Radial hole arrangement that separates a rotational lubrication

Abstract

Lubrication system for a gearbox, comprising: a shaft of the transmission having a fluid passage, the fluid passage being centered on an axis that is parallel and not coaxial with a rotational axis of the shaft, the shaft being centered on the rotational axis; and at least two axially spaced radial channels, the axially spaced radial channels being in fluid communication with the fluid passage and being inclined at different angles with respect to a plane intersecting the shaft in a longitudinal direction with respect to the axis of rotation, the plane including the axis of rotation and the axis of the fluid passage, the different angles decreasing in magnitude for each axially spaced radial channel that is farther from an inlet than a previous spaced radial channel.

Description

TECHNICAL FIELD

[0001] This description relates to a shaft containing a lubrication system. The shaft and the lubrication system comprise a lubrication line that runs parallel and not coaxially to a rotational axis of the shaft. The lubrication system distributes the fluid and lubricates the support structures for the rotating elements of a gearbox in which the shaft is housed. BACKGROUND AND SUMMARY

[0002] Vehicles, such as electrified vehicles, may have a transmission that shifts a variety of different gears, with each of the different gears capable of delivering different torque and speeds for the same input torque. At higher speeds, the focus is on the efficiency with which heat energy is removed from the transmission components and friction is reduced through lubrication. A friction force greater than a first threshold and heat energy greater than a second threshold can lead to transmission degradation. Transmission lubrication may be provided by one or more pumps.

[0003] In an example transmission with rotating shafts, each shaft may be hollow and have a central passage coaxial with the centerline and axis of rotation of the shaft, and a plurality of radially arranged channels configured to deliver lubricant from the central passage to the components of the transmission. However, with such an arrangement, the amount of lubricant delivered to the channels may decrease with distance from the lubricant supply (e.g., the pump), resulting in fluid starvation in some channels. The fluid starvation may become more severe at higher shaft speeds because the lubricant is displaced from the channels at larger flow rates. In some examples, the lubricant may be completely depleted before reaching a channel. Similarly, if fluid starvation occurs in a channel, the lubricant may lower the fluid level above the surface of the central passage below a first threshold.Below the first threshold, the fluid may not flow through the channels at a flow rate appropriate for the load. Furthermore, adhesion to the passage surface or turbulence may cause the lubricant entering the channel to fall below a minimum flow rate required to lubricate the components complementary to the channel. Fluid deficiencies can lead to damage to transmission components.

[0004] Fluid deficiency can be remedied by increasing the volumetric flow rate in the central passage. The volumetric flow rate can raise the fluid level above the surface of the central passage. The volumetric flow rate can be increased by increasing the pressure of the pump supplying the inlet of each shaft and each of its central passages. Increasing the pump pressure can increase power losses in the lubrication system, thereby reducing the efficiency of the lubrication system and the efficiency of the transmission system in terms of power / energy consumption and heat dissipation. In addition, fluid deficiency can be remedied by reducing the dimensions (e.g., volume, diameter) of the additional channels. However, reducing the dimensions of the channels can complicate the production process and lead to greater clogging and blockage of the channels, thereby reducing lubrication via the channel.

[0005] A lubrication system for a transmission, comprising: wherein a shaft of the transmission has a fluid passage, the fluid passage centered on an axis that is parallel and non-coaxial with a rotational axis of the shaft, the shaft centered on the rotational axis; and at least two axially spaced radial channels, the two axially spaced radial channels in fluid communication with the fluid passage and inclined at different angles with respect to a plane intersecting the shaft in a longitudinal direction with respect to the rotational axis, the plane including the rotational axis and the axis of the fluid passage, the different angles decreasing in magnitude for each axially spaced radial channel that is farther from an inlet than a previous spaced radial channel.

[0006] Offsetting the axial passage from the axis can prevent or reduce the spread of lubricant on the inner surface of the axial passage. Offsetting the axial passage from the axis of rotation can allow the lubricant in the axial passage to have a maximum height and a minimum height, where the height can be the distance between the closest point on the surface of the axial passage and the surface of the lubricant. The offset axial passage can be radially centered about a first axis that is parallel to the axis of rotation. The lubricant can pool and have a fluid level at the maximum height from the inner surface at a second axis on the inner surface. The second axis is parallel to the first axis and the axis of rotation and is located at a position on the inner surface approximately farthest from the axis of rotation.Each of the radial channels may have an inner opening and an outer opening, whereby the radial channels are in fluid communication with the axial passageway and with an outer surface of the shaft, respectively. Each inner opening may be positioned flush with the conduit. The maximum height is selected to be above the inner openings to reduce resistance due to adhesion between the inner surface and the fluid, which could prevent or reduce penetration of the lubricant into the inner openings. In such an arrangement, the radial channels may be feed channels. Likewise, the at least two axially spaced radial channels may be angled with respect to height, the height being included by a plane that intersects the shaft in a longitudinal direction with respect to the axis of rotation.At speeds that meet or exceed a first threshold, the shaft may exert one or more radially directed forces on the lubricant, reducing splashing of the lubricant in the axial passage and thus reducing power losses. At speeds that meet or exceed a second threshold, the shaft may have such a centripetal force that the surface of the lubricant in the axial passage is a nearly fluid-free surface. Such an arrangement may enable a constant volume flow of fluid through each of the axially spaced radial channels. There may be a plurality of axially spaced radial channels greater than two.

[0007] It should be understood that the above summary is intended to introduce, in simplified form, a selection of concepts that are further explained in the detailed description. It is not intended to identify the most important or essential features of the claimed subject matter, the scope of which is clearly defined by the claims that follow the detailed description. Furthermore, the claimed subject matter is not limited to implementations that address the disadvantages noted above or elsewhere in this disclosure. SHORT DESCRIPTION OF THE CHARACTERS Fig. 1 shows an exemplary schematic representation of a vehicle that may include the transmission of the present disclosure. Fig. 2 shows a schematic example of a gear arrangement of the transmission including shafts and the lubrication system of the present disclosure. Fig. 3 shows a sectional view of an eight-speed gear case of the present disclosure. Fig. 4 shows a side view of a first shaft of the present disclosure, partially cut away and exploded. Fig. 5 shows a cross-sectional view and a schematic example of a shaft and a complementary axial passage of the present disclosure. Fig. Figure 6 shows a sectional view and a schematic example of a shaft and a complementary axial passage from the prior art. Fig. 7 shows a sectional view of the example of the present disclosure with the angles of the specific features. Fig. 8 shows a cross-sectional view of a schematic example of a shaft, an axial passage and fluid channels in accordance with the present disclosure. Fig. Figure 9 shows a sectional view of the shaft with an angle of the fluid channels relative to the axial passage. Fig. Figure 10 shows a composite cross-sectional view of the fluid channels and their respective angles superimposed on the shaft. DETAILED DESCRIPTION

[0008] The following description refers to one or more shafts integrated as part of a lubrication system. Each shaft is in fluid communication and supplied with lubricant. The lubricant may be supplied to one or more shafts, for example, via a pump. Another example is the supply of lubricant to one or more shafts by gravity. At least one of the shafts has an axial passage parallel to a rotational axis of the shaft and not coaxial with the rotational axis, with the axial passage centered on an axis parallel to the rotational axis. One, several, or all of the shafts may have an axial passage specific to that shaft. Each shaft containing the axial passage has at least two axially spaced radial channels in fluid communication with the axial passage. There may be two or more axially spaced radial channels.Each of the axially spaced radial channels may be inclined at different angles with respect to a plane intersecting the shaft in a longitudinal direction with respect to the axis of rotation. The plane includes the axis of rotation and the axis on which the fluid passage is centered. Each of the radial channels may be inclined and extend at a different angle than the other radial channels that the shaft includes. The radial channels may be inclined and extend at different angles such that a centerline (e.g., an axis) on which the radial channel is centered is inclined and extends at one of the different angles. The axial passage has at least one first opening, wherein the first opening may be located at one end of the shaft and have a surface perpendicular to an axis. The first opening may be an inlet that can receive lubricant from at least one pump.Each of the different angles decreases in magnitude for each axially spaced radial port that is farther from the inlet than a previous spaced radial port.

[0009] Each shaft can distribute fluid to lubricant consumers located around the shaft, e.g., around the shaft, via a plurality of channels and complementary openings in communication with one or more outer surfaces of the shaft. The fluid channels can be arranged radially around and extend radially from the axial passage. The fluid channels can extend radially outward from the axial passage at a variety of different angles. Each of the fluid channels can have an inner and an outer opening, the inner opening being flush and adjacent to the surface of the axial passage and the outer opening being adjacent and flush to an outer surface of the shaft. Some consumers can be complementary to at least one fluid channel, such that the consumers can be arranged around the outer opening of a complementary fluid channel of the fluid channels.Other consumers may be located sufficiently close to the outer opening of one of the fluid passages to be lubricated via the outer opening. The shaft with the axial passage may have a variety of inner and outer diameters, wherein the inner and outer diameters may be of different sizes. The shape of the shaft may be unlimited, and the shaft may have a variety of surfaces, lands, and other features of different diameters extending outwardly and / or radially from a cylindrical or partially cylindrical core of the shaft.

[0010] Gearboxes, transmissions, and drivetrains, as well as all mechanical systems with moving / rotating / rolling / sliding components such as gears or bearings, require lubrication. Furthermore, for proper system functioning, lubricant must be present at all times at most locations and components of the rotating elements where heat can accumulate or friction can occur (e.g., bearings, gear meshes, etc.). It is common practice to use an electrically or mechanically driven volumetric pump to generate a lubricant flow that can be effectively directed to the components to be lubricated and cooled. The lubrication system of the present disclosure can be used for a transmission in the form of a gearbox, an axle, or a transaxle.Furthermore, the lubrication system of the present disclosure may be used for a system of gear sets or other gear reduction sets that are not part of a transmission, e.g., in a gear box that is not a transmission. The transmission and gear box may be an eight-speed configuration in a two-shaft pattern; however, the transmission and gear box may also have other patterns. For example, the transmission and / or gear box may have more or fewer gears than an eight-speed transmission / gear box. In this or another example, the transmission and / or gear box may have a shaft pattern with a greater number of shafts than two shafts.

[0011] Furthermore, the shafts are approximately horizontal with respect to the gravitational field. The shafts may each have at least one fluid passage through which a fluid can flow when the respective shaft of the fluid passage is rotated. The fluid passage of the shaft is intended to channel the oil flow supplied at a first end of the shaft to a plurality of bearings, such as a plurality of needle bearings, of one or more idler gears. The fluid passage may be a bore, such as a gun bore. A plurality of channels may be in fluid communication with the fluid passage of the shaft. The channels may be arranged radially around the fluid passage and extend radially outwardly therefrom; the channels may be referred to herein as radial channels.The idler gears may be disposed near a second end of the first end, the second end being on the opposite side of the upper shaft from the first end. Each idler gear may be complementary to and supported by one or more sets of bearings, such as needle bearings. The idler gears and the bearings complementary to the idler gears may be disposed around the shaft such that the idler gears and the bearings may be disposed radially around the shaft. Each idler gear and the bearings to the idler gears may be supplied with lubricant via at least one of the radial channels.

[0012] For example, there may be at least four idler gears with complementary needle bearings for lubrication. In this or any other example, the number of radial channels, e.g., feed ports, for the lubrication of each idler gear may vary. There may be two sets of bearings closest to the first end, and there may be two sets of bearings closest to the second end. The two sets of bearings closest to the first end may be complementary to and lubricated through a single radial channel. The two sets of bearings closest to the second end may be supplemented and lubricated through multiple feed ports. The flow injected into the first end of the shaft is sized to ensure that the progressive emptying of the first bearing bores leaves a minimum of oil to avoid starvation of the most distant consumer.The higher the shaft speed, the more flow the first hole allows to drain away from the cascaded consumers, exposing even more of the rear bearing(s). In this context, if the bearing(s) are more exposed, they will be coated with less lubricant than a less exposed or unexposed bearing. To overcome this problem, the oil supplied to the shaft is sized so that the first holes cannot drain all of the flow, leaving a sufficient amount for the last hole. Generally, on a fast-rotating shaft, the amount of oil drained through a 2-millimeter hole during a first flow exceeds the amount of lubricant required for a second flow to keep the bearing cooled and lubricated. Reducing the hole diameter increases the complexity of the production process and can increase hole clogging.Hole blockages can lead to deterioration, as a load in a hole, channel, or other secondary passage no longer receives lubricant. The use of bore diameters based on proven technology can therefore result in oversizing the oil flow, requiring a larger pump and causing excessive splash power loss, which reduces the overall efficiency of the transmission. Efficient power transmission may be particularly desirable for environmentally friendly and sustainable battery-powered electric vehicles. The overall efficiency of the transmission system can relate to both the heat dissipated by the lubrication system and the amount of energy consumed by the transmission. A transmission that has more friction and / or splash water may have higher power losses and be less efficient.

[0013] The loads to be lubricated may be lubricated at a flow rate above a first threshold, the first threshold being a minimum flow rate that allows for sufficient margin. With sufficient margin, the functional minimum flow rate may be increased by at least an order of magnitude above an actual minimum. The functional and actual minimum flow rate for bearings and other loads may depend on the performance specifications of a transmission. For example, the transmission of the present disclosure may be a 200-kilowatt transmission, and the actual minimum flow rate may be 0.1 liters per minute (L / min) for each of a plurality of bearings. In this example, the transmission may have a functional minimum flow rate at or above a threshold of approximately 0.6 L / min.To provide the minimum volumetric flow, a first diameter of 3 mm may be sufficient; however, the fluid passage may have a second diameter which may be substantially larger, e.g., 20 millimeters. Substantial may refer to two or more components, features, or measurements being compared, with one component being substantially larger or smaller than another component by a factor of two or more, unless otherwise specified. At the minimum volumetric flow through the second diameter, the resultant flow from fluid mechanics and through the fluid passage may be open channel flow. In open channel flow, the fluid, e.g., a lubricant, in the fluid passage may have a fluid-free surface on which the fluid moves under the action of the applied force field(s) rather than under a pressure gradient.The acting force field may include the centripetal force from the shaft rotation and gravity. The acting force field may drive the lubricant from the fluid-free surface in a radial direction away from the axis. There may be a fluid-free surface with a nearly constant pressure along the fluid passage. (This applies to low flow rates for fluid passages above a threshold diameter; in the case of excessive flow to transport the lubricant to the farthest bearing, this is pipe flow without a fluid-free surface, and a pressure drop along the line (fluid passage) drives the fluid.)

[0014] In this or another example, the shaft may additionally or alternatively include at least one second fluid passage. The axis of the shaft may lie in a horizontal plane with respect to the gravitational field. The second fluid passage may be offset from the axis of rotation and the centerline of the shaft. However, the second fluid passage may also be arranged about an axis parallel to the axis of rotation and the centerline of the shaft, for example, parallel to this axis and centered on this axis. The second fluid passage may alternatively be referred to as an axial passage. The second fluid passage may be a bore, e.g., a gun bore. The second fluid passage may include a plurality of first fluid channels and a plurality of second fluid channels in fluid communication with and extending radially from the second fluid passage.The first fluid channels may be axially separated fluid channels, similar to the axially separated fluid channels described above. The first channels may be vents, each supplying lubricant to one or more users. The second fluid channels may transport and distribute a fluid, e.g., a lubricant, from the second fluid passage to the outer surfaces of the shaft. Each of the second fluid channels may be complementary to at least one user, where the user may be positioned around the surface to which a complementary second fluid channel of the second fluid channel distributes the lubricant. The users may also be referred to as consumers. The second fluid channels may also be referred to as second fluid distribution channels. The second fluid channels may be offset from the second fluid passage, e.g., extending radially outward from the second fluid passage.The second fluid passage can supply a plurality of consumers via the second fluid channels, wherein each of the second fluid channels can supply a specific consumer or a plurality of consumers.

[0015] The second fluid passage has a single opening, the opening being an inlet for the lubricant to be supplied. Regardless of whether the lubricant is supplied from the first or second end of the shaft, e.g., from a left or right end, each of the first fluid channels and each of the second fluid channels can divert the lubricant flow via an opening to one or two downstream users. The openings of the first channels and the second channels can have a first threshold diameter to achieve a minimum flow rate. For example, the first channels can have an opening with a diameter of at least 4 millimeters (mm). To achieve a minimum oil flow to the most distant users, the pressure in the second fluid passage ensures that the oil flow is balanced between the at least four second channels.To maintain pressure and minimum flow rate for users, each of the second channels may have a second threshold diameter. For example, the second channels may have an opening of at least 1.6 mm in diameter. Likewise, each of the second fluid channels may have a minimum length, for example, 17 mm or more. In this example, one or more of the second channels may have a constant diameter equal to the threshold diameter. In this or another example, one or more of the second channels may have a variable diameter, including diameters smaller and / or larger than the threshold diameter of the opening.

[0016] For example, there may be two lubricant consumers, namely two needle bearings and two radial bores on a shaft, where each radial bore can supply its own needle bearing with lubricant. Each radial bore can be fluidly connected to an axial passage on the shaft. The axial passage is centered on a shaft axis. The axial passage can have an opening through which fluid can be supplied to the axial passage. The radial hole closest to the opening with respect to and along the axis can be referred to as the first user in this example. The radial hole furthest from the opening with respect to the axis can be referred to as the second user in this example. Each bearing that can be supplied with lubricant via a consumer can have a minimum flow rate, e.g. 0.1 l / min.The minimum flow rate can be significantly lower than the flow rates allowed by a radial bore or other channel, for example, a flow rate of 2.1 l / min. If 0.2 l / min is injected as flow into the axial passage, the first user can completely vent the flow and no lubricant can be provided to the second user. Under a centrifugal force field, a 4 mm diameter radial hole can discharge a fluid flow on the order of liters per minute (L / min). Assuming the first user has a 4 mm diameter radial hole, the first user can discharge 2 l / min of fluid. It may be sufficient to supply a fluid flow of 2.1 l / min or more to supply lubricant to the second user. However, the pump may need to be designed to deliver 2.1 l / min instead of 0.2 l / min.In addition, at least 1.9 l / min is lost through the first consumer, causing fluid to splash around the gearbox and the 1.9 l / min of lubricant to be lost. To avoid performance losses, the radial holes of the first and second user can be manufactured with different diameters. For example, the radial hole of the first user can be manufactured with a diameter of 1.6 mm. In the same centrifugal field, the first user can discharge 0.6 l / min, and the pump can deliver 0.7 l / min instead of 0.2 l / min. Oversizing the pump is somewhat less, and 0.5 l / min of fluid flow contributes to the splash loss. The diameter of an opening, such as the radial holes of the first or second user, cannot be arbitrarily reduced due to technological limitations in the machining process and can increase clogging of the radial hole for the first user compared to a larger hole.

[0017] To avoid performance losses and oversizing without changing the sizing and dimensions of the channels connected to the fluid passage, a shaft of the present disclosure may be used as part of the forced lubrication system. The shaft of the present disclosure may include an axial passage, such as a fluid passage. The axial passage is offset from the central axis and the axis of rotation of the shaft. The axial passage is centered on another axis that is parallel and not coaxial with the central and rotational axis of the shaft. The shaft includes at least two axially spaced radial channels that communicate with the fluid passage and are inclined at different angles with respect to a plane that intersects the shaft longitudinally with respect to the axis of rotation. The plane includes the central and rotational axis of the shaft and includes the other axis on which the axial passage is centered.The angles of the two axially spaced radial channels can prevent a fluid (e.g., lubricant) specific to the diameter and cross-sectional area of each radial channel from flowing through the radial channels at its maximum flow rate. A fluid in the axial passage may have a fluid surface equidistant from the central and rotational axes of the shaft. An offset of the axial passage from the central axis and the rotational axis can cause the fluid surface to assume a circular curved shape. The circular curved shape of the fluid surface follows the circumference of a circle or cylinder in the radial direction around the central axis. The shape of the fluid surface and the angulation of each of the two axially spaced radial channels can prevent a maximum volume of fluid from flowing through each of the two axially spaced radial channels.A first radial channel at a first angle can receive fluid from the axial passage until a fluid surface elevation falls below a first opening of the first radial channel. Similarly, the second radial channel at a second angle can receive fluid from the axial passage until the fluid surface elevation falls below a second opening to the second radial channel. The first angle can be greater than the second angle such that the second radial channel can receive fluid that is at a lower elevation than the first radial channel. Each of the two axially spaced radial channels can be supply openings that can supply a consumer and can be part of a user.For example, the two axially spaced radial channels may be used instead of the radial holes of the above example, with a first radial channel belonging to a first user and a second radial channel belonging to a second user. Additionally or alternatively, there may be more than two axially spaced radial channels, each of the axially spaced radial channels extending at a different angle from the plane. Wherein each angle for a radial channel is smaller than the angle of the last radial channel, the radial channel being further axially from the inlet than the last radial channel. Additionally or alternatively, there may be one or more vents which are axially spaced radial channels. The one or more vents may comprise one or more of the two axially spaced radial channels.

[0018] Fig. 1 shows an exemplary schematic representation of a vehicle that may include the transmission of the present disclosure. The vehicle in Fig. 1 may be an electrified vehicle, such as an electric vehicle or a hybrid vehicle with multiple torque sources, which may include an electric motor, a hydrogen fuel cell, and / or an internal combustion engine. Fig. 1 shows an exemplary schematic representation of a vehicle that may include the transmission of the present disclosure. Fig. 2 shows a schematic example of a gear arrangement of the transmission including shafts and the lubrication system of the present disclosure. Fig. 3 shows a sectional view of an eight-speed gear box of the present disclosure. The eight-speed gear box in Fig. 3 is a two-shaft gearbox with two axle shafts, which can be coupled optionally via one or more of the couplings shown. Fig. Figure 4 shows a side view of a first shaft of the present disclosure, partially cut and exploded. The first shaft of Fig. 4 can be used instead of one of the two waves of Fig. 3 can be used.

[0019] Fig. 5 shows a cross-sectional view and a schematic example of a shaft and a complementary axial passage of the present disclosure. Fig. Figure 6 shows a sectional view and a schematic example of a shaft and a complementary axial passage from the prior art. Fig. 5 may form a circular arc with a different height from the surface of the axial passage compared to the fluid surface of Fig. 6. The fluid surface of Fig. 6 is annular and is located at an approximately constant height from the surface of a central passage. Fig. 7 shows a sectional view of the example of the present disclosure with the angles of the specific features. Fig. 8 shows a cross-sectional view of a schematic example of a shaft, an axial passage and fluid channels in accordance with the present disclosure. Fig. Figure 9 shows a sectional view of the shaft with an angle of the fluid channels relative to the axial passage. Fig. Figure 10 shows a composite sectional view of the fluid channels and their respective angles superimposed on the shaft. The schematic representations of the shaft in the Fig. 7-10 schematic configurations of the shaft in Fig. 4 be.

[0020] It should also be understood that the specific arrangements and systems illustrated in the accompanying drawings and described in the following description are exemplary embodiments of the inventive concepts defined herein. For purposes of explanation, the drawings will be described together. Thus, like elements may be referred to by like reference numerals and need not be repeated.

[0021] Fig. 1-2 and Fig. 5-10 show schematic representations of an example configuration with relative positioning of the various components. Fig. 3-4 show example configurations with approximate position. Fig. Figures 3-4 are shown approximately to scale, but other relative dimensions may be used. The term "about," unless otherwise noted, means plus or minus five percent of the range. The term "substantially" is understood herein to mean greater or less than a factor of two when comparing one component / feature to one or more other components / features.

[0022] Furthermore, Fig. 1-10 show example configurations with the relative arrangement of the various components. When these elements are in direct contact with one another or are directly coupled, they may be referred to as being in direct contact or directly coupled, respectively, in at least one example. Similarly, elements shown side by side or adjacent to one another may be adjacent to one another or adjacent to one another, in at least one example. For example, components that are in surface-to-surface contact with one another may be referred to as being in surface-to-surface contact. As another example, in at least one instance, elements that are separated from one another with only a space between them and that do not have any other components may be referred to as such.In yet another example, elements displayed above / below, on opposite sides, or to the left / right of each other may be referred to as such, relative to each other. Further, in at least one example, as illustrated in the figures, a topmost element or point of an element may be referred to as a "top" of the component, and a bottommost element or point of the element may be referred to as a "bottom" of the component. As used herein, the terms top / bottom, upper / lower, above / below may refer to a vertical axis of the figures and may be used to describe the positioning of elements of the figures relative to each other. Thus, in one example, elements displayed above other elements are arranged vertically above the other elements.As another example, the shapes of the elements depicted in the figures may be referred to as such (e.g., circular, straight, flat, curved, rounded, beveled, angled, or the like). Further, in at least one example, depicted elements that intersect each other may be referred to as intersecting elements or as intersecting elements. Furthermore, an element depicted inside or outside another element may be referred to as such. Additionally, the components may be described with respect to the reference axes included in the drawings.

[0023] Features described as axial may be approximately parallel to a datum axis unless otherwise specified. Features described as counter-axial may be approximately perpendicular to the datum axis unless otherwise specified. Features described as radial may circumferentially surround or extend outwardly from an axis, such as the datum axis, or a component or feature previously described as radial to a datum axis, unless otherwise specified.

[0024] Features described as longitudinal can be approximately parallel to a long axis. A lateral axis can be perpendicular to a long axis and a vertical axis. Features described as lateral can be approximately parallel to the lateral axis. A vertical axis can be perpendicular to a transverse axis and a long axis. Features described as vertical can be approximately parallel to a vertical axis.

[0025] In Fig. 1, a vehicle 100 is illustrated that includes a powertrain 101 and a transmission 103. The vehicle 100 may have a front end 132 and a rear end 134 located on opposite sides of the vehicle 100. Objects, components, and features of the vehicle 100 referred to as being near the front may be closest to the front end 132 compared to the rear end 134. Objects, components, and features of the vehicle 100 referred to as being near the rear may be closest to the rear end 134 compared to the front end 132. The powertrain 101 includes a prime mover 106 and a transmission 108. The prime mover 106 may be, for example, an internal combustion engine (ICE) or an electric motor and operates to provide rotational power to the transmission 108. The transmission 108 may be any type of transmission, such asa manual transmission, an automatic transmission, or a continuously variable transmission. Furthermore, the transmission 108 can be a gear box, an axle, or a transaxle. The transmission can be a forced lubrication transmission system in which the lubricant for lubrication is pumped under pressure and applied, for example, as a spray, mist, or droplet. The transmission 108 receives the torque generated by the prime mover 106 as input and outputs the torque to the gear train 103 according to a selected gear ratio or setting. Furthermore, there can be other drives in the vehicle besides the prime mover 106. If the prime mover 106 is an internal combustion engine, there can be at least one second drive with an input to the transmission 108, wherein the second drive can be an electric machine such as an electric motor.In one example, vehicle 100 may be a hybrid vehicle if there are one or more second drives in addition to prime mover 106, with multiple torque inputs to transmission 108. Vehicle 100 may have a longitudinal axis 130. Driveline 101 and transmission line 103 may have a length parallel to longitudinal axis 130.

[0026] The prime mover 106 may be powered by energy from an energy storage device 105. In one example, the energy storage device 105 is a battery configured to store electrical energy. An inverter 107 may be disposed between the energy storage device 105 and the prime mover 106 and configured to convert direct current (DC) to alternating current (AC). The inverter 107 may include a variety of components and circuits with thermal requirements that affect the efficiency of the inverter.

[0027] The vehicle 100 may be a light, medium, or heavy-duty vehicle. The vehicle 100 may be an on-road vehicle, a passenger vehicle, including a car, a commercial vehicle that is an on-road vehicle, a semi-trailer truck, and / or a sports car. The vehicle may be an off-road vehicle or a vehicle that can be used both on-road and off-road, such as a construction vehicle, an agricultural vehicle, a sport utility vehicle, and / or a commercial vehicle that is an off-road vehicle. In one embodiment, the vehicle 100 may be a wheeled vehicle, such as an automobile. Additionally or alternatively, the vehicle 100 and / or one or more of its components, such as components of the powertrain 101 and / or the drivetrain 103, may be used in industrial, locomotive, military, agricultural, and / or aerospace applications.Additionally or alternatively, vehicle 100 may be an aircraft, a boat, or other vehicle system that utilizes lubricants. In one example, vehicle 100 is an all-electric vehicle or a vehicle with an all-electric mode of operation, such as a plug-in hybrid vehicle. Thus, prime mover 106 may be an electric machine. In one example, prime mover 106 may be an electric motor / generator.

[0028] In some examples, such as Fig. 1, the geartrain 103 includes a first axle assembly 102 and a second axle assembly 112. The first axle assembly 102 may be configured to drive a first set of wheels 104, and the second axle assembly 112 may be configured to drive a second set of wheels 114. In one example, the first axle assembly 102 is located near a front end of the vehicle 100 and therefore includes a front axle, and the second axle assembly 112 is located near a rear end of the vehicle 100 and therefore includes a rear axle. The geartrain 103 is shown in an all-wheel drive configuration, although other configurations are possible. The geartrain 103 may include, for example, rear-wheel drive or all-wheel drive. Additionally, the geartrain 103 may include one or more tandem axle assemblies.Thus, the transmission train 103 may have other configurations without departing from the scope of this disclosure, and the configurations shown in . Fig. 1 is for illustrative purposes and is not limiting. In addition, the vehicle 100 may include additional wheels that are not coupled to the transmission 103.

[0029] In some configurations, such as Fig. 1, the powertrain 103 includes a transfer case 110 configured to receive the rotary power output from the transmission 108. A first input shaft 113 is drivingly connected to a first output 111 of the transfer case 110, while a second input shaft 122 is drivingly coupled to a second output 121 of the transfer case 110. The first input shaft 113 (e.g., a front input shaft) transmits the rotary power from the transfer case 110 to a first differential 116 of the first axle assembly 102 to drive the first set of wheels 104, while the second input shaft 122 (e.g., a rear input shaft) transmits the rotary power from the transfer case 110 to a second differential 126 of the second axle assembly 112 to drive the second set of wheels 114.For example, the first differential 116 is drivingly coupled to a first set of axleshafts 118 connected to the first set of wheels 104, and the second differential 126 is drivingly coupled to a second set of axleshafts 128 coupled to the second set of wheels 114. It should be understood that the first set of axleshafts 118 and the second set of axleshafts 128 may be disposed within a housing. The first drive shaft 113 and the second drive shaft 122 may be arranged to extend parallel to the longitudinal axis 130. In one example configuration of the vehicle 100, the second drive shaft 122 may be centered about the longitudinal axis 130.

[0030] The first differential 116 may provide some front-wheel drive to the vehicle 100 as part of the rotational power transmitted via the first driveshaft 113. Similarly, the second differential 126 may provide rear-wheel drive to the vehicle 100 as part of the rotational power transmitted via the second driveshaft 122. The first differential 116 and the second differential 126 may provide front-wheel drive and rear-wheel drive, respectively, as part of an all-wheel drive mode for the vehicle 100.

[0031] The adjustment of the transmission 103 between the various modes, as well as the control of operation within each mode, may be based on a vehicle control system 154, including a controller 156. The controller 156 may be a microcomputer, including components such as a microprocessor unit, input / output ports, an electronic storage medium for executable programs and calibration values, e.g., a read-only memory chip, random access memory, diagnostic memory, and a data bus. The storage medium may be programmed with computer-readable data representing instructions executable by a processor to perform the methods described below, as well as other variations that are expected but not explicitly listed. In one example, the controller 156 may be a powertrain control module (PCM).

[0032] The controller 156 may receive various signals from sensors 158 coupled to various areas of the vehicle 100. The sensors 158 may include, for example, sensors on the prime mover 106 or another prime mover for measuring the speed and temperature of the prime mover, a pedal position sensor for detecting the actuation of a pedal actuated by the driver, e.g., an accelerator or brake pedal, a lever position sensor for detecting the adjustment of a lever, e.g., a brake lever, speed sensors on the first and second wheel sets 104, 114, etc. After receiving the signals from the various sensors 158 Fig. 1, the controller 156 processes the received signals and deploys various actuators 160 of the vehicle 100 to adjust the operation of the transmission based on the received signals and the instructions stored in the memory of the controller 156. For example, the controller 156 may receive an indication of brake pedal application, signaling a desire for a lower vehicle speed. Vehicle braking may be directly proportional to the position of the accelerator pedal, e.g., the degree of application. Another example is that the controller 156 may receive an indication of accelerator pedal application, signaling a desire for a higher vehicle speed. Vehicle acceleration may be directly proportional to the accelerator pedal position, e.g., the degree of application. In response, the controller 156 may command actions such as shifting gears of the transmission 108.Alternatively, the gears of the transmission 108 can also be shifted manually, e.g., if the transmission 108 is a manual transmission.

[0033] In some examples, the vehicle 100 may additionally or alternatively be a hybrid vehicle that includes both an engine and an electric machine, each configured to power one or more of the first axle assembly 102 and the second axle assembly 112. For example, one or both of the first axle assembly 102 and the second axle assembly 112 may be powered by power from the electric machine in a first operating mode in which the electric machine is not operating to provide power (e.g., a motor-only mode), by power from the electric machine in a second operating mode in which the engine is not operating to provide power (e.g., a pure electric mode), and by power from both the engine and the electric machine in a third operating mode (e.g., an electric-assist mode).In another example, one or both of the first axle assembly 102 and the second axle assembly 112 may be an electric axle assembly configured to be driven by an integrated electric machine.

[0034] In some embodiments, the transmission 108 may additionally or alternatively be a first transmission that further includes a second transmission disposed on the second set of axle shafts 128. The transmission 108 may be a gear box. Alternatively, the transmission 108 may also be an axle transmission or a transaxle transmission.

[0035] In Fig. 2 is a schematic representation 200 of the Fig. 1. The transmission 108 includes a volume that may be referred to as a gear box 203. In one example configuration, the transmission housing 203 may house a gear assembly 202. The transmission housing 203 may house portions of a plurality of shafts that support rotating elements of the transmission assembly 202. The transmission 108 may be a multi-stage reduction gear, where the gear assembly 202 functions as a system of multiple reduction sets. Alternatively, the transmission 108 may be another form of multi-stage transmission, such as a multi-stage axle drive or a multi-stage transaxle, where the transmission functions as a system of multiple reduction sets. The gear assembly 202 may be formed of at least two reduction sets, which can decrease the speed (e.g., revolutions per minute (RPM)) and increase the torque.The reduction sets may be referred to herein as stages. The stages may be gear sets. However, the stages may also be another type of reduction gear or other power transmission gear, such as a belt and pulley system. There may be at least one first stage 204. The first stage 204 may include gears, e.g., fixed gears. It should be understood that the gear assembly 202 may also be used for another gear system that is not a gearbox, for example, in a gear box that is not a transmission.

[0036] For example, the housing 203 of the gear assembly 202 may include at least two shafts. The two shafts include a first shaft 208 and a second shaft 210. The first stage 204 may be supported by the first shaft 208 and the second shaft 210. The first shaft 208 may be an input to the first stage 204. The second shaft 210 may be an output for the first stage 204. The first stage 204 may drivingly connect the first shaft 208 to the second shaft 210. The first shaft 208 may be centered about a first axis 216. The second shaft 210 may be centered about a second axis 218. The first axis 216 and the second axis 218 may be parallel to each other. The first stage 204 may traverse the first axis 216 to the second axis 218.

[0037] The first and second shafts 208, 210 may be hollow. The first shaft 208 may have at least one first passage 211. The second shaft 210 may have at least one second passage 213. The first passage 211 may have a length parallel to the first axis 216 when the first shaft 208 is parallel to and / or centered about the first axis 216. The second passage 213 may have a length parallel to the second axis 218 when the second shaft 210 is parallel to and / or centered about the second axis 218. The first and second axes 216, 218 may be horizontal and perpendicular to a vertical axis and the direction of gravity. A plurality of additional passages, channels, and openings of the first shaft 208 may fluidly couple the first passage 211. A plurality of additional passages, channels, and openings of the second shaft 210 may fluidically couple the second passage 213.

[0038] The first shaft 208 may drivingly couple a first input shaft to the gear assembly 202. The first shaft is an input that transmits rotational energy to the gear assembly 202. The first shaft may also be a first input to the transmission 108. For example, the first input shaft of the gear assembly 202 may be an output shaft 214 of the prime mover 106. The output shaft 214 may be referred to herein as a prime mover output shaft 214. In this example, the prime mover 106 may be a first electric machine. Shafts and other components that are drivingly coupled and not directly contacting are represented by dashed lines 220.

[0039] However, other gear box configurations are possible. For example, the first input shaft may be a shaft drivingly connected to the output shaft 214 or the output of another gear reduction set. In other configurations, there may be additional stages that selectively and drivingly couple the first shaft 208 to the second shaft 210. For example, there may be a second stage separate from the first stage 204 that drivingly and selectively couples the first shaft 208 to the second shaft 210. The second stage may have a different ratio and effective diameter than the first stage 204. In this or other examples, there may be a third stage separate from the second stage and the first stage 204 that can drivingly and selectively couple the first shaft 208 to the second shaft 210.The third stage may have a different ratio and effective diameter than the second stage and the first stage 204. In these or other examples, there may be a fourth stage separate from the third stage, the second stage, and the first stage 204, which may drivingly and selectively couple the first shaft 208 to the second shaft 210. The fourth stage may have a different ratio and effective diameter than the third stage, the second stage, and the first stage 204. In these or other examples, there may be an n-stage separate from an n-1 stage, the fourth stage, the third stage, the second stage, and the first stage 204. The n-stage may have a different ratio and effective diameter than the n-1 stage, the fourth stage, the third stage, the second stage, and the first stage 204.

[0040] The transmission 108 may be a configuration with at least one gear, where the transmission 108 outputs rotational speed to an output shaft of the transmission. The second shaft 210 may be drivingly coupled to at least a first output shaft. For example, the first output shaft may be a drive shaft, such as the second drive shaft 122. The rotational energy of the first shaft 208 may be transferred to the second shaft 210 and an output shaft, such as the second drive shaft 122, when it is selectively and drivingly coupled via the first stage 204. When it is not selectively and drivingly coupled to the second shaft 210 via the first stage 204, the first shaft 208 may be driven and not output to another shaft. However, other configurations of the gear assembly 202 and the housing 203 are possible.Alternatively, the first output shaft may be a shaft connected to a drive shaft, such as the second drive shaft 122, or to another reduction gear. As another example, the transmission 108 may be a two-speed transmission that allows for a second gear. In this example, the first shaft 208 and the second shaft 210 may result in different output shafts, with the first shaft 208 leading to a second output shaft separate from the first output shaft, such as the first drive shaft 113 of FIG. Fig. 1, and may be drivingly connected thereto. In this or other examples, the first shaft 208 and / or the second shaft 210 may also be output shafts. Furthermore, in this or other examples, the first shaft 208 and the second shaft 210 may be drivingly and selectively coupled via one or more additional sets of the first stage 204, e.g., a second stage. The additional set or sets may have different gear ratios than the first stage 204 such that a different speed is delivered to the second shaft 210 and the first output shaft when the first shaft 208 is selectively and drivingly coupled to the second shaft 210 via the second stage or a stage other than the first stage 204.

[0041] It should be understood that the number of shafts, the number of sets, and the number of gears output by the transmission 108 may be unlimited. In other examples, the transmission unit 202 may include more than two shafts. In these examples, the additional shafts of the transmission assembly 202 may be hollow, such as the first and second shafts 208, 210, with each shaft having a passageway extending between the opposite ends of the respective shaft, such as the first and second passageways 211, 213. Each additional shaft may be drivingly and selectively coupled to either the first shaft 208 or the second shaft 210. In other examples, the transmission 108 may have additional sets from the first stage 204, where the additional sets may drivingly and selectively couple the first shaft 208 to the second shaft 210, each of the sets having a different gear ratio enabling a different speed.For example, an alternative configuration of the transmission assembly 202 may include two sets, such as gear sets, with different gear ratios that can driveably and selectively couple the first shaft 208 to the second shaft 210. For example, an alternative configuration of the transmission assembly 202 may include three sets with different gear ratios that can driveably and selectively couple the first shaft 208 to the second shaft 210. Another example is an alternative configuration of the transmission assembly 202 with four sets of different gear ratios that can driveably and selectively couple the first shaft 208 to the second shaft 210. Another example is an alternative configuration of the transmission assembly 202 with five sets of different gear ratios that can driveably and selectively couple the first shaft 208 to the second shaft 210.Another example is an alternative configuration of the transmission assembly 202 having six sets of different gear ratios that can driveably and selectively couple the first shaft 208 to the second shaft 210. Another example is an alternative configuration of the transmission assembly 202 having seven sets of different gear ratios that can driveably and selectively couple the first shaft 208 to the second shaft 210. Another example is an alternative configuration of the transmission assembly 202 having eight sets of different gear ratios that can driveably and selectively couple the first shaft 208 to the second shaft 210. In such examples, each of the above configurations can provide a number of n selectable gears based on the number of sets of gear ratios of the transmission.

[0042] In other examples, alternative configurations of the transmission 108 and the transmission assembly 202 with more than two shafts and / or additional stages may enable more than two speeds at the output. For example, in an alternative configuration, the transmission 108 may be an eight-speed transmission and the assembly 202 may be an eight-speed assembly enabling eight speeds, such as the assembly 302 in Fig. 3. Another example: The transmission 108 and the transmission assembly 202 may enable three gears. Another example: In an alternative configuration, the transmission 108 and the transmission assembly 202 may enable four gears. Another example: In an alternative configuration, the transmission 108 and the transmission assembly 202 may enable five gears. Another example: In an alternative configuration, the transmission 108 and the transmission assembly 202 may enable six gears. Another example: In an alternative configuration, the transmission 108 and the transmission assembly 202 may enable seven gears. Another example: In an alternative configuration, the transmission 108 and the transmission assembly 202 may enable nine gears. Another example: In an alternative configuration, the transmission 108 and the transmission assembly 202 may enable n gears.

[0043] An actuator 222 may selectively and drivingly couple the first stage 204 to the first shaft 208. The actuator 222 may be slidably coupled to a shift rod 224, wherein the actuator 222 may translate the shift rod 224 in one direction. The actuator 222 may be attached to the transmission 108 or to a component of the transmission 108, e.g., to the walls and surfaces of the housing 203. For example, the actuator may be attached by a variety of fasteners, such as screws. In another example, the actuator may be fitted into a recess or cavity in the surfaces and material of the transmission 108. The actuator 222 may be one of the actuators 160 of Fig. 1 act.

[0044] The actuator 222 can translate the shift rod 224 along the third axis 226. When translated in a first direction, e.g., toward the front end 132, the shift rod 224 can drivingly couple the first stage 204 to the first shaft 208. When translated in a second direction, e.g., toward the rear end 134, the shift rod can decouple the first stage 204 from the first shaft 208. The shift rod 224 can be guided by the housing of the transmission 108 and / or the housing 203. In other examples, the shift rod 224 and another stage (e.g., a set / gear set) can be drivingly connected to the first shaft 208, where the other stage is different than the first stage 204. In these examples, the shift rod 224 is translated in a direction different from the first direction, e.g., B. a further distance in the second direction.

[0045] The housing 203 may include a sump 228 in which a working fluid 230 is collected. The working fluid 230 may be a lubricant, such as oil. The sump 228 may be located below the gear assembly 202 so that the working fluid 230 can be returned to the sump 228 by gravity 260. After lubricating the first-stage gears 204, the working fluid 230 may be returned to the sump 228 by splashing and dripping.

[0046] The first stage 204 may include at least a first gear 232 and a second gear 234. The first gear 232 may be rotatably connected to the first shaft 208, and the second gear 234 may be rotatably connected to the second shaft 210. When the first gear 232 and the second gear 234 are rotatably connected to a shaft, they may rotate with their respective shafts. The first gear 232 or the second gear 234 may be physically connected to the first shaft 208 or the second shaft 210, respectively. At least one of the first gear 232 or the second gear 234 may be supported by bearings, races, and / or bushings so that the first gear 232 and / or the second gear 234 can rotate freely from the first shaft 208 or the second shaft 210, respectively. The first gear 232 may, for example, be supported by at least one first bearing 252.The first bearing 252 may be radially disposed between the first gear 232 and the first shaft 208 such that the first bearing 252 can rotate freely from the first shaft 208. The first gear 232 may be selectively and rotatably coupled to the first shaft 208 via the selective coupling of a first engagement component 240 and a first engagement component 244. The first gear 232 may rotate freely about the first shaft 208 when the first engagement element 240 and the first engagement component 244 are not selectively coupled.

[0047] The first shaft 208 may be supported by a plurality of second bearings 254, and the second shaft 210 may be journaled by a plurality of third bearings 256. The second bearings 254 and the third bearings 256 may be arranged radially around the first and second shafts 208, 210, respectively. The second bearings 254 may be arranged at opposite ends of the first shaft 208. Likewise, the third bearings 256 may be arranged around the second shaft 210 at opposite ends of the second shaft 210.

[0048] To select reduction sets, at least one arm and one mesh may be drivingly coupled to the shift rail 224. The number of arms and meshes drivingly coupled to the shift rail 224 may depend on the number of sets to be engaged. The first stage 204 may be drivingly coupled to the first shaft 208 via a first engaging component 240 and a first engaging component 244. The first engaging component 240 may be slidably connected to the shift rail 224 via a first arm 248. The shift rail 224 may translate the first engaging component 240 to engage and lock it with the first engaging component 244. The first engaging component 244 may be drivingly coupled to the first gear 232. The first engaging component 240 and the first engaging component 244 may form a clutch, such as a clutch. B. a synchronization clutch or a dog clutch.As part of a clutch, the first engaging component 240 can be a shift sleeve—for example, a shift ring. The first engagement element 240 can be a synchronizer if the first engagement element 240 and the first engagement component 244 are part of a synchronizer clutch. The first engagement component 240 can be a dog collar if the first engagement component 240 and the first engagement component 244 are part of a dog clutch.

[0049] The diagram 200 shows a first flow path 262 that the working fluid 230 can take from the sump 228. The flow of the working fluid 230 on the first flow path 262 can be driven by suction from a first pump 266. Likewise, the diagram 200 shows a second flow path 264 that the working fluid 230 can take from the sump 228. The flow of the working fluid 230 on the second flow path 264 can be driven by suction from a second pump 268. Both the first flow path 262 and the second flow path 264 are routed to at least the first and second shafts 208 and 210, respectively, via a forced lubrication system.

[0050] For example, components of the transmission 108 and the gear assembly 202 may be lubricated in one process via the first flow path 262. The first flow path 262 may begin at the sump 228. The working fluid 230 may be supplied to the first pump 266. The first pump 266 may increase the pressure of the working fluid 230 and direct it to the first shaft 208. A pressure gradient created by the first pump 266 may drive the working fluid 230 to the first shaft 208. The first shaft 208 may receive the working fluid 230 via an inlet into the first passage 211. The working fluid 230 in the first flow path 262 may flow through the first passage 211. The working fluid 230 may travel along the first flow path 262 to other fluid passages, openings, and other cavities of the first shaft 208 that are in fluid communication with the first passage 211.It should be understood that the working fluid 230 in the first shaft 208 on the first flow path 262 must not be driven by a pressure gradient or other means of forced lubrication. In the first passage 211 and other volumes of the first shaft 208, the working fluid may flow in an open channel. The working fluid on the first flow path 262 in the first shaft 208 may have a fluid-free surface and be driven under the action of an applied force, e.g., the forces from the rotation of the first shaft 208. By rotating the first shaft 208, working fluid may be driven radially outward from the first passage 211 and the first shaft 208 through a plurality of channels and openings. The lubricant driven radially outward by the first shaft 208 may lubricate the components arranged about the first shaft 208, such as the bearings. B. the first gear 232, the first engagement component 244 and the first engagement component 240.The lubricant in the first flow path 262 can also be used to lubricate other components of the first stage 204. For example, the lubricant in the first flow path 262 can be carried by the first gear 232 to lubricate the second gear 234 and the meshing between the first gear 232 and the second gear 234. The working fluid in the first flow path 262 can be returned to the sump 228 after lubricating components arranged around the first shaft 208 or a portion of the first stage 204. The working fluid 230 in the first flow path 262 can also exit the first passage 211 via an outlet and return to the sump 228.

[0051] Components of the transmission 108 and the gear assembly 202 may be lubricated in a second method via the second flow path 264. In one example, the second method may be similar to the first method, but the lubricant is driven and distributed via the second shaft 210 to other components of the transmission assembly 202. For example, the second flow path 264 may begin at the sump 228. The working fluid 230 may be drawn to the second pump 268 and directed to the second shaft 210. By rotating the second shaft 210, working fluid may be driven radially outward from the second passage 213 and the first shaft 208 through a plurality of channels to lubricate the components arranged about the second shaft 210.The working fluid on the second flow path 264 can be returned to the sump 228 after lubricating the components arranged around the second shaft 210 and can leave the second passage 213 via an outlet.

[0052] It should be understood that the arrangement of the first flow path 262 and the second flow path 264 may be unlimited. For example, the first flow path 262 may be extended by additional channels and openings of the first shaft 208. The additional channels and openings may extend radially from and be fluidly coupled to the first passage 211. For example, the additional channels and openings may lubricate additional components of gear sets, such as additional gear sets. Likewise, the additional channels and openings may lubricate additional components of clutches to selectively connect the first shaft 208 to additional stages. The additional channels and openings may lubricate additional engagement components separate from the first engagement component 240 and the first engagement component 244.The first flow path 262 and additional channels and openings of the first shaft 208 can also direct the lubricant to lubricate other support elements, such as additional bearings, races, and bushings. Similarly, the second flow path 264 can be expanded by additional channels and openings of the second shaft 210. The additional channels and openings can extend radially from and be fluidly connected to the second passage 213, thereby directing the lubricant to other elements, such as additional gears, bearings, races, and bushings.

[0053] Likewise, the additional channels and openings may lubricate additional components of clutches to selectively connect the first shaft 208 to additional stages. The additional channels and openings may lubricate additional engagement components separate from the first engagement component 240 and the first engagement component 244.

[0054] Likewise, the additional channels and openings may lubricate additional components of clutches, such as additional engagement and engagement components separate from the first engagement component 240 and the first engagement component 244.

[0055] In an alternative example, the first and second flow paths 262, 264 may be driven by a common pump. In this example, the first pump 266 may provide fluid to the first and second flow paths 262, 264, and the second pump 268 may not be included in the transmission 108.

[0056] The diagram 200 shows a single shift rod, shift rod 224, which can be translated by the actuator 222. The shift rod 224 can be physically connected to and actuate the first arm 248. However, it should be understood that the diagram 200 is not limiting and that there can be a plurality of shift rods and actuators. For example, there can be a plurality of shift rods translated by the actuator 222. In another example, there can be a plurality of shift rods, with each shift rod translated by an actuator specifically coupled to each shift rod. In these examples, each shift rod can be specific to an arm, such as the first arm 248, which can be used to actuate engagements, such as the first engagement member 240.

[0057] A set of reference axes 301 is provided for comparison between the views in Fig. 3-10. The reference axes 301 indicate a y-axis, an x-axis, and a z-axis. In one example, the z-axis may be parallel to a direction of gravity and the xy-plane may be parallel to a horizontal plane on which an assembly 302 may rest. In another example, the xy-plane may be parallel to a horizontal plane on which an assembly 402 and a shaft 412 may rest. In another example, the xy-plane may be parallel to a horizontal plane on which a first shaft 612 may rest. In another example, the xy-plane may be parallel to a horizontal plane on which a second shaft 662 may rest. When indicating direction, "positive" may refer to the arrow direction of the y-axis, x-axis, and z-axis, and "negative" may refer to the opposite arrow direction of the y-axis, x-axis, and z-axis.A circle may represent an axis of the reference axes 301 that is perpendicular to a view. A circle may represent an axis of the reference axes 301 that is perpendicular to a view. A filled circle may represent an arrow and an axis that is directed toward or positively toward a view. An open circle may represent an arrow and an axis that is directed away from or negatively toward a view.

[0058] Fig. 3 shows a first view 300 of the assembly 302. The first view 300 is a sectional view of the assembly 302, wherein the first view 300 may be taken on a plane parallel to a plane formed by the yz-axis. The assembly 302 has a first side 304 and a second side 306, wherein the first side 304 is opposite the second side 306. The assembly 302 includes a housing 303. The assembly 302 may include a plurality of shafts, for example, at least two shafts. The housing 303 may receive a plurality of rotating elements, including shafts and gears of the assembly 302. The at least two shafts include a first shaft 312 and a second shaft 314. The assembly 302 is a transmission and / or gear box that can provide and output multiple gears at the same input speed.The assembly 302 is an eight-speed assembly, and the two-shaft scheme may enable at least eight speeds to be output through the assembly.

[0059] The first shaft 312 may have a first passage 316 and the second shaft 314 may have a second passage 318. The first passage 316 may extend through a first material 315 of the first shaft 312. The second passage 318 may extend through a second material 317 of the second shaft 314. The first passage 316 and the second passage 318 may be made from their respective materials and shafts. For example, the first passage 316 and the second passage 318 may be drilled through the first material 315 and the second material 317, respectively, e.g., with a drill. The first passage 316 may be a blind passage, such as a pocket hole. The first passage 316 may extend from an opening at a first end and toward a second end of the first shaft 312. The first end of the first shaft 312 may be opposite the second end of the first shaft 312. Likewise, the second passage 318 can be a blind hole.The second passage 318 may extend from an opening at a first end to and toward a second end of the second shaft 314. The first end of the second shaft 314 may be opposite the second end of the second shaft 314. The first passage 316 and the second passage 318 may be fluid passages, such as lubrication lines, for their respective shafts. The first passage 316 and the second passage 318 may have lengths that are parallel to the centerlines of the first shaft 312 and the second shaft 314, respectively. The first passage 316 and the second passage 318 may be central passages for the first shaft 312 and the second shaft 314, respectively. As central passages, the first passage 316 and the second passage 318 may be arranged approximately radially about and coaxial with the centerline of the first shaft 312 and the second shaft 314, respectively.

[0060] The first passage 316 may run parallel to the first axis 308 when the first shaft 312 is centered about the first axis 308. The first passage 316 may be coaxial with the first axis 308 when the first shaft 312 is centered about the first axis 308, such that the first passage 316 is arranged approximately radially about the first axis 308. The second passage 318 may run parallel to the second axis when the second shaft 314 is centered about the second axis 310. A working fluid, e.g., a lubricant, may be transported through the first passage 316 and the second passage 318.

[0061] The first passage 316 can receive fluid through at least one first opening, such as a port 321. The opening 321 can be located closest to the second side 306 of the assembly 302. The opening 321 can selectively admit lubricant and other fluids into the first passage 316. When engaged or open, the opening 321 can connect a lubricant supply. In the disengaged / closed state, the opening 321 can seal the first passage 316 from the lubricant supply. The lubricant can enter the first passage 316 from the second side 306 via the opening 321. The lubricant can flow from the second side 306 to the first side 304 via a first flow path 320 when entering the first passage 316. The fluid can flow on a flow path through the second shaft 314 via the second passage 318.Similar to the first passage 316, the second passage 318 may also be supplied with fluid via a second opening. For example, the second flow path through the second passage 318 may be parallel and in the same direction as the first flow path 320, with the second flow path running from the second side 306 to the first side 304. As another example, a second flow path through the second passage 318 may be parallel and opposite to the direction of the first flow path 320, with the second flow path running from the first side 304 to the second side 306.

[0062] The first shaft 312 and / or the second shaft 314 may, for example, be integrated into a lubrication system of the assembly 302. As part of a method for lubricating the assembly 302, the lubrication system may transport lubricant to the openings of the first shaft 312 and / or the second shaft 314 via a method of forced lubrication, for example via pressure differentials, such as specific pressure differentials for the first shaft 312 and / or the second shaft 314. Each pressure differential may, as a first example, be created by a pump or by pressure head, e.g., by gravity. The lubricant may, for example, be transported to the port 321 via a pressure differential. Upon entering the first passage 316 or the second passage 318, the fluid may be in the open channel and not via pressure differentials or other forced lubrication methods, as described above with reference to Fig. 2 described.

[0063] The first shaft 312 may include a plurality of first channels extending radially outward from the first passage 316 to the outer surfaces of the first shaft 312. Each channel may include a first outer shaft opening and a first inner shaft opening, each radially disposed around, adjacent to, and flush with the outer surface and the inner surface of the first shaft 312. The inner surface of the first shaft may be the surface of the first passage 316. Lubricant may be expelled radially outward from the first passage 316 and the first shaft 312 via the first shaft channels through a plurality of inlets of the first flow path 320. Lubricant in the first flow path 320 that is not expelled via the first shaft channels through the inlets may exit the first passage 316 and the first shaft 312 via the second opening.

[0064] Likewise, the second shaft 314 may include a plurality of second shaft channels extending radially outward from the second passage 318 to the outer surfaces of the second shaft 314 and may be arranged similarly to the first shaft channels of the first shaft 312. Each channel may include a second outer shaft opening and a second inner shaft opening, each radially disposed around, adjacent to, and flush with the outer surface and the inner surface of the second shaft 314. The inner surface of the second shaft 314 may be the surface of the second passage 318. Lubricant may be expelled radially outward from the second passage 318 and the second shaft 314 via the second shaft channels via a plurality of second inlets. Lubricant not expelled from the second shaft channels through the second inlets may exit the second passage 318 and the second shaft 314 via the fourth opening.

[0065] The first shaft and second shaft passages can supply lubricant to a variety of consumers located around the first shaft 312 and the second shaft 314, respectively, including bearings, races, bushings, gears, gear meshes, clutches, and mechanical systems with moving / rotating / rolling / sliding components.

[0066] The assembly 302 may include one or more gear sets, such as gear sets, that may rotatably and drivingly couple the first shaft 312 to the second shaft 314. In one embodiment, the assembly may include eight sets, each set having a different gear ratio that allows for a different output speed when the first shaft 312 is drivingly coupled to the second shaft 314. The eight sets may include a first gear set 322, a second gear set 324, a third gear set 326, a fourth gear set 328, a fifth gear set 332, a sixth gear set 334, a seventh gear set 336, and an eighth gear set 338.Each gear set or any other set of the gear sets may be complementary to a clutch assembly, the complementary clutch assembly including a complementary clutch that selectively couples the set to either the first shaft 312 or the second shaft 314. When selectively coupled to the first shaft 312 or the second shaft 314 via a complementary clutch, a set may drivingly couple the first shaft 312 to the second shaft 314. The first gear set 322 and the second gear set 324 may be complementary to a first clutch assembly 342. The third gear set 326 and the fourth gear set 328 may be complementary to a second clutch assembly 344. The fifth gear set 332 and the sixth gear set 334 may be complementary to a third clutch assembly 346. The seventh gear set 336 and the eighth gear set 338 may be complementary to a fourth clutch arrangement 348.The first clutch assembly 342 can selectively connect the first gear set 322 or the second gear set 324 to the second shaft 314. The second clutch assembly 344 can selectively connect the third gear set 326 or the fourth gear set 328 to the second shaft 314. The third clutch assembly 346 can selectively connect the fifth gear set 332 or the sixth gear set 334 to the first shaft 312. The fourth clutch assembly 348 can selectively connect the seventh gear set 336 or the eighth gear set 338 to the first shaft 312. The first clutch assembly 342, the second clutch assembly 344, the third clutch assembly 346, and the fourth clutch assembly 348 can be synchronizers. The fifth gear set 332, the sixth gear set 334, the seventh gear set 336 and the eighth gear set 338 may include idler gears.

[0067] A variety of bearings, bearing assemblies, and bushings may support components and features of assembly 302. A bushing 350 may be inserted near opening 321 near second side 306 (e.g., the right side). Bushing 350 may fit within first passage 316. Bushing 350 may be disposed between first side 304 and opening 321 along first axis 308. Bushing 350 may be disposed opposite the end of opening 321 closest to second side 306. Bushing 350 may prevent backflow of fluid toward second side 306 through opening 321.

[0068] A first bearing assembly 352 may support and be positioned around the first shaft 312. The first bearing assembly 352 may be positioned around the first shaft 312, e.g., radially around it, and in surface contact with it. A second bearing assembly 354 may support and be positioned around the second shaft 314. The second bearing assembly 354 may be arranged around the second shaft 314, e.g., radially around it, and in surface contact with it. The first and second bearing assemblies 352, 354 may include an inner ring, an outer ring, and a plurality of bearings. For example, the first and second bearing assemblies 352, 354 may include ball bearings. Alternatively, the first and second bearing assemblies 352, 354 may also include needle bearings or roller bearings.

[0069] In addition to the bearings of the first and second bearing assemblies 352, 354, the assembly 302 may include a plurality of third bearings 356, a plurality of fourth bearings 358, a sixth bearing 362, a seventh bearing 364, a plurality of eighth bearings 366, a plurality of ninth bearings 368, a plurality of tenth bearings 370, a plurality of eleventh bearings 372, and a plurality of twelfth bearings 374. The third bearings 356, the fourth bearings 358, the fifth bearings 360, the eighth bearings 366, the ninth bearings 368, the tenth bearings 370, the eleventh bearings 372, and the twelfth bearings 374 may be roller bearings and / or needle bearings, such as needle bearings. The sixth bearings 362 and the seventh bearings 364 may be cylindrical roller bearings.

[0070] The third bearings 356, fourth bearing 358, fifth bearing 360, sixth bearing 362, and twelfth bearing 374 may be arranged radially around the second shaft 314. The third bearings 356 may be arranged radially between the second shaft 314 and a complementary gear of the first gear set 322. The third bearings 356 may support the complementary gear and allow it to rotate about the second shaft 314. The fourth bearings 358 may be arranged radially between the second shaft 314 and a complementary gear of the second gear set 324. The fourth bearings 358 may support the complementary gear and allow it to rotate about the second shaft 314. The fifth bearings 360 may be arranged radially between the second shaft 314 and a complementary gear of the third gear set 326. The fifth bearings 360 can support the complementary gear and allow it to rotate around the second shaft 314.The twelfth bearings 374 may be disposed radially between the second shaft 314 and a complementary gear of the fourth gear set 328. The twelfth bearings 374 may support the complementary gear and allow it to rotate about the second shaft 314.

[0071] The seventh bearing 364, the eighth bearing 366, the ninth bearing 368, the tenth bearing 370, and the eleventh bearing 372 may be arranged radially around the first shaft 312. The eighth bearing 366 may be arranged radially between the first shaft 312 and a complementary gear of the fifth gear set 332. The eighth bearing 366 may support the complementary gear and allow it to rotate about the first shaft 312. The ninth bearing 368 may be arranged radially between the first shaft 312 and a complementary gear of the sixth gear set 334. The ninth bearing 368 may support the complementary gear and allow it to rotate about the first shaft 312. The tenth bearing 370 may be arranged radially between the first shaft 312 and a complementary gear of the seventh gear set 336. The tenth bearings 370 can support the complementary gear and allow it to rotate around the first shaft 312.The eleventh bearings 372 may be radially disposed between the first shaft 312 and a complementary gear of the eighth gear set 338. The eleventh bearings 372 may support the complementary gear and allow it to rotate about the first shaft 312. The seventh bearing 364, the eighth bearing 366, the ninth bearing 368, the tenth bearing 370, and the eleventh bearing 372 may support and complement the idler gears of the respective gear sets.

[0072] The described first shaft channels for the first shaft 312 and the first passage 316 include a first channel 375, a second channel 376, a third channel 378, and a fourth channel 380. The first channel 375, the second channel 376, the third channel 378, and the fourth channel 380 can each be supply channels, such as supply openings, that can transport the lubricant to the consumers. The first channel 375 can supply the consumer with lubricant via a first branch 382 of the first flow path 320. The second channel 376 can supply the consumer with lubricant via a second branch 384 of the first flow path 320. The third channel 378 can supply the consumer with lubricant via a third branch 386 of the first flow path 320. The fourth channel 380 can supply the consumer with lubricant via a fourth branch 388 of the first flow path 320.The consumers supplied with lubricant via the first channel 375 may include the eighth bearing 366, the gears of the fifth gear set 332, and the third clutch unit 346. The consumers supplied with lubricant via the second channel 376 may include the ninth bearing 368, the gears of the sixth gear set 334, and the third clutch unit 346. The consumers supplied with lubricant via the third channel 378 may include the tenth bearing 370, the gears of the seventh gear set 336, and the fourth clutch unit 348. The consumers supplied with lubricant via the fourth channel 380 may include the eleventh bearing 372, the gears of the eighth gear set 338, and the fourth clutch unit 348. There may be a plurality of first channels 375, second channels 376, third channels 378 and fourth channels 380.

[0073] It should be understood that the first shaft 312 and the second shaft 314 may be prior art shafts; however, the other components of the assembly 302, including the eight gear sets, the gear ratios of the eight gear sets, the clutches, and the supporting components such as bearings, bearing assemblies, and bushings, are example embodiments of components and features of the present disclosure.

[0074] It should be understood that the configuration of the assembly 302 is not limited, and the structure may include a multi-shaft scheme with more than two shafts that may be rotationally coupled via the gear sets of the assembly. The assembly 302 may also be configured to output fewer than eight or more than eight speeds. Similar to the Fig. 2, alternative configurations of the assembly 302 may allow for two and up to n speeds.

[0075] Fig. 4 shows a second view 400 of the assembly 402. The second view 400 is a side view of an assembly 402. The second view 400 shows the assembly 402 in section and partially exploded so that a variety of internal features of the assembly 402 can be illustrated by section volumes, e.g., cuts.

[0076] The assembly 402 may have a first side 404 and a second side 406, with the first side 404 opposite the second side 406 with respect to the assembly 402. The assembly 402 may be centered about a first axis 408. A second axis 410 may be offset from the first axis 408. The second axis 410 is parallel to the first axis 408. A plane 409 may include the first axis 408 and the second axis 410. The first axis 408 may be parallel or coaxial with the first axis 408 of Fig. 3 or enclose them. The assembly 402 includes the shaft 412 and a gear 414, wherein the shaft 412 supports the gear 414. The gear 414 may be positioned around the shaft 412 such that the gear 414 may be positioned around and radially around the shaft 412. An outer side 415 may represent a volume, such as a packaging space, around the assembly 402. The outer side 415 may be located around the shaft 412 and the gear 414. The first side 404 and the second side 406 may be connected to the first side 304 and the second side 306 of Fig. 3 match.

[0077] The arrangement 402 may be a length 430. The length 430 may correspond to the length of the shaft 412. The cut volumes of the arrangement 402 include a first cut 416, a second cut 418, a third cut 420, and a fourth cut 421. The first cut 416, the second cut 418, and the third cut 420 are made on the shaft 412. The surfaces of the first cut 416, the second cut 418, and the third cut 420 are approximately perpendicular to the first axis 408 and the second axis 410. The fourth cut 421 may be made on the gear 414 and the shaft 412. A first passage 422 may be visible across the first cut 416, the second cut 418, and the third cut 420. The assembly 402 is shown translucent so that the first passage 422 through the shaft 412 and the gear 414 is visible and shown by dashed lines.The first passage 422 may extend through a material of the shaft 412 and parallel to the second axis 410. The first passage 422 may be positioned around the second axis 410, e.g., so that it is centered around the second axis 410. When centered around the second axis 410, the first passage 422 may be arranged radially or approximately radially around the second axis 410. The first passage 422 may be milled through the material of the shaft 412. For example, the first passage 422 may be drilled through the shaft 412, e.g., with a drill.

[0078] The shaft 412 may have a surface 424 on the second side 406. The surface 424 may be perpendicular to the first axis 408 and the second axis 410. The surface 424 may have an elliptical, e.g., circular, shape. The surface 424 may be centered on the first axis 408 such that a midpoint of the surface 424 and the first axis 408 intersect. The first passage 422 may have an opening 426, and the first passage 422 may be flush with and adjacent to the surface 424 via the first opening 426. The first opening 426 and the second opening 428 may be positioned on the surface 424 such that their respective perimeters are flush with and adjacent to the surface 424. The first passage 422 and the first opening 426 may be arranged about the second axis 410 such that the first passage 422 has a length parallel to the second axis 410.The first passage 422 and the first opening 426 may be centered around the second axis 410 so that they surround the second axis 410 and have a surface that is radially curved thereabout. The length of the first passage 422 may be parallel to the length 430. The second opening 428 may be arranged around the first axis 408, for example around the first axis 408. The second opening 428 need not be an opening to a fluid passage or a plurality of fluid passages, but may also serve another function, such as physically connecting the shaft 412 to another component. The second opening 428 may be centered around the first axis 408 so that it surrounds the first axis 408 and has a surface that is radially curved thereabout. The first passage 422 may receive a bushing, such as the bushing 350 in FIG. Fig. 3, which can prevent the backflow of the fluid accommodated in the passage 422 through the first opening 426.

[0079] The first passage 422 may be a fluid passage, e.g., a fluid channel, such as a lubrication line. The lubricant may enter the first passage 422 via the first opening 426. The first opening 426 may be an inlet for lubricant, and the second side 406 may be an inlet side for lubricant to be received by the assembly 402. The shaft 412 may, for example, be integrated into a lubrication system for a transmission. As part of a lubrication method, the lubrication system may convey the lubricant to the first opening 426 via a pressure differential, e.g., via a pressure differential created by a pump. Upon entering the first opening 426 and the first passage 422, the lubricant or other fluid may flow under open channel flow rather than via pressure differentials or other forced methods of lubrication, as discussed above with reference to Fig. 2-3 described.

[0080] The gear 414 may include a plurality of teeth 442. The teeth 442 may be mated to and complementary to at least one other gear, forming a gear set with the other gear. The gear 414 may be physically and rotatably connected to the shaft 412. Additionally or alternatively, the shaft 412 and the gear 414 may be part of a single, unitary component, and the assembly 402 may be a unitary component. When rotatably coupled to the shaft 412, the gear 414 may rotate / spin with the shaft 412. The gear 414 may include a surface 446 and a lip 450 disposed around the shaft 412, e.g., surrounding and enclosing the shaft 412 at its periphery. The teeth 442 may be journaled by the lip 450. The teeth 442 may physically couple the lip 450, for example, by bonding them together or by being machined or formed from the same material.The teeth 442 may be arranged radially around the lip 450 so as to enclose the lip 450. A valley 448 may be arranged axially and radially between the lip 450 and the surface 446 with respect to the first axis 408. The valley 448 may curve radially inward from the lip 450 toward the surface 446.

[0081] The diameter of the shaft 412 can be variable, so that the shaft 412 can include a plurality of lands with different diameters. In one embodiment, the shaft 412 can have a first land 452, a second land 454, a third land 456, a fourth land 460, and a fifth land 462 with different diameters. The first land 452, the second land 454, the third land 456, the fourth land 460, and the fifth land 462 can each have an outer surface, wherein the outer surfaces can be cylindrical and curve around the respective land of that surface. For example, the second land 454 can have a first outer surface 458 and the third land 456 can have a second outer surface 459. The first outer surface 458 and the second outer surface 459 can curve around the second land 454 and the third land 456, respectively, and have a cylindrical shape. The first web 452 may be located between the first side 404 and the second side 406.For example, the lubricant may be distributed in a radial direction relative to the first axis 408 from the inner passages of the shaft 412 to the outer surfaces of the shaft 412, including the first outer surface 458 and / or the second outer surface 459.

[0082] The shaft 412 may include a plurality of channels extending radially outward from the first axis 408 and in fluid communication with the first passage 422, including a first channel 474 and a second channel 476. The plurality of channels may include at least two axially spaced radial channels. When axially spaced, the channels are arranged to lie on different, non-parallel axes. The two axially spaced radial channels may extend radially to an axis, e.g., to extend radially from the first axis 408. The axially spaced radial channels may include the first channel 474 and the second channel 476. The first channel 474 may have a first centerline 478 (e.g., a first axis) about which the first channel is radially centered. The second channel 476 may have a second centerline 480 (e.g., a second axis) about which the first channel is radially centered.The first centerline 478 and the second centerline 480 may intersect the first axis 408, e.g., be perpendicular to the first axis 408. The first centerline 478 and the second centerline 480 may be at different angles to the plane 409. The first passage 422 may be in fluid communication with the outer surfaces of the shaft 412 through the first channel 474 and the second channel 476. For example, the first channel 474 may place the first passage 422 in fluid communication with the first outer surface 458. The second channel 476 may place the first passage 422 in fluid communication with the second outer surface 459. The first channel 474 and the second channel 476 may each have a first opening (e.g., an inner opening) flush with and adjacent to the first passage 422.Each first opening of the first channel 474 or the second channel 476 can fluidly connect the first channel 474 or the second channel 476 to the first passage 422. The first channel 474 and the second channel 476 can each have a second opening (e.g., an outer opening) flush with and adjacent to an outer surface complementary to the first channel 474 or the second channel 476. The second opening of the first channel 474 can be flush with and adjacent to the first outer surface 458. The second opening of the second channel 476 can be flush with and adjacent to the second outer surface 459. Each second opening of the first channel 474 or the second channel 476 can fluidly connect the first channel 474 or the second channel 476 to a complementary outer surface of the shaft 412. For example, the first channel 474 may fluidly connect the first passage 422 to a first outer surface of the second land 454.The fluid may exit the first passage 422 and be distributed via the first channel 474 to the first outer surface of the second land 454. In this or another example, the second channel 476 may fluidly connect the first passage 422 to a third outer surface of the third land 456. The fluid may exit the first passage 422 and be distributed via the second channel 476 to the third outer surface of the third land 456.

[0083] For example, the first channel 474 and / or the second channel 476 may be supply channels, such as supply openings, that can supply lubricant to consumers positioned around the shaft 412. The lubricant withdrawn from a fluid passage via supply openings can be directed to lubricate consumers connected to the first channel 474 and / or the second channel 476. The shaft 412 may have additional radial channels whose centerlines extend at a different angle to the plane 409 than the first channel 474 and the second channel 476. The additional channels may be supply channels. For example, there may be four supply channels with centerlines extending at different angles from the plane 409, the four supply channels comprising the first channel 474 and the second channel 476. Each of the four supply channels can direct the lubricant to a separate consumer, such asthe eighth camp 366, the ninth camp 368, the tenth camp 370 and the eleventh camp 372 in . Fig. 3.

[0084] The first channel 474 and / or the second channel 476 may, for example, be vent channels, such as vent openings. As vent channels, the first channel 474 and / or the second channel 476 may remove lubricant from the first passage 422. Lubricant removed from a fluid passage via vent openings may be directed to users, such as users connected to the first channel 474 and / or the second channel 476. Users may use lubricant without being lubricated as consumers of lubricant. A user may, for example, be a reservoir and / or a pump that can collect and direct lubricant to lubricate other components of the assembly 302 or the vehicle in which the assembly 302 is housed, such as the vehicle 100 of Fig. 1. Another example of a user is a fluid motor / generator that can recover power and energy from the fluid flow of excess lubricant. Another example of a user is a heat exchanger or a fluid passage with a lubricant flow to a heat exchanger.

[0085] Fig. 5 shows a third view 600 of the first shaft 612. The third view 600 is a sectional view of the first shaft 612 in a plane parallel to a plane formed by the x and z axes of the reference axes 301. Fig. 6 shows a fourth view 650 of the second shaft 662. The fourth view 650 is a sectional view of the second shaft 662 in a plane parallel to a plane formed by the x- and z-axes of the reference axes 301. The components and features in the Fig. 5 to 6 can be discussed together here.

[0086] The first wave 612 and the second wave 662 are waves of various embodiments. The first wave 612 is an example of a wave within the meaning of the present disclosure. The second wave 662 is an example of a prior art wave. The first wave 612 and the second wave 662 are illustrated schematically with relative scaling and positioning. The first wave 612 may be a schematic and simplified representation of waves of the present disclosure previously discussed, such as the wave 412 in Fig. 4.

[0087] The first shaft 612 may be centered about a first axis 608 such that the first shaft 612 may be positioned approximately radially about the first axis 608. The first axis 608 is a rotational axis for the first shaft 612. There is also a second axis 610 that is parallel to and offset from the first axis 608. The first axis 608 and the second axis 610 may be longitudinal axes for the first shaft 612. The first shaft 612 has an outer surface 614. The first shaft 612 and the outer surface 614 may have an approximately cylindrical shape. Additionally or alternatively, the first shaft 612 may have a variety of cylindrical shapes with a plurality of cylindrical outer surfaces including the outer surface 614.

[0088] The first shaft 612 may have a first passage 622. The second shaft 662 may have a second passage 672. The first passage 622 may be a volume that extends through the material 620 of the first shaft 612. The first passage 622 may have a surface 624 that separates the volume of the first passage 622 from the material 620. The surface 624 is an inner surface of the first shaft 612. The first passage 622 is offset from the center of the shaft and the first axis 608. The first passage 622 and the surface 624 may be arranged radially about the second axis 610, where the second axis 610 may be a central axis for the first passage 622. The first shaft 612 may not have a passage that encloses or surrounds the first axis 608. The first axis 608 may extend through the material 620 of the first shaft 612. The surface 624 may be an inner surface for the first passage 622 and the first shaft 612.The second passage 672 may be concentric with the second shaft 662, with the second passage 672 having a surface 674. Both the first passage 622 and the second passage 672 are arranged longitudinally.

[0089] The first passage 622 and the second passage 672 may receive a fluid 632 for their respective shafts 612, 662. The fluid 632 may be a lubricant, e.g., oil. Likewise, the first shaft 612 and the second shaft 662 may be rotated at an angular velocity (ω) 630, where ω 630 is the same for both the first shaft 612 and the second shaft 662. When the second shaft 662 is rotated at ω 630, the fluid 632 may have a height 686 extending away from the surface 674. The fluid 632 may be equidistant from the axis of the second shaft 662 when it is received by the second shaft 662, e.g., when the second shaft 662 rotates about ω 630. The height 686 may be approximately uniform between the surface 674 and the surface of the fluid 632. The fluid 632 may be equidistant from the first axis 608 (e.g., the axis of rotation) when it is received by the first shaft 612, e.g.when the first shaft 612 rotates about the ω 630. When the first shaft 612 is rotated with the ω 630, the fluid 632 may have a height 636 extending away from the surface 624. The height 636 may be a distance between the surface 624 of the first passage 622 and a fluid surface 634 created by the fluid 632. The fluid surface 634 may be a film or part of one. The fluid surface 634 may be a fluid-free surface on which the fluid moves under the action of the applied force field, e.g., gravity or a centripetal force of ω 630. Because it is equidistant from the first axis 608, the fluid surface 634 has the shape of an arc of a circle located on the circumference of a circle extending radially from the first axis.

[0090] Because the first passage 622 is offset from the first axis 608 and the fluid surface 634 is equidistant from the first axis 608, the height 636 is not uniform and varies at different points on the surface 624. The fluid surface 634 lies on a cylinder or circle, where the cylinder / circle represents an orbit around the first axis 608 (e.g., the axis of rotation of the first shaft 612). Centering the first passage 622 on an orbit around the axis of rotation as opposed to the axis of rotation can change the height of the fluid surface 634 and cause the fluid surface 634 to have the shape of an arc of a circle. The height 636 is smaller at positions on the surface 624 closer to the first axis 608. The height 636 is greater at positions on the surface 624 farther from the first axis 608. The height 636 may be greatest at a position on the surface 624 that is farthest from the first axis 608.

[0091] In Fig. 7 shows a fifth view 700 of the first shaft 612. The fifth view 700 is a cross-sectional view of the first shaft 612 in a plane parallel to a plane formed by the x and z axes of the reference axes 301. The fifth view 700 is a schematic view schematically illustrating the first shaft 612, other features, and dimensions.

[0092] The first shaft 612 may be divided by a first line 712—line AA. The first line 712 may be perpendicular to the first axis 608 and vertical to the z-axis of the reference axes 301. A cross-sectional view of the first shaft 612 may be taken along the first line 712, wherein the cross-sectional view may be a perspective view of a plane parallel to a plane formed on the y- and z-axes that includes the first line 712. The plane may be a plane 724. The plane 724 intersects the first shaft 612 longitudinally. The plane 724 may intersect the first shaft 612 along the first axis 608 and the second axis 610. The first shaft 612 may also include a cylinder / circle 720. The cylinder / circle 720 may be an orbit and axis of rotation about the first axis 608. The fluid surface 634 may meet and curve with the cylinder / circle 720.The circular arc shape of the fluid surface 634 may curve and touch the circumference of the cylinder / circle 720. The cylinder / circle 720 may have a radius 728.

[0093] An alpha angle (α) 722 may be marked on the first shaft 612. The alpha angle 722 is a first angle at which a channel, such as a vent or supply port, may be angled from the axis of the channel and a plane containing the axis of the shaft and the axis of the lubrication line, such as the first axis 608 of the first shaft 612 or the second axis 610 of the first passage 622, respectively. In this example, the alpha angle 722 lies between the plane 724 and an axis 726. The axis 726 may be separated from the plane 724, extended, and inclined by the alpha angle 722. The plane 724 includes the first axis 608 and the second axis 610. In one embodiment of the first shaft 612, the alpha angle 722 may be an angle of 30 degrees. The axis 726 may be the centerline of a channel, such as a vent or a supply port.

[0094] The first passage 622 may have a first diameter 730. A distance (e distance) 732 may separate the first axis 608 and the second axis 610. The first shaft 612 is operable to rotate at an ω 630 that is greater than a first threshold, the first threshold being a minimum angular velocity (ω min ). At ω min and larger angular velocities, a force can be generated by the first shaft 612 that drives the lubricant radially outward from the first axis 608, keeps the height 636 variable, and maintains the fluid surface 634 as a fluid-free surface. ω min can be represented by the following first equation (e.g. equation 1). ωmin=g / e ω min is the square root of the quotient of the gravitational acceleration acting on the wave and the e-distance 732, where g is the gravitational acceleration and e is the e-distance 732.

[0095] Fig. 7 shows additional details regarding the height 636 of the fluid 632. The height 636 may be a first height 744 at a first point on a first axis 742. Likewise, the height 636 may be a second height 754 at a second point on a second axis 752. The first axis 742 and the second axis 752 may be longitudinally extending and contacting the surface 624. The first axis 742 may be positioned on the surface 624 at a greatest distance from the first axis 608. The second axis 752 may be positioned on the surface 624 at a closest distance from the first axis 608. The height 636 may be a third height 756 from a third point, where the third point is a point on the surface 624 between the first axis 742 and the second axis 752. The first height 744 may be a maximum (e.g., a maximum height), where the height 636 is the greatest distance with respect to the distance between the fluid surface 634 and the surface 624. At ωminand larger angular velocities, the first height 744 may be a distance that prevents adhesion forces between the fluid 632 and the surface 624 from stopping the flow of the fluid 632 in a longitudinal direction or a radial direction with respect to the first shaft 612. The third height 756 may be a minimum (e.g., a minimum height), with the height 636 being the smallest distance relative to the distance between the fluid surface 634 and the surface 624. The third height 756 may be located at a point where the cylinder / circle 720 meets / intersects the surface 624. The third height 756 may extend from a point on the surface that is approximately the same distance from the first axis 608 as the radius 728. The third height 756 may be approximately zero or infinitesimal. However, it should be understood that the third height 756 need not be zero. The second height 754 can be zero (e.g.approximately zero) or infinitesimally small, such that no or only a vanishingly small amount of fluid 632 is present. The second axis 752 may be at a distance from the first axis 608 that is less than the radius 728. The height 636 may be zero or infinitesimally small at points on the surface 624, where the points are at a distance from the first axis 608 that is less than the radius 728. At points between the point on the surface 624 for the third height 756 and points on the second axis 752, the height 636 may be zero or vanishingly small. At the aforementioned locations on the surface 624, there may be approximately no or a vanishingly small amount of lubricant in contact with the surface 624.

[0096] The height 636 may decrease longitudinally from an inlet to the first passage 622 due to vents, supply ports, and other fluid passages connected to the first passage 622. For example, the first height 744 may decrease at points on the first axis 742 farther from an inlet to the first passage 622. Likewise, the cylinder / circle 720 may widen, and the third height 756 may be positioned at points on the surface 624 closer to the first axis 608.

[0097] Fig. 8 shows a sixth view 800 of the first shaft 612. The sixth view 800 is a sectional view, wherein the sixth view 800 is on the first line 712 of Fig. 7. The first shaft 612 has a first side 804 and a second side 806, with the first side 804 opposite the second side 806. The views of Fig. 5 and Fig. 7 were shown from the perspective of the first side 804. A second line (line BB) 812 and a third line (line CC) may subdivide the first shaft 612. A sectional view may be taken on the second line 812, wherein the sectional view may be taken on a plane that includes the second line 812 and is parallel to a plane formed by the x and z axes. A sectional view may be taken on the third line 814, wherein the sectional view may be taken on a plane that includes the third line 814 and is parallel to a plane formed by the x and z axes. The sectional view on the second line 812 is in Fig. 9. A composite view of sectional views may be taken on the second line 812 and the third line 814, wherein the composite view may be a composite of a first plane including the second line 812 and a second plane including the third line 814, which are parallel to a plane formed by the x- and z-axes. The composite view of sectional images may be Fig. 10 will be shown.

[0098] The first passage 622 may have an inlet 822. The inlet 822 may be an opening through which the first passage 622 can receive a working fluid, e.g., a lubricant. The first passage 622 may be a blind passage, e.g., a pocket hole. A counterbore 824 may be located at the end of the first passage 622 opposite the inlet 822. The inlet 822 may be located on the first side 804 of the first shaft 612, and the counterbore 824 may be closer to the second side 806 of the inlet 822.

[0099] The first passage 622 may be in fluid communication with a plurality of channels, each of which may have an opening that provides an outlet for the first passage 622. Openings that are outlets may place the first passage 622 and their respective channels in fluid communication with the surface 614 and the exterior 415. Some or all of the channels may extend radially outward with respect to the first axis 608. At least two channels (e.g., a pair of channels) may be in fluid communication with the first passage 622, including outlets. The first shaft 612 includes a first channel 832 and a second channel 834 that communicate with the first passage 622. The first channel 832 and the second channel 834 may each be vent channels, such as vent openings, for the first shaft 612 and the first passage 622.The first channel 832 and the second channel 834 may be fluidly connected and in fluid communication with the surface 614 and the outer side 415. The surface 614 and / or other outer surfaces of the first shaft 612 may be lubricated via the first channel 832 and the second channel 834. For example, there may be at least two supply channels, where the first channel 832 and the second channel 834 may be the two supply channels. Another example is that there are at least two vent channels, where the first channel 832 and the second channel 834 may be the two vent channels. Another example: The first shaft 612 may have at least one supply channel and at least one vent channel, where the first channel 832 or the second channel 834 may be either the supply channel or the vent channel.

[0100] It should be understood that in addition to the first channel 832 and the second channel 834, the first shaft 612 may have additional channels extending radially from the first axis 608 and fluidly coupling the first passage 622. Another example is a third channel fluidly connected to the first passage 622 and extending radially from the first axis 608. The third channel may be located longitudinally between the second channel 834 and the second side 806, for example, longitudinally between the second channel 834 and the counterbore 824. The third channel may be in fluid communication with the first passage 622 and place the first passage 622 in fluid communication with the surface 614 and / or other exterior surfaces of the first shaft 612 and the exterior side 415.In this or other examples, a channel may be present fluidically coupling the first passage 622 and extending radially from the first axis 608. The n-channel may extend longitudinally between the n. -1 -channel (e.g., a previous channel closest to the n-channel from the first side 804) and the second side 806, e.g., longitudinally between the n -1 -channel and the counterbore 824. The n-channel may be in fluid communication with the first passage 622 and may place the first passage 622 in fluid communication with the surface 614 and / or other exterior surfaces of the first shaft 612 and the exterior side 415.

[0101] The first channel 832 is centered about a first centerline 842 (e.g., a first axis) such that the first channel 832 extends radially about and curves around the first centerline 842. The second channel 834 is centered about a second centerline 844 (e.g., a second axis) such that the second channel 834 extends radially about and curves around the second centerline 844. A first plane, parallel to the x- and z-axes of the reference axes 301 and on the second line 812, may include the first centerline 842. A second plane, parallel to the x- and z-axes of the reference axes 301 and on the third line 814, may include the second centerline 844. The first centerline 842 and the second centerline 844 may extend and incline in radial directions from the first axis 608.

[0102] The first channel 832 has at least two openings, such as a first opening 852 and a third opening 862. The second channel 834 has at least two openings, such as a second opening 854 and a fourth opening 864. The first opening 852 and the second opening 854 may be flush with and adjacent to the surface 614. The third opening 862 and the fourth opening 864 may be flush with and adjacent to the surface 624. The third opening 862 may fluidically couple and communicate the first passage 622 with the first channel 832 such that fluid from the first passage 622 may pass into the first channel 832 via the third opening 862. The first channel 832 may fluidically couple and communicate the third opening 862 with the first opening 852.The first opening 852 can fluidly couple the first channel 832 and place it in fluid communication with the surface 614 so that lubricant or other fluid can exit the first channel 832 via the first opening 852 and coat the surface 614. The fourth opening 864 can fluidly couple the first passage 622 and place it in fluid communication with the second channel 834 so that fluid from the first passage 622 can enter the second channel via the fourth opening 864. The second channel 834 can fluidly couple the fourth opening 864 and place it in fluid communication with the second opening 854. The second opening 854 can place the second channel 834 in fluid communication with the surface 614 so that lubricant can exit the second channel 834 via the second opening 854 and coat the surface 614. The lubricant may also exit from the first and second channels 832, 834 and flow through the first opening 852 and 854, respectively.the second opening 854 to the outside 415. The first opening 852 and the second opening 854 may be outlets for their respective channels 832, 834 and for the first passage 622.

[0103] In other examples, other fluid channels, such as a third channel, a fourth channel, or an n-channel (n-channel), may have at least one opening in fluid communication with the first passage 622 and at least one other opening in fluid communication with the surface 614, another outer surface of the first shaft 612, and / or the outer surface 415. In these examples, the at least one opening of each of the other fluid channels may be flush with and adjacent to the surface 624 of the first passage 622. Likewise, the at least one other opening of each of the other fluid channels may be flush with and adjacent to the surface 614 or another outer surface of the first shaft 612.

[0104] Fig. 9 shows a seventh view 900 of the first shaft 612. The seventh view 900 is a sectional view, wherein the seventh view 900 is taken on the second line 812 of Fig. 8 is recorded.

[0105] The first shaft 612 may include a bushing 940. The bushing 940 may have a first diameter and a second diameter 942, wherein the first diameter is an outer diameter and the second diameter 942 is an inner diameter of the bushing 940. The first diameter of the bushing 940 may approximately correspond to the first diameter 730 of the first passage 622. Likewise, the bushing 940 has a thickness 944. The thickness may approximately correspond to the difference between the first diameter 730 and the second diameter 942. The bushing 940 may allow a return flow to the inlet 822 of Fig. 8. A schematic limitation of the dimensions of the bushing 940 is shown by dashed lines. The bushing 940 can be arranged longitudinally between the inlet 822 and the first channel 832 and therein toward the first side 804 of the first channel 832 in the seventh view 900.

[0106] The seventh view 900 shows that the first center line 842 is parallel to the axis 726 of Fig. 7 so that the first center line 842 is separated from the plane 724, extended through it and inclined by the alpha angle 722.

[0107] Fig. 10 shows an eighth view 1000 of the first shaft 612. The eighth view 1000 is a compilation of sectional views, wherein the eighth view 1000 includes the features and components of the seventh view 900, but wherein features and components are taken from a sectional view taken on the third line 814 of Fig. 8. The features and components in the sectional view on the third line 814 include the second channel 834, including the second opening 854 and the fourth opening 864.

[0108] The eighth view 1000 shows a beta angle (β), where beta angle 1022 is a second angle at which a channel, such as a vent or supply port, may be angled. Each beta angle 1022 is complementary to one or more channels that are further longitudinally spaced from inlet 822 compared to first channel 832. In this example, second channel 834 is complementary to beta angle 1022 such that second centerline 844 is separated, extended, and tilted from plane 724 across beta angle 1022. Beta angle 1022 has a different magnitude than alpha angle 722. Beta angle 1022 may be smaller than alpha angle 722. The relationship between the alpha angle 722 and the beta angle 1022 can be represented by a second equation (e.g., equation 2). β≤α2

[0109] The beta angle 1022 can be less than or equal to half the alpha angle 722. For example, if the alpha angle 722 is 30 degrees, the beta angle 1022 is at least 15 degrees. Another example: If the alpha angle 722 is 30 degrees, the beta angle 1022 can be less than 15 degrees, for example, 14 degrees. Or, as another example, if the alpha angle 722 is 60 degrees, the beta angle 1022 is at least 30 degrees. Another example: If the alpha angle 722 is 60 degrees, the beta angle 1022 is less than 30 degrees, for example, 29 degrees.

[0110] It should be understood that each additional channel (e.g., the n channels described) may have a centerline that extends at an angle of n to the plane 724 and is inclined. The angle n is half or less than half the angle of the last channel (e.g., an n -1-channel), the last channel being the channel closest to the additional channel and extending longitudinally between the inlet 822 of Fig. 8 and the additional channel. For example, the first shaft 612 may include a third channel adjacent to the first channel 832 and the second channel 834, the third channel being longitudinally farther from the inlet 822 than the second channel 834. The third channel may include and be centered around a third centerline (e.g., a third axis), the third centerline extending from the plane 724 at an angle of gamma (γ) and being inclined. The gamma angle may be a third angle. The gamma angle is a different quantity than the beta angle 1022 and the alpha angle 722. The mathematical relationship between the beta angle 1022 and the gamma angle is represented by a third equation (e.g., Equation 3) below. γ≤β2

[0111] The gamma angle may be less than or equal to half of the beta angle 1022. For example, the alpha angle 722 may be 60 degrees, the beta angle 1022 may be at least 30 degrees, and the gamma angle may be at least 15 degrees. In other examples, the alpha angle 722 may be 60 degrees, the beta angle 1022 may be 30 degrees, and the gamma angle may be less than 15 degrees, such as 14 degrees.

[0112] The third channel can, for example, be a vent channel, e.g., a third vent channel. As a third vent channel, the third channel can be in fluid communication with a user and supply the user with lubricant. Another example: The third channel can be a supply channel, e.g., a third supply channel, where the third channel can supply a user with lubricant.

[0113] The alpha angle 722, the beta angle 1022, and the gamma angle can prevent the maximum volume flow of lubricant from entering the first channel 832, the second channel 834, and the third channel, respectively. The lubricant housed in and flowing through the first passage 622 can have a fluid surface, such as a fluid-free surface, that has a circular curvature and is equidistant from the axis of rotation, such as the fluid surface 634 in Fig. 5. The circular curvature may have the circumference of a cylinder or a circle centered around the first axis 608. Due to the equidistance to the axis of rotation and the curvature, the fluid attains a variable height from the surface 624, e.g., height 636. Due to the curvature of the fluid surface and the variable height, the fluid below the lubricant may be lower than the full cross-sectional area of the openings to each of the first channels 832, the second channel 834, and the third channel, where portions of the diameters of the openings to the first channel 832, the second channel 834, and the third channel may be within the diameter of the curvature of the fluid surface. A portion of the surface 624 or a feature in fluid communication with the first passage 622 and within the radius of curvature of the fluid surface may have almost no or a negligible amount of lubricant.In this example, the lubricant may not be received at all points in the cross-sectional area of the third opening 862. Likewise, the lubricant may not be received at all points in the cross-sectional area of the fourth opening 864. Furthermore, the lubricant may not be received at all points in the cross-sectional area of an opening of the third channel that is in fluid communication with the first passage 622. The maximum fluid flow through an opening may depend on how much lubricant reaches a cross-sectional area of the opening, where the cross-sectional area of the opening depends on the diameter of the opening. In this case, only a portion of the cross-sectional areas of the first channel 832, the second channel 834, or the third channel may receive a fluid flow, and the fluid flow is reduced compared to the maximum fluid flow rate of the respective channel.Likewise, as the fluid is drained, the fluid height may decrease and the radius of curvature of the fluid surface may increase. The radius of curvature of the fluid surface may increase so that the openings to the first channel 832, the second channel 834, and / or the third channel are completely within the radius. Openings located within the radius of curvature of the fluid surface must not receive lubricant or other fluid accommodated via the first passage 622. Reducing the fluid flow through the first channel 832, the second channel 834, and / or the third channel may reduce the excess lubricant flow, where the excess lubricant flow may be the amount of volumetric flow greater than a desired threshold volumetric flow to supply a load. Reducing the excess lubricant flow may reduce power losses, e.g.,by performance losses due to lubricant splashes and by the loss of lubricant that can be used by users or other consumers.

[0114] For example, the first shaft 612 may have four supply channels. The four supply channels may include axially spaced channels of the first shaft 612, such as the first channel 832, the second channel 834, the third channel, and a fourth channel. The fourth supply channel may be located after the third supply channel, with the fourth channel being longitudinally farther from the inlet 822 than the third supply channel. The fourth channel may have and be centered around a fourth centerline (e.g., a fourth axis), the fourth centerline being inclined at a fourth angle to plane 724. The fourth angle is half or less than half the gamma angle from plane 724. Each of the four supply channels may direct the lubricant to a different consumer than the consumers that may be supplied via the first channel 832, the second channel 834, or the third channel.At least four consumers can be supplied via the four supply channels, such as the eighth warehouse 366, the ninth warehouse 368, the tenth warehouse 370 and the eleventh warehouse 372 of . Fig. 3.

[0115] In other examples, the first shaft 612 includes one or more supply channels capable of supplying lubricant to the consumers and fluidly connected to the first passage 622. In these examples, one or more supply channels may be coupled to the first passage 622, with the fluid coupling occurring longitudinally between the fluid coupling of vent channels, for example, longitudinally between the first channel 832 and the second channel 834 and / or longitudinally between the second channel 834 and the third channel.

[0116] The first channel 832 may have a first counterbore 1042. The second channel 834 may have a second counterbore 1044. The first and second counterbores 1042, 1044 may be located above the first passage 622 and the second axis 610. The first and second counterbores 1042, 1044 may be located at the radially innermost positions of the first channel 832 and the second channel 834, respectively. The first counterbore 1042 may be located radially between the third opening 862 and the first axis 608. The second counterbore 1044 may be located radially between the fourth opening 864 and the first axis 608.

[0117] The first channel 832 may have a first length 1072, and the second channel 834 may have a second length 1074. The first length 1072 may be a distance extending from the first opening 852 to the approximate point where the first counterbore 1042 ends. The second length 1074 may be a distance extending from the second opening 854 to the approximate point where the second counterbore 1044 ends. The first length 1072 and the second length 1074 may extend radially inward from the surface 614.

[0118] The first channel 832 may have a third diameter 1082, and the second channel 834 may have a fourth diameter 1084. The third diameter 1082 and the fourth diameter 1084 may be approximately equally spaced. For example, the third diameter 1082 may be between 5 mm and 8 mm. Likewise, in this or another example, the fourth diameter 1084 may be between 5 mm and 8 mm.

[0119] A force (e.g., a centripetal force) may be generated by the first shaft 612 to drive lubricant radially outward from the first axis 608, keep the height 636 variable, and maintain the fluid surface 634 as a fluid-free surface.

[0120] The first shaft 612 may be integrated into a lubrication system for a transmission. Within a lubrication method that includes the lubrication methods using the first and second shafts 208, 210 of Fig. 2 and wave 412 of Fig. 4, the first shaft 612 may be provided with ω in addition to the lubrication via the first shaft 612. min and higher angular speeds. The lubrication system can transport lubricant, such as fluid 632, to an inlet of the first shaft 612, such as the inlet 822 of Fig. 8. The lubrication system may deliver the lubricant to the inlet via a forced lubrication method, such as a pressure differential. The pressure differential may be provided by a pump, such as the first pump 266 or the second pump 268 of Fig. 2. The lubricant can enter a passage of the shaft via the inlet, e.g., the first passage 622 in Fig. 5. Upon entering the passage, the lubricant may be driven by open channel flow rather than by pressure differentials or other forced lubrication methods, and therein, the lubricant may be driven by open channel flow under the action of applied forces and have a fluid-free surface. The applied forces may also include the force resulting from the rotation of the first shaft 612. At ω minand larger angular velocities, the rotational force on the first shaft 612 may force the fluid to have a variable height (e.g., a variable height), such as the height 636 in Fig. 5. The height of the fluid may be radial relative to a rotational axis of the first shaft 612, such as the first axis 608. The height of the fluid may be relative to and a distance between a surface of the passage and a fluid surface of the fluid, such as the surface 624 or the fluid surface 634, respectively. The fluid surface may be equidistant from the axis of the first shaft 612. The fluid surface may have a circular curvature that follows the circumference of a cylinder or a circle arranged radially around the rotational axis. The variable height may vary between the first height and the second height at a first point on a first axis or at a second point on a second axis, respectively, where the first axis and the second axis lie on the surface of the passage. The first height may be a maximum height, such as the first height 744 in Fig. 7. The second height can be a minimum height, such as the third height 756 in Fig. 7. The forces caused by the rotation of the first shaft 612 with ω min and higher angular velocities can act in a radial direction relative to the axis of rotation and push the fluid radially outward via channels connected to the passage.

[0121] In a first example of the lubrication method, there may be at least two channels, each connected to the passage via an opening. Each passage may fluidly connect a corresponding opening to the passage and at least one outer surface of the first shaft 612, e.g., surface 614. The two channels include a first and a second channel. The first channel may be the first channel 832 and the second channel may be the second channel 834. The method includes driving the first fluid flow from the passage through a first opening, e.g., by forcing the fluid via one or more of the plurality of radially directed forces on the first shaft 612. The first opening fluidly couples the first channel. The method includes driving the first fluid flow 632 through the first opening and the first channel, e.g., via one or more of the radially directed forces on the first shaft 612.The first channel extends along a first axis, e.g., the first centerline 842. The first axis is at a first angle to a longitudinal plane including the axis of rotation. The method includes expelling the first flow from the first channel via a second opening by forces on the first shaft 612. The method includes forcing a second flow of fluid from the fluid passageway through a third opening, e.g., by forcing the fluid via one or more of the radially directed forces on the first shaft 612. The third opening is fluidly connected to the second channel. The method includes forcing the second flow through the second opening and the second channel, e.g., by the radially directed forces. The second channel extends along a second axis, e.g., the second centerline 844. The second axis is at a second angle to the longitudinal plane including the axis of rotation.The second angle has a different size than the first angle. The method includes expelling the second flow from the second channel through a fourth opening, for example, via the radially directed forces on the first shaft 612. The first and second openings of the first channel may be the third opening 862 and the first opening 852, respectively. Fig. 8. The third and fourth opening of the fourth channel may be the fourth opening 864 and the second opening 854 of Fig. 8. The method may include expelling the lubricant from the passageway via one or more of a plurality of streams, wherein the plurality of streams of fluid may be expelled from the passageway via other passageways that are longitudinally farther from the inlet than the first and second channels. The other channels may be feed channels. The fluid may be forced through the other channels by being urged by the one or more radial forces on the first shaft 612. The method may include expelling the remaining fluid in the passageway that was not expelled from the first shaft 612 via the other channels from the first shaft 612 via an outlet.

[0122] In a second example of the lubrication method, there may be at least three channels connected to the passageway via a respective opening. The three channels include a first channel, a second channel, and a third channel, each channel fluidly connecting a corresponding opening to the passageway and at least one outer surface of the first shaft 612, e.g., surface 614. The first channel may be the first channel 832 and the second channel may be the second channel 834. The first channel and the second channel may be the first channel and the second channel described in the first example. The first channel extends along a first axis; the second channel extends along a second axis; and the third channel extends along a third axis. The first axis is at a first angle to the longitudinal plane including the axis of rotation.The second axis is at a second angle to the longitudinal plane including the axis of rotation. The second angle is a different magnitude than the first angle, wherein the first angle is greater than the second angle. The method includes forcing the first fluid flow through a first opening of the first channel and the second fluid flow to a third opening of the second channel, for example, by forcing the fluid via one or more of the plurality of radially directed forces on the first shaft 612. The fluid can be forced in the first flow through the first opening to the outer surfaces of the first shaft 612 via the first channel and a second opening, as described in the first example above. The fluid can be forced in a second flow through the third opening to the outer surfaces of the first shaft 612 via the second channel and a fourth opening, as described in the first example above.The method includes driving a third flow of fluid from the fluid passageway via a fifth opening, for example, by pushing the fluid through one or more of the radially directed forces on the first shaft 612. The fifth opening is fluidly connected to the third channel. The method includes driving the third flow through the fifth opening and the third channel, for example, by the radially directed forces. The third channel extends along a third axis. The third axis extends at a third angle from the longitudinal plane including the axis of rotation. The third angle is different than the first and second angles. The method includes driving the third flow from the second channel via a sixth opening, for example, by the radially directed forces on the first shaft 612. The first and second openings of the first channel can be the third opening 862 and the first opening 852, respectively. Fig. 8. The third and fourth opening of the fourth channel may be the fourth opening 864 and the second opening 854 of Fig. 8. The method may include expelling the lubricant from the passageway via one or more of a plurality of streams, wherein the plurality of streams of fluid may be expelled from the passageway via other channels that are longitudinally farther from the inlet than the first channel, the second channel, and the third channel. The other channels may be feed channels. The fluid may be forced through the other channels, e.g., by being driven by one or more of the radial forces. The method may include expelling the remaining fluid in the passageway that was not expelled from the first shaft 612 via the other channels from the first shaft 612 via an outlet.

[0123] In this way, a lubrication system for a shaft is disclosed herein, wherein the shaft has at least one fluid passage offset from a central and rotational axis of the shaft such that an axis and centerline on which the fluid passage is centered is not coaxial with the central and rotational axis of the shaft. The offset fluid passage can lubricate multiple consumers, e.g., eight consumers, via multiple complementary fluid passages, e.g., eight fluid channels, whereby the consumers can receive constant lubrication while avoiding a lack of fluid upstream of an outlet to the shaft. The offset position and angular velocity can maintain a fluid-free surface for the lubricant received by the fluid passage. A plurality of channels can communicate with the fluid passage, extend radially from the central axis of the shaft, and conduct the lubricant to the consumers.The plurality of channels includes at least two axially spaced channels. The axially spaced channels are centered about axes extending radially from the axis of the fluid passage, and the axes extend at different angles from a plane including the axis of the fluid passage and the central and rotational axis of the shaft. Each spaced channel that is farther from an inlet to the fluid passage than a previous axially spaced channel extends at a smaller angle than the previous axially spaced channel. Each spaced axial channel is centered about a centerline (e.g., an axis), and each centerline extends at one of the different angles. For example, a first angle of an axially spaced channel may be half or more smaller than a second angle of the previous axially spaced channel.The axially spaced channels can be supply channels or vent channels.

[0124] In another representation, the axially spaced channels comprise at least two feed channels. Each feed channel that is farther axially from the inlet to the fluid passage than the previous feed channel extends at a smaller angle than the previous feed channel. A first angle of a feed channel may be half or more smaller than the second angle of the previous feed channel. The first channel is centered on a first centerline and the second channel is centered on a second centerline, the first centerline and the second centerline extending at a first angle and a second angle, respectively, from the plane.

[0125] In another embodiment, there may be at least four axially spaced channels. The axially spaced channels may include at least four feed channels. Each feed channel that is further axially from the inlet to the fluid passage than a previous feed channel extends at a smaller angle than the previous feed channel. The first angle of a feed channel may be half or more smaller than the second angle of the previous feed channel. The four feed channels include a first channel, a second channel, a third channel, and a fourth channel, with the first channel being axially closest to the inlet, followed by the second channel, the third channel, and the fourth channel, with the fourth channel being axially farthest from the inlet.A fourth angle of the fourth channel is less than a third angle of the third channel, the third angle is less than a second angle of the second channel, and the second angle is less than a first angle of the first channel, wherein the fourth angle, the third angle, the second angle, and the first angle originate from the plane. In a first example, the fourth angle may be half the size of the third angle, the third angle may be half the size of the second angle, and the second angle may be half the size of the first angle. In a second example, the fourth angle may be less than half the third angle, the third angle may be less than half the second angle, and the second angle may be less than half the first angle.The first channel is centered on a first centerline, the second angle is centered on a second centerline, the third channel is centered on a third centerline, and the fourth channel is centered on a fourth centerline, the first centerline, the second centerline, the third centerline, and the fourth centerline extending from the plane at the first angle, the second angle, the third angle, and the fourth angle, respectively.

[0126] In these or other representations, the shaft may include a plurality of other axially spaced channels. The other axially spaced channels are centered about centerlines (e.g., axes) extending radially from the axis of the fluid passage, and the centerlines extend at different angles from the plane including the axis of the fluid passage and the central and rotational axes of the shaft. An axially spaced channel that is farther from an inlet to the fluid passage than a previous axially spaced channel extends at a smaller angle than the previous axially spaced channel. A first angle of the other axially spaced channel may be half or more smaller than a second angle of the previous other axially spaced channel. The other axially spaced channels are vent channels.

[0127] Although various embodiments have been described above, they are to be considered as examples and not as limitations. Those skilled in the art will appreciate that the disclosed subject matter may be embodied in other specific forms without departing from the spirit of the subject matter. The embodiments described above are, therefore, to be considered in all respects as illustrative and not limiting. Thus, the configurations and routines disclosed herein are exemplary, and the specific examples are not to be considered limiting, as numerous variations are possible. For example, the technology described above may be applied to powertrains that include various types of power sources, including various types of prime movers, internal combustion engines, and / or transmissions.The subject matter of the present disclosure includes all novel and non-obvious combinations and sub-combinations of the various systems and configurations, as well as other features, functions and / or properties disclosed herein.

[0128] It should be understood that the configurations and routines disclosed herein are exemplary in nature, and that these specific embodiments are not to be considered limiting, as numerous variations are possible. Unless expressly stated otherwise, the terms "first," "second," "third," etc., are not intended to denote an order, position, quantity, or importance, but are used merely to distinguish the individual elements. The subject matter of the present disclosure includes all novel and non-obvious combinations and sub-combinations of the various systems and configurations, as well as other features, functions, and / or characteristics disclosed herein.

[0129] The following claims particularly point out certain combinations and sub-combinations that are considered novel and non-obvious. These claims may refer to "a" element or "a first" element, or the equivalent thereof. Such claims are to be construed as including the inclusion of one or more such elements, neither requiring nor excluding two or more such elements. Other combinations and sub-combinations of the disclosed features, functions, elements, and / or properties may be claimed by amending the present claims or by filing new claims in this or a related application. Such claims, whether broader, narrower, equal, or different in scope than the original claims, are also to be considered included within the subject matter of the present disclosure.

Claims

[1] Lubrication system for a gearbox, comprising: a shaft of the transmission having a fluid passage, the fluid passage being centered on an axis that is parallel and not coaxial with a rotational axis of the shaft, the shaft being centered on the rotational axis; and at least two axially spaced radial channels, the axially spaced radial channels being in fluid communication with the fluid passage and being inclined at different angles with respect to a plane intersecting the shaft in a longitudinal direction with respect to the axis of rotation, the plane including the axis of rotation and the axis of the fluid passage, the different angles decreasing in magnitude for each axially spaced radial channel that is farther from an inlet than a previous spaced radial channel. [2] The lubrication system of claim 1, wherein the lubrication system is a forced lubrication gear system, wherein the shaft is horizontal to a vertical axis and the vertical axis is parallel to a direction of gravity. [3] A lubrication system according to claim 2, wherein the axially spaced radial channels comprise at least one vent channel. [4] The lubrication system of claim 3, wherein the axially spaced radial channels comprise at least two vent channels, the vent channels comprising a first vent channel and a second vent channel. [5] The lubrication system of claim 4, wherein the first vent passage and the second vent passage are angled at first and second angles from the plane, a first centerline of the first vent passage being separated from the plane by the first angle, a second centerline of the second vent passage being separated from the plane by the second angle. [6] The lubrication system of claim 5, wherein the first vent passage is closer to the inlet along a longitudinal axis of the shaft than the second vent passage and the second angle is half the first angle. [7] The lubrication system of claim 5, wherein the first vent passage is located closer to the inlet along a longitudinal axis of the shaft than the second vent passage and the second angle is less than half the first angle. [8] A lubrication system according to any one of claims 5 to 7, wherein the axially spaced radial channels include a third vent channel, the third vent channel being angled at a third angle such that a third centerline of the third vent channel is separated from the plane by the third angle, the third angle being of a different magnitude than the first angle and the second angle. [9] The lubrication system of claim 8, wherein the second vent passage is located closer to the inlet along the axis of the shaft than the third vent passage and the second angle is greater than the third angle. [10] The lubrication system of claim 9, wherein the third angle is at least half the size of the second angle. [11] A lubrication system according to any one of the preceding claims, comprising at least the features of claim 3, wherein the axially spaced radial channels comprise at least two of a plurality of supply channels, each of the supply channels having a first opening and a second opening, the first opening being flush with and adjacent to an inner surface of the fluid passage and the second opening being flush with an outer surface of the shaft, each supply channel being centered on a centerline, each centerline extending at one of the different angles from the plane. [12] A lubrication system according to claim 11, wherein each supply channel is complementary to at least one consumer, the consumer being positioned to receive lubricant from the second opening. [13] The lubrication system of claim 12, wherein the shaft has at least four supply channels, including a first supply channel, a second supply channel, a third supply channel, and a fourth supply channel, wherein the first supply channel extends at a first angle from the plane, the second supply channel extends at a second angle from the plane, the third supply channel extends at a third angle from the plane, and the fourth supply channel extends at a fourth angle from the plane, wherein the first angle, the second angle, the third angle, and the fourth angle are different.

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