.
Referring to
Compressor assembly 90 may include numerous features that help to reduce or eliminate gaps between vane tips 178 and inner wall 132 of compressor housing 40. For example, compressor assembly 90 may include a wave spring 184 disposed between second web face 130 and back plate 146 of diffuser ring 60. Wave spring 184 may exert an axial force on back plate 146 forcing diffuser ring 60 to move towards compressor front end 62 and pushing vane tips 178 to firmly come into contact with inner wall 132 of compressor housing 40. By forcing vane tips 178 to firmly abut on inner wall 132, wave spring 184 may help reduce or eliminate gaps between vane tips 178 and inner wall 132 at all operating conditions of turbocharger 10. Wave spring 184 may also help reduce or eliminate damage caused to vanes 148 when the turbocharger is not operational by helping to urge vane tips 178 to come into contact with inner wall 132. Allowing vane tips 178 to remain in contact with inner wall 132 in this manner may help prevent excessive vibration of vanes 148, which in turn may help reduce or eliminate damage to vanes 148.
Furthermore, during operation of turbocharger 10, high pressure air from volute 72 may bleed through radial gap 168 into cavity 172. The high pressure air may help push back plate 146 away from second web face 130 toward compressor front end 62, which in turn may urge vane tips 178 to firmly come into contact with inner wall 132 of compressor housing 40. By forcing vane tips 178 to firmly abut on inner wall 132, bleed air in cavity 172 may help reduce or eliminate gaps between vane tips 178 and inner wall 132 during high pressure operation of compressor stage 12.
Radial gap 168 and seal member 170 may also help back plate 146 of diffuser ring 60 to freely expand thermally during operation of compressor stage 12. For example, diffuser ring 60 may be made of aluminum, aluminum alloy, or other alloys, which has a relatively high coefficient of thermal expansion compared to compressor housing 40 and bearing housing 44, both of which may be made of an iron alloy or other alloys. The radial gap 168 and the compressive nature of seal member 170 may allow back plate 146 to expand without coming into contact with or interfering with inner face 166 of volute rear wall 100 of bearing housing 44. Moreover, because seal member 170 is disposed on ledge outer surface 136, which is disposed generally orthogonal to wave spring 184, the axial force exerted by wave spring 184 may not diminish the compressive forces generated in seal member 170. As a result operation of wave spring 184 may not diminish the strength of the seal generated by seal member 170 between ledge outer surface 136 and bottom face 158 of back plate 146. Consequently, seal member 170 may be able to maintain a very effective seal, preventing recirculation of air from volute 72 through cavity 172 and into passageway 134 during the entire range of operation of turbocharger 10, helping to improve the efficiency of compressor stage 12.
Referring to
Referring to
Referring to
Additionally, when turbocharger 10 with four tabs 226 is mounted on a horizontal surface with the gravitational direction being generally orthogonal to the horizontal surface, first and second diametrical axes 237 and 238 may be positioned symmetrically about the gravitational direction. Positioning first and second diametrical axes 237, 238 in this manner may allow an entire weight of turbocharger 10 to be about equally distributed on each of the four tabs 226. Furthermore, such an arrangement may also allow additional radial loads generated by the operation of turbocharger 10 to be distributed about equally between the four tabs 226.
Referring to
Referring to
It will be apparent to those skilled in the art that various modifications and variations can be made to the disclosed compressor assembly. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the disclosed compressor assembly. It is intended that the specification and examples be considered as exemplary only, with a true scope being indicated by the following claims and their equivalents.
Claims
1. A compressor assembly, comprising:
- a compressor housing, including an inner wall inclined at a first angle relative to a plane disposed generally orthogonal to a rotational axis of the compressor assembly;
- a compressor impeller disposed within the compressor housing;
- a bearing housing attached to the compressor housing, the bearing housing including: a body portion; and a web extending outward from the body portion to a web end, the web being inclined at a second angle relative to the plane;
- a diffuser ring disposed between the inner wall and the web; and
- a spring disposed between the web and the diffuser ring, the spring being configured to apply a generally axial load on the diffuser ring.
2. The compressor assembly of claim 1, wherein the web includes:
- a ledge disposed between the body portion and the web end;
- a first web face extending from the body portion to the ledge; and
- a second web face extending from the ledge to the web end, wherein the diffuser ring is disposed between the second web face and the inner wall.
3. The compressor assembly of claim 2, wherein the ledge includes:
- a ledge outer surface extending axially from the first web face to a ledge end disposed between the first web face and a compressor rear end; and
- a ledge axial face extending radially outward from the ledge end to the second web face.
4. The compressor assembly of claim 3, wherein the diffuser ring includes:
- a back plate extending from a back plate leading edge to a back plate trailing edge, wherein the back plate leading edge is disposed adjacent the ledge outer surface, and the back plate is separated from the second web face by a cavity; and
- a vane extending from the back plate towards the inner wall.
5. The compressor assembly of claim 4, wherein the vane includes a vane tip configured to abut on the inner wall.
6. The compressor assembly of claim 5, wherein the back plate includes:
- a front face disposed opposite the inner wall;
- a bottom face configured to abut on the ledge outer surface;
- a rear face separated from the second web face by the cavity; and
- a recess disposed between the bottom face and the rear face, the recess being located adjacent the ledge outer surface, the recess including: a recess upper face extending axially from the rear face towards the front face; and a recess side face extending between the recess upper face and the bottom face.
7. The compressor assembly of claim 6, wherein the spring is disposed in the recess between the ledge axial face and the recess side face.
8. The compressor assembly of claim 7, wherein the spring is a generally annular wave spring having an inner radius larger than a radius of the ledge outer surface.
9. The compressor assembly of claim 8, wherein
- the ledge outer surface includes an annular groove, and
- a seal member is disposed in the annular groove between the ledge outer surface and the bottom face of the back plate.
10. The compressor assembly of claim 8, wherein
- the compressor housing includes a volute having a volute rear wall; and
- the bearing housing includes a bearing housing flange extending radially outward from the web end, the bearing housing flange being configured to be connected to the volute rear wall.
11. The compressor assembly of claim 10, wherein
- the volute rear wall has an inner face, and
- the back plate includes a top face separated from the inner face by a radial gap.
12. The compressor assembly of claim 1, wherein the first angle is about equal to the second angle.
13. A diffuser ring comprising:
- a back plate, including: a front face inclined at a first angle relative to a plane disposed generally orthogonal to a rotational axis; a rear face inclined at a second angle relative to the plane; a top face extending axially from the front face towards the rear face; and a bottom face extending axially from the front face towards the rear face; and
- a vane extending outward from the front face.
14. The diffuser ring of claim 13, wherein
- the front face extends from a back plate leading edge to a back plate trailing edge; and
- the vane extends from a vane leading edge to a vane trailing edge disposed between the back plate leading edge and the back plate trailing edge.
15. The diffuser ring of claim 14, further including a recess disposed adjacent the bottom face, the recess including:
- a recess upper face extending axially from the rear face towards the front face; and
- a recess side face extending radially inwards from the recess upper face to the bottom face.
16. The diffuser ring of claim 14, wherein the vane leading edge intersects with the front face at a location disposed between the back plate leading edge and the back plate trailing edge.
17. A turbocharger, comprising:
- a turbine housing;
- a turbine wheel disposed within the turbine housing and configured to be driven by exhaust received from an engine;
- a compressor housing, including an inner wall inclined at a first angle relative to a plane disposed generally orthogonal to a rotational axis of the turbocharger;
- a compressor impeller disposed within the compressor housing;
- a shaft connecting the turbine wheel and the compressor impeller;
- a bearing housing attached to the compressor housing and the turbine housing, the bearing housing including: a body portion; and a web extending outward from the body portion to a web end, the web being inclined at a second angle relative to the plane;
- a diffuser ring disposed between the inner wall and the web; and
- a spring disposed between the web and the diffuser ring, the spring being configured to apply a generally axial load on the diffuser ring.
18. The turbocharger of claim 17, wherein the web includes:
- a ledge disposed between the body portion and the web end;
- a first web face extending from the body portion to the ledge; and
- a second web face extending from the ledge to the web end, wherein the diffuser ring is disposed between the second web face and the inner wall.
19. The turbocharger of claim 18, wherein the ledge includes:
- a ledge outer surface extending axially from the first web face to a ledge end disposed between the first web face and a compressor rear end; and
- a ledge axial face extending radially outward from the ledge end to the second web face.
20. The turbocharger of claim 19, wherein the diffuser ring includes:
- a back plate extending from a back plate leading edge to a back plate trailing edge, wherein the back plate leading edge is disposed adjacent the ledge outer surface, and the back plate is separated from the second web face by a cavity; and
- a vane extending from the back plate towards the inner wall.
Type: Application
Filed: Mar 9, 2015
Publication Date: Sep 15, 2016
Applicant: Caterpillar Inc. (Peoria, IL)
Inventors: Richard E. ANNATI (Lafayette, IN), Jeffrey W. McCORMACK (Fishers, IN), Thomas J. WILLIAMS (Milford, MI), Gary W. POWERS (Lafayette, IN), David E. HARNADEK (Waterford, MI)
Application Number: 14/642,110