US20210123363A1 - Axle assembly - Google Patents
Axle assembly Download PDFInfo
- Publication number
- US20210123363A1 US20210123363A1 US16/662,678 US201916662678A US2021123363A1 US 20210123363 A1 US20210123363 A1 US 20210123363A1 US 201916662678 A US201916662678 A US 201916662678A US 2021123363 A1 US2021123363 A1 US 2021123363A1
- Authority
- US
- United States
- Prior art keywords
- fluid
- fluid flow
- axle
- assembly
- axle assembly
- 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
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
- F01M11/0004—Oilsumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
- F16H57/0483—Axle or inter-axle differentials
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
- B60B35/12—Torque-transmitting axles
- B60B35/16—Axle housings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
- B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
- F01M9/12—Non-pressurised lubrication, or non-closed-circuit lubrication, not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
- F16H57/0452—Oil pans
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0457—Splash lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0471—Bearing
Abstract
Description
- The presently disclosed subject matter relates to a vehicle, and more particularly to an axle assembly for the vehicle including a disconnect assembly an integrated fluid flow system.
- Electric drive axles are known of the type which comprises an electric motor, a gear assembly, and an axle assembly. The axle assembly typically includes a carrier housing for storing an amount of lubricating oil therein, a differential rotatably mounted within the carrier housing, a ring gear contained within the carrier housing and mounted on the differential for rotation therewith, and a pair of axle half shafts which extend outwardly to respective wheel ends (i.e. a wheel set). In an all-wheel drive (“AWD”) vehicle, a primary wheel-set may be continually connected to a power source of the AWD vehicle while a secondary wheel-set is selectively connected thereto via a disconnect assembly. The disconnect assembly may include a clutch mechanism to selectively disconnect components of the secondary wheel-set and associated driveline, thereby improving a fuel efficiency of the AWD vehicle.
- In such axle assemblies as described above, components such as bearing for rotatably supporting the differential within the carrier housing are typically positioned facing an interior of the carrier housing and directly splashed with lubricating oil picked up by rotation of the ring gear. However, other components (i.e. the disconnect assembly) disposed within the axle assembly, and more particularly the carrier housing, may not be splashed with the lubricating oil splashed by the ring gear. It is, therefore, necessary to provide positive lubrication of the other components disposed within the carrier housing so as to ensure durability of the axle assembly.
- Conventionally, there have been lubrication systems, wherein an oil supply passage is formed in an upper portion of the carrier housing to receive the lubricating oil picked up by rotation of the ring gear and supply it into an annular space around a drive pinion shaft, and an oil return passage is formed in the bottom portion of the carrier housing to permit the lubricating oil passing through around the drive pinion shaft to return into an interior of the carrier housing. In such arrangements, it is still difficult to supply a sufficient and consistent amount of lubricating oil since the oil supply passage receives the lubricating oil splashed from the ring gear and not a controlled amount.
- It would be desirable to produce an axle assembly including a disconnect assembly and an integrated fluid flow system, which enhances durability, efficiency and manufacturability, while a cost and weight thereof is minimized.
- In concordance and agreement with the present disclosure, a disconnect assembly and an integrated fluid flow system, which enhances durability, efficiency and manufacturability, while a cost and weight thereof is minimized, has surprisingly been discovered.
- In one embodiment, an axle assembly, comprises: a housing having a fluid sump provided with a fluid disposed therein; and a fluid flow member rotatably disposed in the housing, wherein the fluid flow member is configured to collect a portion of the fluid from the fluid sump and at least partially direct a flow of the fluid to at least one desired component disposed within the housing.
- As aspects of certain embodiments, the fluid flow member is one of disc shaped, elliptical shaped, and irregular shaped.
- As aspects of certain embodiments, the fluid flow member includes a main body having a first surface and an opposing second surface.
- As aspects of certain embodiments, at least one of the first surface and the second surface of the main body is substantially planar.
- As aspects of certain embodiments, the fluid flow member includes at least one retention feature formed on at least one of the first surface and the second surface of the main body.
- As aspects of certain embodiments, the fluid flow member includes at least one surface feature formed on at least one of the first surface and the second surface of the main body.
- As aspects of certain embodiments, the at least one surface feature is one of an arcuate shape and an involute shape.
- As aspects of certain embodiments, the fluid flow member includes at least one catch formed on at least one of the first surface and the second surface of the main body.
- As aspects of certain embodiments, the axle assembly further comprises at least one rotatable shaft at least partially disposed in the housing.
- As aspects of certain embodiments, the fluid flow member is disposed about and rotatably coupled to the at least one rotatable shaft at least partially disposed in the housing.
- As aspects of certain embodiments, the at least one desired component is a portion of a disconnect assembly.
- As aspects of certain embodiments, the at least one desired component is a bearing interposed between a rotatable link shaft and an axle half shaft.
- As aspects of certain embodiments, the fluid flow member forms part of a fluid flow system.
- As aspects of certain embodiments, the fluid flow system further includes at least one fluid passageway formed in at least one of the housing and a rotatable shaft at least partially disposed in the housing.
- In another embodiment, an axle assembly, comprises: a housing having a first axle shaft and a second axle shaft connected by a differential and a link shaft, wherein a bearing is interposed between the second axle shaft and the link shaft; and a disconnect assembly including a clutch member configured to selectively couple the second axle shaft and the link shaft.
- In yet another embodiment, a method of lubrication for an axle assembly, comprising: providing a housing having fluid sump and a fluid flow member rotatably disposed in the housing; and causing a rotational movement of the fluid flow member to collect a portion of the fluid from the fluid sump and at least partially direct a flow of the fluid to at least one desired component disposed within the housing.
- The accompanying drawings are incorporated herein as part of the specification. The drawings described herein illustrate embodiments of the presently disclosed subject matter, and are illustrative of selected principles and teachings of the present disclosure. However, the drawings do not illustrate all possible implementations of the presently disclosed subject matter, and are not intended to limit the scope of the present disclosure in any way.
-
FIG. 1 schematically depicts a vehicle driveline including an axle assembly according to an embodiment of the presently disclosed subject matter; -
FIG. 2 is a cross-sectional view of a portion of the axle assembly shown inFIG. 1 , wherein the portion of the axle assembly includes a differential and a disconnect assembly with a fluid flow member according to an embodiment of the presently disclosed subject matter; -
FIG. 3A is a side elevational view of the fluid flow member shown inFIG. 2 according to an embodiment of the presently disclosed subject matter; -
FIG. 3B is a rear elevational view of the fluid flow member ofFIG. 3A ; -
FIG. 3C is a rear perspective view the fluid flow member ofFIGS. 3A-3B ; -
FIG. 4A is a side elevational view of the fluid flow member shown inFIG. 2 according to another embodiment of the presently disclosed subject matter; -
FIG. 4B is a rear elevational view of the fluid flow member ofFIG. 4A ; -
FIG. 4C is a rear perspective view the fluid flow member ofFIGS. 4A-4B ; -
FIG. 5A is a side elevational view of the fluid flow member shown inFIG. 2 according to another embodiment of the presently disclosed subject matter; -
FIG. 5B is a rear elevational view of the fluid flow member ofFIG. 5A ; -
FIG. 5C is a rear perspective view the fluid flow member ofFIGS. 5A-5B ; -
FIG. 6A is a side elevational view of the fluid flow member shown inFIG. 2 according to yet another embodiment of the presently disclosed subject matter; -
FIG. 6B is a rear elevational view of the fluid flow member ofFIG. 6A ; -
FIG. 6C is a rear perspective view the fluid flow member ofFIGS. 6A-5B ; -
FIG. 7A is a side elevational view of a housing portion of the axle assembly shown inFIG. 2 according to an embodiment of the presently disclosed subject matter; -
FIG. 7B is a front elevational view of the housing portion of the axle assembly ofFIG. 7A ; and -
FIG. 7C is a rear elevational view of the housing portion of the axle assembly of 7B. - It is to be understood that the presently disclosed subject matter may assume various alternative orientations and step sequences, except where expressly specified to the contrary. It is also to be understood that the specific assemblies and systems illustrated in the attached drawings, and described in the following specification are simply exemplary embodiments of the inventive concepts defined herein. Hence, specific dimensions, directions or other physical characteristics relating to the embodiments disclosed are not to be considered as limiting, unless expressly stated otherwise. Also, although they may not be, like elements in various embodiments described herein may be commonly referred to with like reference numerals within this section of the application.
-
FIG. 1 illustrates an all-wheel-drive (AWD)vehicle 10 includes anaxle assembly 100 according to the presently disclosed subject matter. Embodiments of theaxle assembly 100 are described below. Theaxle assembly 100 may be utilized with an all-wheel drive vehicle, a pure electric vehicle and a hybrid four-wheel-drive (4WD) vehicle wherein at least one of the front axle and the rear axle includes theaxle assembly 100. In still other embodiments, theaxle assembly 100 may be utilized in a hybrid commercial vehicle (not depicted) comprising a tandem axle in which the front tandem axle is driven by an internal combustion engine, and the rear tandem axle includes the axle assembly 100 (or vice versa). Theaxle assembly 100 may have applications in commercial vehicles, both light duty and heavy duty vehicles, and for passenger, off-highway, and sport utility vehicles. Additionally, theaxle assembly 100 described herein may be adapted for use in front and/or rear driving axles, and in steerable and non-steerable axles. It would be understood by one of ordinary skill in the art that theaxle assembly 100 also may have industrial, locomotive, military, agricultural, and aerospace applications. - In certain embodiments, the
axle assembly 100 may employed in an integrated drive system. Theaxle assembly 100 may include an electric motor-generator 101 coupled with a power source (not depicted). The electric motor-generator 101 may be a permanent magnet synchronous machine comprising a stator disposed concentrically about a rotor. Theaxle assembly 100 may additionally comprise an inverter (not depicted) for converting direct current to alternating current when the electric motor-generator 101 is utilized to drive thevehicle 10, and for converting alternating current to direct current when thevehicle 10 decelerates. Further, theaxle assembly 100 may include cooling fluid (not depicted) such as, but not limited to, automatic transmission fluid or axle oil integrated with theaxle assembly 100 for cooling the electric motor-generator 101 and the inverter. In another embodiment (not depicted), the cooling fluid for the electric motor-generator 101 and the inverter may not be integrated with the axle oil. Theaxle assembly 100 may also include a lubricating fluid (not depicted) such as, but not limited to, the axle oil, for example. Theaxle assembly 100 may have either a co-axial layout where an axle shaft connecting the wheel to a differential passes through a center of the electric motor-generator 101, or an off-axis layout where the axle shaft connecting the wheel to the differential does not pass through the center of the electric motor-generator 101 but rather parallel to an axis thereof. - The
axle assembly 100 depicted inFIG. 2 includes acarrier housing 102 having afirst housing portion 104, asecond housing portion 106 as described in more detail forFIGS. 5A-5C , and athird housing portion 108. It is understood, however, that thehousing portions carrier housing 102 may have a differential 110 and adisconnect assembly 111 disposed therein. Various types of differentials may be employed for the differential 110 as desired such as a split-case differential, a clamshell differential, a hub style differential, and the like, for example. It should also be appreciated that the differential 110 may formed from any suitable material using any suitable process as desired such as stamping or forming from a powered metal material, for example. - In certain embodiments, the differential 110 includes a
differential case 112 mounted for rotation within thecarrier housing 102. The electric motor-generator 101 may be drivingly coupled with aring gear 114 of the differential 110 by at least one gear assembly (not depicted). Thering gear 114 may be formed on thedifferential case 112 by any suitable method as desired such as by welding, for example. It is understood that thering gear 114 and thedifferential case 112 may be formed as an integral, unitary structure or as separate and distinct components if desired. In certain embodiments, the electric motor-generator 101 conveys torque to the differential 110 via the at least one gear assembly, and in turn to thedifferential case 112 via thering gear 114. Thering gear 114 may be integrally formed with thedifferential case 112, or may be coupled with thedifferential case 112 via welding, mechanical fasteners, or other suitable methods as desired. - The
differential case 112 may be mounted for rotation within thecarrier housing 102 via a pair ofbearings bearings second trunnion differential case 112. Various types of bearings may be employed for each of thebearings differential case 112 may be produced via the process of flow forming a metallic material such as, but not limited to, steel, premium carbon steel, aluminum, and aluminum alloys. - With reference to
FIG. 2 , afirst pinion shaft 122 is disposed in thedifferential case 112. In an embodiment, thefirst pinion shaft 122 extends through thedifferential case 112 and is coupled at its ends in two opposingapertures differential case 112. First and second pinion gears 127, 128, are mounted on each end of thefirst pinion shaft 122, respectively. In certain embodiment, a second pinion shaft (not depicted) extends into thedifferential case 112 transverse thefirst pinion shaft 122 and is coupled at its ends with thedifferential case 112. Third and fourth pinion gears (not depicted) may be rotatably supported on the ends of the second pinion shaft. In other embodiments, not shown, the pinion gears (not depicted) are supported by a unitary cross pin. - The pinion gears 127, 128, (not depicted) may be meshed with a
first side gear 132 and asecond side gear 134 within thedifferential case 112. The side gears 132, 134 shown include radially inward projectingsplines side gear 132 is in splined engagement with a firstaxle half shaft 140 and theside gear 134 is in splined engagement with alink shaft 142. It should be appreciated that the side gears 132, 134 may be engaged with the firstaxle half shaft 140 and thelink shaft 142, respectively, by any suitable method as desired such as a press fit, for example. Thedifferential case 112 may includeopenings trunnions differential case 112 to accommodate the firstaxle half shaft 140 and thelink shaft 142 coupled with the side gears 132, 134. As illustrated, the firstaxle half shaft 140 and afirst end 141 of thelink shaft 142 are inserted into and through theopenings splines shafts splines shafts axle assembly 100 by respective c-clips shafts - In the embodiment shown, the
link shaft 142 includes at least onefluid passageway 155 formed therethrough. The at least onefluid passageway 155 is formed as part of afluid flow system 153. In certain embodiments, the at least onefluid passageway 155 is configured to permit a flow of a fluid (e.g. a lubricant) from a fluid source 156 (e.g. a fluid sump of the axle assembly 100) to other locations within thecarrier housing 102 to provide lubrication to various components disposed within thecarrier housing 102 of theaxle assembly 100. As a non-limiting example, the at least onefluid passageway 155 is configured to permit the flow of the fluid from thefluid source 156 to within aninner cavity 168 formed in thelink shaft 142 of thedisconnect assembly 111 and abearing 170 disposed within theinner cavity 168 and interposed between an inner surface of thelink shaft 142 and an outer surface of a secondaxle half shaft 160. Various types of bearings may be employed for thebearing 170 such as a roller bearing, a tapered roller bearing, a ball bearing, a needle bearing, and the like, for example. - As illustrated, the
link shaft 142 includes a pair of thefluid passageways 155 circumferentially spaced equidistant from each other. Each of thefluid passageways 155 shown has a substantially constant inner diameter. It is understood, however, that each of thefluid passageways 155 may be tapered, wherein the inner diameter of each of thefluid passageways 155 gradually increases from an end thereof adjacent the fluid source to an end thereof adjacent theinner cavity 168 of thelink shaft 142. The gradually taperedfluid passageways 155 direct the fluid towards the bearing 170. It is further understood that thefluid passageways 155 of thelink shaft 142 may have any number, size, shape, and configuration as desired to provide a desired flow rate of the fluid from thefluid source 156 to thedisconnect assembly 111. - As illustrated in
FIG. 2 , thelink shaft 142 may also include aninner portion 171 formed adjacent the at least onefluid passageway 155 which is configured to further direct the fluid from thefluid source 156 towards the bearing 170 and militate against a substantial pooling of the fluid within theinner cavity 168. In one embodiment, theinner portion 171 is formed with a substantially 90° angle defining a shoulder thereof. It is understood, however, that theinner portion 171 may have any suitable shape and configuration as desired such as an inwardly tapered configuration to direct the fluid towards an inner portion of thebearing 170 or an outwardly tapered configuration to direct the fluid towards an outer portion of thebearing 170, for example. - A
fluid flow member 157 of thefluid flow system 153 is disposed about thelink shaft 142 and rotatable therewith. Various embodiments of the fluid flow member are shown inFIGS. 3A-3C, 4A-4C, 5A-5C, and 6A-6C . In certain embodiments shown inFIGS. 3A-3C, 4A-4C, 5A-5C , thefluid flow member 157 is formed by amain body 158 having a generally elliptical shape. In other embodiments shown inFIGS. 6A-6C , themain body 158 of thefluid flow member 157 may have a generally disc shape. Themain body 158 includes a substantially planarfirst surface 173 and a substantially planar opposingsecond surface 175. A plurality of retention features 177 may be disposed on thefirst surface 173 of themain body 158. Each of the retention features 177 may include aprotuberance 179 configured to cooperate with a corresponding feature (i.e. an annular groove) provided with thelink shaft 142 to securely maintain a position of thefluid flow member 157 on thelink shaft 142. The retention features 177 may be equidistantly spaced apart around circumference of acentral bore 165 formed in themain body 158. As non-limiting embodiments shown inFIGS. 3A-3C and 5A-5C , thefluid flow member 157 may include any number, shape, size, and configuration of the retention features 177 as desired. - As illustrated, the
main body 158 may also include at least onefirst surface feature 161 for directing the flow of the fluid obtained from thefluid source 156 into at least onecatch 159. In a non-limiting example, thefirst surface feature 161 may be generally arcuate shaped or generally involute shaped, substantially corresponding to an outer peripheral edge of themain body 158. In certain other embodiments, themain body 158 may further include at least onesecond surface feature 163 formed thereon. It should be appreciated that each of themain body 158, the retention features 177, and the surface features 161, 163 may be formed from any suitable material such as a metal, a non-metal material (i.e. a plastic), or any combination thereof, for example. In a non-limiting example, thesecond surface feature 163 may be generally circular shaped to substantially surround thecentral bore 165 formed in themain body 158. As shown, the surface features 161, 163 may be connected if desired. In certain embodiments, a face of at least one of the surface features 161, 163 abuts a substantiallyplanar face 181 of thelink shaft 142 to cause the fluid to flow therebetween. - An
end portion 167 of thefirst surface feature 161 opposite the at least onecatch 159 is configured to first rotate into thefluid source 156, when thefluid flow member 157 is rotated in a first direction, to collect and direct or funnel the fluid on themain body 158 to thedisconnect assembly 111. In other embodiments, the first surface features 161 may be formed on thesecond surface 175 so theend portions 167 are formed in alternating configurations so that when thefluid flow member 157 is rotated in either the first direction or an opposite second direction, thefluid flow member 157 collects and directs or funnels the fluid on themain body 158 to thedisconnect assembly 111. - In certain embodiments, the at least one
fluid catch 159 may be formed on thesecond surface 175 of themain body 158 of thefluid flow member 157. The at least onecatch 159 is substantially aligned with thefluid passageways 155 formed in thelink shaft 142 to permit fluid communication between thefluid source 156 and thefluid passageways 155. At least a portion of each of thecatches 159 may extend into thefluid passageway 155 to militate against a flow of the fluid across thesecond surface 175 of themain body 158 and direct or funnel the flow of the fluid through thefluid passageway 155 into thedisconnect assembly 111. In certain embodiments, at least one of thecatches 159 includes a protuberance (not depicted) extending radially outwardly therefrom to cooperate with an inner surface of thecavity 168 to maintain the position of thefluid flow member 157. - It is understood that the
fluid flow member 157 may have any shape, size, and configuration of themain body 158, any shape, size, number, and configuration of the at least onecatch 159, and any shape, size, number, and configuration of the first and second surface features 161, 163 as desired to provide the desired flow rate of the fluid from thefluid source 156 to thedisconnect assembly 111. - It is further understood that the
fluid flow member 157 may also include at least one of the first and second surface features 161, 163 and thecatch 159 formed on thefirst surface 173 thereof to provide lubrication to other various desired locations or components within thecarrier housing 102. It should be appreciated that when theaxle assembly 100 is configured so that thefirst surface 173 abuts a surface similar to theface 181 of the link shaft 42, the first and second surface features 161, 163 and thecatch 159 of thefluid flow member 157 collect and direct or funnel the fluid on themain body 158 to at least one of a desired location or component as described above. On the contrary, when theaxle assembly 100 is configured so that thefirst surface 173 of thefluid flow member 157 is open, the first and second surface features 161, 163 and thecatch 159 perform as a fluid dispersing device (i.e. a fluid slinger) sporadically disseminating the fluid throughout thecarrier housing 102 and not to a certain desired location. - Another preferred embodiment of the
fluid flow member 157′ is depicted inFIGS. 4A-4C wherein the first surface features 161′ are formed radially inwardly from the outer peripheral edge of themain body 158′ towards thecentral bore 165′. The structure of thefluid flow member 157′ which correspond to those ofFIGS. 3A-3C are given the same reference numerals with a prime (′) symbol. The manner of operation offluid flow member 157′ is the same as thefluid flow member 157. - Another preferred embodiment of the
fluid flow member 157″ is depicted inFIGS. 5A-5C wherein thefirst surface 173′ of themain body 158′ includes additional retention features 177′ formed thereon. The structure of thefluid flow member 157″ which correspond to those ofFIGS. 3A-3C and 4A-4C are given the same reference numerals with a double prime (″) symbol. The manner of operation offluid flow member 157″ is the same as thefluid flow members - Yet another preferred embodiment of the
fluid flow member 157′″ is depicted inFIGS. 6A-6C wherein themain body 158′″ is substantially disc shaped. The structure of thefluid flow member 157′″ which correspond to those ofFIGS. 3A-3C, 4A-4C, and 5A-5C , are given the same reference numerals with a triple prime (′″) symbol. The manner of operation offluid flow member 157′″ is the same as thefluid flow members - Referring now to
FIGS. 7A-7C , thesecond housing portion 106 of thecarrier housing 102 may include at least onefluid passageway 169 formed therethrough, which also forms part of thefluid flow system 153. In certain embodiments, thefluid passageways 169 is formed in a lower region of thesecond housing portion 106 to perform as a fluid return and permit the flow of the fluid from thedisconnect assembly 111 back to thefluid source 158. It is understood that thefluid passageways 169 of thesecond housing portion 106 may have any number, size, shape, and configuration as desired to provide a desired flow rate of the fluid from thedisconnect assembly 111 to thefluid source 156. - As more clearly shown in
FIGS. 7B and 7C , thesecond housing portion 106 may further include a firstfluid channel 183 and a secondfluid channel 185 formed therein, which also form part of thefluid flow system 153. In certain embodiments, thefluid channels second housing portion 106 radially outward from the outer peripheral edge of themain body 158 of thefluid flow member 157. Accordingly, each of thefluid channels fluid source 156 to thedisconnect assembly 111. It is understood that thefluid channels fluid source 156 to thedisconnect assembly 111. Further, the secondfluid channel 185 may further perform as a fluid catch to cause at least a portion of the fluid collected by thefluid flow member 157 but not distributed through thefluid passageways 155 to be recollected by the surface features 161, 163 and directed into thecatches 159 for distributing the fluid through thefluid passageway 155 into thedisconnect assembly 111. - Referring back to
FIG. 2 illustrates thedisconnect assembly 111 according to an embodiment of the present disclosure. Thedisconnect assembly 111 shown is configured to connect and disconnect components (e.g. axle half shafts or link shafts) in thevehicle 10. In a non-limiting example, thedisconnect assembly 111 connects and disconnects thelink shaft 142 from the secondaxle half shaft 160. It should be appreciated, however, that thedisconnect assembly 111 may be employed to connect and disconnect components of any suitable application as desired. In the embodiment shown, thelink shaft 142 is mounted for rotation within thesecond housing portion 106 via abearing 162 disposed about asecond end 164 thereof. Similarly, the secondaxle half shaft 160 is mounted for rotation within thethird housing portion 108 via abearing 166 disposed about afirst end 186 thereof. Various types of bearings may be employed for each of thebearings - As illustrated, the
second end 164 of thelink shaft 142 is disposed about thefirst end 186 of the secondaxle half shaft 160, which is received in theinner cavity 168 formed therein. In certain embodiments, thelink shaft 142 and the secondaxle half shaft 160 rotate relative to each other. In a non-limiting example, theshafts bearing 170 disposed therebetween. Various types of bearings may be employed for thebearing 170 such as a roller bearing, a tapered roller bearing, a ball bearing, a needle bearing, and the like, for example. - The
second end 164 of thelink shaft 142 shown has a generally cylindrical shape and includes a radiallyouter surface 172. In certain embodiments, the radiallyouter surface 172 includes a plurality ofsplines 174 formed thereon. Thelink shaft 142 may receive aclutch member 176 of thedisconnect assembly 111 thereon. Likewise, thefirst end 186 of the secondaxle half shaft 160 shown has a generally cylindrical shape and includes a radiallyouter surface 178. In certain embodiments, the radiallyouter surface 178 includes a plurality ofsplines 180 formed thereon. The secondaxle half shaft 160 may receive theclutch member 176 of thedisconnect assembly 111 thereon. In certain embodiments, thedisconnect assembly 111 includes theclutch member 176 rotatably coupled to one oflink shaft 142 and the secondaxle half shaft 160 and selectively coupled to a remaining one of thelink shaft 142 and the secondaxle half shaft 160 by any suitable method as desired. - The
disconnect assembly 111 illustrated includes theclutch member 176 and the splined ends 164, 186 of therespective shafts clutch member 176 shown has a generally cylindrical shape and includes a radiallyinner surface 182. In certain embodiments, the radiallyinner surface 182 includes a plurality ofsplines 184 formed thereon. Theclutch member 176 may receive therein and be in splined engagement with thesecond end 164 of thelink shaft 142. Various other suitable methods of engagement may be employed to engage the clutch member and thesecond end 164 of thelink shaft 142 such as a press fit, for example. In certain embodiments, theclutch member 176 is axially movable and rotatably fixed to thelink shaft 142. Theclutch member 172 may also removably receive therein and be in selective splined engagement with thefirst end 186 of the secondaxle half shaft 160. In certain embodiments, theclutch member 176 is axially movable and selectively rotatably fixed to the secondaxle half shaft 160. It should be appreciated that other suitable methods of selective engagement may be employed between theclutch member 172 and thefirst end 186 of the secondaxle half shaft 160 if desired. - The
disconnect assembly 111 may further include anactuator assembly 190. As a non-limiting example, theactuator assembly 190 may be an electromagnetic solenoid. It is understood, however, that various other types of actuator assemblies may be employed such as a mechanical, an electro-mechanical, pneumatic, or hydraulic actuator assembly, if desired. The actuator,assembly 190 may be mounted on thecarrier housing 102 of theaxle assembly 100. In certain embodiments, theactuator assembly 190 may be coupled with thethird housing portion 108 such that theactuator assembly 100 is fixed against rotation relative to thecarrier housing 102. Referring now toFIG. 2 , theactuator assembly 190 includes ahousing 192. Anactuator component 196 such as an electromagnetic coil, for example, is disposed within thehousing 192. Theactuator component 196 is in electrical communication with a power source (not depicted), such as, but not limited to, a battery. Theactuator component 196 may also be in communication with a controller (not depicted). In an embodiment, the controller may be mounted to an inboard surface or an outboard surface of thecarrier housing 102. The electric motor-generator 101 may be in electrical communication with the controller. The controller may determine an operation of the electric motor-generator 101 and a state (e.g. engaged and disengaged) of thedisconnect assembly 111. - A generally hollow-
cylindrical armature 198 is disposed in thehousing 192, radially between theactuator component 196 and an inner portion of thethird housing portion 108. In an embodiment, thearmature 198 does not rotate relative to thecarrier housing 102. Thearmature 198 comprises a ferromagnetic material. It should be appreciated that theactuator assembly 190 may be designed with an additional spacer and pressure plate, if desired. - In an embodiment, the
armature 198 is coupled with theclutch member 176. In one embodiment, thearmature 198 may be coupled with theclutch member 176, such that they move axially as a single unit. Thearmature 198 and theclutch member 176 may be coupled together via a snap-fit connection, for example. In the embodiment shown, theclutch member 176 includes aradially extending flange 199 received into thearmature 198. Coupling thearmature 198 and theclutch member 176 prevents thearmature 198 from being vibrated into a disengaged position while theclutch member 176 remains in an engaged position. - A biasing
member 200 is disposed at least partially about thearmature 198 and axially adjacent thehousing 192 and thearmature 198. In an embodiment, the biasingmember 200 is disposed axially between thehousing 192 and a retention element 202 (i.e. a snap ring) which is received in a groove located in an outer surface of thearmature 198. The biasingmember 200 may be, but is not limited to, one or more springs, one or more wave springs, or one or more Bellville-type washers. - As shown in
FIG. 1 , thedisconnect assembly 111 of theaxle assembly 100 is typically in a default disengaged position with theclutch member 176 in a first position. To engage thedisconnect assembly 111, a signal from the controller causes electricity, which may also be referred to herein as an excitation voltage, to be supplied to theactuator component 196. The energizedactuator component 196 generates a magnetic flux. The magnetic flux of theactuator component 196 causes thearmature 198 to move in a first axial direction and urge theclutch member 176 in the first axial direction from the first position to a second position and into engagement with the secondaxle half shaft 160, thereby compressing the biasingmember 200. In the embodiment shown, when theclutch member 176 is engaged with the secondaxle half shaft 160, a desired torque is transferred between thelink shaft 142 to the secondaxle half shaft 160, and to the wheels of thevehicle 10. - To return the
clutch member 176 to the first position, and urge theclutch member 176 in a second axial direction from the second position back to the first position and into disengagement with the secondaxle half shaft 160, the controller causes the supply of electricity to theactuator component 196 to be interrupted or reduced. The termination or reduction in the energization of theactuator component 196 enables the biasingmember 200 to urge theclutch member 176 in the second axial direction and disengage the secondaxle half shaft 160, which thereby disconnects the torque transfer between thelink shaft 142 and the secondaxle half shaft 160. When theactuator component 196 is energized, theclutch member 176 may not immediately engage the secondaxle half shaft 160. This time delay may lead to an uncertainty regarding the locked/un-locked state of thedisconnect assembly 160. To determine the axial position of theclutch member 176, and therefore the locked/un-locked state of thedisconnect assembly 111, a sensor (not depicted) may be utilized. Various types of sensors may be utilized for the sensor such as an eddy current sensor, for example. - During operation of the
vehicle 10, the electric motor-generator 101 generates a torque which is transferred from an output shaft thereof through the at least one gear assembly to the differential 110 via thering gear 114. The differential 110 in turn transfers a desired torque to the firstaxle half shaft 140 and thelink shaft 142 causing a rotational movement thereof. When thedisconnect assembly 111 is engaged, the torque is further transferred from thelink shaft 142 to the secondaxle half shaft 160 causing a rotational movement thereof. On the contrary, when thedisconnect assembly 111 is disengaged, the torque is not transferred from thelink shaft 142 to the secondaxle half shaft 160. However, the rotational movement of the firstaxle half shaft 140 and thelink shaft 142 is continued. Accordingly, the desired flow rate of the fluid fromfluid source 156 through thefluid flow system 153 is essential for proper operation of theaxle assembly 100 as well as to militate against undesired friction and wear of the components therewithin. - Since the rotational movement of the
link shaft 142 occurs during the operation of thevehicle 10, when thedisconnect assembly 111 is both engaged and disengaged, thefluid flow member 157 coupled to thelink shaft 142 is also caused to rotate therewith. As thefluid flow member 157 is rotated, at least one of the surface features 161, 163 is rotated through the fluid disposed in thefluid source 156 of thecarrier housing 102. As thefluid flow member 157 continues to rotate, the surface features 161, 163 and centrifugal force acting on the fluid, then cause the collected fluid to flow and funnel into thecatches 159 and through thefluid passageways 155 of thelink shaft 142. Once the fluid flows through thefluid passageways 155, a centrifugal force caused by the rotational movement of thelink shaft 142 causes the fluid to flow into thecavity 168 and in and around the bearing 170 disposed therein to provide lubrication thereto. Thereafter, the fluid begins to flow to the lower portion of thecarrier housing 102 due to a decrease in the centrifugal force and an increase in a gravitational effect on the fluid flow. As the fluid flows to the lower portion of thecarrier housing 102, it flows through thefluid passageway 169 formed in thesecond housing portion 106 and back to the fluid source to be redistributed throughout thecarrier housing 102 or recollected by thefluid flow member 157. Additionally, thefluid channel 183 further facilitates the flow of fluid from thefluid source 156 to thedisconnect assembly 111. - While various embodiments have been described above, it should be understood that they have been presented by way of example, and not limitation. It will be apparent to persons skilled in the relevant arts that the disclosed subject matter may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The embodiments described above are therefore to be considered in all respects as illustrative, not restrictive.
Claims (20)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/662,678 US10968793B1 (en) | 2019-10-24 | 2019-10-24 | Axle assembly |
DE202020106034.1U DE202020106034U1 (en) | 2019-10-24 | 2020-10-22 | Axle assembly |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/662,678 US10968793B1 (en) | 2019-10-24 | 2019-10-24 | Axle assembly |
Publications (2)
Publication Number | Publication Date |
---|---|
US10968793B1 US10968793B1 (en) | 2021-04-06 |
US20210123363A1 true US20210123363A1 (en) | 2021-04-29 |
Family
ID=74495221
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/662,678 Active US10968793B1 (en) | 2019-10-24 | 2019-10-24 | Axle assembly |
Country Status (2)
Country | Link |
---|---|
US (1) | US10968793B1 (en) |
DE (1) | DE202020106034U1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220111892A1 (en) * | 2019-02-21 | 2022-04-14 | Schaeffler Technologies AG & Co. KG | Motor vehicle with driven wheels on a number of axles and method for controlling same |
US20230046751A1 (en) * | 2021-08-13 | 2023-02-16 | Warn Automotive, Llc | Ev disconnect control |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3652462B2 (en) * | 1997-01-14 | 2005-05-25 | 本田技研工業株式会社 | Rear differential casing structure for vehicles |
JP3406169B2 (en) * | 1997-01-14 | 2003-05-12 | 本田技研工業株式会社 | Driving force control device for four-wheel drive vehicle |
JP3252095B2 (en) * | 1997-01-14 | 2002-01-28 | 本田技研工業株式会社 | Lubrication structure of clutch in power transmission device |
JPH10194005A (en) * | 1997-01-14 | 1998-07-28 | Honda Motor Co Ltd | Four-wheel drive vehicle |
JP3683062B2 (en) * | 1997-01-14 | 2005-08-17 | 本田技研工業株式会社 | Power transmission device for vehicle |
JP3299465B2 (en) * | 1997-01-14 | 2002-07-08 | 本田技研工業株式会社 | Electromagnetic clutch |
DE102010017864A1 (en) * | 2010-04-22 | 2011-10-27 | Daimler Ag | Oil supplying device for gear box for motor vehicle, comprises disk shaped conveyor wheel, which is arranged on shaft in torque-proof manner, where shaft has axial oriented oil supplying channel, and radial oriented supply opening |
JP5720165B2 (en) * | 2010-10-05 | 2015-05-20 | 株式会社ジェイテクト | Four-wheel drive vehicle |
PL2574827T3 (en) * | 2011-09-30 | 2014-06-30 | Gkn Driveline Koeping Ab | Coupling assembly with oil drainage device |
JP6318622B2 (en) * | 2014-01-06 | 2018-05-09 | 株式会社ジェイテクト | Driving force distribution device for vehicle |
WO2016089764A1 (en) * | 2014-12-02 | 2016-06-09 | Robert Bosch Gmbh | Seal protection and lubricant in worm drive power tool |
US9885415B2 (en) * | 2015-06-25 | 2018-02-06 | Dana Automotive Systems Group, Llc | Differential clutch carrier lubrication and cooling system |
CN107166018A (en) * | 2016-03-07 | 2017-09-15 | 舍弗勒技术股份两合公司 | Speed changer, oil feeding device |
DE112017001447A5 (en) * | 2016-03-23 | 2018-12-27 | Schaeffler Technologies AG & Co. KG | Planet drive with at least one planet carrier, planetary gears, planet pins and with a lubricator |
-
2019
- 2019-10-24 US US16/662,678 patent/US10968793B1/en active Active
-
2020
- 2020-10-22 DE DE202020106034.1U patent/DE202020106034U1/en active Active
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220111892A1 (en) * | 2019-02-21 | 2022-04-14 | Schaeffler Technologies AG & Co. KG | Motor vehicle with driven wheels on a number of axles and method for controlling same |
US11884346B2 (en) * | 2019-02-21 | 2024-01-30 | Schaeffler Technologies AG & Co. KG | Motor vehicle with driven wheels on a number of axles and method for controlling same |
US20230046751A1 (en) * | 2021-08-13 | 2023-02-16 | Warn Automotive, Llc | Ev disconnect control |
Also Published As
Publication number | Publication date |
---|---|
DE202020106034U1 (en) | 2021-01-19 |
US10968793B1 (en) | 2021-04-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2712066B1 (en) | Axle assembly having an electric motor module | |
US7094172B2 (en) | Differential and differential system | |
US11674575B2 (en) | Drive axle with a disconnect device | |
US9931930B2 (en) | Driving force transmission apparatus and four-wheel drive vehicle | |
US11118665B2 (en) | Electrical differential locker with eddy current sensor | |
CN211852691U (en) | Electric drive axle | |
US10968793B1 (en) | Axle assembly | |
US11415208B2 (en) | Multi-speed gearbox with a gear-clutch assembly | |
US11149823B2 (en) | Planetary gear system with disconnect and the drive axle made therewith | |
CN102985723A (en) | Torque-distribution control device | |
EP1666771A1 (en) | Pinion Unit in Axle Assembly | |
US20210285536A1 (en) | Ultra-lightweight rear axle drive (ulrad) assembly with clutch lubrication system | |
US10808775B2 (en) | Torque limiter | |
US11639102B2 (en) | Integrated power source and housing | |
JP4195534B2 (en) | Coupling | |
US20050247148A1 (en) | Output yoke shaft and assembly | |
EP3559490B1 (en) | A joint assembly with an installation aid | |
US6475091B1 (en) | Linking structure for power transmission device | |
US20040168845A1 (en) | Transfer case bushing | |
US20240051385A1 (en) | Wheel hub clutch, wheel hub, wheel end system, axle, drivetrain, and vehicle | |
JP3989655B2 (en) | Coupling and differential equipment | |
US11242899B2 (en) | Fluid distribution apparatus and the axle assembly made therewith | |
JP4918523B2 (en) | Coupling and coupling assembly method | |
JP2001153203A (en) | Cam groove, coupling using it and differential gear | |
JP2002266897A (en) | Electromagnetic coupling |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
FEPP | Fee payment procedure |
Free format text: ENTITY STATUS SET TO UNDISCOUNTED (ORIGINAL EVENT CODE: BIG.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
AS | Assignment |
Owner name: DANA AUTOMOTIVE SYSTEMS GROUP, LLC, OHIO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KRISHNAN, SAJEEV C.;LONGARDNER, BRIAN S.;BILLMAIER, NICHOLAS C.;AND OTHERS;SIGNING DATES FROM 20191026 TO 20191218;REEL/FRAME:051860/0792 |
|
AS | Assignment |
Owner name: CITIBANK, N.A., NEW YORK Free format text: SECURITY AGREEMENT SUPPLEMENT;ASSIGNORS:DANA HEAVY VEHICLE SYSTEMS GROUP, LLC;DANA LIMITED;DANA AUTOMOTIVE SYSTEMS GROUP, LLC;AND OTHERS;REEL/FRAME:052459/0224 Effective date: 20200416 Owner name: CITIBANK, N.A., NEW YORK Free format text: SECURITY AGREEMENT (BRIDGE);ASSIGNORS:DANA HEAVY VEHICLE SYSTEMS GROUP, LLC;DANA LIMITED;DANA AUTOMOTIVE SYSTEMS GROUP, LLC;AND OTHERS;REEL/FRAME:052459/0001 Effective date: 20200416 |
|
AS | Assignment |
Owner name: DANA LIMITED, OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CITIBANK, N.A.;REEL/FRAME:053309/0686 Effective date: 20200619 Owner name: DANA AUTOMOTIVE SYSTEMS GROUP, LLC, OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CITIBANK, N.A.;REEL/FRAME:053309/0686 Effective date: 20200619 Owner name: DANA HEAVY VEHICLE SYSTEMS GROUP, LLC, OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CITIBANK, N.A.;REEL/FRAME:053309/0686 Effective date: 20200619 Owner name: FAIRFIELD MANUFACTURING COMPANY, INC., OHIO Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CITIBANK, N.A.;REEL/FRAME:053309/0686 Effective date: 20200619 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |