The present invention relates generally to a vehicle and, in particular, to a vehicle with a charged powertrain assembly.
Vehicles including utility vehicles, all-terrain vehicles, tractors, and others are known. Such vehicles may include engines, transmissions, and forced-air inducers (e.g., superchargers, turbochargers). By providing a vehicle with a charged powertrain assembly, the power output of the powertrain assembly may be increased.
A forced-air inducer, such as a supercharger or a turbocharger, operates by compressing pre-combustion air flowing into the engine. However, compressing the pre-combustion air may increase the temperature of the air. In order to maintain the temperature of the intake air, an intercooler may be provided to decrease the temperature of the charged or pressurized air flowing from the forced-air inducer and into the engine.
In one embodiment of the present disclosure, a utility vehicle, comprises a plurality of ground-engaging members, a lower frame supported by the ground-engaging members which has a front portion and a rear portion, an open-air seating area supported by the lower frame between the front and rear portions, an upper frame coupled to the lower frame and cooperating to generally surround the seating area, a powertrain assembly supported by the lower frame and including an engine, a shiftable transmission, and a continuously variable transmission, and a cooling assembly operably coupled to the powertrain assembly and extending from the front portion to the rear portion of the lower frame. The cooling assembly has a first cooling circuit configured to alter a temperature of the engine and a second cooling circuit configured to alter a temperature of intake air received within the engine.
In another embodiment of the present disclosure, a utility vehicle comprises a plurality of ground-engaging members and a frame assembly supported by the ground-engaging members, which has a lower frame and an upper frame. The lower frame has a front portion and a rear portion. The utility vehicle further comprises an open-air operator area supported by the frame assembly, a powertrain assembly supported by the rear portion of the lower frame which includes an engine, a shiftable transmission, and a clutch assembly, and a cooling assembly including a first heat exchanger positioned at the front portion of the lower frame for cooling the engine and a second heat exchanger positioned at the rear portion of the lower frame for cooling intake air for the engine.
In a further embodiment of the present disclosure, a utility vehicle comprises a plurality of ground-engaging members, a frame supported by the ground-engaging members, and a powertrain assembly supported by the frame. The powertrain assembly includes an engine supported by the frame having a crankshaft and a continuously variable transmission having a first clutch assembly operably coupled to the crankshaft, a second clutch assembly operably coupled to the first clutch assembly, and a housing generally enclosing the first and second clutch assemblies. The second clutch assembly includes a stationary sheave and a moveable sheave. The powertrain assembly also includes a shiftable transmission operably coupled to the engine through the continuously variable transmission. The shiftable transmission includes a housing having a mounting surface for coupling to the housing of the continuously variable transmission and a shaft operably coupled to the second clutch assembly. The shaft extends less than 160 mm from the mounting surface of the housing of the shiftable transmission and an inner surface of the moveable sheave is positioned less than 55 mm from the mounting surface of the shiftable transmission.
In another embodiment of the present disclosure, a utility vehicle comprises a plurality of ground-engaging members, a frame supported by the ground-engaging members, and a powertrain assembly supported by the frame. The powertrain assembly includes an engine supported by the frame, a continuously variable transmission supported by the frame and having a structural housing member, and a shiftable transmission operably coupled to the engine through the structural housing member of the continuously variable transmission. The shiftable transmission includes a first mounting surface coupled to a first portion of the structural housing member of the continuously variable transmission and the engine has a second mounting surface coupled to a second portion of the structural housing member of the continuously variable transmission, and mounting the first mounting surface of the shiftable transmission to the structural housing member fixes an orientation of the shiftable transmission relative to the engine.
In a further embodiment of the present disclosure, a utility vehicle comprises a plurality of ground-engaging members, a frame supported by the ground-engaging member, an operator area having side-by-side seating supported by the frame, and a powertrain assembly which includes an engine having a first cylinder, a second cylinder in line with the first cylinder, and a crankshaft. The engine is configured for a 270-degree firing timing. The powertrain assembly further includes a gaseous charger operably coupled to the engine.
In yet another embodiment of the present disclosure, a utility vehicle includes a plurality of ground-engaging members, a frame supported by the ground-engaging members, an operator area including side-by-side seating, and a powertrain assembly supported by the frame. The powertrain assembly includes an engine supported by the frame, a turbocharger operably coupled to the engine and having a turbine housing and a compressor housing, and an exhaust manifold integral with the turbine housing of the turbocharger.
In yet a further embodiment of the present disclosure, a unitary housing member for a powertrain assembly of a vehicle comprises an exhaust manifold configured to mount to an engine, and a turbine housing of a turbocharger integral with the exhaust manifold.
The above mentioned and other features of this invention, and the manner of attaining them, will become more apparent and the invention itself will be better understood by reference to the following description of embodiments of the invention taken in conjunction with the accompanying drawings, where:
Corresponding reference characters indicate corresponding parts throughout the several views. Unless stated otherwise the drawings are proportional.
The embodiments disclosed below are not intended to be exhaustive or to limit the invention to the precise forms disclosed in the following detailed description. Rather, the embodiments are chosen and described so that others skilled in the art may utilize their teachings. While the present disclosure is primarily directed to a utility vehicle, it should be understood that the features disclosed herein may have application to other types of vehicles such as other all-terrain vehicles, motorcycles, snowmobiles, and golf carts.
Referring to
Vehicle 2 further includes a lower frame assembly 10 (partially shown in
Vehicle 2 also includes an open-air operator area 20 which includes seating 22 for one or more passengers. As such, operator area 20 is exposed to ambient air and is not fully enclosed. Upper frame assembly 19 may be positioned generally around operator area 20 such that seating 22 is at least partially surrounded by upper frame assembly 19. Additionally, side nets or doors 29 may be positioned along the sides of operator area 20 and seating 22. Illustratively, seating 22 includes an operator seat and a passenger seat, however, seating 22 may also include rear seats for additional passengers. Seating 22 may include a seat back 24 and a seat bottom 26 for at least the operator and a passenger.
Operator area 20 further includes a plurality of operator controls 28, such as a steering wheel 27, by which an operator may provide input for operating vehicle 2. Additionally, the steering assembly, which includes steering wheel 27, may be configured for a 1.5 turn for lock to lock. Various operator controls, including the steering assembly, are further described in International Patent Application No. PCT/US13/64516, filed on Oct. 11, 2013, the complete disclosure of which is expressly incorporated by reference herein. Operator area 20 and controls 28 may further include an HVAC system for the comfort of the operator and the passengers.
Referring to
Referring to
Referring to
Referring to
Cover shim 512 directly abuts and contacts shock cylinder 36a and is coupled to shock cylinder with fasteners 518 which extend through apertures 520 in cover shim 512 and apertures 522 in shock cylinder 36a. Additionally, the length of cover shim 512 may be greater than the length of preload shim 514 and top shim 516.
Preload shim 514 is positioned adjacent cover shim 512 such that cover shim 512 is intermediate preload shim 514 and shock cylinder 36a. Preload shim 514 includes a center opening 524 through which fasteners 518 extend when coupling to shock cylinder 36a. As shown in
In operation, when vehicle 2 is traversing level terrain, gases, hydraulic fluid, or other fluid within shock cylinder 36a flows through passageways 506, 508, thereby bypassing the damping system of shock absorbers 36. The fluid then travels downward through channels 504 and through bleed hole 509 which allows fluid to then flow along the underside of piston 500. However, as shock absorber 36 compresses, for example during jounce when vehicle 2 contacts an object, the fluid then flows from the upper end of shock cylinder 36a and along the upper surface of piston 500. During rebound, fluid bypasses piston 500 by flowing downwardly through shock cylinder 36a, through bleed hole 509, and upwardly through channels 504. Fluid may then flow into inner sleeve 501 through additional bleed holes at a top portion of inner sleeve 501. Additional details of shock absorbers 36 may be disclosed in International Patent Application No. PCT/US13/64516, filed on Oct. 11, 2013, the complete disclosure of which is expressly incorporated by reference herein.
Referring to
As shown in
Preload shim 514′ is positioned adjacent cover shim 512′ and includes a center opening 524′ through which fasteners 518 extend through when coupling to shock cylinder 36a. As shown in
As shown in
Referring to
By providing three pistons 58a, 58b, and 58c and three respective sets of brake pads 60a and 60b, 62a and 62b, and 64a and 64b, the size of brake caliper 54 remains compact while providing sufficient braking for an off-road vehicle on various terrain. In one embodiment, brake caliper 54 is operably coupled to a master cylinder and may be configured to provide braking power to less than all of pistons 58a, 58b, 58c at any given time, or alternatively, may be configured to provide braking power to all three pistons 58a, 58b, 58c simultaneously to increase braking power. Additionally, the triple-piston configuration of brake caliper 54 allows brake pads 60a and 60b, 62a and 62b, and 64a and 64b to wear more evenly. The triple-piston configuration of brake caliper 54 also may slow the increase in temperature of brake disc 52 and brake caliper 54 during operation thereof.
Rear wheels 8 may also include hub assemblies similar to hub assemblies 50, including a brake disc and a triple-piston brake caliper. Alternatively, rear wheels 8 may include dual-piston calipers.
Referring to
As shown in
Illustrative engine 72 may be 925 cc and be configured for 135 horsepower at approximately 8,000 rpm. As shown in
During operation of engine 72, pistons 82 are configured to reciprocate within cylinders 80 and crankshaft 84 rotates. In one embodiment, engine 72 is configured to operate with a 270-degree firing timing or order, which may be initiated by an engine control unit of powertrain assembly 270. More particularly, as shown in
As shown from below in
Engine 72 includes a mounting surface 88 for coupling with CVT 76. In particular, CVT 76 includes a housing 90 having an inner portion or cover 92 and an outer portion or cover 94 coupled together. CVT housing 90 also includes an intake port 95 for receiving air to cool CVT 76 and an exhaust port 97 to exhaust air from CVT 76. Inner cover 92 includes a mounting surface 96 which generally abuts mounting surface 88 of engine 72 to couple engine 72 to CVT 76. More particularly, upper and lower crankcase portions 83a, 83b each include mounting bosses 99 for coupling with CVT 76. As such, engine 72 and CVT 76 are in direct contact with each other which allows for a compact configuration of powertrain assembly 70. Additionally, as shown in
Referring to
Referring to
As shown in
Conversely, moveable sheave 120 of drive clutch 110 is configured for lateral movement relative to stationary sheave 122 in order to engage belt 116 and effect various drive ratios. Washers 148 and a bearing 150 are positioned intermediate stationary sheave 122 and moveable sheave 120 to define a belt groove or path for belt 116. Washers 148 and bearing 150 are not positioned within center opening 124 of stationary sheave 122 because the diameter of center opening 124 is less than the diameter of washers 148 and the diameter of bearing 150.
Moveable sheave 120 includes a tower or base member 130, an intermediate member or spider member 132 positioned adjacent tower member 130, and a cover member 134 positioned adjacent spider member 132, such that spider member 132 is intermediate tower member 130 and cover member 134. Cover member 134 is coupled to tower member 130 with fasteners 144 which are received within mounting bosses 146 on tower member 130. Cover member 134 includes a center opening 154 for engaging fastener 98.
Moveable sheave 120 also includes a plurality of weights, illustratively flyweights 136, which are rotatably coupled to tower member 130 with pins 138 and fasteners 140. Flyweights 136 are centrifugal weights which may pivot radially to cause moveable sheave 120 to move or slide laterally relative to stationary sheave 122, as detailed further herein.
As shown in
Position members 142 are generally “U” shaped and extend around a closed side 175 of posts 156 of spider member 132. An open end 176 of position members 142 generally aligns with an open side 178 of posts 156 such that bearing 160 is exposed, as detailed further herein. Position members 142 are removably coupled to spider member 132 and are configured to slide radially relative to tower member 130 and spider member 132 through angled or tapered side walls 180. In one embodiment, side walls 180 of position members 142 are angled 15-30 degrees relative to the radial direction of drive clutch 110. More particularly, side walls 180 of position member 142 have an inner surface 182 angled relative to posts 156 and an outer surface 184 which is angled relative to post 156 but is generally parallel to an angled inner portion 186 of tower member 130. In this way, position members 142 locate spider member 132 within tower member 130 and take up any tolerance between tower member 130 and posts 156 of spider member 132. Additionally, if posts 156 and/or angled inner portion 186 of tower member 130 become worn, position member 142 can slide relative to tower member 130 and posts 156 in order to take up additional tolerances therebetween.
As with stationary sheave 122, moveable sheave 120 also engages post 123. More particularly, splined center opening 152 of spider member 132 engages second splined portion 128 of post 123. Additionally, a bushing 188 and a bearing 190 are positioned within a center opening 202 of tower member 130 in order to engage an additional portion of post 123. Post 123 is further coupled to cover member 134 of moveable sheave 120 through a bearing 204, a sleeve member 206, a stop member 208, a washer or spacer 210, and fastener 98. More particularly, bearing 204 is positioned within center opening 154 of cover member 134 and sleeve member 206 is received through bearing 204 and engages a distal portion of post 123. Sleeve member 206 includes a shoulder 212 which may abut cover member 134 in order to prevent lateral movement of sleeve member 206. Post 123 includes a cylindrical opening 214 and stop member 208 is received therein. A lip 216 of stop member 208 engages the distal end of post 123. Spacer 210 abuts lip 216 of stop member 208 and a head 218 of fastener 98 abuts spacer 210. Fastener 98 is received within cylindrical opening 214 of post 123 to secure post 123 to drive clutch 110.
During operation of CVT 76, drive clutch 110 rotates with crankshaft 84 through post 123 because a distal end of crankshaft 84 is received within tapered volume 125 of post 123. At various operating conditions of vehicle 2, drive clutch 110 rotates at a speed which causes flyweights 136 to pivot about pin 138. The centrifugal force on flyweights 136 causes flyweights 136 to pivot or rotate radially against bearing 160 of spider member 132. This movement of flyweights 136 applies a force to moveable sheave 120 to cause moveable sheave 120 to slide or translate laterally along sleeve member 206 and bearing 150 relative to stationary sheave 122. In this way, the radial position of belt 116 on moveable sheave 120 and stationary sheave 122 may be adjusted to accommodate various operating conditions of vehicle 2, thereby resulting in various drive ratios. During operation, drive clutch 110 is configured to move between an open position, as shown in
The rotation of belt 116 caused by drive clutch 110 drives driven clutch 112. Referring to
Additionally, within nose 228, stationary sheave 220 further includes a plurality of raised surfaces 238 which are configured to couple with brackets 240 through fasteners 242. Stationary sheave 220 further includes a post 236 projecting laterally inwardly from nose 228 and toward moveable sheave 222. In one embodiment, post 236 is integral with stationary sheave 220 and, therefore, comprised of the same material as body 227 and nose 228 of stationary sheave 220. In this way, driven clutch 112 is a post-less design because stationary sheave 220 and moveable sheave 222 directly couple with shaft 118 of shiftable transmission 74, rather that requiring a further post for engaging shaft 118. Illustrative post 236 extends a distance D1 from the proximate end thereof to the outer surface of nose 228 and D1 may be approximately 60-70 mm, and illustratively, 65 mm. Additionally, a diameter D2 of post 236 may be approximately 20-30 mm and, illustratively, 25 mm. The length/diameter ratio of post 236 is indicative of the stability provided to driven clutch 112 as moveable sheave 222 translates relative to stationary sheave 220. Alternatively, post 236 may be press fit or otherwise coupled within nose 228 and comprised of a different material than body 227 and nose 228. For example, in one embodiment, post 236 may be comprised of aluminum. Post 236 is configured to provide stability to stationary sheave 220 during operation of CVT 76.
Post 236 also is configured to receive at least one bearing 244 therein, through which shaft 118 of shiftable transmission 74 may be received. Shaft 118 may be secured to driven clutch 112 with at least one spacer 246 and a fastener at the distal end thereof, illustratively, a snap ring 248. Additionally, a sleeve 250, which may be a bushing, is received over post 236 in order to slidably receive moveable sheave 222.
Moveable sheave 222 may be configured for translational movement along sleeve 250 between a closed position when adjacent stationary sheave 220, as shown in
Moveable sheave 222 includes a body portion 254 and a nose 256 projecting laterally outwardly from body portion 254. Nose 256 is received within nose 228 of stationary sheave 220. An outer surface of body portion 254 includes a plurality of ribs 255 which strengthens moveable sheave 222. A center aperture 258 of nose 256 is configured to receive a bearing 252 for sliding along sleeve 250. Additionally, nose 256 includes recesses 260 which align with brackets 240 and raised surfaces 238 on stationary sheave 220 in order to locate moveable sheave 222 on stationary sheave 220. Within nose 256 of moveable sheave 222, each of a plurality of projections 266 is configured to receive a bracket 262. Brackets 262 are coupled to projections 266 with fasteners 264. Helix 224 is positioned adjacent brackets 262 and cover member 226 is positioned adjacent helix 224 such that helix 224 is intermediate cover member 226 and the outer surface of moveable sheave 222. Helix 224 includes a splined center opening 225 for engaging shaft 118 of shiftable transmission 74. Additionally, when driven clutch 112 is assembled, ears 223 of helix are positioned intermediate adjacent projections 266 in an alternating configuration. Cover member 226 is coupled to the outer surface of moveable sheave 222 with fasteners 265 and a bearing 268 is positioned within a center aperture 269 of cover member 226.
As shown in
During operation of CVT 76, rotation of crankshaft 84 of engine 72 causes rotation of drive clutch 110. Drive clutch 110 engages belt 116 and when belt 116 engages driven clutch 112, driven clutch 112 rotates, which causes shaft 118 of shiftable transmission 74 to rotate. As belt 116 engages driven clutch 112, a load is applied thereto. More particularly, the load (e.g., torque) is transmitted from stationary sheave 220, through raised surfaces 238, through projections 266 of moveable sheave 222, and to helix 224, which then applies the torque to shaft 118 of shiftable transmission 74. In this way, the torque is centralized at helix 224, rather than applied to other components of CVT 76, for transferring to shiftable transmission 74. CVT 76 also may be electronically controlled in order to allow for operation at low vehicle speeds. As such, electronic operation of CVT 76 (“eCVT”) may allow for CVT 76 to operate without being limited to a specific speed range and/or without reaching the revolutions limit for engine 72. This functionality of eCVT may be utilized when overboosting so that CVT 76 may be controlled without reaching a revolutions limit for engine 72. Additionally, use of eCVT may allow for operating vehicle 2 at low rpm while maintaining fuel economy. Additional details of CVT 76 may be disclosed in U.S. patent application Ser. No. 14/475,385, filed on Sep. 2, 2014, the complete disclosure of which is expressly incorporated by reference herein.
An alternative embodiment of driven clutch 112 is shown as driven clutch 112′ in
Additionally, within nose 228′, stationary sheave 220′ further includes raised surfaces 238 which are configured to couple with brackets 240 through fasteners 242. Interior ribs 270 are also positioned within nose 228′ to provide additional strength and stability to stationary sheave 220′. Stationary sheave 220′ further includes a post 236′ received through center opening 232 and coupled to a portion of nose 228′. Post 236′ projects laterally inwardly from nose 228′ and toward moveable sheave 222′. In one embodiment, post 236′ may be press fit or otherwise coupled within nose 228′ and comprised of a different material than body 227′ and nose 228′. For example, in one embodiment, post 236′ may be comprised of aluminum. Post 236′ is configured to stabilize stationary sheave 220′ during operation of CVT 76.
Post 236′ is configured to receive bearings 244 therein, through which shaft 118 of shiftable transmission 74 may be received. Additionally, moveable sheave 222′ may be configured for translational movement along post 236′. Moveable sheave 222′ includes a body portion 254′ and a nose 256′ projecting laterally outwardly from body portion 254′. An outer surface of body portion 254′ includes a plurality of ribs 255′ for increasing the strength of moveable sheave 222′. Additionally, the outer surface of body portion 254′ includes a ring 272 with a plurality of recesses 274. Ring 272 may be a balance ring with a diameter less than the outer diameter of moveable sheave 222′ to decrease the stress on moveable sheave 222′ when CVT 76 operates at a high speed. More particularly, by positioning ring 272 adjacent nose 256′, rather than proximate the outer perimeter, moveable sheave 222′ may be sufficiently balanced to lower the stress on moveable sheave 222′ and manage the rotational inertia of moveable sheave 222′.
As shown in
As shown in
Referring still to
A flange 290 is positioned forward of snorkel 284 to couple with a driveline assembly 300 of vehicle 2 (
Referring to
Driveline assembly 300 also includes a front differential 304, which is operably coupled to front wheels 6 through front axles. As such, operation of shiftable transmission 74 rotates rear wheels 8 through the rear axles and causes rotation of the front wheels 6 through rotation of prop shaft 302 and operation of front differential 304.
Referring to
Air intake assembly 320 may also include a blow-off valve 334 fluidly coupled to charged air conduit 330 and fluidly coupled to conduit 328 through a blow-off tube 336. Blow-off valve 334 is downstream from charger 78, as shown in
During operation of vehicle 2, ambient air necessary for combustion within engine 72 enters engine air intake tube 324 and flows into airbox 322 to filter particulates and other matter therefrom. The filtered air from airbox 322 then flows into gaseous charger 78 through conduit 328. Operation of charger 78 may be done manually by the operator or automatically based on throttle conditions. When operating, charger 78 compresses the filtered air such that a higher number of air molecules may enter engine 72 through charged air conduit 330. As such, engine 72 is configured to received charged, pre-combustion air to increase the power output of powertrain assembly 70. However, depending on throttle and charger conditions (e.g., compressor surge conditions), it may be necessary to bleed off or exhaust at least a portion of the charged, pre-combustion air from charger 78 before entering engine 72. As such, blow-off valve 334 may be moved from a closed position to an open position in response to compressor surge conditions to allow a portion of the charged air in charged air conduit 330 to be routed back to conduit 328 through blow-off tube 336 or otherwise exhausted from vehicle 2. In this way, the quantity of charged, pre-combustion air entering engine 72 may be controlled in response to various throttle conditions or other parameters. Blow-off valve 334 may be electronically, mechanically, and/or fluidly controlled. Additionally, by routing air in blow-off tube 336 back to conduit 328, the sound from blow-off valve 334 may be reduced and the air within air intake assembly 320 downstream of airbox 322 remains filtered.
Referring to
Driven housing 342 is supported by a frame arm 344 which extends between driven housing 342 and engine mount 13 and which may reduce resonant frequencies at charger 78. More particularly, frame arm 344 is coupled to brackets 15 of engine mount 13, such that brackets 15 are coupled to both engine 72 and frame arm 344. In this way, frame arm 344 may be uncoupled from engine mount 13 and swung or otherwise moved away therefrom in order to service charger 78. As such, other components of vehicle 2, including components of frame assembly 10 and powertrain assembly 70 are not affected when charger 78 is serviced because frame arm 344 is removed only through brackets 15 while all other components remain coupled at their respective positions. Drive housing 340 is cantilevered from a front portion of engine 72 and, as such, is supported via its mounting to engine 72. In this way, exhaust manifold 346 also is cantilevered from engine 72.
As shown in
Additionally, exhaust manifold 346 includes a second surface 354 for abutting and coupling with an exhaust tube 356 of exhaust assembly 360. Second surface 354 is integral with exhaust intake ports 348, 350 and drive housing 340 of charger 78. A waste gate 358 is positioned adjacent second surface 354. Waste gate 358 may include a solenoid valve and is configured to bleed off or exhaust at least a portion of the exhaust gases operating the turbine of charger 78 so as to be able to alter the speed of the turbine and, therefore, operation of charger 78. However, overboost may occur when charger 78 boosts higher than waste gate 358 is configured to allow, therefore, boost pressure may be monitored and internally read by the engine control unit, rather than displayed on a gauge to the operator. Waste gate 358 may be electronically, mechanically, and/or fluidly controlled. Waste gate 358 further includes a waste gate rod 353a and a waste gate mass 353b coupled to waste gate rod 353a. Waste gate mass 353b counteracts resonance or movement in waste gate rod 353a. In one embodiment, as shown in
Referring to
The exhaust gases from engine 72 have an elevated temperature and, therefore, the components of exhaust assembly 360 also be at an elevated temperature. For example, charger 78 may be a heat sink. Heat shield assemblies 366, 368 are comprised of insulating materials to shield various components of vehicle 2 from the heat of exhaust assembly 360. Heat shield assembly 368 includes a forward member 380 positioned forward of muffler 362 and a rearward member 382 positioned rearward of muffler 362. Forward and rearward members 380, 382 of heat shield assembly 368 are coupled together with conventional fasteners and shield various components of vehicle 2 from the heat of muffler 362.
Heat shield assembly 366 is positioned longitudinally forward of heat shield assembly 368 and includes an upper member 370 positioned above exhaust manifold 346, a forward member 372 positioned longitudinally forward of exhaust manifold 346, a lateral member 374 positioned above a portion of exhaust tube 356, and a conduit member 376 having a generally semi-circular cross-section and extending around at least a portion of the outer perimeter of exhaust tube 356. Additionally, heat shield assembly 366 includes an upper manifold member 384, a lower manifold member 386, and a forward manifold member 388 which may be coupled together with convention fasteners, for insulating various components of vehicle 2 from the heat of exhaust manifold 346. In one embodiment, upper and lower manifold members 384, 386 define a “clam shell” configuration which generally surrounds exhaust manifold 346. Furthermore, charger 78 and/or exhaust manifold 346 includes mounting bosses 377 for coupling heat shield assembly 366 thereto. Fasteners 379, such as high-strength steel bolts, may be received within mounting bosses 377 (
In order to reduce the temperature of various components of powertrain assembly 70, a cooling assembly 410 is provided. Additionally, oil for lubricating engine 72, charger 78, and other components of powertrain assembly 70 may be cooled by cooling assembly 410. With reference to
Referring to
Second cooling circuit 414 a low-temperature circuit which includes a heat exchanger or radiator 416 supported by front portion 12 of lower frame assembly 10. Heat exchanger 416 is positioned forward of operator area 20. Heat exchanger 416 is fluidly coupled to a coolant reservoir, illustratively a coolant bottle 424, and a plurality of low-temperature cooling lines 418. Low-temperature cooling lines 418 extend from front portion 12 to rear portion 14 of lower frame assembly 10. Illustratively, as shown in
A first low-temperature cooling line 418a is a cooling supply line which is coupled to a pump 420 for pumping cooling fluid to a heat exchanger, illustratively an intercooler 426 (
As shown in
Referring to
Heat exchanger 434 is fluidly coupled to coolant bottle 424 and a plurality of high-temperature cooling lines 436. High-temperature cooling lines 436 extend from front portion 12 to rear portion 14 of lower frame assembly 10. As shown in
As shown in
The cooling fluid is stored in coolant bottle 424, which is also position rearward of heat exchangers 416, 434 and fan 440. Coolant bottle 424 is a pressurized reservoir which includes a pressurized cap 442, a first housing member 444, an intermediate member 446, and a second housing member 448. As shown in
As shown in
During operation of vehicle 2, ambient airflow A passes through a mesh or grille 464 and through heat exchangers 416, 434 to decrease the temperature of the cooling fluid flowing therethrough. However, because heat exchanger 434 is positioned rearward of heat exchanger 416, the ambient flowing through heat exchanger 434 may be at an elevated temperature after flowing through heat exchanger 416, thereby decreasing the cooling effect on the cooling fluid in heat exchanger 434. Therefore, in order to supplement cooling at heat exchanger 434, a secondary mesh or grille 466 allows ambient airflow B to pass therethrough, which is then directed downwardly toward heat exchanger 434 for additional cooling at heat exchanger 434. Secondary grille 466 is positioned below a hood 468 of body 18 and ambient airflow B is directed toward secondary grille 466 by front body panel 469 positioned generally forward of and below secondary grille 466.
Referring to
In operation, cooling fluid flows through first cooling circuit 412 and to engine 72 in order to alter the temperature of engine 72. In particular, the cooling fluid is cooled at heat exchanger 434 and then flows through cooling line 436a and to engine 72. When the cooling fluid has circulated about engine 72, the temperature of the cooling fluid may be elevated, and therefore, the cooling fluid flows back to heat exchanger 434 to decrease the temperature of the cooling fluid when ambient air passes through heat exchanger 434. Additionally, cooling fluid flows simultaneously through second cooling circuit 414 and to engine 72 in order to alter the temperature of the pre-combustion air. In particular, the cooling fluid is cooled at heat exchanger 416 and then flows through cooling line 418a, to pump 420, into conduit 422, and to intercooler 426. As such, when the pre-combustion air passes through intercooler 426, the temperature of the pre-combustion air decreases before entering cylinders 80 of engine 72. When the cooling fluid has circulated about intercooler 426, the temperature of the cooling fluid may be elevated, and therefore, the cooling fluid flows back to heat exchanger 416 to decrease the temperature of the cooling fluid when ambient air passes through heat exchanger 416. In this way, cooling assembly 410 is configured to both alter the temperature of engine 72 and alter the temperature of the pre-combustion air entering engine 72.
While this invention has been described as having an exemplary design, the present invention may be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the invention using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains.
The present application is a divisional of U.S. patent application Ser. No. 14/577,902, filed on Dec. 19, 2014, the complete disclosure of which is expressly incorporated by reference herein.
Number | Name | Date | Kind |
---|---|---|---|
1989585 | Bigelow | Jan 1935 | A |
2623612 | Andreas | Dec 1952 | A |
2839038 | Middlebrooks | Jun 1958 | A |
4010725 | White | Mar 1977 | A |
4022272 | Miller | May 1977 | A |
4061187 | Rajasekaran | Dec 1977 | A |
4150655 | Gaggiano | Apr 1979 | A |
4236492 | Tholen | Dec 1980 | A |
4294073 | Neff | Oct 1981 | A |
4434934 | Moser | Mar 1984 | A |
4474162 | Mason | Oct 1984 | A |
4598687 | Hayashi | Jul 1986 | A |
4685430 | Ap | Aug 1987 | A |
4733639 | Kohyama | Mar 1988 | A |
4848294 | Yamamoto | Jul 1989 | A |
4890586 | Fujii | Jan 1990 | A |
4898261 | Winberg | Feb 1990 | A |
4907552 | Martin | Mar 1990 | A |
5018490 | Kroner | May 1991 | A |
5086858 | Mizuta | Feb 1992 | A |
5251588 | Tsujii | Oct 1993 | A |
5251713 | Enokimoto | Oct 1993 | A |
5255733 | King | Oct 1993 | A |
5359247 | Baldwin | Oct 1994 | A |
5407130 | Uyeki | Apr 1995 | A |
5408965 | Fulton | Apr 1995 | A |
5549153 | Baruschke | Aug 1996 | A |
5647534 | Kelz | Jul 1997 | A |
5971290 | Echigoya | Oct 1999 | A |
5976044 | Kuyama | Nov 1999 | A |
6062024 | Zander | May 2000 | A |
6184603 | Hamai | Feb 2001 | B1 |
6196168 | Eckerskorn | Mar 2001 | B1 |
6198183 | Baeumel | Mar 2001 | B1 |
6217758 | Lee | Apr 2001 | B1 |
6311676 | Oberg | Nov 2001 | B1 |
6591896 | Hansen | Jul 2003 | B1 |
6761748 | Schenk | Jul 2004 | B2 |
6810667 | Jung | Nov 2004 | B2 |
6810977 | Suzuki | Nov 2004 | B2 |
6822353 | Koga | Nov 2004 | B2 |
6966395 | Schuehmacher | Nov 2005 | B2 |
7051824 | Jones | May 2006 | B1 |
7152706 | Pichler | Dec 2006 | B2 |
7427248 | Chonan | Sep 2008 | B2 |
7431024 | Buchwitz | Oct 2008 | B2 |
7451808 | Busse | Nov 2008 | B2 |
7455134 | Severinsky | Nov 2008 | B2 |
7559308 | Matsuda | Jul 2009 | B2 |
7621262 | Zubeck | Nov 2009 | B2 |
7769505 | Rask | Aug 2010 | B2 |
8011342 | Bluhm | Sep 2011 | B2 |
8047451 | McNaughton | Nov 2011 | B2 |
8051842 | Hagelstein | Nov 2011 | B2 |
8074753 | Tahara | Dec 2011 | B2 |
8186333 | Sakuyama | May 2012 | B2 |
8215427 | Rouaud | Jul 2012 | B2 |
8272685 | Lucas | Sep 2012 | B2 |
8353265 | Pursifull | Jan 2013 | B2 |
8439019 | Carlson | May 2013 | B1 |
8479854 | Gagnon | Jul 2013 | B1 |
8561403 | Vandyne | Oct 2013 | B2 |
8573348 | Cantemir | Nov 2013 | B2 |
8590651 | Shigematsu | Nov 2013 | B2 |
8671919 | Nakasugi | Mar 2014 | B2 |
8834307 | Itoo | Sep 2014 | B2 |
8869525 | Lingenauber | Oct 2014 | B2 |
9133730 | Joergl | Sep 2015 | B2 |
9186952 | Yleva | Nov 2015 | B2 |
9194282 | Serres | Nov 2015 | B2 |
9328652 | Bruss | May 2016 | B2 |
9752489 | Chu | Sep 2017 | B2 |
9895946 | Schlangen | Feb 2018 | B2 |
20010043808 | Matsunaga | Nov 2001 | A1 |
20030066696 | Nakamura | Apr 2003 | A1 |
20030070849 | Whittaker | Apr 2003 | A1 |
20040031451 | Atschreiter | Feb 2004 | A1 |
20040083730 | Wizgall | May 2004 | A1 |
20040168455 | Nakamura | Sep 2004 | A1 |
20040177827 | Hoyte | Sep 2004 | A1 |
20040188159 | Yatagai | Sep 2004 | A1 |
20040195797 | Nash | Oct 2004 | A1 |
20040226761 | Takenaka | Nov 2004 | A1 |
20050052080 | Maslov | Mar 2005 | A1 |
20050173180 | Hypes | Aug 2005 | A1 |
20050205319 | Yatagai | Sep 2005 | A1 |
20060112695 | Neubauer | Jun 2006 | A1 |
20060130888 | Yamaguchi | Jun 2006 | A1 |
20060270503 | Suzuki | Nov 2006 | A1 |
20070144800 | Stone | Jun 2007 | A1 |
20070251744 | Matsuzawa | Nov 2007 | A1 |
20080023240 | Sunsdahl | Jan 2008 | A1 |
20080178830 | Sposato | Jul 2008 | A1 |
20080257625 | Stranges | Oct 2008 | A1 |
20080271937 | King | Nov 2008 | A1 |
20080299448 | Buck | Dec 2008 | A1 |
20080308337 | Ishida | Dec 2008 | A1 |
20090015023 | Fleckner | Jan 2009 | A1 |
20090177345 | Severinsky | Jul 2009 | A1 |
20090179509 | Gerundt | Jul 2009 | A1 |
20090314462 | Yahia | Dec 2009 | A1 |
20100019729 | Kaita | Jan 2010 | A1 |
20100163324 | Jyoutaki | Jul 2010 | A1 |
20110168126 | Fujikawa | Jul 2011 | A1 |
20110240393 | Hurd | Oct 2011 | A1 |
20120031688 | Safranski | Feb 2012 | A1 |
20120055729 | Bessho | Mar 2012 | A1 |
20120125022 | Maybury | May 2012 | A1 |
20120217078 | Kinsman | Aug 2012 | A1 |
20120283930 | Venton-Walters | Nov 2012 | A1 |
20120297765 | Vigild | Nov 2012 | A1 |
20140103627 | Deckard | Apr 2014 | A1 |
20140311143 | Speidel | Oct 2014 | A1 |
20150071759 | Bidner | Mar 2015 | A1 |
20150275742 | Chekaiban | Oct 2015 | A1 |
20170166255 | Peterson | Jun 2017 | A1 |
20170248087 | Reisenberger | Aug 2017 | A1 |
Number | Date | Country |
---|---|---|
1268997 | Oct 2000 | CN |
101424200 | May 2009 | CN |
103075278 | May 2013 | CN |
203702310 | Jul 2014 | CN |
4447138 | Dec 1997 | DE |
19735021 | Feb 1999 | DE |
102005003077 | Aug 2006 | DE |
102007024126 | Dec 2008 | DE |
0511654 | Nov 1992 | EP |
0856427 | Aug 1998 | EP |
13 82475 | Jan 2004 | EP |
1433645 | Jun 2004 | EP |
2033878 | Mar 2009 | EP |
2145808 | Jan 2010 | EP |
2454349 | May 2009 | GB |
61135910 | Jun 1986 | JP |
2005130629 | May 2005 | JP |
2005299469 | Oct 2005 | JP |
2009281330 | Dec 2009 | JP |
20080028174 | Mar 2008 | KR |
WO 2014047488 | Mar 2014 | WO |
Entry |
---|
Letter Exam Report issued by the State Intellectual Property Office (SIPO), dated Mar. 18, 2015, for Chinese Patent Application No. 201080046628.5; 20 pages. |
International Search Report and Written Opinion of the International Searching Authority, dated Aug. 12, 2016, for International Patent Application No. PCT/US2015/061272; 15 pages. |
“Engine firing change '13 850”, PolarisATVForums.com, interne forum discussion thread, dated Nov. 21, 2012; 6 pages. |
“Who makes the best turbo kit for the Polaris' RZR??”, RZRforums.net, intemet forum discussion thread, dated Jun. 25, 2010; 17 pages. |
International Preliminary Report on Patentability issued by the European Patent Office, dated May 12, 2017, for International Patent Application No. PCT/US2015/061272; 22 pages. |
“Straight-twin engine”, Article, Wikipedia.org; 8 pages. |
“Honda Develops a Powerful, Fuel-Efficient 700cc Engine for Midsize Motorcycle”, Honda news release, www.world.honda.com, dated Sep. 26, 2011; 3 pages. |
Office Action issued by the U.S. Patent and Trademark Office, dated Oct. 1, 2018, for U.S. Appl. No. 15/751,403; 7 pages. |
Response to Office Action filed with the U.S. Patent and Trademark Office, filed Dec. 19, 2018, for U.S. Appl. No. 15/751,403; 9 pages. |
Number | Date | Country | |
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20190248227 A1 | Aug 2019 | US |
Number | Date | Country | |
---|---|---|---|
Parent | 14577902 | Dec 2014 | US |
Child | 16397177 | US |