System and method for variable compression ratio phasing

Abstract

A phasing system is provided. A phase angle between a gear hub and a carrier rotor can be driven by a planetary actuator. In some non-limiting examples, an input shaft is rotationally coupled between the rotary actuators to rotate therewith. Rotation of the input shaft can unlock relative rotation between the carrier rotor and the gear hub. In some non-limiting examples, the phasing system can include a gear hub and a carrier rotor, and a torsion spring disposed therebetween. The torsion spring can be configured to exert an internal torque load between the gear hub and the carrier rotor to counteract an external torque load applied to the gear hub or the carrier rotor.

Description

[0001] Cross-reference to related applications

[0002] This application is based on and claims priority to U.S. Provisional Patent Application No. 63 / 066,659, filed August 17, 2020, entitled "Systems and Methods for Variable Compression Ratio Phaser," the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to a system and method for a variable compression ratio phaser. Background Technology

[0004] Typically, a rotating phasing system for rotating applications (e.g., engines, motors, etc.) may include a first component and a second component that can be rotated and phased with the first component. Summary of the Invention

[0005] In one aspect, this disclosure provides a variable compression ratio (VCR) phasing system for changing the rotational relationship between a crankshaft and an eccentric shaft. The VCR phasing system includes: a gear hub configured to rotate in communication with the crankshaft; a carrier rotor configured to rotate in communication with the eccentric shaft; a star rotor disposed between the gear hub and the carrier rotor and configured to selectively lock and unlock the relative rotation between the gear hub and the carrier rotor; and a planetary actuator connected to the gear hub and the star rotor. The planetary actuator is configured to receive a rotational input to provide an output to the star rotor to unlock the relative rotation between the carrier rotor and the gear hub. The VCR phasing system also includes a torsion spring coupled between the gear hub and the carrier rotor. The torsion spring is configured to apply a torque load in a first direction between the gear hub and the carrier rotor to counteract a torque load applied in a second direction by one of the eccentric shafts or the crankshaft.

[0006] In one aspect, this disclosure provides a phasing system for changing the rotational relationship between a first rotating component and a second rotating component. The phasing system includes a gear hub, a carrier rotor, a star rotor disposed between the gear hub and the carrier rotor and configured to selectively lock and unlock relative rotation between the gear hub and the carrier rotor, and a torsion spring coupled between the gear hub and the carrier rotor. The torsion spring is configured to apply a torque load between the gear hub and the carrier rotor. The phasing system also includes a planetary actuator coupled to the gear hub and the star rotor. The planetary actuator is operable between a steady-state mode and a phasing mode, in which relative rotation between the gear hub and the carrier rotor is suppressed, and in the phasing mode, the planetary actuator receives a rotational input at a predetermined amplitude to selectively provide relative rotation between the gear hub and the carrier rotor.

[0007] In one aspect, this disclosure provides a variable compression ratio (VCR) phasing system for changing the rotational relationship between a crankshaft and an eccentric shaft. The VCR phasing system includes: a gear hub configured to rotate in communication with the crankshaft; a carrier rotor configured to rotate in communication with the eccentric shaft; a star rotor disposed between the gear hub and the carrier rotor and configured to receive an input to selectively lock and unlock the relative rotation between the gear hub and the carrier rotor; a spring sleeve coupled to and rotatably fixed thereto by the gear hub; and a torsion spring coupled between the gear hub and the carrier rotor. The torsion spring is configured to apply a torque load between the gear hub and the carrier rotor. The preload of the torsion spring is set by coupling a first end of the torsion spring to the carrier rotor, coupling an opposing second end of the torsion spring to a spring seat, and rotating the spring seat relative to the spring sleeve to selectively align at least one of a plurality of first slots disposed on the spring sleeve and at least one of a plurality of second slots disposed on the spring seat. The selective alignment of at least one first slot and at least one second slot configures to rotatably lock the spring sleeve to the spring seat.

[0008] In one aspect, this disclosure provides a VCR phasing system for changing the rotational relationship between a crankshaft and an eccentric shaft. The VCR phasing system may include: a gear hub configured to rotate in communication with the crankshaft, a carrier rotor configured to rotate in communication with the eccentric shaft, and a star rotor disposed between the gear hub and the carrier rotor. The star rotor may be configured to selectively lock and unlock the relative rotation between the gear hub and the carrier rotor. The VCR phasing system may also include a planetary actuator coupled to the gear hub and the star rotor. The planetary actuator may be configured to receive a rotational input to provide an output to the star rotor to selectively lock and unlock the relative rotation between the carrier rotor and the gear hub. The planetary actuator may operate between a steady-state mode and a phasing mode, in which the relative rotation between the gear hub and the carrier rotor is suppressed, and in the phasing mode, rotation input to the planetary actuator at a predetermined amplitude may be configured to rotate the carrier rotor relative to the gear hub in a desired direction. Attached Figure Description

[0009] The invention will be better understood by considering the following specific embodiments, and features, aspects, and advantages other than those set forth above will also become apparent. This specific embodiment is illustrated in the following figures.

[0010] Figure 1 This is a perspective view of a cross-section of a rotating phase-fixing system according to one aspect of this disclosure.

[0011] Figure 2 This is an exploded view of a planetary actuator according to one aspect of this disclosure.

[0012] Figure 3 yes Figure 2 A rear-view stereoscopic view of the planetary actuator.

[0013] Figure 4 yes Figure 3 A front-view stereoscopic view of the planetary actuator.

[0014] Figure 5 yes Figure 3 Front view of the planetary actuator in steady-state operation mode.

[0015] Figure 6 yes Figure 3 The front view of the planetary actuator when it is phased in the first direction.

[0016] Figure 7 yes Figure 3 The front view of the planetary actuator when it is phased in the second direction.

[0017] Figure 8 yes Figure 1 A cross-sectional view of a rotating phase-fixing system.

[0018] Figure 9 yes Figure 8 Exploded view of a rotating phase-fixed system.

[0019] Figure 10 yes Figure 8 A three-dimensional view of the gear hub of a rotating phase-fixed system.

[0020] Figure 11 yes Figure 8 An exploded view of the torsion spring assembly of a rotating phase-fixed system.

[0021] Figure 12 yes Figure 11 A perspective view of the spring seat of a torsion spring assembly.

[0022] Figure 13 It is along line 13-13 (see Figure 8 ) cut Figure 11 A cross-sectional view of the torsion spring assembly.

[0023] Figure 14 yes Figure 8 An exploded view of the bracket rotor of a rotating phase-fixed system.

[0024] Figure 15 yes Figure 8 A three-dimensional diagram of a spider rotor in a rotating phased system.

[0025] Figure 16 yes Figure 15 A three-dimensional view of a star-shaped rotor, in which multiple locking components are installed.

[0026] Figure 17 yes Figure 8 An exploded view of the connection components of the rotating phase-fixing system.

[0027] Figure 18 It is installed in the planetary actuator and Figure 8 Between mechanical phasing components Figure 17 A three-dimensional view of the connecting components.

[0028] Figure 19 It is a section taken from line 19-19. Figure 8 A cross-sectional view of the mechanical phasing assembly.

[0029] Figure 20 This is a cross-sectional view of a rotating phase-fixing system according to another aspect of this disclosure.

[0030] Figure 21 yes Figure 20 An exploded view of the torsion spring assembly of a rotating phase-fixed system.

[0031] Figure 22 It is a section taken along line 22-22. Figure 20 A cross-sectional view of the torsion spring assembly of the rotating phase-fixing system.

[0032] Figure 23 yes Figure 20 A three-dimensional view of the star rotor of the rotating phased system.

[0033] Figure 24 yes Figure 20 A three-dimensional view of a rotating phase-fixed system, wherein the phase is not shown. Figure 21 The torsion spring assembly exposes the structure below.

[0034] Figure 25 It is a curve showing the change of eccentric shaft torque pulse over time.

[0035] Figure 26 It is a graph showing the change of the phase angle between the eccentric shaft and the crankshaft over time. Detailed Implementation

[0036] As used herein, the term "axial" and its variations refer to a direction that extends generally along an axis of symmetry, a central axis, or the elongated direction of a particular component or system. For example, an axially extending feature of a component may be a feature that extends generally along a direction parallel to the component's axis of symmetry or elongated direction. Similarly, as used herein, the term "radial" and its variations refer to a direction that is generally perpendicular to the corresponding axial direction. For example, a radially extending structure of a component may extend generally, at least partially, along a direction perpendicular to the component's longitudinal or central axis. As used herein, the term "circumference" and its variations refer to a direction that extends around the perimeter of an object, or around an axis of symmetry, a central axis, or the elongated direction of a particular component or system.

[0037] Traditional rotational phasing (i.e., selective relative rotation or rotational offset) systems require an input mechanism to apply force or displacement to achieve the desired relative rotation between two components. In some systems, the axial / linear input is provided by an actuator. The magnitude of the force required to achieve the desired phasing increases the cost of a traditional phasing system exponentially. Furthermore, the amount of relative rotation provided by the phasing system increases the system's height. That is, as the required amount of relative rotation increases in a given application, the actuator providing the axial / linear input needs increased stroke, which increases the actuator height and the overall package size of the phasing system.

[0038] Generally, this disclosure provides systems and methods for selectively controlled relative rotation in a rotating system. In some non-limiting examples, a planetary actuator may be configured to be coupled between a rotary actuator and a two-way clutch or locking mechanism. The locking mechanism may be coupled between two rotating components. For example, the first rotating component may be driven by an external source at a desired rotational speed, while the second rotating component may be rotaryly driven by the two-way clutch or locking mechanism. The planetary actuator may also rotate together with the two-way clutch or locking mechanism. The rotary actuator may apply an input to the planetary actuator, which may be configured to allow selective relative rotation between the first and second rotating components. For example, the planetary actuator may be configured to rotaryly displace / push a portion of the two-way clutch or locking mechanism to provide a predetermined relative rotation (i.e., a predetermined rotational offset) in a desired direction between the first and second rotating components.

[0039] Because the relative rotational motion is facilitated using rotational displacement / force instead of axial / linear displacement / force, the axial height of the phasing system can be reduced using the planetary actuator according to this disclosure. Furthermore, the magnitude of the force required to achieve the relative rotational motion can be significantly reduced compared to conventional phasing systems, which lowers the cost of phasing systems utilizing planetary actuators.

[0040] Figure 1A non-limiting example of a rotating phasing system 10 according to this disclosure is shown. In some non-limiting examples, the rotating phasing system 10 can be used in a variable compression ratio (VCR) system on an internal combustion engine to facilitate selective rotating phasing (i.e., a predetermined amount of relative rotation) between a crankshaft and an eccentric shaft. Such a VCR system arrangement is described in U.S. Patent Application Publication No. US2019 / 0323390. The rotating phasing system 10 can be rotatedly driven by a crankshaft 12. For example, the crankshaft 12 can have a gear fixed thereto that rotates together with the engine crankshaft. As will be described herein, the crankshaft gear can mesh with a first gear coupled to the rotating phasing system and provide a rotational drive input thereto. The rotating phasing system 10 can then rotately drive an eccentric shaft 14. For example, the eccentric shaft 14 can have a gear fixed thereto that rotates together with the eccentric shaft 14. As will be described herein, the eccentric shaft gear can mesh with a second gear coupled to the rotating phasing system 10 and receive a rotational drive input from that second gear. Typically, the rotational position of the eccentric shaft 14 is displaced relative to the crankshaft 12 to change the compression ratio of the internal combustion engine. For example, the rotational position of the eccentric shaft 14 is displaced relative to the rotational position of the crankshaft 12 via an angular displacement of the eccentric shaft 14. As will be described in detail below, the rotational phasing system 10 facilitates selective rotational phasing (i.e., a predetermined amount of relative rotation or angular displacement) between the crankshaft 12 and the eccentric shaft 14.

[0041] In the illustrated non-limiting example, the rotating phasing system 10 may include a planetary actuator 100 and a mechanical phasing assembly 300 in the form of a bidirectional clutch or locking mechanism. In some applications, the planetary actuator 100 may be used to directly or indirectly drive or actuate phasing between a crankshaft and an eccentric shaft. In the illustrated non-limiting example, the planetary actuator 100 may be used in conjunction with the mechanical phasing assembly 300, wherein a bidirectional clutch or locking mechanism is coupled between the eccentric shaft 14 and the crankshaft 12 to selectively allow relative rotation therebetween. In these applications, the planetary actuator 100 may be configured to provide a predetermined amount of rotational force / displacement to the bidirectional clutch or locking mechanism, determined by the rotational input provided to them. In the illustrated non-limiting example, the rotating phasing system 10 may include a rotary actuator 313 to provide a rotational input to the planetary actuator 100, thereby selectively changing the alignment between the two gear rings of the planetary actuator 100 by a predetermined amount as the planetary actuator 100 rotates. As will be described, the rotary input provided by the rotary actuator 313 facilitates selective relative rotation between the eccentric shaft 14 and the crankshaft 12 in the desired direction.

[0042] Figure 2A non-limiting example of a planetary actuator 100 according to the present disclosure is shown. In the non-limiting example shown, the planetary actuator 100 may include a first ring gear 200, a first sun gear 202, a planet carrier assembly 204, a second ring gear 206, a second sun gear 208, and an input shaft 315 (see [link to documentation]). Figure 1 In the non-limiting example shown, the components of the planetary actuator 100 may be arranged along a common central axis C.

[0043] Reference Figure 2 The first gear ring 200 may include a toothed inner surface 212 and an outer surface 214. The toothed surface 212 may extend radially inward from an axial end of the first gear ring 200 and may include a plurality of gear teeth extending circumferentially around the toothed surface 212. The outer surface 214 of the first gear ring 200 extends axially from its radially outer edge to form a cavity 215 within the first gear ring 200. The outer surface 214 may include a plurality of slots 216. The plurality of slots 216 form rectangular cuts in the first gear ring 200 and extend axially along a portion of the length of the outer surface 214. In the non-limiting example shown, the first gear ring 200 includes two slots 216 that are circumferentially spaced apart (e.g., circumferentially spaced 180°) around the outer surface 214. In other non-limiting examples, the first gear ring 200 may include more or fewer than two slots 216 arranged circumferentially around the outer surface 214 in any incremental manner.

[0044] Compared to the toothed surface 212, the axial end of the slot or notch 216 that extends can be positioned on the axially opposite side of the first gear ring 200. When the planetary actuator 100 is assembled into the rotating phasing system 10 as will be described herein, one or more compliant members can be received within the cavity 215 and can be configured to apply force to the edge of the slot 216. The first gear ring 200 may also include a retaining ring groove 218 configured to receive a retaining ring to maintain the axial position of the compliant member in the assembly.

[0045] Continue to refer to Figure 2 The planetary carrier assembly 204 may include a first set of planetary gears 222, a second set of planetary gears 224, and a planetary carrier plate 226. The first set of planetary gears 222 and the second set of planetary gears 224 may be arranged on opposite axial sides of the planetary carrier plate 226. In the illustrated non-limiting example, the first set of planetary gears 222 may include three planetary gears 228 circumferentially arranged around and meshing with the first sun gear 202. In other non-limiting examples, the first set of planetary gears 222 may include more or fewer than three planetary gears 228 circumferentially arranged around and meshing with the first sun gear 202.

[0046] In the non-limiting example shown, the first sun gear 202 may be centrally arranged relative to the planet gear 228 and may include a coupling aperture 230 extending axially therethrough. The coupling aperture 230 may define a keyway or rectangular recess to receive from the rotary actuator 313 (see [link to documentation]). Figure 1 The input shaft 315 of the rotary actuator 313 rotates the first sun gear 202, causing the input shaft 315 and the first sun gear 202 to rotate together. In other non-limiting examples, the coupling aperture 230 can define any geometry (e.g., elliptical, square, triangular, polygonal, etc.) that allows the input shaft 315 to be rotatably coupled to the first sun gear 202. It should be understood that the end of the input shaft 315 of the rotary actuator 313 can extend axially into the first sun gear 202 and define generally complementary shapes to match the shape defined by the coupling aperture 230 of the first sun gear 202. Thus, for example, the end of the input shaft 315 can be inserted into the coupling aperture 230 to allow the input shaft 315 to be rotatably coupled to the first sun gear 202, causing the input shaft 315 and the first sun gear 202 to rotate together.

[0047] An input shaft 315 from the rotary actuator 313 may be received in and inserted through a central aperture 234, which extends axially through the planet carrier plate 226. The input shaft 315 may also extend axially through the second sun gear 208 to engage the first sun gear 202. Although the input shaft 315 extends through the second sun gear 208, the first sun gear 202 can rotate independently relative to the second sun gear 208. In some non-limiting examples, a retaining ring (not shown) may be used on the end of the input shaft 315 adjacent to the first sun gear 202 to prevent axial displacement of the input shaft 315 relative to the planet carrier plate 226, thereby preventing axial displacement of the first sun gear 202 relative to the planet carrier plate 226.

[0048] In the illustrated non-limiting example, the second set of planetary gears 224 may include three planetary gears 236 arranged circumferentially around and meshing with the second sun gear 208. In other non-limiting examples, the second set of planetary gears 224 may include more or fewer than three planetary gears 236 arranged circumferentially around and meshing with the second sun gear 208. The second sun gear 208 may be centrally located relative to the planetary gears 236 and may define a height sufficient to ensure that at least a portion of the second sun gear 208 axially protrudes beyond the axial height of the planetary gears 236. That is, the axial height defined by the second sun gear 208 is greater than the axial height defined by the planetary gears 236 to allow at least a portion of the second sun gear 208 to axially protrude beyond the planetary gears 236 (e.g., in a direction away from the planet carrier 226).

[0049] Planetary gear 228 of the first set of planetary gears 222 and planetary gear 236 of the second set of planetary gears 224 can be axially fixed relative to the planet carrier plate 226. For example, as Figure 2 As shown, the planetary carrier assembly 204 may include a plurality of support rods 238 and a pair of annular plates 240. In some non-limiting examples, each of the plurality of support rods 238 may include a groove (not shown) disposed on its distal end opposite the flange end of the support rod 238. The groove may extend radially inward into the corresponding support rod 238. Each support rod 238 may be axially inserted through one of the annular plates 240, then through one of the planet gears 228 of the first set of planetary gears 222 or one of the planet gears 236 of the second set of planetary gears 224, and then through a rod aperture 243 in the planetary carrier plate 226. In some non-limiting examples, a retaining ring (not shown) may be inserted into each groove to prevent, for example, axial displacement of each planet gear 228 of the first set of planetary gears 222 and each planet gear 236 of the second set of planetary gears 224 relative to the planetary carrier plate 226.

[0050] Continue to refer to Figure 2 The second gear ring 206 may include a toothed inner surface 246 and a flange 248, as well as a pair of tabs 250. The toothed surface 246 may include a plurality of gear teeth extending circumferentially around the toothed surface 246. The flange 248 may extend radially outward from an axial end of the second gear ring 206. The pair of tabs 250 extend radially outward from the flange 248. In the non-limiting example shown, the tabs 250 are arranged on opposite circumferential sides of the flange 248. As will be described herein, the tabs 250 of the second gear ring 206 are configured to rotatably lock the second gear ring to a spring sleeve for rotation therewith.

[0051] Typically, one of the first sun gear 202 and the second sun gear 208 is rotatably fixed to prevent rotation. Figure 1-2In an illustrative, non-limiting example, the second sun gear 208 may be coupled to an anti-rotation ring (not shown) to rotatably lock the second sun gear 208 to the rotary actuator housing. An axial projection of the second sun gear 208 beyond the planet gear 236 of the second set of planet gears 224 provides a passage for the anti-rotation ring to axially insert onto a portion of the second sun gear 208. It should be understood that the anti-rotation ring may include an inner surface that matches the gear profile of the second sun gear 208 so that the inner surface can axially insert onto the second sun gear 208. The anti-rotation ring may be coupled to a rotationally fixed external component, such as the rotary actuator housing, which prevents the anti-rotation ring from rotating, thereby preventing the second sun gear 208 from rotating. In some non-limiting examples, the first sun gear 202 may be rotatably fixed, and the second sun gear 208 may be coupled to an input shaft 315 to rotate therewith.

[0052] Reference Figure 3-4 The assembled planetary carrier assembly 204 can be at least partially inserted into the cavity 215 of the first ring gear 200, such that the toothed surface 212 meshes with the planet gear 228 of the first set of planetary gears 222. The second ring gear 206 can be inserted into the planetary carrier assembly 204, such that the toothed surface 246 meshes with the planet gear 236 of the second set of planetary gears 224. Note that the annular plate 240 is not in... Figure 3-4 As shown, the engagement of the gears in the planetary actuator 100 will be covered by the annular plate 240.

[0053] Typically, during operation of the planetary actuator 100, the first ring gear 200 and the second ring gear 206 are able to rotate freely in a desired direction. For example, when the toothed surface 212 meshes with planet gear 228 of the first set of planetary gears 222, the first ring gear 200 is able to rotate around the first sun gear 202. Similarly, when the toothed surface 246 meshes with planet gear 236 of the second set of planetary gears 224, the second ring gear 206 is able to rotate around the second sun gear 208.

[0054] Since the second sun gear 208 can be rotatably fixed relative to the planetary actuator 100, the first sun gear 202 can be selectively rotated to change the rotational relationship between the first ring gear 200 and the second ring gear 206. For example, rotary actuator 313 (see...) Figure 1The input shaft 315 can be selectively rotated by a desired amount of rotation in a first direction, which in turn causes the first sun gear 202, rotatably coupled to the input shaft 315, to rotate in the first direction. Rotation of the first sun gear 202 in the first direction can cause the planet gears 228 of the first set of planetary gears 222 to rotate in the opposite direction to the first direction, which ultimately causes the first ring gear 200 to rotate relative to the second ring gear 206 in the opposite direction to the first direction. The magnitude of the relative rotation or rotational offset between the first ring gear 200 and the second ring gear 206 can depend on the transmission ratio defined between the input shaft 315 and the first ring gear 200. For example, the combined transmission ratio takes into account each of the transmission ratio between the input shaft 315 and the first sun gear 202, the transmission ratio between the first sun gear 202 and the planet gears 228 of the first set of planetary gears 222, and the transmission ratio between the planet gears 228 of the first set of planetary gears 222 and the first ring gear 200. In any case, given a known combined gear ratio, the degree of rotation of the input shaft 315 can be related to a known degree of rotation of the first gear ring 200 relative to the second gear ring 206. Therefore, the direction and magnitude of rotation of the input shaft 315 driven by the rotary actuator 313 can be related to a predetermined direction and magnitude of the relative rotation or rotational offset between the first gear ring 200 and the second gear ring 206.

[0055] As will be described herein, the planetary actuator 100 can be rotatably coupled between a first rotating component and a second rotating component to selectively apply relative rotation or rotational offset between the first rotating component and the second rotating component. Typically, the planetary actuator 100 can operate in a steady-state mode and a phase-fixed mode, in which the rotational relationship between the first rotating component and the second rotating component is maintained (e.g., locked), and in the phase-fixed mode, the rotational relationship between the first rotating component and the second rotating component is offset in a desired direction and with a desired magnitude.

[0056] Figure 5 A planetary actuator 100 operating in steady-state mode is shown. (Example) Figure 5 As shown by the arrows, the first gear ring 200 and the second gear ring 206 are in the first direction (e.g., from...). Figure 5 Rotating counterclockwise (viewed from the angle). In steady-state mode, the rotary actuator 313 (see...) rotates... Figure 1The input shaft 315 can remain rotatably fixed, and therefore, due to the rotational connection between the input shaft 315 and the first sun gear 202, the first sun gear 202 can be rotatably fixed. Furthermore, the second sun gear 208 can be rotatably fixed (e.g., by means of the anti-rotation ring described previously herein). With the first sun gear 202 and the second sun gear 208 rotatably fixed, the planet gear 228 of the first set of planetary gears 222 can rotate in a first direction, and due to the rotation of the first ring gear 200, the planet gear 228 itself can rotate about the first sun gear 202 in the first direction (e.g., the planet gear 228 can rotate about the central axis C). Similarly, due to the rotation of the second ring gear 206, the planet gear 236 of the second set of planetary gears 224 can rotate about the second sun gear 208. Thus, the relative rotational orientation between the first ring gear 200 and the second ring gear 206, and consequently the relative rotational orientation between the first rotating component and the second rotating component, can be maintained in a steady-state mode.

[0057] In the non-limiting example shown, the first gear ring 200 and the second gear ring 206 rotate in the first direction, but it should be understood that they can also rotate in the second direction (e.g., from...). Figure 5 (Viewed clockwise from the angle). Thus, planetary gear 228 of the first set of planetary gears 222 can rotate in the second direction, and due to the rotation of the first ring gear 200, planetary gear 228 itself can rotate in the second direction about the first sun gear 202 (e.g., planetary gear 228 can rotate about the central axis C). Similarly, due to the rotation of the second ring gear 206, planetary gear 236 of the second set of planetary gears 224 can rotate about the second sun 208. In the non-limiting example shown, the first ring gear 200 and the second ring gear 206 rotate at the same speed in steady-state mode.

[0058] Figure 6 A planetary actuator 100 operating in phasing mode is shown, wherein phasing occurs in a first direction. (See diagram) Figure 6 As shown by the arrow in the image, the first gear ring 200 can be in a first direction (e.g., from...). Figure 6 The first gear ring 200 rotates selectively relative to the second gear ring 206 (viewed counterclockwise). To facilitate the rotation of the first gear ring 200 relative to the second gear ring 206, it is rotatably connected to a rotary actuator 313 (see...). Figure 1 The input shaft 315 can be in a second direction opposite to the first direction (e.g., from...). Figure 6(Viewed clockwise) The rotation of the input shaft 315 in the second direction causes the first sun gear 202 to rotate in the second direction. The rotation of the first sun gear 202 in the second direction causes the planet gear 228 of the first set of planet gears 222 to rotate in the first direction, which in turn causes the first ring gear 200 to rotate in the first direction. With the second sun gear 208 rotated and fixed, this selective rotation of the first sun gear 202 and thus the first ring gear 200 allows the first ring gear 200 to rotate relative to the second ring gear 206 in the first direction.

[0059] Figure 7 A planetary actuator 100 operating in phasing mode is shown, wherein phasing occurs in a second direction. (See diagram.) Figure 7 As indicated by the arrow, the first gear ring 200 can be in the second direction (e.g., from...). Figure 7 The first gear ring 200 rotates selectively relative to the second gear ring 206 (viewed clockwise from the angle of rotation). To facilitate the rotation of the first gear ring 200 relative to the second gear ring 206, it is rotatably coupled to a rotary actuator 313 (see...). Figure 1 The input shaft 315 can be in a first direction opposite to the second direction (e.g., from...). Figure 7 (Viewed from the angle counterclockwise) Rotation. The rotation of the input shaft 315 in the first direction causes the first sun gear 202 to rotate in the first direction. The rotation of the first sun gear 202 in the first direction causes the planet gear 228 of the first set of planet gears 222 to rotate in the second direction, which in turn causes the first ring gear 200 to rotate in the second direction. With the second sun gear 208 rotated and fixed, this selective rotation of the first sun gear 202 and thus the first ring gear 200 allows the first ring gear 200 to rotate relative to the second ring gear 206 in the second direction.

[0060] As described herein, the magnitude of the relative rotation between the first gear ring 200 and the second gear ring 206 can be determined by the known transmission ratio between the input shaft 315 and the first gear ring 200. It should be understood that... Figure 6-7 The diagram illustrates the relative rotation between the first gear ring 200 and the second gear ring 206; however, in applications, the first gear ring 200 and the second gear ring 206 can rotate simultaneously with phasing or relative rotation occurring. Furthermore, the planetary actuator 100 is designed to allow a full 360-degree relative rotation between the first gear ring 200 (and any other rotating components rotatably coupled thereto) and the second gear ring 206 (and any other rotating components rotatably coupled thereto).

[0061] Typically, the planetary actuator 100 is designed and implemented to require only an input signal (i.e., input torque / speed / displacement provided from the rotary actuator 313 to the input shaft 315, and thus to the first sun gear 202) to rotate when a desired relative rotation is desired, rather than requiring the input signal to always cause the first ring gear 200 and / or the second ring gear 206 to rotate together. During steady-state operation, when no relative rotation is desired, the input shaft 315 may be rotationally fixed (e.g., stationary). During phase changes (i.e., relative rotation), it is not necessary for the input shaft 315 to rotate at the same speed as the first ring gear 200 or the second ring gear 206. For example, the input shaft 315 and thus the first sun gear 202 may only need to rotate at the desired rate of change of relative angle. Thus, for example, in phase-fixed mode, the rotation (i.e., speed / displacement) of the input shaft 315 can be proportional to the magnitude of the desired relative rotation between the first ring gear 200 and the second ring gear 206. Therefore, the power and speed required to rotate the input shaft 315 to achieve the desired relative rotation can be independent of the speeds of the first gear ring 200 and / or the second gear ring 206. Furthermore, in a non-limiting example, if a gear reducer exists between the input shaft 315 and the second gear ring 206, the gear reducer can reduce the amount of torque required to achieve the desired relative rotation.

[0062] Typically, the planetary actuator 100 can be used in a rotating system in which selective, controllable relative rotation is desired. For example, the planetary actuator 100 can be implemented in a mechanical phasing assembly. Figure 8-9 A non-limiting example of a rotating phasing system 10 having a planetary actuator 100 mounted in a mechanical phasing assembly 300 is shown. In the illustrated non-limiting example, the mechanical phasing assembly 300 may include a gear hub 302 (e.g., a first rotating component), a carrier rotor 304 (e.g., a second rotating component), a carrier cage or star rotor 308, a plurality of locking assemblies 310, the planetary actuator 100, and a torsion spring assembly 400. The planetary actuator 100, the torsion spring assembly 400, the gear hub 302, the carrier rotor 304, the star rotor 308, and the plurality of locking assemblies 310 may each share a common central axis C when assembled. As will be described herein, the torsion spring assembly 400 may be configured to apply a torque load between the carrier rotor 304 and the gear hub 302. The torsion spring assembly 400 may include a torsion spring 402 and a spring sleeve 403. In the non-limiting example shown, the spring sleeve 403 is configured as a two-piece spring sleeve, including a first spring sleeve 404 and a second spring sleeve 406. As will be described herein, the torsion spring assembly 400 may be configured to rotatably secure the second gear ring 206 to the gear hub 302. The torsion spring assembly may also be configured to attach the end of the torsion spring 402 to the gear hub 302.

[0063] In the non-limiting example shown, the star rotor 308 (including multiple locking assemblies 310) can be radially arranged between the bracket rotor and the gear hub. The spring sleeve 403 of the torsion spring assembly can be coupled to the gear hub 302 and extend axially away from it. In the example shown, the helical portion of the torsion spring 402 can extend circumferentially around the outer side of the spring sleeve 403. As shown, the spring sleeve 403 can define an internal cavity 418 (see figure). Figure 11 Furthermore, at least a portion of the planetary actuator 100 may be received within the internal cavity 418. According to the non-limiting example shown, at least a portion of the rotary actuator 313 may also be received within the internal cavity 418 of the spring sleeve 403.

[0064] In the illustrated non-limiting example, the mechanical phasing assembly 300 may include a rotary actuator 313. In some non-limiting examples, the rotary actuator 313 may include a stator and a rotor (not shown) electromagnetically coupled to the stator. A current may be applied to the rotary actuator 313, causing a rotational output at the input shaft 315 to be provided by the rotary actuator 313 with a desired force in a desired direction. In some non-limiting examples, the rotary actuator 313 may be in the form of a brushless direct current (BLDC) motor. In the illustrated non-limiting example, the mechanical phasing assembly 300 may include one or more bearings 317 configured to rotatably support internal components of the mechanical phasing assembly, or to rotatably support the mechanical phasing assembly 300 relative to components of the engine. For example, via a structure or bracket included in or formed as part of the engine block or other engine components. In the illustrated non-limiting example, the bearing 317 is arranged between the gear hub 302 and the carrier rotor 304, and along an axis extending from the carrier rotor. Additional bearing 317 is arranged along the outer side of gear hub 302.

[0065] Specific reference Figure 9-11 The gear hub 302 may include a first gear 311 disposed on its outer diameter, which can engage with the crankshaft 12 of the internal combustion engine (see [link to relevant documentation]). Figure 1Rotational communication (e.g., connection to crankshaft 12), for example, via belt, chain, or gear train assembly. Gear hub 302 may include an inner surface 316 and a front surface 320. The front surface 320 of gear hub 302 may include a plurality of orifices 322 configured to receive fastening elements for, for example, fixingly attaching a spring sleeve 403 (e.g., a first spring sleeve 404) to gear hub 302 for rotation therewith. In some non-limiting examples, gear hub 302 may define a plurality of circumferential slots (not shown) that are axially recessed and configured to receive radially projecting portions (not shown) protruding from the outer periphery of the first spring sleeve. In any case, the first spring sleeve 404 may be coupled to gear hub 302 such that the first spring sleeve 404 rotates with gear hub 302 (e.g., rotationally fixed). Gear hub 302 may also include an arcuate recess 323 extending radially outward from shaft portion 325 (see Figure 10 ).

[0066] Specific reference Figure 9 and 11 The first spring sleeve 404 may include a flange 412 and an annular protrusion 414. As described above, the flange 412 may include a plurality of orifices 416. Each of the plurality of orifices 416 may be arranged to align with a corresponding orifice 322 on the front surface 320 of the gear hub 302. The annular protrusion 414 may extend axially away from the flange 412 to define an internal cavity 418. The internal cavity 418 may be sized to axially receive at least a portion of the planetary actuator 100 therein. The internal cavity 418 may have a cutout 420 extending axially along the internal cavity 418, thereby forming an opening along the length of the internal cavity 418. The cutout 420 is configured to receive a first helical end (not shown) of the torsion spring 402 through it.

[0067] The first spring sleeve 404 and the second spring sleeve 406 may include toothed features at their axial ends. The toothed features may include a plurality of axial protrusions 422 and a plurality of axial recesses 424. The axial protrusions 422 of the first spring sleeve 404 are configured to engage with the axial recesses 424 of the second spring sleeve 406 to rotatably lock the first spring sleeve 404 to the second spring sleeve 406 for rotation therewith. Similarly, the axial protrusions 422 of the second spring sleeve 406 are configured to engage with the axial recesses 424 of the first spring sleeve 404. During assembly, a retaining ring 426 may be received in a retaining ring groove on the axial protrusions 422 on each of the first spring sleeve 404 and the second spring sleeve 406 to engage the first spring sleeve 404 to the second spring sleeve 406. The second spring sleeve 406 may include a plurality of first slots 428 configured as splines at axial ends opposite to the toothed features. The second spring sleeve 406 may also include tab recesses 429 within the internal cavity 431 of the second spring sleeve (see Figure 8The tab recess 429 is configured to receive the tab 250 of the second toothed ring 206 (see...). Figure 8 This causes the second gear ring 206 to be rotatably fixed to the second spring sleeve 406, thereby rotatably fixing the second gear ring 206 to the first spring sleeve 404 and the gear hub 302 so that they can rotate together.

[0068] Reference Figure 11-13 The torsion spring assembly 400 may also include a spring seat 430 coupled to a spring sleeve 403 (e.g., coupled to a second spring sleeve 406). The spring seat 430 may be configured to secure and engage the second helical end 432 of the torsion spring 402 (see [link to spring seat 400]). Figure 13 For example, the spring seat 430 may include a first spring support 433 that projects axially toward the flange 412 of the first spring sleeve 404 away from the spring seat 430. The first spring support is also arranged radially outward of the torsion spring 402. The first spring support 433 is configured to engage the second helical end 432 of the torsion spring 402 and prevent the torsion spring 402 from unfolding toward an unloaded state (e.g., unbiased or unpreloaded). The spring seat 430 may also include a second spring support 437 and a third spring support 439. In the non-limiting example shown, the second spring support 437 and the third spring support 439 project axially toward the flange 412 of the first spring sleeve 404 away from the spring seat 430. The second spring support 437 is arranged radially outward of the torsion spring 402 to support the outer side of the helical portion of the torsion spring 402. The third spring support 439 is arranged radially inward of the torsion spring 402 to support the inner side of the helical portion of the torsion spring 402.

[0069] In the non-limiting example shown, the first spring support 433, the second spring support 437, and the third spring support 439 extend circumferentially along the spring seat 430 to form an arcuate protrusion that defines a radius of curvature that shares the same center as the radius of curvature defined by the helical portion of the torsion spring 402. That is, the arcuate protrusion formed by the first spring support 433, the second spring support 437, and the third spring support 439 is concentric with the circular profile of the helical portion of the torsion spring 402. The first spring support 433, the second spring support 437, and the third spring support 439 can be configured together to prevent stress rise in the torsion spring 402 and to prevent lateral loads between components cooperating with the torsion spring 402. For example, the first spring support 433, the second spring support 437, and the third spring support 439 can engage both internally and externally with the torsion spring 402 to prevent lateral loading.

[0070] The spring seat 430 may include a plurality of second slots 434 configured as splines complementary to the first slot 428 of the second spring sleeve 406, such that the spring seat 430 is rotatably secured to the second spring sleeve for rotation therewith. During assembly, a retaining ring 436 may be received in a retaining ring groove adjacent to the first slot 428 of the second spring sleeve 406 to prevent axial displacement of the spring seat 430 relative to the second spring sleeve 406.

[0071] As previously described herein, the first helical end 401 of the torsion spring 402 is connectable to the bracket rotor 304, and the second helical end 432 of the torsion spring is connectable to the spring seat 430, thereby connecting to the gear hub 302 via the first spring sleeve 404 and the second spring sleeve 406. In this configuration, a torque load can be applied by the torsion spring 402 between the gear hub 302 and the bracket rotor 304.

[0072] Reference Figure 14 The bracket rotor 304 can be configured to interact with the eccentric shaft 14 of the internal combustion engine via the second gear 332 (see...). Figure 1 Rotary communication (e.g., coupled to eccentric shaft 14). The carrier rotor 304 includes a splined shaft 331 extending axially away from the end of the carrier rotor 304. The second gear 332 includes a splined recess 333, which is complementaryly formed to the splined shaft 331 and configured to receive therein for coupling to the splined shaft 331. In the non-limiting example shown, the second gear 332 is rotatably fixed to the carrier rotor 304 for rotation therewith. The carrier rotor 304 may also include at least one axial protrusion 337 configured to receive and engage an end of the torsion spring 402. In the non-limiting example shown, the carrier rotor 304 includes two axial protrusions 337 extending axially away from the end opposite the splined shaft 331. In the non-limiting example shown, the axial protrusions 337 extend into an internal cavity 418 formed by the spring sleeve 403 to engage the torsion spring 402 (see...). Figure 8 Axial protrusions 337 are circumferentially spaced apart (e.g., circumferentially spaced 180°) around the bracket rotor 304. In other non-limiting examples, the bracket rotor 304 may include more or fewer than two axial protrusions 337 arranged circumferentially around the bracket rotor. Each axial protrusion 337 includes a spring recess 339 extending axially into the axial protrusion 337. The spring recess 339 is configured to receive therein a first helical end 401 of a torsion spring 402 (see...). Figure 8 This allows the torsion spring 402 to apply torque to the bracket rotor 304.

[0073] The second gear 332 may include an arcuate protrusion 335 extending axially away from the second gear 332. The number of arcuate protrusions 335 may correspond to the number of arcuate recesses 323 in the gear hub 302 (see...). Figure 10 When assembling (see...) Figure 8 The splined shaft 331 of the carrier rotor 304 can be received within and extend through the shaft portion 325 of the gear hub 302. A second gear 332 can then be mounted on the splined shaft 331, such that the arcuate protrusion 335 of the second gear 332 is received within the arcuate recess 323 of the gear hub 302. The arcuate protrusion 335 of the second gear 332, connected to the carrier rotor 304, can engage the end of the arcuate recess 323 in the gear hub 302 to mechanically restrict the carrier rotor 304 (rotatably connected to the eccentric shaft 14) and the gear hub 302 (rotatably connected to the crankshaft 12, see...) Figure 1 The overall relative rotation between the eccentric shaft and the crankshaft is limited. This mechanically restricts the amount of relative rotation that can exist between the eccentric shaft and the crankshaft, because the end of the arcuate recess 323 in the gear hub 302 can act as a rotation end stop for the arcuate protrusion on the second gear 332 connected to the carrier rotor 304. In the event of failure of the mechanical phasing assembly 300, or if the rotary actuator fails, the rotary phasing system 10 can be protected from catastrophic failure, thereby protecting the internal combustion engine from catastrophic failure.

[0074] Reference Figure 14 Typically, the outer surface 336 of the bracket rotor 304 can engage with the locking assembly 310. It should be understood that alternative configurations are possible for the relative connection of the gear hub 302, bracket rotor 304, eccentric shaft 14, and crankshaft 12. For example... Figure 15-16 As shown, the star rotor 308 may include a plurality of arms 338 extending axially between a first cage ring 340 and a second cage ring 342. One of a plurality of locking assemblies 310 may be circumferentially arranged between each circumferentially adjacent pair of arms 338. The star rotor 308 may include a plurality of axial protrusions 344 extending axially away from its first surface 346. The number of axial protrusions 344 may correspond to a connecting ring 360 arranged between the first gear ring 200 of the planetary actuator 100 and the star rotor 308 (see...). Figure 17 The number of slots in the base 308. In the non-limiting example shown, the star rotor 308 may include two axial protrusions 344. In other non-limiting examples, the base 308 may include more or fewer than two protrusions 344. The star rotor 308 may also include an opening 347 extending through the first surface 346. The opening 347 is configured to receive an axial protrusion 337 extending from the carrier rotor 304.

[0075] Each locking assembly 310 may include a first locking feature 350, a second locking feature 352, and a corresponding locking feature support 353 that engages with a corresponding one of the first locking feature 350 and the second locking feature 352. The first locking feature 350 and the second locking feature 352 may be forced apart from each other by one or more biasing members 358. The biasing members 358 may be arranged between and engage with the corresponding pairs of locking feature supports 353, thereby forcing the first locking feature 350 and the second locking feature 352 apart from each other. Each illustrated locking assembly 310 may include a biasing member 358 in the form of a spring. In other embodiments, each locking assembly 310 may include more than one biasing member 358, and / or the biasing members 358 may be in the form of any feasible mechanical connection capable of forcing the first locking feature 350 and the second locking feature 352 apart from each other.

[0076] In the non-limiting example shown, the first locking feature 350 and the second locking feature 352 may be in the form of circular bearing rollers. It should be understood that the first locking feature 350 and the second locking feature 352 can be defined in any shape, capable of selectively locking and unlocking between the gear hub 302 and the carrier rotor 304. It should also be understood that alternative mechanisms to the first locking feature 350 and the second locking feature 352, other than bearings, are possible. For example, the first locking feature 350 and the second locking feature 352 may be in the form of wedge-shaped features.

[0077] Specific reference Figure 9 and 17 -18, the coupling assembly 330 may be arranged between the mechanical phasing assembly 300 and the planetary actuator 100. The coupling assembly 330 may include a coupling ring 360, one or more compliance members 348, one or more washers 349, and a retaining ring 351. When assembled (see...) Figure 18 The compliant member 348 and the washer 349 are received within the cavity 215 of the first gear ring 200. The compliant member 348 and the washer 349 are secured within the cavity 215 of the first gear ring 200 by a retaining ring 351 to prevent axial displacement of the compliant member relative to the first gear ring 200. The retaining ring 351 can be secured to the first gear ring 200 by insertion into a retaining ring groove 218 along the inner side of the cavity 215 (see...). Figure 3 The dimensions of the connecting ring 360 are set such that the first gear ring 200 can be received therein.

[0078] In the non-limiting example shown, the compliant member 348 may be coupled between the first gear ring 200 and the coupling ring 360, such that rotation of the first gear ring 200 is rotationally transmitted to the coupling ring 360. The coupling ring 360 is configured to transmit rotation from the first gear ring 200 to the star rotor 308. As will be described below, the rotational transmission between the first gear ring 200 and the coupling ring 360 may be provided by the compliant member 348, while also allowing rotation of the actuator 313 ( Figure 8 Input is provided to the planetary actuator 100 while the mechanical phasing assembly 300 is in a locked state.

[0079] The connecting ring 360 may define an annular sleeve having a hollow core 361. The connecting ring 360 includes a first set of axially recessed slots 362 and a second set of axially recessed slots 364. The number of slots 362 in the first set may correspond to the number of slots 216 in the first gear ring 200. In the non-limiting example shown, the first set of slots 362 includes two slots circumferentially spaced apart (e.g., circumferentially spaced 180°) around the outer surface 366 of the connecting ring 360. In other non-limiting examples, the first set of slots 362 may include more or fewer than two slots 362 arranged circumferentially around the outer surface 366 of the connecting ring 360 in any incremental manner, such that the slots 362 are circumferentially aligned with the slots 216 on the first gear ring 200.

[0080] When assembling (see...) Figure 18 The helical portion 368 of the compliant member 348 may be received within the cavity 215 of the first gear ring 200. A first end 370 and a second end 372 of the compliant member 348 may project radially outward from the helical portion 368 and extend through a slot 216 in the first gear ring 200 and a first set of slots 362 in the connecting ring 360. In some non-limiting examples, the compliant member 348 may be pre-biased such that its first end 370 and second end 372 extend circumferentially away from each other in a free state. For example, the first end 370 and the second end 372 of the compliant member 348 may extend away from each other to form a circumferential gap between them, which is larger in the free state compared to an assembled or compressed state.

[0081] When assembling (see...) Figure 18Furthermore, during steady-state operation where relative rotation is not desired, the first end 370 and the second end 372 of the compliant member 348 engage with the edges of the slots 216 in the first gear ring 200 and the edges of the first set of slots 362 in the connecting ring 360 to maintain rotational alignment between the first gear ring 200 and the connecting ring 360. In the non-limiting example shown, the edges of the slots 216 in the first gear ring 200 and the edges of the first set of slots 362 in the connecting ring 360 may define the same circumferential spacing, such that the openings formed by the first set of slots 362 and the slots 216 have the same circumferential width.

[0082] Continue to refer to Figure 17-18 The number of slots 364 in the second set may correspond to the number of axial protrusions 344 in the star rotor 308. In the non-limiting example shown, the second set of slots 364 includes two slots circumferentially spaced apart (e.g., circumferentially spaced 180°) around the outer surface 366 of the connecting ring 360. In other non-limiting examples, the second set of slots 364 may include more or fewer than two slots 364 arranged circumferentially around the outer surface 366 of the connecting ring 360 in any incremental manner, such that the slots 364 are circumferentially aligned with the axial protrusions 344 in the star rotor 308.

[0083] When assembling (see...) Figure 18 The axial protrusion 344 in the star rotor 308 engages with the second set of slots 364 in the connecting ring 360 to maintain rotational alignment between the star rotor 308 and the connecting ring 360. That is, the connecting ring 360 and the star rotor 308 are rotationally locked to each other. In the non-limiting example shown, the shape of the axial protrusion 344 is complementary to the second set of slots 364 in the connecting ring 360. See specifically... Figure 18 The coupling assembly 330 is arranged between the mechanical phasing assembly 300 and the planetary actuator 100. The first gear ring 200 can be rotatably coupled to the coupling ring 360 via the compliant member 348, and the coupling ring 360 can be rotatably coupled to the star rotor 308, but the first gear ring 200 may not be in direct contact with the star rotor 308. Therefore, due to the compliant member 348, the rotation or angular displacement between the star rotor 308 and the first gear ring 200 can be achieved by driving the rotary actuator 313 of the planetary actuator 100.

[0084] Reference Figure 18-19When the planetary actuator 100 is mounted onto the star rotor 308, the ends 370, 372 of each compliance member 348 extend radially outward and engage a corresponding one of the recessed slots 216 formed in the first gear ring 200 and the first set of slots 362 formed in the connecting ring 360. With the compliance members 348 mounted, the recessed slots 216 of the first gear ring 200 and the first set of slots 362 of the connecting ring 360 can each define a circumferential width to ensure that the ends 370, 372 of the compliance members 348 are biased against each other relative to their free state. Therefore, the pre-biasing of the compliance members 348 ensures that the force generated by the relative rotation between the first gear ring 200 and the star rotor 308 remains on the star rotor 308 until the star rotor 308 is rotatably aligned with the first gear ring 200 (i.e., not rotating relative to it).

[0085] A rotary actuator 313 is rotatably coupled to and controls the rotation of a first sun gear 202, which in turn controls the rotation of a first ring gear 200. Typically, a second ring gear 206 is configured to be rotatably coupled to a gear hub 302 via a spring sleeve 403 of a torsion spring assembly 400, such that the second ring gear 206 rotates together with the gear hub 302. In the non-limiting example shown, the second ring gear 206 may be fixed to a second spring sleeve 406, which is rotatably connected to the gear hub 302 via a first spring sleeve 404 to rotate with it.

[0086] In operation, the rotary actuator 313 can be configured to apply rotational displacement / torque to the first sun gear 202 to achieve a known rotational displacement of the first ring gear 200, corresponding to a known desired rotational displacement of the star rotor 308. The rotary actuator 313 can be controlled and powered by the engine control module (ECM) of the internal combustion engine.

[0087] During operation, the gear hub 302 can be coupled to the crankshaft 12 of the VCR internal combustion engine. The eccentric shaft 14 in the VCR internal combustion engine can be coupled to the carrier rotor 304. Therefore, the eccentric shaft 14 and the crankshaft 12 can be coupled together via a mechanical phasing assembly 300 to rotate together, wherein the rotational speed of the eccentric shaft 14 is half that of the crankshaft 12. The eccentric shaft 14 can be configured to change the compression ratio of the internal combustion engine during engine operation. During engine operation, the mechanical phasing assembly 300 can be used to change the rotational relationship of the eccentric shaft 14 relative to the crankshaft 12, which in turn changes the compression ratio (i.e., VCR), typically via a multi-link arrangement between the piston, crankshaft 12, and eccentric shaft 14. Changing the rotational relationship between the eccentric shaft 14 and the crankshaft 12 can be used to reduce engine emissions and / or improve engine efficiency / performance under given operating conditions.

[0088] When the engine is running and rotational adjustment of the eccentric shaft is not desired, the mechanical phasing assembly 300 can lock the rotational relationship between the gear hub 302 and the carrier rotor 304, thereby locking the rotational relationship between the eccentric shaft and the crankshaft. In this locked state (see, for example, see...) Figures 19-20 The rotary actuator 313 does not provide a rotational output to the input shaft 315 of the planetary actuator 100, and the first gear ring 200 and the second gear ring 206 rotate in unison with the gear hub 302. Therefore, the star rotor 308 does not rotate relative to the gear hub 302, and the first locking feature 350 and the second locking feature 352 of each locking assembly 310 can extend completely away from each other via the biasing member 358. As the first locking feature 350 and the second locking feature 352 extend completely away from each other, the first locking feature 350 and the second locking feature 352 can engage with at least one of the inner surface 359 of the gear hub 302 and the outer surface 336 of the carrier rotor 304, wedging the first locking feature 350 and the second locking feature 352 between the carrier rotor 304 and the gear hub 302 (see...). Figure 19 The wedge can lock or restrict the movement of the bracket rotor 304 relative to the gear hub 302 (i.e., the rotational position of the bracket rotor 304 relative to the gear hub 302 is locked). Therefore, when the mechanical phasing assembly 300 is in the locked state, the rotational relationship between the eccentric shaft 14 and the crankshaft 12 remains unchanged.

[0089] If it is desired to advance or delay the eccentric shaft relative to the crankshaft, the rotary actuator 313 can be instructed via the ECM to provide rotational displacement / torque to the planetary actuator 100 via the input shaft 315. The direction and magnitude of rotation of the input shaft 315 can be related to the rotation of the first ring gear 200 relative to the second ring gear 206. Since the second ring gear 206 is rotatably connected to the gear hub 302 via the spring sleeve 403, the first ring gear 200 can rotate relative to the gear hub 302. The desired magnitude and direction of the relative rotation applied to the first ring gear 200 can be rotatably transmitted to the star rotor 308 via the compliant member 348 and the coupling ring 360. For example, as the first ring gear 200 rotates, the slot 216 of the first ring gear 200 engages and circumferentially biases one of the ends 370, 372 of the compliant member 348 (depending on the direction of relative rotation). This circumferential bias of the compliant member 348 causes it to apply a corresponding force to the first set of slots 362 of the coupling ring 360, which is then transmitted via the second set of slots 364 to the protrusions 344 of the star rotor 308. The force applied to the star rotor 308 is held thereon by the compliant member 348 until the carrier rotor 304 reaches the desired rotational position relative to the gear hub 302, determined by the rotational input displacement / force provided by the rotary actuator 313. In other words, the force is held on the star rotor 308 until the carrier rotor 304 is rotatably aligned with the star rotor 308 and the mechanical phasing assembly 300 returns to the locked state.

[0090] While the mechanical phasing assembly 300 is locked, the compliant member 348 also allows the rotary actuator 313 to rotate. Figure 8 The planetary actuator 100 is supplied with input. For example, when the first gear ring 200 rotates (via the rotational input provided by the rotary actuator 313), Figure 8 The slot 216 of the first gear ring 200 engages and circumferentially biases one of the ends 370, 372 of the compliant member 348 (depending on the direction of relative rotation). This circumferential bias of the compliant member 348 allows the coupling ring 360 to remain rotationally fixed relative to the star rotor 308 while the first gear ring 200 rotates, which may occur simultaneously with the locking of the mechanical phasing assembly 300. When the mechanical phasing assembly 300 enters the unlocked state, the compliant member 348 maintains force on the first set of slots 362 of the coupling ring 360. The compliant member 348 then transmits this force via the second set of slots 364 to the protrusions 344 of the star rotor 308 until the carrier rotor 304 reaches the desired rotational position relative to the gear hub 302.

[0091] The rotational force applied to the star rotor 308 by the compliant member 348 can cause the arm 338 of the star rotor 308 to circumferentially displace, thereby engaging either the first locking feature 350 or the second locking feature 352, disengaging it from a locked or wedged position, while the other of the first locking feature 350 or the second locking feature 352 remains in the locked position. For example, the star rotor 308 can be rotated clockwise from the locked state (from...) Figure 19 The desired amount of rotation (angle). This rotation of the star rotor 308 can engage the first locking features 350 and rotate them clockwise to the unlocked position, wherein the first locking features 350 are displaced from engagement with the inner surface 359 of the gear hub 302 and the outer surface 336 of the bracket rotor 304. At the same time, the second locking feature 352 cannot be rotated and can remain in the locked position.

[0092] Unlocking the first locking feature 350 allows the carrier rotor 304 to rotate in the same direction as the rotation of the star rotor 308. Simultaneously, the locked position of the second locking feature 352 prevents the carrier rotor 304 from rotating in the opposite direction to the rotation of the star rotor 308. Therefore, in a non-limiting example where the star rotor 308 is clockwise biased, the unlocked position of the first locking feature 350 allows the carrier rotor 304 to rotate clockwise, while the locked position of the second locking feature 352 prevents the carrier rotor 304 from rotating counterclockwise. This allows the mechanical phasing assembly 300 to harvest energy from eccentric shaft torque pulses occurring in the same direction as the desired relative rotational input provided by the first gear ring 200 on the star rotor 308. Therefore, the planetary actuator 100 is configured to receive a rotational input from the rotary actuator 313 and, in response, provide an output to the star rotor 308 to selectively lock / unlock the relative rotation between the carrier rotor 304 and the gear hub 302.

[0093] For example, in a non-limiting example where the first gear ring 200 rotates clockwise to bias the star rotor 308, as an eccentric shaft torque pulse is applied clockwise to the carrier rotor 304, the carrier rotor 304 and the second locking feature 352 can rotate clockwise. Once the clockwise eccentric shaft torque pulse decreases, the carrier rotor 304 can be in a new rotational position relative to the gear hub 302, where the second locking feature 352 locks the carrier rotor 304 again until the next clockwise eccentric shaft torque pulse is applied to the carrier rotor 304. This process can continue until the carrier rotor 304 has rotated sufficiently so that the first locking feature 350 can return to the locked position. When this occurs, both the first locking feature 350 and the second locking feature 352 can be in the locked position and the mechanical phasing assembly 300 can return to the locked state. The star rotor 308 can then maintain its rotational position (until it is commanded again to change the rotational relationship of the eccentric shaft relative to the crankshaft) to ensure that the first locking feature 350 and the second locking feature 352 remain locked, thereby locking the angular position of the carrier rotor 304 relative to the gear hub 302. It should be understood that for counterclockwise rotation of the star rotor 308, the process will be reversed as described above.

[0094] In response to a given rotational input displacement / force applied to the star rotor 308 via the planetary actuator 100, the carrier rotor 304 rotates following the star rotor 308 and eventually reaches the predetermined final rotational position of the star rotor 308, regardless of the amplitude of the eccentric shaft torque pulse. That is, the compliance member 348 will maintain the input displacement / force provided to the star rotor 308 by the rotary actuator 313 via the planetary actuator 100 until the compliance member 348 no longer biases the star rotor 308, and the carrier rotor 304 rotates following to rotate the star rotor 308 relative to the gear hub 302 to the desired rotational position.

[0095] The rotation of the carrier rotor 304 relative to the gear hub 302 during this phasing process alters the rotational relationship between the eccentric shaft 14 and the gear hub 302, which in turn alters the rotational relationship between the eccentric shaft 14 and the crankshaft 12. As described above, for a given rotational input displacement / torque provided by the rotary actuator 313, the amount of rotation achieved by the star rotor 308 can be known based on the gear transmission between the first sun gear 202 and the first ring gear 200 and the resulting gear ratio defined between them. Furthermore, the mechanical phasing assembly 300 is designed so that the carrier rotor 304 is only allowed to rotate in the same direction as the star rotor 308. Therefore, during engine operation, the mechanical phasing assembly 300 can alter the rotational relationship between the eccentric shaft and the crankshaft, regardless of the engine speed and the direction and magnitude of the eccentric shaft torque pulses. Moreover, the mechanical phasing assembly 300 does not need to continuously cycle to achieve the desired rotational position (i.e., the desired rotational offset between the eccentric shaft and the crankshaft) because the carrier rotor 304 is constrained to follow the star rotor 308 to the desired position.

[0096] Typically, the planetary actuator 100 is designed and implemented to require only an input signal (i.e., the input torque / displacement provided from the rotary actuator 313 to the input shaft 315, and thus to the first sun gear 202) to rotate when a relative rotation is desired, rather than requiring the rotary actuator 313 to rotate continuously at the same speed as the eccentric shaft and gear hub 302. During steady-state operation, when relative rotation is not desired, the rotary actuator 313 and thus the input shaft 315 can be rotationally fixed (e.g., stationary). During phase changes (i.e., relative rotation), it is not necessary for the rotary actuator 313 and thus the input shaft 315 to rotate at the same speed as the eccentric shaft and gear hub 302. For example, the output provided by the rotary actuator 313 to the input shaft 315 and thus the first sun gear 202 may only need to rotate at the desired rate of change of relative angle. Thus, for example, the rotation (i.e., speed / displacement) of the input shaft 315 during phasing can be proportional to the magnitude of the desired relative rotation between the carrier rotor 304 and the gear hub 302. In this way, the power and speed required for the rotary actuator 313 to rotate the input shaft 315 and achieve the desired relative rotation can be independent of the engine speed. That is, the power and speed output by the rotary actuator 313 will not change due to variations in engine speed / eccentric shaft speed. Furthermore, in a non-limiting example, if a gear reducer exists between the input shaft 315 and the second gear ring 206, the gear reducer can reduce the magnitude of the torque required by the rotary actuator 313 to achieve the desired relative rotation.

[0097] Figure 20Another non-limiting example of a phasing system 1000 is shown. The phasing system 1000 is similar to the phasing system 10, having similar elements identified using the same reference numerals as indicated in 1000 (e.g., gear hub 302 is related to gear hub 1302), unless otherwise described herein or obvious from the drawings.

[0098] For example, similar to phasing system 10, phasing system 1000 is a planetary actuator 1100 mounted in a mechanical phasing assembly 1300. In the illustrated non-limiting example, the mechanical phasing assembly 1300 includes a gear hub 1302 (e.g., a first rotating component), a carrier rotor 1304 (e.g., a second rotating component), a star rotor 1308, multiple locking assemblies 1310, the planetary actuator 1100, and a torsion spring assembly 1400. The planetary actuator 1100, torsion spring assembly 1400, gear hub 1302, carrier rotor 1304, star rotor 1308, and multiple locking assemblies 1310 may each share a common central axis C during assembly. The torsion spring assembly 1400 may be configured to apply a torque load between the carrier rotor 1304 and the gear hub 1302. The torsion spring assembly 1400 may include a torsion spring 1402 and a spring sleeve 1403. The torsion spring assembly 1400 can be configured to rotatably secure the second gear ring 1206 to the gear hub 1302. The torsion spring assembly can also be configured to attach the end of the torsion spring 1402 to the gear hub 1302 by means of a spring sleeve 1403 and a spring seat 1430 connected thereto.

[0099] In the illustrated non-limiting example, the mechanical phasing assembly 1300 may include one or more bearings 1317 configured to rotatably support internal components of the mechanical phasing assembly, or to rotatably support the mechanical phasing assembly 1300 relative to components of the engine. In the illustrated non-limiting example, the bearings 1317 are arranged along an axis extending from the carrier rotor 1304. According to some non-limiting examples, one or more thrust bearings 1317a may be arranged adjacent to the first gear 1311 and / or the second gear 1332, particularly when the first gear 1311 or the second gear 1332 is configured as a helical gear. Additional bearings 1317 are arranged along the outer side of the gear hub 1302.

[0100] Reference Figure 21-22 The spring sleeve 1403 is constructed as a single-piece spring sleeve. The following figures show sub-assemblies of various aspects of the phasing system 1000, and it should be understood that some components (e.g., planetary actuator 1100 and / or gear hub 1302) may not be shown to improve clarity of the aspects to be described.

[0101] Spring sleeve 1403 may include a flange 1412 and an annular protrusion 1414. The annular protrusion 1414 may extend axially away from the flange 1412 to define an internal cavity 1418. Spring sleeve 1403 may have one or more slits 1420a, 1420b extending axially along a portion of the annular protrusion 1414. Slit 1420a may also include a slot 1421 extending axially along the length of the annular protrusion 1414 from slit 1420a to a distal end of spring sleeve 1403 opposite the flange 1412. Slit 1420a forms an opening configured to receive a first helical end (not shown) of torsion spring 1402 through it to allow assembly of torsion spring 1402 therewith. Slits 1420a, 1420b together may provide clearance for an axial protrusion 1337 extending from the carrier rotor 1304 during rotation from a phasing event.

[0102] Spring sleeve 1403 may include a fourth spring support 1451 that projects axially away from the flange 1412 of spring sleeve 1403. The fourth spring support 1451 is arranged radially outward of torsion spring 1402. In the non-limiting example shown, the fourth spring support 1451 extends circumferentially along spring seat 1430 to form an arcuate protrusion defining a radius of curvature that shares the same center as the radius of curvature defined by the helical portion of torsion spring 1402. Similar to the first spring support 1433, the second spring support 1437, and the third spring support 1439, the fourth spring support 1451 may be configured to prevent stress rise in torsion spring 1402 and to prevent lateral loads between components cooperating with torsion spring 1402. For example, the fourth spring support 1451 may engage the exterior of torsion spring 1402 adjacent to the first helical end opposite spring seat 1430 to prevent lateral loads.

[0103] In the non-limiting example shown, the spring sleeve 1403 may include a plurality of first slots 1428, and the spring seat 1430 coupled to the spring sleeve 1403 may include a plurality of second slots 1434 complementary to the first slots 1428, such that the spring seat 1430 is rotatably fixed to the second spring sleeve to rotate therewith. In the non-limiting example shown, the second slots 1434 extend axially through a third spring support 1439 on the spring seat 1430. See particularly Figure 22During assembly, the spring seat 1430 can be rotatably aligned with the spring sleeve 1403 such that at least one of the first slots 1428 is aligned with at least one of the second slots 1434, such that the first slots 1428 and the second slots 1434 together form a keyway to receive a key 1435 therein. The key 1435 is configured to rotatably secure the spring seat 1430 to the spring sleeve 1403. An annular ring 1436 can be received within the opening formed by the spring seat 1430 to prevent axial displacement of the key 1435 relative to the spring seat 1430.

[0104] As shown in the figure, the first helical end 1401 of the torsion spring 1402 can be connected to the bracket rotor 1304, and the second helical end 1432 of the torsion spring can be engaged by the spring seat 1430, thereby engaging the gear hub 1302 via the spring sleeve 1403 (see figure). Figure 20 In this configuration, the torque load can be applied by the torsion spring 1402 between the gear hub 1302 and the bracket rotor 1304.

[0105] Now refer to Figure 23-24 The star rotor 1308 of the mechanical phasing assembly 1300 may include a plurality of arms 1338 extending axially between a first cage ring 1340 and a second cage ring 1342, and one of a plurality of locking assemblies 1310 may be circumferentially arranged between each pair of circumferentially adjacent arms 1338. In the non-limiting example shown, the star rotor 1308 may include an oil passage 1380 integrally formed into the star rotor 1308. The oil passage 1380 is configured to receive oil at an inlet 1382 and to distribute the oil to one or both components of the mechanical phasing assembly 1300 or the planetary actuator 1100 via at least one outlet. In the non-limiting example shown, the oil passage 1380 includes a first outlet 1384 extending axially away from a first surface 1346 of the star rotor 1308 and guided at the planetary actuator 1100 (see also...). Figure 20 The oil passage 1380 also includes a second outlet 1386 defined by a conduit formed along and guided radially outward from the star rotor 1308 on a first surface 1346. In the non-limiting example shown, the second outlet 1386 is arranged orthogonally to the first outlet 1384.

[0106] The star rotor 1308 may also include an arcuate protrusion 1335 extending axially away from the first surface 1346 of the star rotor 1308. When assembled (see...) Figure 24The spring sleeve 1403 can be mounted onto the gear hub 1302, such that the arcuate protrusion 1335 of the star rotor 1308 is received within the opening 1420a of the spring sleeve 1403. The arcuate protrusion 1335 of the star rotor 1308 can engage the end of the opening 1420a in the spring sleeve to mechanically restrict the bracket rotor 1304 (rotatably connected to the eccentric shaft 14) and the gear hub 1302 (rotatably connected to the crankshaft 12, see...) Figure 1 The overall relative rotation between the eccentric shaft and the crankshaft can be mechanically limited, as the end of the opening 1420a in the spring sleeve 1403 can act as a rotation end stop for the arcuate protrusion 1335 on the star rotor 1308, which follows the rotation of the bracket rotor 1304.

[0107] In the following operational description, reference will be made to rotating phasing system 10. It should be understood that the following description also applies to rotating phasing system 1000. Now refer to... Figure 25 It can be seen that torsion springs 402 and 1402 can be configured to apply offset torque within the rotating phasing system 10 and 1000. That is, by applying a torque difference across the gear hub 302 and the carrier rotor 304, torsion spring 402 can counteract the net torque caused by torque pulses from the eccentric shaft or between the eccentric shaft and the crankshaft (i.e., between the first gear 311 on the gear hub 302 and the second gear 332 attached to the carrier rotor 304). For example, a torque pulse from the eccentric shaft can result in a net torque applied between the gear hub 302 and the carrier rotor 304 in a first direction (i.e., a net positive torque pulse). Torsion spring 402 can be configured to apply a torque load between the gear hub 302 and the carrier rotor 304 in a second direction opposite to the first direction (i.e., a negative torque). The torque load delivered by the torsion spring 402 can counteract the net positive torque pulse between the gear hub 302 and the carrier rotor 304 in the second direction (e.g., causing a vertical displacement or offset of the torque pulse from the eccentric shaft, as shown). Figure 25 (Vertical shift of the pulse curve in the image). It should be understood that positive or negative torque is a relative term depending on the angle of the load condition being analyzed; therefore, positive and negative terms can be interchanged. Furthermore, it should be understood that a torsion spring can be constructed or mounted to provide torque in any direction, as long as it counteracts the torque pulses from the eccentric shaft.

[0108] In some applications, such as Figure 20 As illustrated in the non-limiting example, a torque pulse applied to the carrier rotor 304 from the eccentric shaft may not result in a net zero or bidirectional torque pulse between the carrier rotor 304 and the gear hub 302. In some cases, this may prevent the mechanical phasing assembly from achieving bidirectional locking functionality because the torque pulse (e.g., net torque) must be applied in both directions (i.e., positive and negative / must be applied in both directions). Figure 25(passing zero on the y-axis) to more effectively lock the bracket rotor 304 to the gear hub 302 via the "wedge" action of the locking assembly 310.

[0109] like Figure 25 As shown, the arrangement of the torsion spring 402 can apply an offset torque within the mechanical phasing assembly 300. The torque load applied by the torsion spring 402 results in a constant torque load being applied between the gear hub 302 and the carrier rotor 304, which counteracts the torque pulses from the eccentric shaft. In the non-limiting example shown, the torque load applied by the torsion spring 402 is unidirectional. The offset torque load applied by the torsion spring 402 can counteract the net torque load experienced by the mechanical phasing assembly 300 (i.e., including the eccentric shaft torque pulses), such that the net torque experienced by the mechanical phasing assembly 300 is bidirectional (i.e., in...). Figure 25 (The y-axis passes zero). Therefore, the torsion spring 402 enables the mechanical phasing assembly to achieve a bidirectional locking function, more effectively locking the carrier rotor 304 to the gear hub 302 via the "wedge" action of the locking assembly 310. This is particularly relevant in cases such as some VCR internal combustion engines, where the net torque pulse delivered by the eccentric shaft may be net positive or net negative. In some non-limiting examples, the torsion spring 402 can apply a linear offset to the eccentric shaft torque pulse. In other non-limiting examples, the torsion spring 402 can apply a constant unidirectional torque load.

[0110] In some non-limiting examples, the torsion spring 402 may be pre-biased (e.g., preloaded). For example, see reference... Figure 11 and 22 Spring seats 430 and 1430 can be rotated and locked with spring sleeves 403 and 1403 in multiple different positions. Each of these multiple different positions defines a unique torque load provided by torsion springs 402 and 1402, which determines the magnitude of the pre-bias of torsion springs 402 and 1402. The pre-bias of torsion springs 402 and 1402 can be adjusted based on the rotational position of spring seats 430 and 1430 relative to bracket rotors 304 and 1304 (see [reference]). Figure 9 , 11 And 22). That is, the positions of the spring seats 430, 1430 relative to the spring sleeves 403, 1403 can be adjusted by means of the first slots 428, 1428 and the second slots 434, 1434 thereon. For example, see specifically... Figure 11The torsion spring assembly 400, wherein the pre-biasing of the torsion spring 402 can be set by connecting the first helical end 401 of the torsion spring 402 to the carrier rotor 304. The opposing second helical end 432 of the torsion spring 402 can then be connected to the spring seat 430. The spring seat 430 can then be rotated relative to the spring sleeve 403 to a position providing the desired preload on the torsion spring. At this point, at least one of the plurality of first slots 428 on the spring sleeve 403 can be selectively aligned with at least one of the plurality of second slots 434 on the spring seat 430. Once selectively aligned, the first slots 428 and second slots 434, configured as splines in this example, can engage with each other to rotatably lock the spring sleeve 403 to the spring seat 430. In the non-limiting example shown, the plurality of splines of the first slot 428 engage with the plurality of splines of the second slot 434.

[0111] For example, the torsion spring assembly 400 can be assembled in a first orientation, wherein the first helical end 401 of the torsion spring 402 is mounted in a spring groove 339 on the bracket rotor 304, and the second helical end of the torsion spring 402 can be mounted in a spring seat 430. In the first orientation, the spring seat 430 can be in a first rotational position relative to the spring sleeve 403, thereby defining a first torque load (in some cases, a zero torque load). Then, by rotating the spring seat 430 relative to the spring sleeve 403, the torsion spring assembly 400 can be adjusted to a second rotational position among a plurality of possible rotational positions, while the second slot 434 of the spring seat 430 disengages from the first slot 428 on the spring sleeve 403. The second slot 434 of the spring seat 430 can then re-engage with the first slot 428 on the spring sleeve 403, thereby securing the spring seat 430 in the second rotational position defining the second torque load.

[0112] In some non-limiting examples, the torsion spring 402 can apply a torque load between approximately 5 Nm and approximately 200 Nm. In other non-limiting examples, the torsion spring 402 can apply a torque load between approximately 20 Nm and approximately 100 Nm. In some non-limiting examples, the torsion spring 402 can apply a torque load between approximately 40 Nm and approximately 80 Nm. The arrangement of the first slot 428 and the second slot 434 can provide rotational adjustment between the spring sleeve 403 and the spring seat 430 between approximately 1 degree and approximately 10 degrees. In some non-limiting examples, the slots can provide rotational adjustment between approximately 3 degrees and approximately 5 degrees. In some non-limiting examples, two or more spring seats 430 can be provided, each having multiple slots slightly offset from the other spring seats, to further improve the rotational adjustment capability.

[0113] Similarly, special reference Figure 22 The torsion spring assembly 1400, wherein the pre-biasing of the torsion spring 1402 can be set by connecting the first helical end 1401 of the torsion spring 1402 to the bracket rotor 1304. Then, the opposing second helical end 1432 of the torsion spring 1402 can be connected to the spring seat 1430. The spring seat 1430 can then be rotated relative to the spring sleeve 1403 to a position providing the desired preload on the torsion spring. At this point, at least one of the plurality of first slots 1428 on the spring sleeve 1403 can be selectively aligned with at least one of the plurality of second slots 1434 on the spring seat 1430. Once selectively aligned, one slot from each of the first slots 1428 and the second slots 1434 together form a keyway, into which a key 1435 can be inserted to rotatably lock the spring sleeve 1403 to the spring seat 1430. In the non-limiting example shown, only one slot from the plurality of first slots 1428 is aligned with only one slot from the plurality of second slots 1434. That is, in any given rotational orientation of the spring seat 1430, only a single first slot 1428 can be aligned with a single second slot 1434.

[0114] In some non-limiting examples, the torque load applied by the torsion springs 402, 1402 may depend on the relative rotational offset between the first gear rings 200, 1200 and the second gear rings 206, 1206. That is, particularly referring to... Figure 11 As the first gear ring 200 rotates relative to the second gear ring 206 via the rotary actuator 313, the star rotor 308, connected to the first helical end 401 of the torsion spring 402, rotates from the spring seat 430, connected to the second helical end 432 of the torsion spring 402 (see...). Figure 8 The rotational displacement between the first helical end 401 and the second helical end 432 of the torsion spring 402 alters the torque load delivered from it. This also applies to... Figure 22 Torsion spring assembly 1400.

[0115] Now refer to Figure 11 and 21 In some non-limiting examples, the mechanical phasing assembly 300 can be mechanically limited to a predefined phase angle or rotational offset range. In the non-limiting example shown, the gear hub 302 and the carrier rotor 304 can rotate from a minimum phase angle (e.g., a phase angle of 0°) to a maximum phase angle (e.g., a phase angle of 60°, such as...). Figure 21(As shown, -30° to +30°). When the phase angle between the gear hub 302 and the carrier rotor 304 is at its minimum phase angle, the VCR internal combustion engine can be configured in a high compression ratio (CR) configuration, while when the phase angle between the gear hub 302 and the carrier rotor 304 is at its maximum phase angle, the VCR internal combustion engine can be configured in a low CR configuration. As mentioned above, the torque load applied by the torsion spring 402 can depend on the phase angle. As the phase angle increases, the torque load applied by the torsion spring 402 may also increase. Therefore, when the VCR internal combustion engine is in a high CR configuration (i.e., at the minimum phase angle), the torque load applied by the torsion spring 402 can be at its minimum torque load, and as the phase angle increases toward the maximum phase angle, the torque load provided by the torsion spring 402 also increases toward the maximum torque load. In some non-limiting examples, the torsion spring 402 can hold the mechanical phasing assembly 300 such that there is a 0° phase angle between the gear hub 302 and the carrier rotor 304. That is, the torsion spring 402 is configured to bias the phasing system 10 toward the minimum phase angle configuration. Therefore, the torsion spring 402 can keep the VCR internal combustion engine in a high CR configuration. This also applies to... Figure 22 Torsion spring assembly 1400.

[0116] In this specification, embodiments are described in a manner that allows for clear and precise description, but it is intended and will be understood that these embodiments can be combined or separated in various ways without departing from the invention. For example, it should be understood that all preferred features described herein are applicable to all aspects of the invention described herein.

[0117] The full disclosure of each patent and publication cited herein is incorporated herein by reference, just as each patent or publication is incorporated herein by reference individually.

Claims

1. A variable compression ratio (VCR) phasing system for altering a rotational relationship between a crankshaft and an eccentric shaft, the system comprising: a gear hub configured to be rotationally coupled with the crankshaft; a carrier rotor configured to be rotationally coupled with the eccentric shaft; a star rotor disposed between the gear hub and the carrier rotor and configured to selectively lock and unlock relative rotation between the gear hub and the carrier rotor; a planetary actuator coupled to the gear hub and the star rotor, the planetary actuator configured to receive a rotational input to provide an output to the star rotor to unlock relative rotation between the carrier rotor and the gear hub; and a torsion spring coupled between the gear hub and the carrier rotor, wherein the torsion spring is configured to exert a torque load in a first direction between the gear hub and the carrier rotor to counteract a torque load exerted in a second direction by either of the eccentric shaft or the crankshaft. The torque load is between 5 Nm and 200 Nm.

2. The system of claim 1, wherein, Further comprising a spring sleeve coupled to the gear hub, wherein the spring sleeve extends axially away from the gear hub and defines an interior cavity.

3. The system of claim 1, wherein, A helical portion of the torsion spring extends circumferentially around an outer side of the spring sleeve.

4. The system of claim 3, wherein, The planetary actuator is received within the interior cavity of the spring sleeve.

5. The system of claim 3, wherein, The torsion spring includes a first helical end and a second helical end opposite the first helical end, 6. The system of claim 3, wherein, wherein the first helical end of the torsion spring engages the carrier rotor and the second helical end engages a spring seat coupled to the spring sleeve. The carrier rotor includes at least one protrusion that extends axially into the interior cavity of the spring sleeve, the at least one protrusion including a recess configured to receive the first helical end of the torsion spring.

7. The system of claim 6, wherein, The spring seat is rotatably lockable with the spring sleeve at a plurality of different positions, such that each of the plurality of different positions defines a unique torque load from the torsion spring.

8. The system of claim 6, wherein, The spring sleeve includes a first plurality of slots and the spring seat includes a second plurality of slots, 9. The system of claim 8, wherein, such that selective alignment between at least one of the first plurality of slots and at least one of the second plurality of slots rotatably locks the spring sleeve to the spring seat. The first plurality of slots and the second plurality of slots are configured as splines that are configured to mesh with one another.

10. The system of claim 9, wherein, Only one of the first plurality of slots is aligned with only one of the second plurality of slots.

11. The system of claim 9, wherein, The at least one of the first plurality of slots and the at least one of the second plurality of slots, when aligned, together form a keyway configured to receive a key.

12. The system of claim 9, wherein, 13. A phasing system for altering a rotational relationship between a first rotating component and a second rotating component, the phasing system comprising: a gear hub; a carrier rotor; a star rotor disposed between the gear hub and the carrier rotor and configured to selectively lock and unlock relative rotation between the gear hub and the carrier rotor; ​ a torsion spring coupled between the gear hub and the carrier rotor, wherein the torsion spring is configured to apply a torque load between the gear hub and the carrier rotor; and a planetary actuator coupled to the gear hub and the star rotor, the planetary actuator operable between a steady state mode in which relative rotation between the gear hub and the carrier rotor is inhibited and a phasing mode in which the planetary actuator receives a rotational input at a predetermined amplitude to selectively provide relative rotation between the gear hub and the carrier rotor.

14. The system of claim 13, wherein, Further comprising a spring sleeve coupled to the gear hub, wherein the spring sleeve extends axially away from the gear hub.

15. The system of claim 14, wherein, the torsion spring includes a first helical end and a second helical end opposite the first helical end, wherein the first helical end of the torsion spring is engaged with the carrier rotor and the second helical end is engaged with a spring seat coupled to the spring sleeve.

16. The system of claim 15, wherein, the spring seat is rotatably lockable with the spring sleeve at a plurality of different positions such that each position of the plurality of different positions defines a unique torque load from the torsion spring.

17. The system of claim 16, wherein, the spring sleeve includes a plurality of first slots and the spring seat includes a plurality of second slots, such that selective alignment between at least one first slot of the plurality of first slots and at least one second slot of the plurality of second slots rotatably locks the spring sleeve to the spring seat.

18. The system of claim 17, wherein, the at least one first slot and the at least one second slot, when aligned, together form a keyway configured to receive a key.

19. A variable compression ratio (VCR) phasing system for altering a rotational relationship between a crankshaft and an eccentric shaft, the system comprising: a gear hub configured to be rotationally coupled with a crankshaft; a carrier rotor configured to be rotationally coupled with an eccentric shaft; a star rotor disposed between the gear hub and the carrier rotor and configured to receive an input to selectively lock and unlock relative rotation between the gear hub and the carrier rotor; a spring sleeve coupled to the gear hub and rotationally fixed with the gear hub; and a torsion spring coupled between the gear hub and the carrier rotor, wherein the torsion spring is configured to apply a torque load between the gear hub and the carrier rotor, wherein a preload of the torsion spring is set by: coupling a first end of the torsion spring to the carrier rotor; coupling an opposite second end of the torsion spring to a spring seat; and rotating the spring seat relative to the spring sleeve to selectively align at least one first slot of a plurality of first slots disposed on the spring sleeve with at least one second slot of a plurality of second slots disposed on the spring seat, wherein selective alignment of the at least one first slot and the at least one second slot is configured to rotatably lock the spring sleeve to the spring seat. ​ 20. The system of claim 19, wherein, when the phase angle between the gear hub and the carrier rotor is at a minimum phase angle, the torque load provided by the torsion spring is at a minimum torque load; and wherein the torque load provided by the torsion spring increases as the phase angle between the gear hub and the carrier rotor increases.

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