Variable shunt phase shifter with pressure relief mechanism

Abstract

A variable shunt phase shifter includes a housing that rotates with a rotor shaft. The housing includes a shell, a gear plate, a back plate coupled to form an enclosed space. Rotation of the housing creates a pressure differential between an outer diameter of the housing and an inner diameter of the housing. An inner rotor within the enclosed space rotates relative to the shell. A pressure relief hole is located in the back plate at the outer diameter. A vane is coupled to an outer portion of the inner rotor, outside of the housing, and is rotatable relative to the back plate. An escape hole is in the vane. Rotation of the inner rotor relative to the shell moves the escape hole to align with the pressure relief hole to open the pressure relief hole, reducing the pressure differential within the enclosed space.

Description

Technical Field

[0001] This subject matter discloses electric motors for electric vehicles, and more particularly, a variable shunt phase shifter used in the electric motor and a method for mitigating pressure imbalances within the variable shunt phase shifter caused by centrifugal pressure effects at high motor speeds. Background Technology

[0002] Electric vehicles include electric motors with rotors and stators. The rotor generates a rotor magnetic field, and the stator generates a stator magnetic field. At high motor speeds, a back electromotive force (EMF) is generated due to the interaction of the rotor and stator magnetic fields. A variable shunt phaser (VSP) is used to change the phase relationship between the rotor and stator to reduce this back EMF. The VSP is connected to the rotor. The VSP includes a housing and an inner rotor configured to rotate within the housing. Increasing the pressure within the chamber of the VSP changes the relative angular position of the inner rotor with respect to the housing. Recent advancements in electric motors allow the motor and VSP to operate at speeds exceeding 20,000 rpm. Above a certain threshold (typically around 6,000 rpm), a significant pressure differential appears within the VSP. This pressure differential affects the structural integrity of the VSP, thereby impacting the operation of the motor. Therefore, it is desirable to provide a method for reducing the pressure differential within the VSP. Summary of the Invention

[0003] In one exemplary embodiment, a variable shunt phase shifter is disclosed. The variable shunt phase shifter includes a housing configured to rotate with the rotor shaft of an electric motor of an electric vehicle. The housing includes a casing, a gear plate, and a back plate connected to form an enclosed space within the housing, wherein rotation of the housing generates a pressure difference between the outer diameter and the inner diameter of the housing. An inner rotor is disposed within the enclosed space and configured to rotate relative to the casing. A pressure relief hole is located in the back plate at the outer diameter of the casing. Blades are connected to an outer portion of the inner rotor, wherein the blades are outside the casing and rotatable relative to the back plate. An escape hole is located in the blades. Rotation of the inner rotor relative to the casing causes the escape hole to move to align with the pressure relief hole to open the pressure relief hole, thereby reducing the pressure difference within the enclosed space.

[0004] In addition to one or more features described herein, the vent is located at the back plate, and the escape hole is in the same radial position as the vent.

[0005] In addition to one or more features described herein, the blade includes a first seal at a first circumferential side of the escape orifice and a second seal at a second circumferential side of the escape orifice.

[0006] In addition to one or more features described herein, the variable shunt phase shifter also includes a channel extending radially through the housing, and the inner rotor includes blades that rotate within the housing.

[0007] In addition to one or more features described herein, the variable shunt phaser also includes a seat and a ball within the channel, the ball being radially inwardly biased against the seat by a spring, wherein the ball moves away from the seat when the pressure within the enclosed space reaches a critical pressure defined by the spring.

[0008] In addition to one or more features described herein, the variable shunt phaser also includes a disc valve configured to slide radially along the housing and be biased above the channel, wherein the disc valve moves radially along the housing when the pressure within the enclosed space reaches a critical pressure.

[0009] In addition to one or more features described herein, the angular rotation range of the inner rotor is defined by the circumferential width of the internal chamber in the enclosed space.

[0010] In another exemplary embodiment, an electric motor for an electric vehicle is disclosed. The motor includes a rotor shaft and a variable shunt phase shifter rotatable with the rotor shaft. The variable shunt phase shifter includes a housing configured to rotate with the rotor shaft, the housing including a casing, a gear plate, and a back plate, the gear plate and back plate being coupled to form an enclosed space within the housing, wherein rotation of the housing generates a pressure difference between the outer diameter and the inner diameter of the housing, an inner rotor disposed within the enclosed space, the inner rotor being configured to rotate relative to the casing, a pressure relief hole in the back plate at the outer diameter of the housing, blades coupled to an outer portion of the inner rotor, wherein the blades are outside the housing and rotatable relative to the back plate, and escape holes in the blades, wherein rotation of the inner rotor relative to the casing causes the escape holes to move to align with the pressure relief holes to open the pressure relief holes, thereby reducing the pressure difference within the enclosed space.

[0011] In addition to one or more features described herein, the vent is located at the back plate, and the escape hole is in the same radial position as the vent.

[0012] In addition to one or more features described herein, the blade includes a first seal at a first circumferential side of the escape orifice and a second seal at a second circumferential side of the escape orifice.

[0013] In addition to one or more features described herein, the motor also includes a channel extending radially through the housing, and the inner rotor includes blades that rotate within the housing.

[0014] In addition to one or more features described herein, the electric motor also includes a ball within a valve seat and a passageway, the ball being radially inwardly biased against the valve seat by a spring, wherein the ball moves away from the valve seat when the pressure within the enclosed space reaches a critical pressure defined by the spring.

[0015] In addition to one or more features described herein, the motor also includes a disc valve configured to slide radially along the housing and biased above the channel, wherein the disc valve moves radially along the housing when the pressure within the enclosed space reaches a critical pressure.

[0016] In addition to one or more features described herein, the angular rotation range of the inner rotor is defined by the circumferential width of the internal chamber in the enclosed space.

[0017] In yet another exemplary embodiment, an electric power system is disclosed. The electric power system includes a stator, a rotor, and a variable shunt phase shifter that rotates with the rotor to control timing between the stator and the rotor. The variable shunt phase shifter includes a housing configured to rotate with the rotor, the housing including a casing, a gear plate, and a back plate connected to form an enclosed space within the housing, wherein rotation of the housing generates a pressure differential between the outer diameter and the inner diameter of the housing, an inner rotor disposed within the enclosed space, the inner rotor being configured to rotate relative to the casing, a pressure relief orifice in the back plate at the outer diameter of the casing, blades connected to an external portion of the inner rotor, wherein the blades are outside the casing and rotatable relative to the back plate, and escape orifices in the blades, wherein rotation of the inner rotor relative to the casing causes the escape orifices to move to align with the pressure relief orifices to open the pressure relief orifices, thereby reducing the pressure differential within the enclosed space.

[0018] In addition to one or more features described herein, the vent is located at the back plate, and the escape hole is in the same radial position as the vent.

[0019] In addition to one or more features described herein, the blade includes a first seal at a first circumferential side of the escape orifice and a second seal at a second circumferential side of the escape orifice.

[0020] In addition to one or more features described herein, the power system also includes a channel extending radially through the housing, and the inner rotor includes blades that rotate within the housing.

[0021] In addition to one or more features described herein, the power system also includes a valve seat and a ball within a passage, the ball being radially inwardly biased against the valve seat by a spring, wherein the ball moves away from the valve seat when the pressure within the enclosed space reaches a critical pressure defined by the spring.

[0022] In addition to one or more features described herein, the power system also includes a disc valve configured to slide radially along the housing and biased above the passage, wherein the disc valve moves radially along the housing when the pressure within the enclosed space reaches a critical pressure.

[0023] The above-described features and advantages, as well as other features and advantages, of this disclosure will become apparent when taken in conjunction with the accompanying drawings and the following detailed description. Attached Figure Description

[0024] Other features, advantages, and details appear by way of example only in the following detailed description, which is described in detail with reference to the accompanying drawings, wherein:

[0025] Figure 1 An embodiment of a vehicle according to an exemplary embodiment is shown;

[0026] Figure 2 It is a partial exploded view of a portion of the vehicle's electric motor;

[0027] Figure 3 This is an external perspective view showing the variable split phase shifter (VSP);

[0028] Figure 4 A perspective view of the interior of the VSP is shown;

[0029] Figure 5 The first side of the rotary valve of the VSP is shown in one embodiment;

[0030] Figure 6 The second side of the rotary valve in the embodiment is shown;

[0031] Figure 7 An external view of the VSP is shown, with the rotary valve in a partially rotated position;

[0032] Figure 8 A view inside the VSP at its maximum hinge angle is shown;

[0033] Figure 9 This is a view of the interior of the VSP in the embodiment;

[0034] Figure 10 It is along a structure Figure 9 An axial view of the cross-section of the housing in an embodiment;

[0035] Figure 11 Is along another configuration Figure 9 An axial view of the cross section of the VSP in an embodiment;

[0036] Figure 12 It is used in yet another configuration. Figure 9An axial view of the cross section of the VSP in an embodiment;

[0037] Figure 13 It is used in yet another configuration. Figure 9 An axial view of the cross section of the VSP in the embodiment; and

[0038] Figure 14 This is a view of the interior of the VSP in another embodiment. Detailed Implementation

[0039] The following description is exemplary in nature only and is not intended to limit this disclosure, its application, or use. It should be understood that throughout the drawings, corresponding reference numerals denote the same or corresponding parts and features.

[0040] According to an exemplary embodiment, Figure 1 An embodiment of vehicle 10 is shown, which includes a body 12 that at least partially defines a passenger compartment 14. The body 12 also supports various vehicle subsystems, including a propulsion system 16 and other subsystems to support the functions of the propulsion system 16 and other vehicle components, such as a braking subsystem, a suspension system, a steering subsystem, etc.

[0041] Vehicle 10 may be an electric vehicle (EV), a hybrid vehicle, or any other vehicle. In one embodiment, vehicle 10 is an electric vehicle that includes multiple electric motors and / or drive systems. In an alternative embodiment, vehicle 10 may be an internal combustion engine vehicle, a hybrid vehicle, etc. Any number of drive units may be included, such as one or more drive units for applying torque to the front wheels (not shown) and / or the rear wheels (not shown). The drive units are controllable to operate vehicle 10 in various operating modes, such as normal mode, high-performance mode (where additional torque is applied), all-wheel drive (“AWD”), front-wheel drive (“FWD”), rear-wheel drive (“RWD”), etc.

[0042] For example, propulsion system 16 is a multi-drive system that includes a front drive unit 20 for driving the front wheels and a rear drive unit for driving the rear wheels. The front drive unit 20 includes a front motor 22 and a front inverter 24 (e.g., a front power inverter module or FPIM), as well as other components such as a cooling system. The left rear drive unit 30L includes a left rear motor 32L and a left rear inverter 34L. The right rear drive unit 30R includes a right rear motor 32R and a right rear inverter 34R. The front inverter 24, left rear inverter 34L, and right rear inverter 34R (e.g., a power inverter unit or PIM) each convert direct current (DC) power from the high-voltage (HV) battery system 40 into multiphase (e.g., two-phase, three-phase, six-phase, etc.) alternating current (AC) power to drive the front motor 22, left rear motor 32L, and right rear motor 32R.

[0043] like Figure 1 As shown, the drive system has a separate electric motor. However, the embodiments are not limited to this. For example, instead of a separate electric motor, multiple drives can be provided by a single machine with multiple physically independent sets of windings.

[0044] For example Figure 1 As shown, the drive system is configured such that the front motor 22 drives the front wheels (not shown), and the left rear motor 32L and the right rear motor 32R drive the rear wheels (not shown). However, the embodiment is not limited to this, as any number of drive systems and / or motors (e.g., a motor driving each wheel, dual motors per axle, etc.) can be present in various locations. Furthermore, the embodiment is not limited to a dual drive system, as it can be used with vehicles having any number of motors and / or power inverters.

[0045] In the propulsion system 16, the front drive unit 20, the left rear drive unit 30L, and the right rear drive unit 30R are electrically connected to the battery system 40. The battery system 40 may also be electrically connected to other electrical components (also referred to as “electrical loads”), such as vehicle electronics (e.g., via an auxiliary power module or APM 42), heaters, cooling systems, etc. The battery system 40 may be configured as a rechargeable energy storage system (RESS).

[0046] In one embodiment, the battery system 40 includes a plurality of individual battery components, each of which can be charged independently and can be used to independently power one or more drive systems. For example, the battery system 40 includes a first battery pack 44 connected to a front inverter 24, and a second battery pack 46. The first battery pack 44 includes a first plurality of battery modules 48, and the second battery pack 46 includes a second plurality of battery modules 50. Each of the first plurality of battery modules 48 and the second plurality of battery modules 50 includes a plurality of individual batteries (not shown).

[0047] Each of the front motor 22, the left rear motor 32L, and the right rear motor 32R is a three-phase motor with three-phase motor windings. However, the embodiments described herein are not limited thereto. For example, the motor can be any multi-phase machine powered by a multi-phase inverter, and the drive unit can be implemented using a single machine with independently grouped windings.

[0048] The battery system 40 and / or propulsion system 16 include a switching system having various switching devices for controlling the operation of the first battery pack 44 and the second battery pack 46, and selectively connecting the first battery pack 44 and the second battery pack 46 to the front drive unit 20, the left rear drive unit 30L, and the right rear drive unit 30R. Switching devices can also be operated to selectively connect the first battery pack 44 and the second battery pack 46 to a charging system. The charging system can be used to charge the first battery pack 44 and the second battery pack 46, and / or supply power from the first battery pack 44 and / or the second battery pack 46 to charge another energy storage system (e.g., vehicle-to-vehicle (V2V) and / or vehicle-to-everything (V2X) charging). The charging system includes one or more charging modules. For example, a first on-board charging module (OBCM) 52 is electrically connected to a charging port 54 for charging and receiving AC systems or devices, such as public AC power. A second OBCM 53 may be included for DC charging (e.g., DC fast charging or DCFC).

[0049] In this embodiment, the switching system includes a first switching device 60 and a second switching device 62. The first switching device 60 selectively connects the first battery pack 44 to the front inverter 24, the left rear inverter 34L, and the right rear inverter 34R. The second switching device 62 selectively connects the second battery pack 46 to the front inverter 24, the left rear inverter 34L, and the right rear inverter 34R. The switching system also includes a third switching device 64 (also referred to as a "battery pack switching device") for selectively connecting the first battery pack 44 in series to the second battery pack 46.

[0050] Any of a variety of controllers can be used to control the functions of the battery system 40, the switching system, and the drive unit. The controller includes any suitable processing device or unit, and existing controllers such as drive system controllers, RESS controllers, and / or controllers within the drive system can be used. For example, controller 65 may be included for controlling the switching and drive control operations as discussed herein.

[0051] Vehicle 10 also includes a computer system 55, which includes one or more processing units 56 and a user interface 58. The computer system 55 can communicate with the charging system controller, for example, to provide commands to it in response to user input. Various processing devices, modules, and units can communicate with each other via communication devices or systems such as Controller Area Network (CAN) or Transmission Control Protocol (TCP) buses.

[0052] Figure 2This is a partial exploded view 200 of a portion of the electric motor of vehicle 10. The rotor 201 includes rotor core laminations 202 disposed on a rotor shaft 204 extending along a longitudinal axis 205. The rotor core laminations 202 include recesses in which magnets 206 are disposed. The rotor core laminations 202 are axially constrained to the rotor shaft 204 by first end members 208 and second end members 210. The rotor 201 is disposed within a housing or stator 209 having stator coils (not shown). When the rotor magnets 206 are in a predetermined angular relationship (or phase relationship) with respect to the stator coils, the timing of the stator coils is set to generate a changing stator magnetic field, thereby rotating the rotor shaft 204. Field shunts 212 are attached to the rotor core laminations 202 at various circumferential positions around the rotor shaft 204, and the field shunts 212 extend along the longitudinal axis 205. The variable shunt phaser (VSP 216) includes a sun gear (not shown) on its outer surface. Each magnetic field shunt 212 includes a pinion 214. Each pinion 214 is coupled to the VSP 216 via the sun gear.

[0053] Figure 3 This is a perspective view 300 showing the exterior of VSP 216. VSP 216 is a housing forming an enclosed space. The housing is formed by a gear plate 302, a back plate 304, a housing 306, and a collar 310. Gear plate 302 is an annular ring having an outer diameter and an inner diameter. Back plate 304 is similarly an annular ring having an outer diameter and an inner diameter identical to the outer diameter of gear plate 302. Housing 306 has a cylindrical outer surface at its outer diameter. Collar 310 is a cylindrical housing at its inner diameter. A set of mounting bolts 308 connects gear plate 302 to back plate 304, wherein housing 306 and collar 310 separate gear plate from back plate to form an enclosed space within VSP 216. VSP 216 is mounted to rotor shaft 204 via collar 310, thereby rotating with rotor shaft. The sun gear 312 is located at the inner diameter of the gear plate 302 and is stationary relative to the gear plate. The sun gear 312 and the pinion 214 ( Figure 2 )touch.

[0054] Figure 4 A perspective view 400 of VSP 216 is shown, revealing the interior of the VSP. In perspective view 400, back plate 304 faces forward and gear plate 302 faces rearward. Back plate 304 is not shown to expose the interior of VSP 216. Housing 306 defines the outer diameter of VSP 216. Lugs 402a-402c extend radially inward from the inner surface of housing 306 to define internal chambers 404a-404c within VSP 216. Mounting bolts 308 pass through lugs 402a-402c to secure gear plate 302 to back plate 304.

[0055] The inner rotor 406 of VSP 216 is rotatable within VSP 216. The inner rotor 406 includes a hub 408 having a collar 310 and blades 407a-407c extending radially outward from the hub 408 and entering corresponding internal chambers 404a-404c. The circumferential width of the internal chambers 404a-404c (as defined by lugs 402a-402c) defines the angular rotation range of the blades 407a-407c, and thus defines the angular rotation range of the inner rotor 406. The hub 408 includes an outer portion extending through a backplate 304 and outside VSP 216. A rotary valve 409 is mounted on the inner rotor at the outer portion of the collar 310. When mounted, the rotary valve 409 rotates together with the inner rotor 406. Rotary valve 409 includes blades 410a-410c extending radially outward from the outer portion of hub 408. Thus, blades 410a-410c are outside VSP 216 but overlap with corresponding internal chambers 404a-404c. Blades 410a-410c function as valves for balancing the pressure within VSP 216.

[0056] A control system (e.g., controller 65) can control the hydraulic pressure within the enclosed space to cause the inner rotor 406 to rotate relative to the housing 306. The hydraulic pressure can increase proportionally to the commanded motor speed. Alternatively, the hydraulic pressure can be varied independently of the motor speed. The hydraulic pressure can be transmitted via a fluid (e.g., oil) in the VSP 216.

[0057] The backplate 304 includes relief orifices 412a-412c located at or near the outer diameter of the housing 306. The relief orifices 412a-412c are equidistant from each other at an angle in the circumferential direction, and each internal chamber has one relief orifice.

[0058] The first tab 420 is located at the outer edge of the blade (e.g., blade 410c) and moves with the blade. The second tab 422 is located at the outer edge of the back plate 304 of the VSP 216 and is stationary. The first tab 420 and the second tab 422 serve as read indicators for the position sensors of the motor control system. When the VSP 216 operates with the inner rotor 406 in the default position, the first tab 420 and the second tab 422 overlap or are spaced apart from each other by a predetermined angular interval. The control system can determine the rotation angle of the inner rotor 406 by determining the angular spacing between the first tab 420 and the second tab 422. Based on the rotation angle, the control system can trigger a signal to command the rotation of the magnetic field shunt 212, thereby changing the timing of the magnetic field shunt 212 and causing flux extraction or "leakage," which reduces the occurrence of back electromotive force (BEMF) at high speeds. This results in improved motor performance. The relative rotation of the shunt 212 is related to the angle indicated by the first tab 420 and the second tab 422.

[0059] Figure 5 A first side 500 of the rotary valve 409 in the embodiment is shown. Each blade 410a-410c includes an escape orifice 502a-502c. Each escape orifice 502a-502c is centered along the outer edge of its corresponding blade 410a-410c. When the inner rotor 406 is mounted in the VSP 216, the first side 500 faces away from the VSP 216, and the radial distance of the escape orifices 502a-502c from the axial center of the VSP 216 is the same as the radial distance of the pressure relief orifices 412a-412c of the back plate 304 from the axial center of the VSP 216.

[0060] Figure 6 A second side 600 of the rotary valve 409 in the embodiment is shown. When the inner rotor 406 is mounted in the VSP 216, the second side 600 faces the gear plate 302. Each blade 410a-410c includes a first seal on one side of its escape orifices 502a-502c and a second seal on the second side of the escape orifice. The first and second seals are located at the same radial position from the escape orifice. Thus, escape orifice 502a is surrounded on a first circumferential side by seal 602a and on a second circumferential side by seal 602b, escape orifice 502b is surrounded on a first circumferential side by seal 604a and on a second circumferential side by seal 604b, and escape orifice 502c is surrounded on a first circumferential side by seal 606a and on a second circumferential side by seal 606b. Each seal extends circumferentially from the escape orifice to the radial edge of its corresponding blade.

[0061] Return to Figure 4VSP 216 is shown in its default position. The default position corresponds to normal operation of the motor (e.g., front motor 22), where there is no need to reduce the reverse EMF. In the default position, the inner rotor 406 and blades 410a-410c are in a first phase relationship relative to the housing 306, as can be observed through the position of blade 407a. In the default position, the escape port 502a is misaligned with the pressure relief port 412a located in the back plate 304 and is in a counter-clockwise position relative to the pressure relief port 412a. Instead, the seal 602a is above the pressure relief port 412a, thereby sealingly isolating the interior of VSP 216 from the exterior of the VSP, thus maintaining pressure within the internal chamber.

[0062] Figure 7 An external view 700 of the VSP is shown, with the rotary valve 409 in a partially rotated position. The increasing rotational speed of the motor (e.g., front motor 22) and the VSP 216 creates a pressure differential between the inner and outer diameters of the VSP 216. This pressure differential becomes significant at higher speeds, for example, greater than 6000 rpm. A command pressure signal provided by the control system causes the rotary valve 409 to rotate, causing the vanes 410a-410c to move clockwise. At a selected relative angle between the inner rotor 406 with the rotary valve 409 and the housing, the vanes 410a-410c are in a second phase relationship relative to the housing 306. In this second phase relationship, the escape port 502a is circumferentially aligned with the pressure relief port 412a.

[0063] Figure 7 The images show a first enlarged view 702 and a second enlarged view 704 of the region 701 surrounding the pressure relief orifice 412a. As shown in the first enlarged view 702, the escape orifice 502a is in the crack-open position of the pressure relief orifice 412a. As shown in the second enlarged view 704, the escape orifice 502a achieves perfect alignment with the pressure relief orifice 412a. Perfect alignment typically occurs near the middle of the full rotational range, when the blades 410a-410c reach a critical rotational angle. From the moment the escape orifice 502a is in the crack-open position until the moment the escape orifice 502a achieves maximum alignment with the pressure relief orifice 412a, the high-pressure imbalance (or differential pressure) in the internal chamber 404a decreases, allowing the internal rotor 406 to overcome the load caused by the differential pressure.

[0064] Figure 8A view 800 of the interior of VSP 216 at its maximum hinge angle is shown. Blades 410a-410c are in a third phase relationship relative to housing 306. Escape port 502a is in a clockwise position relative to vent port 412a, thereby placing seal 604a over the vent port. Once the inner rotor 406 has reached its maximum command angle, vent port 412a is sealed, and the actuator maintains the required torque to hold the inner rotor 406 in the desired position until a new command triggers the inner rotor 406 to return to its original position, as shown. Figure 4 As shown.

[0065] Figure 9 This is a view 900 of the interior of VSP 216 in the embodiment. For clarity, the backplate and blades are not shown. Figure 9 As shown in the diagram. For each internal chamber 404, VSP 216 includes a check valve 902 located in the wall of housing 306. Check valve 902 is a ball spring check valve, which includes a passage 904 extending into housing 306. Passage 904 includes a seat 906. A ball 908 in passage 904 is radially inwardly biased against seat 906 by a spring 910 or another suitable biasing device.

[0066] When the inner rotor 406 and the rotary valve 409 ( Figure 9 As the rotation angle (not shown) increases, blade 407a moves clockwise. When blade 407 reaches the selected angle, the pressure relief hole is radially aligned with channel 904, thereby allowing the pressure inside the chamber to press against the ball.

[0067] When the pressure in VSP 216 reaches or exceeds the critical pressure required to overcome the biasing force of spring 910, ball 908 moves against spring 910. The critical pressure is defined by the characteristics of spring 910. When the critical pressure has been reached, spring 910 allows ball 908 to move away from seat 906 even if the pressure relief hole 412a of back plate 304 and the escape hole 502a of blade 410a are not perfectly aligned.

[0068] Figure 10 It is along in a configuration Figure 9 A view 1000 in the axial direction of a portion of the housing of an embodiment. View 1000 shows a gear plate 302, a back plate 304, a housing 306, and a blade 410a. A check valve 902 in the housing 306 shows a channel 904 having a first opening 1002 at the inner surface 1004 of the housing. A second channel 1006 extends along the axis of the housing 306 from the check valve 902 to a second opening 1008 located on the axial surface facing the back plate 304. A pressure relief hole 412a of the back plate 304 is aligned with the second channel 1006 of the housing 306. A blade 410a shows an escape hole 502a. Figure 10The configuration includes an escape orifice 502a aligned with the pressure relief orifice 412a and the second channel 1006, and closed by the check valve 902. In this configuration, no fluid escapes from the interior.

[0069] Figure 11 It is in another configuration Figure 9 View 1100 of the embodiment along the axial direction of the cross section of VSP 216. Figure 11 The configuration includes an escape port 502, which is aligned with a pressure relief port 412a and a second channel 1006, and a check valve 902 is in the open position. In this configuration, fluid inside the VSP 216 can flow out from the inside through channel 904, check valve 902, second channel 1006, pressure relief port 412a, and escape port 502a.

[0070] Figure 12 In yet another configuration Figure 9 View 1200 of the embodiment along the axial direction of the cross section of VSP 216. Figure 12 The configuration includes an escape port 502a that is not aligned with the pressure relief port 412a and the second channel 1006, and a check valve 902 in the closed position. In this configuration, fluid inside the VSP 216 cannot flow out.

[0071] Figure 13 In yet another configuration Figure 9 View 1300 of the embodiment along the axial direction of the cross section of VSP 216. Figure 13 The configuration includes an escape port 502 that is not aligned with the pressure relief port 412a and the second channel 1006 when the check valve 902 is in the open position. In this configuration, fluid inside the VSP 216 cannot flow out from the inside.

[0072] Figure 14 This is a view 1400 of the interior of VSP 216 in another embodiment. Housing 306 includes a channel 1402 extending radially into housing 306. Channel 1402 is connected to a wave spring type check valve, also known as a lamella valve, 1406, which includes a chamber 1404 extending axially along housing 306. Lamella valve 1406 is located between the channel and chamber 1404 and acts as a gate to separate channel 1402 from chamber 1404. When an opening preload value is exceeded, lamella valve allows fluid to flow into chamber 1404, and when the pressure is below the preload value, lamella valve prevents fluid flow. When the pressure in the internal chamber reaches a critical pressure (opening pressure), lamella valve opens the flow path to housing chamber 1404 and allows pressure release (similar to pressure released by...). Figure 11(The pressure relief is provided by the fluid flow in the valve). When the pressure reaches or exceeds the critical pressure, the wave spring of the disc valve 1406 deflects radially (as shown in spring positions 1406a and 1406b) to allow passage 1402 to open. Figure 14 A representative embodiment of a wave spring including radial deflection is shown. In other embodiments, the wave spring may be configured to deflect in the axial direction. The deflection direction can be selected depending on the available package space. Figure 10-13 The configuration shown is suitable for using Figure 14 The check valve 1403 releases pressure.

[0073] Variable shunt phase shifters can be used in any electrical system involving rotary actuators operating at high speeds, such as greater than 6000 rpm or 8000 rpm. The system can be a hydraulic system that powers the variable shunt phase shifter or a general variable phase shifter.

[0074] The term “a” does not indicate a limitation of quantity, but rather that at least one of the referenced items is present. Unless the context clearly indicates otherwise, the term “or” means “and / or”. Throughout the specification, the reference to “aspect” means that a particular element described in connection with that aspect (e.g., a feature, structure, step, or characteristic) is included in at least one aspect described herein and may or may not be present in other aspects. Furthermore, it should be understood that the described elements may be combined in any suitable manner in the aspects.

[0075] When an element, such as a layer, film, region, or substrate, is referred to as being “on” another element, it can be directly on the other element, or there may be intermediate elements present. Conversely, when an element is referred to as being “directly” on another element, there are no intermediate elements present.

[0076] Unless otherwise stated herein, all test standards are the most recent standards in force up to the date of filing of this application, or, if priority is claimed, the date of filing of the earliest priority application in which a test standard appears.

[0077] Unless otherwise defined, the technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure pertains.

[0078] While the foregoing disclosure has been described with reference to exemplary embodiments, those skilled in the art will understand that various changes can be made and elements can be substituted with equivalents without departing from its scope. Furthermore, many modifications can be made to adapt particular situations or materials to the teachings of this disclosure without departing from the basic scope of this disclosure. Therefore, it is intended that this disclosure be limited to the specific embodiments disclosed, but will include all embodiments falling within its scope.

Claims

1. A variable splitter phase shifter, comprising: An outer casing configured to rotate together with the rotor shaft of an electric motor of an electric vehicle, the outer casing including a housing, a gear plate and a back plate, the housing, gear plate and back plate being connected to form an enclosed space within the outer casing, wherein rotation of the outer casing generates a pressure difference between the outer diameter and the inner diameter of the outer casing; An inner rotor is disposed within the enclosed space and configured to rotate relative to the housing; A pressure relief hole, wherein the pressure relief hole is located in the back plate at the outer diameter of the housing; Blades, the blades being coupled to the outer portion of the inner rotor, wherein the blades are outside the housing and rotatable relative to the back plate; and An escape orifice in the blade, wherein rotation of the inner rotor relative to the housing moves the escape orifice to align with the pressure relief orifice to open the pressure relief orifice, thereby reducing the pressure differential within the enclosed space.

2. The variable splitter phaser according to claim 1, wherein, The blade includes a first seal on the first circumferential side of the escape hole and a second seal on the second circumferential side of the escape hole.

3. The variable shunt phaser of claim 1 further includes a channel extending radially through the housing, and the inner rotor includes blades that rotate within the housing.

4. The variable splitter phaser according to claim 3, further comprising a seat and a ball within the channel, the ball being radially inwardly biased against the seat by a spring, wherein, When the pressure within the enclosed space reaches the critical pressure defined by the spring, the ball moves away from the seat.

5. The variable shunt phaser of claim 3, further comprising a plate valve configured to slide radially along the housing and biased above the channel, wherein, When the pressure within the enclosed space reaches the critical pressure, the disc valve moves radially along the housing.

6. An electric motor for an electric vehicle, comprising: Rotor shaft; and A variable shunt phase shifter, which is capable of rotating together with the rotor shaft, the variable shunt phase shifter comprising: A housing configured to rotate together with the rotor shaft, the housing including a shell, a gear plate and a back plate, the gear plate and the back plate being connected to form an enclosed space within the housing, wherein rotation of the housing generates a pressure difference between the outer diameter and the inner diameter of the housing; An inner rotor is disposed within the enclosed space and configured to rotate relative to the housing; A pressure relief hole, located in the back plate at the outer diameter of the housing; Blades, the blades being coupled to the outer portion of the inner rotor, wherein the blades are outside the housing and rotatable relative to the back plate; and An escape orifice in the blade, wherein rotation of the inner rotor relative to the housing moves the escape orifice to align with the pressure relief orifice to open the pressure relief orifice, thereby reducing the pressure differential within the enclosed space.

7. The electric motor according to claim 6, wherein, The blade includes a first seal on the first circumferential side of the escape hole and a second seal on the second circumferential side of the escape hole.

8. The electric motor of claim 6, further comprising a channel extending radially through the housing, and the inner rotor comprising blades that rotate within the housing.

9. The electric motor of claim 8, further comprising a base and a ball located within the channel, the ball being radially inwardly biased against the base by a spring, wherein, When the pressure within the enclosed space reaches the critical pressure defined by the spring, the ball moves away from the seat.

10. The electric motor of claim 8, further comprising a disc valve configured to slide radially along the housing and biased above the channel, wherein, When the pressure within the enclosed space reaches the critical pressure, the disc valve moves radially along the housing.

Images