Patent Grant
11220854
The present disclosure relates generally to power door systems for motor vehicles and, more particularly, to a power swing door actuator operable for moving a vehicle door relative to a vehicle body between an open position and a closed position.
This section provides background information related to the present disclosure which is not necessarily prior art.
The passenger doors on motor vehicles are typically mounted by upper and lower door hinges to the vehicle body for swinging movement about a generally vertical pivot axis. Each door hinge typically includes a door hinge strap connected to the passenger door, a body hinge strap connected to the vehicle body, and a pivot pin arranged to pivotably connect the door hinge strap to the body hinge strap and define the pivot axis. Such swinging passenger doors (“swing doors”) have recognized issues such as, for example, when the vehicle is situated on an inclined surface and the swing door either opens too far or swings shut due to the unbalanced weight of the door. To address this issue, most passenger doors have some type of detent or check mechanism integrated into at least one of the door hinges that functions to inhibit uncontrolled swinging movement of the door by positively locating and holding the door in one or more mid-travel positions in addition to a fully-open position. In some high-end vehicles, the door hinge may include an infinite door check mechanism which allows the door to be opened and held in check at any desired open position. One advantage of passenger doors equipped with door hinges having an infinite door check mechanism is that the door can be located and held in any position to avoid contact with adjacent vehicles or structures.
As a further advancement, power door actuation systems have been developed which function to automatically swing the passenger door about its pivot axis between the open and closed positions. Typically, power door actuation systems include a power-operated device such as, for example, an electric motor and a rotary-to-linear conversion device that are operable for converting the rotary output of the electric motor into translational movement of an extensible member. In most arrangements, the electric motor and the conversion device are mounted to the passenger door and the distal end of the extensible member is fixedly secured to the vehicle body. One example of a power door actuation system is shown in commonly-owned U.S. Pat. No. 9,174,517 which discloses a power swing door actuator having a rotary-to-linear conversion device configured to include an externally-threaded leadscrew rotatively driven by the electric motor and an internally-threaded drive nut meshingly engaged with the leadscrew and to which the extensible member is attached. Accordingly, control over the speed and direction of rotation of the leadscrew results in control over the speed and direction of translational movement of the drive nut and the extensible member for controlling swinging movement of the passenger door between its open and closed positions.
While such power door actuation systems function satisfactorily for their intended purpose, one recognized drawback relates to their packaging requirements. Specifically, since power door actuation systems rely on linear motion of the extensible member, the electric motor and conversion device must necessarily be packaged in a generally horizontal orientation within the passenger door and with respect to at least one of the door hinges. As such, the application of such conventional power door actuation systems may be limited, particularly to only those vehicular doors where such an orientation would not cause interference with existing hardware and mechanisms such as for example, the glass window function, the power wiring and harnesses, and the like. Put another way, the translational motion of the extensible member requires the availability of a significant amount of internal space within the cavity of the passenger door.
In view of the above, there remains a need to develop alternative power door actuation systems which address and overcome packaging limitation associated with known power door actuation systems as well as to provide increased applicability while reducing cost and complexity.
This section provides a general summary of the present disclosure and is not a comprehensive disclosure of its full scope or all of its features, aspects and objectives.
It is an aspect of the present disclosure to provide a power swing door actuator for use in a power swing door actuation system and which is operable for moving a vehicle door between open and closed positions relative to a vehicle body.
It is another aspect of the present disclosure to provide a power swing door actuator for use with swing doors in motor vehicles which can be effectively packaged within the cavity of the door and cooperatively interact with a door hinge.
It is a related aspect of the present disclosure to provide a power swing door actuator having a mounting unit secured to the vehicle door, a power-operated drive mechanism supported by the mounting unit and having an extensible actuation member, and a pivot linkage mechanism arranged to pivotably connect the extensible actuation member to the vehicle body.
It is a further related aspect of the present disclosure to provide the power-operated drive mechanism with a motor-driven spindle unit configured to convert rotation of a rotary drive member into linear movement of the extensible actuation member. In addition, the pivot linkage mechanism includes an elongated connector link having a first link segment pivotably connected to the extensible actuation member and a second link segment pivotably connected to a pivot bracket mounted to the vehicle body.
It is another aspect of the present disclosure to provide a power swing door actuator having a door check mechanism operably disposed between the connector link of the pivot linkage mechanism and the vehicle door.
It is a related aspect to install a door check detent pad to the connector link having a plurality of distinct detents configured to be engaged by a door-mounted check feature to define a corresponding number of intermediate held open positions for the vehicle door.
It is another aspect of the present disclosure to provide a power swing door actuator having a door check mechanism operably disposed between the extensible actuation member of the spindle drive unit and an actuator housing fixed to the vehicle door.
It is a related aspect to install a pair of elongated spring elements within the actuator housing which together define a plurality of distinct detents configured to be engaged by a detent pin extending from the extensible actuation member to define a corresponding number of intermediate held open positions for the vehicle door.
It is another related aspect to install a pair of spring-loaded detent followers on the connector link which move within contoured guide channels formed in the actuator housing and define a plurality of distinct door check detents configured to engage and retain the detent followers to define a corresponding number of intermediate held open positions for the vehicle door.
In accordance with these and other aspects, the power swing door actuator of the present disclosure is configured for use in a power door actuation system in a motor vehicle having a vehicle body defining a door opening and a vehicle door pivotably connected to the vehicle body for movement along a swing path between open and closed positions. The power swing door actuator includes a power-operated drive mechanism connected to the vehicle door and having a linearly moveable actuation member, and an articulating pivot linkage mechanism pivotably connecting the actuation member to the vehicle body. Linear movement of the actuation member in a first direction causes the vehicle door to move in an opening direction from the closed position toward the open position while linear movement of the actuation member in a second direction causes the vehicle door to move in a closing direction from the open position toward the closed position. The pivot linkage mechanism is operable to accommodate pivotal movement of the vehicle door along its swing path in cooperation with bi-directional linear movement of the actuation member.
In accordance with one embodiment of the power swing door actuator, the power-operated drive mechanism includes a mounting unit fixedly secured to the vehicle door, an electric motor supported by the mounting unit, and a spindle drive unit having a rotary leadscrew and a non-rotary, linearly-moveable drive nut defining the actuation member. The pivot linkage mechanism includes a connector link having a first link segment pivotably mounted to the drive nut and a second link segment pivotably mounted to a pivot bracket fixedly secured to the vehicle body. In operation, motor-driven rotation of the leadscrew in a first rotary direction causes translational movement of the drive nut from a retracted position toward an extended position for moving the vehicle door from the closed position toward the open position. Motor-driven rotation of the leadscrew in a second rotary direction causes translational movement of the drive nut from the extended position toward the retracted position for moving the vehicle door from the open position toward the closed position.
In accordance with another embodiment, the power swing door actuator further includes a door check mechanism having a door check pad mounted to, or formed on, the connector link and configured to define a series of detents along its length. Upon movement of the door between its open and closed positions, a door-mounted retention device selectively engages the distinct detents so as to define a corresponding number of door check positions whereat the door is held open via engagement of the retention device within a corresponding one of the detents.
In accordance with yet another embodiment, the power swing door actuator could alternatively further include a door check mechanism having a door check biasing arrangement mounted in the actuator housing and configured to define a series of detents along its length. Upon movement of the door between its open and closed positions, a retention device mounted to the actuation member selectively engages the distinct detents so as to define a corresponding number of door check positions whereat the door is held open.
In accordance with a further embodiment, the power swing door actuator could alternatively include an integrated door check mechanism having a spring-biased follower mounted to the connector link and retained for sliding movement within a corresponding detent guide channel formed in the actuator housing and defining one or more distinct follower retention detents along its length. Upon movement of the vehicle door between its fully-closed and fully-open positions, the follower selectively engages one of the distinct retention detents so as to define a corresponding number of door check positions whereat the door is mechanically held open.
Further areas of applicability will become apparent from the description provided herein. The description and specific embodiments listed in this summary are for purposes of illustration only and are not intended to limit the scope of the present disclosure.
Other advantages of the present disclosure will be readily appreciated, as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:
In general, at least one example embodiment of a power door actuation system having a power swing door actuator constructed in accordance with the teachings of the present disclosure will now be disclosed. The at least one example embodiment is provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, will-known device structures, and well-known technologies are described in detail.
Referring initially to
Each of upper door hinge 16 and lower door hinge 18 include a door-mounting hinge component and a body-mounted hinge component that are pivotably interconnected by a hinge pin or post. While power door actuation system 20 is only shown in association with front passenger door 12, those skilled in the art will recognize that power door actuation system 20 can also be associated with any other door or liftgate of vehicle 10 such as rear passenger doors 17 and decklid 19.
Power door actuation system 20 is diagrammatically shown in
Although not expressly illustrated, electric motor 24 can include Hall-effect sensors for monitoring a position and speed of vehicle door 12 during movement between its open and closed positions. For example, one or more Hall-effect sensors may be provided and positioned to send signals to electronic control module 52 that are indicative of rotational movement of electric motor 24 and indicative of the rotational speed of electric motor 24, e.g., based on counting signals from the Hall-effect sensor detecting a target on a motor output shaft. In situations where the sensed motor speed is greater than a threshold speed and where the current sensor registers a significant change in the current draw, electronic control module 52 may determine that the user is manually moving door 12 while motor 36 is also operating, thus moving vehicle door 12 between its open and closed positions. Electronic control module 52 may then send a signal to electric motor 24 to stop motor 24 and may even disengage slip clutch 28 (if provided). Conversely, when electronic control module 52 is in a power open or power close mode and the Hall-effect sensors indicate that a speed of electric motor 24 is less than a threshold speed (e.g., zero) and a current spike is registered, electronic control module 52 may determine that an obstacle is in the way of vehicle door 12, in which case the electronic control system may take any suitable action, such as sending a signal to turn off electric motor 36. As such, electronic control module 52 receives feedback from the Hall-effect sensors to ensure that a contact obstacle has not occurred during movement of vehicle door 12 from the closed position to the open position, or vice versa.
As is also schematically shown in
Electronic control module 52 can also receive an additional input from an ultrasonic sensor 64 positioned on a portion of vehicle door 12, such as on a door mirror 65 or the like. Ultrasonic sensor 64 assesses if an obstacle, such as another car, tree, or post, is near or in close proximity to vehicle door 12. If such an obstacle is present, ultrasonic sensor 64 will send a signal to electronic control module 52 and electronic control module 52 will proceed to turn off electric motor 24 to stop movement of vehicle door 12, thereby preventing vehicle door 12 from hitting the obstacle. This provides a non-contact obstacle avoidance system. In addition, or optionally, a contact obstacle avoidance system can be placed in vehicle 10 which includes a contact sensor 66 mounted to door, such as in association with molding component 67, and which is operable to send a signal to controller 52.
The swing door 102 includes inner and outer sheet metal panels 110 and 112 with a connecting portion 114 between the inner and outer sheet metal panels 110 and 112. The actuator 100 has a support structure, such as a housing 116, a power-operated drive mechanism 117 mounted within housing 116, and an extensible actuation member 118 drivingly coupled to power-operated drive mechanism 117. The extensible actuation member 118 is moveable relative to housing 116 between retracted and extended positions to effectuate swinging movement of door 102. The actuator 100 may be mounted within an internal door cavity formed between the inner and outer sheet metal panels 110, 112. Specifically, the actuator housing 116 is fixed to the swing door 102 via a mounting bracket 120 mounted to the connecting door portion 114 within the internal door cavity. The terminal end of the extensible actuation member 118 is mounted to the vehicle body 106.
Referring additionally to the sectional view of the actuator 100 shown in
The internally-threaded cylindrical tube 124 (also referred to as a “nut tube”) meshingly engages with external threads formed on a lead screw 128 that is mounted in the housing 116 for rotation in situ. The lead screw 128 is matable with the internally-threaded nut tube 124 to permit relative rotation between lead screw 128 and the internally-threaded nut tube 124. In the embodiment shown, because the nut tube 124 is slidably connected in the housing 116 but is prevented from rotation, as the lead screw 128 rotates the nut tube 124 translates linearly, thereby causing the extensible actuation member 118 to move with respect to the housing 116. Since the extensible actuation member 118 is connected to the vehicle body 106 and the actuator housing 116 is connected to the swing door 102, such movement of the extensible actuation member 118 causes the swing door 102 to pivot relative to the vehicle body 106.
The lead screw 128 is connected to a shaft 130 that is journalled in the housing 116 via ball bearing 132 that provides radial and linear support for the lead screw. In the illustrated non-limiting embodiment, an absolute position sensor 134 is mounted to the shaft 130. The absolute position sensor 134 translates lead screw rotations into an absolute linear position signal so that the linear position of the extensible actuation member 118 is known with certainty, even upon power up. In alternative embodiments, the absolute linear position sensor 134 can be provided by a linear encoder mounted between the nut tube 124 and actuator housing 116 which reads the travel between these components along a longitudinal axis.
The shaft 130 is connected to a clutch unit 136 associated with power-operated drive mechanism 117. The clutch unit 136 is normally operable in an engaged mode and must be energized to shift into a disengaged mode. In other words, the clutch unit 136 normally couples the lead screw 128 with a geartrain unit 137 without the application of electrical power and the clutch unit 136 requires the application of electrical power to uncouple the lead screw 128 from the geartrain unit 137. The clutch unit 136 may engage and disengage using any suitable type of clutching mechanism, such as a set of sprags, rollers, a wrap-spring, a pair of friction plates, or any other suitable mechanism. The geartrain unit 132 is also part of power-operated drive mechanism 117.
Referring additionally to
The worm gear 138 may be a helical gear having gear teeth 148. The worm gear 138 meshes with a worm 150 that is connected to the output shaft of an electric motor 152, which may, for example, be a fractional horsepower motor. The worm 150 may be a single start worm having a thread with a lead angle of less than about 4 degrees. The geartrain unit 137 is thus provided by the worm 150 and worm gear 138 and provides a gear ratio that multiplies the torque of the motor as necessary to drive the lead screw and move the vehicle swing door. The electric motor 152 is operatively connected to the geartrain unit 137 and is operatively connected to an input end 136a of the clutch unit 136 through the geartrain unit 137. The output end (shown at 136b) of the clutch unit 136 is operatively connected to the extensible actuation member 118 (in the embodiment shown, through the lead screw 128 and nut tube 124). In this non-limiting arrangement, the power-operated drive mechanism 117 includes the electric motor 152, the geartrain unit 137, the clutch unit 136, the position sensor 134, and the spindle drive unit comprised of leadscrew 128 and nut tube 124.
The worm 150 and worm gear 138 provide a locking geartrain, which may also be referred to as a geartrain that is non-back drivable. With the clutch unit 136 normally engaged, a relatively large amount of force is required to back-drive the geartrain unit 137 and motor 152. Thus, the power swing door actuator 100 inherently provides an infinite door check function as the force required to back-drive the geartrain unit 137 and motor 152 will be much larger than the force experienced by an unbalanced door as a result of the vehicle being situated on an incline.
However, the clutch unit 136 has an associated slip torque between the input end 136a and the output end 136b, that is a maximum amount of torque that the clutch unit 136 will transmit between the input and output ends 136a and 136b before slipping. Thus, when the clutch unit 136 is engaged, it will slip if a torque is applied at the input end 136a (or at the output end 136b) that exceeds the slip torque. The slip torque for the clutch unit 136 may be selected to be sufficiently low that, in the event of a power loss in the vehicle that would result in no electric power being available to disengage the clutch 136, the swing door 102 can still be manually moved by a person by overcoming the clutch slip torque. However, the slip torque may be selected to be sufficiently high so that it is sufficient to hold the swing door 102 in whatever position the door 102 is in, thereby providing the infinite door check function. In other words, the slip torque is sufficiently high that, if the swing door 102 is left in a particular position and the motor 152 is stopped, the slip torque will prevent movement of the door when the door is exposed to an external torque that is less than a selected value. An example of an external torque that would not overcome the slip torque would be applied by the weight of the swing door 102 when the vehicle is parked on a surface at less than a selected angle of incline. However, the slip torque is sufficiently low that the swing door 102 can be moved manually by a person (e.g. a person having a selected strength that would be representative of a selected percentage of the overall population in which the vehicle is to be sold).
In normal operation, the power swing door actuator 100 can be disengaged to allow for manual movement of the swing door 102 by applying power (i.e. energizing) to the clutch unit 136, in which case the motor 152 and the geartrain unit 137 will be decoupled from the lead screw 128. An example of a suitable slip torque that may be selected for the clutch unit 136 may be in the range of about 2 Nm to about 4 Nm. The slip torque that is selected for a particular application may depend on one or more of several factors. An example factor based on which the slip torque may be selected is the weight of the door 102. Another example factor based on which the slip torque may be selected is the geometry of the door 102. Yet another example factor based on which the slip torque may be selected is the amount of incline on which the vehicle is intended to be parked while still ensuring that the door 102 is holdable in any position.
In an alternative embodiment, the internally-threaded member 124 and the lead screw 128 associated with the power-operated spindle drive mechanism 117 may be switched in position. That is, the internally-threaded member 124 may be driven by the output end 136b of the clutch unit 136 and the externally-threaded lead screw 128 may be slidably connected to the housing 116. Thus, the output end 136b of the clutch unit 136 may be connected to either one of the lead screw 128 and the internally threaded member 124 and the other of the lead screw 128 and the internally threaded member 124 may be connected to the extensible actuation member 118 and may thus be slidable relative to the housing 116. Rotation of the output end 136a of the clutch unit 136 drives rotation of whichever one of the lead screw 128 and the internally threaded member 124 the output end 136a is connected, which in turn drives sliding movement of the other of the lead screw 128 and the internally threaded member 124 relative to the housing 116.
A swing door actuation system is provided that includes the power swing door actuator 100 and a control system 154 shown schematically in
The control system 154 provides system logic for selectively powering the electric motor 152 and the clutch unit 136 based on a number of signal inputs. The control system 154 may include a microprocessor 162 and a memory 164 that contains programming that is configured to carry out the method steps described below, and may be configured to receive inputs and transmit outputs as described below.
While the non-limiting example of the control system 154 has been shown in
The swing door 102 may have a conventional opening lever (not shown) located inside the passenger compartment for manually opening the door latch 155. This opening lever may trigger a switch connected to the control system 154 such that, when the switch is actuated, the control system 154 powers (i.e. energizes) the clutch unit 136 to disengage the actuator 100 and allow for manual movement of the swing door 102.
The control system 154 can operate in a ‘power assist’ mode where the control system 154 determines that a user is trying to manually move the swing door 102 when the actuator 100 is in a power open or power close mode. A current sensor 180 (
In the case where the control system 154 determines that signals indicate that the user wants a manual opening of the swing door 102, the control system 154 energizes the clutch 136 at step 210 (
In the event of a power loss the control system 154 (which may be provided with sufficient battery back-up power to run logic and control functions) enters one of several power loss modes. When the control system 154 is in the manual mode 212 and power is lost, the control system 154 enters a manual mode power loss mode 240 (
When the control system 154 is in the checked mode 218 and power is lost, the control system 154 enters checked mode power loss mode 250 (
When the control system 154 is in the power open mode 202 or the power close mode 230 and power is lost, the control system 154 enters a powered movement power loss mode 260 (
When the control system 154 is in the latched mode 200 and power is lost, the control system 154 enters latched mode power loss state 270 (
The swing door actuation systems of the present disclosure enable a powered open and powered close of the vehicular swing door 102, where the normally engaged clutch 136 enables the motor 152 and the gear train 137 to drive the lead screw 128 in order to open and close the swing door 102. The swing door actuation system also enables the user to manually open and close the vehicle swing door 102 by powering the clutch 136 to disengage the gear train 137 and the motor 152 in a manual mode wherein only the lead screw 128 is back-driven during manual movement with relatively low manual effort and noise. Disengagement of the clutch 136 eliminates the effort and noise that is associated with back-driving the gear train 137 and the motor 152. As a result, the manual effort to move the swing door 102 may be similar in some embodiments, to a conventional non-powered vehicle door. When the clutch 136 is engaged, an infinite position door check function is provided, via engagement of the lead screw 128 to the gear train 137 (and in particular to the worm 150, which has a thread angle configured to prevent back-driving from the worm gear 138). As a result of the normally-engaged clutch 136, the infinite door check function is available in the event of vehicle power loss thereby precluding an uncontrolled swinging of the door 102 during such a power loss event. However, the user can still manually move the swing door 102 open and closed in a power loss event by overcoming an appropriately selected slip torque of the clutch 136. Additionally, the clutch 136 protects the swing door actuation system from shock and abuse loading.
The swing door actuation systems of the present disclosure provide a means for speed control and obstacle detection. Speed control is attained by the control system 154 monitoring the Hall-effect signals and/or the absolute position sensor signal. Either signal could be eliminated depending on the desired control features and redundancy requirements. The absolute position sensor is however highly desired for providing the position of the door upon power up or in case of power loss.
The swing door actuation systems of the present disclosure also provide acceptable sound levels during power and manual operation. This is attained in power mode through proper alignment of gears, proper support of the lead screw and flexibly coupling the gear train and lead screw. Acceptable sound levels are attained in manual mode by disengaging the gear train 137 and motor 152 for manual operation.
The swing door actuation systems of the present disclosure may be suitable for packaging and mounting to a typical vehicle swing door. The connecting bracket could be in the front (as shown in
It will be noted that the lead screw 128 and the nut tube 124 are just one example of an operative connection between the output end 136b of the clutch 136 and the extensible actuation member 118. Any other suitable operative connection may be provided between the output end 136b of the clutch 136 to the extensible actuation member 118 for converting the rotary motion of the output end 136b into extension and retraction of the extensible actuation member 118. Furthermore, the lead screw 128 and nut tube 124 are just one example of a rotary-to-linear conversion mechanism operable to convert rotary motion (i.e. the rotary motion associated with the output end 136b of the clutch 126) into substantially linear motion which drives the extension and retraction of the extensible actuation member 118 relative to the housing 116. The actuator 100 need not include lead screw 128 and nut tube 124 to convert the rotary motion at the output end 136b of the clutch 136 into linear motion of the extensible actuation member 118. Any other suitable mechanism for carrying out such a conversion may be used. For example, the output end 136b of the clutch 136 may connect to a pair of bevel gears to change the axis of the rotary motion by 90 degrees. The second bevel gear may co-rotate with a spur gear, which in turn drives a rack that is connected to the extensible actuation member 118. As a result, the rotation at the output end 136b of the clutch 136 is converted into linear movement of the rack and the extensible actuation member 118. While the lead screw 128 and the nut tube 124, and the gears and rack described above generate pure linear motion of the extensible member (relative to the housing 116), it is possible to instead provide a mechanism that results in substantially linear motion, which may include motion along a relatively large diameter arc, for example. Such motion along a large diameter arc could drive an arcuate extensible member to move along an arcuate path during extension and retraction of the extensible actuation member 118 from the housing 116. In such instances, the housing 116 itself may be slightly arcuate. Such motion of an extensible actuation member 118 would still be effective in driving the opening and closing of the door 102.
The power swing door actuator 100 shown and described in relation to
Referring initially to
Electric motor 302 includes a rotary output shaft driving an input gear component of geartrain unit 304 which, in turn, drives an output gear component of geartrain unit 304 at a reduced speed and with a multiplied torque. The output gear component of geartrain unit 304 drives an input clutch member of clutch unit 306 which, in turn, drives an output clutch member of clutch unit 306 until a predetermined slip torque is applied therebetween. The output clutch member of clutch unit 306 drives a rotary component of spindle drive unit 308 which, in turn, is converted into linear, non-rotary movement of the extensible actuation member. In the non-limiting arrangement shown, the rotary component of spindle drive unit 308 is an externally-threaded leadscrew 330. A first end of leadscrew 330 is rotatably supported by a first bearing (not shown) within geartrain housing 320 while a second end of leadscrew 330 is rotatably supported in a bushing 332 mounted in pivot linkage mechanism 310. Spindle drive unit 308 also includes an internally-threaded drive nut 334 in threaded engagement with externally-threaded leadscrew 330. Drive nut 334 acts as the non-rotary, linearly moveable, extensible actuation member of power-operated drive mechanism 301. Linkage mechanism 310 is generally configured to have a first link segment 340 pivotably connected to drive nut 334 and a second link segment 342 pivotably connected to a body-mounted bracket 344 (
As best seen in
Power swing door actuator 300 provides both push and pull forces to operate the power door system, particularly for passenger-type doors on motor vehicles. While power actuator 300 provides an electrical “checking” function, it is contemplated that a mechanical checklink systems could easily be integrated with power actuator 300. Additionally, articulating pivot linkage mechanism 310, when combined with a mechanical checking mechanism, allows the power-operated swing door to have the same translating path as a non-powered checklink arrangement. Articulating pivot linkage mechanism 310 allows the checklink path to follow the same path as conventional checklink configurations, rather than a linear path. Integrating a checklink mechanism into power swing door actuator 300 would also permit elimination of a separate door check feature. While power door actuator 300 has been described having power-operated drive mechanism 301 configured to convert rotary motion of electric motor 302 into linear, non-rotary motion of pivot linkage mechanism 310, those skilled in the art will appreciate that alternative linear actuators could be used such as, for example, an electromagnetic solenoid-type linear actuator. Additionally, the arrangement of power door actuator 300 could be reversed with it secured to the vehicle body such that linkage mechanism 310 is pivotably connected to the vehicle door, assuming adequate packaging space is available.
Referring now to
Door check mechanism 400 is shown, in the non-limiting embodiment, to include a pair of contoured check pads 402, 404 respectively formed on or mounted to outer surfaces of top plate 352 and bottom plate 354 of connector link 350. Each check pad 402, 404 is configured to define a first detent 402A, 404A and a second detent 402B, 404B. In addition to these detents, each check pad 402, 404 is configured to include a closed seat 402C, 404C and an open seat 402D, 404D. A pair of check retainers 406, 408 are configured to be fixedly secured to the vehicle door and each has a contoured retention feature, hereinafter referred to as check lug 406A, 408A, configured to engage one of the detents and seats formed in the corresponding detent pads 402, 404 so as to define the plurality of mechanically-held door positions. Specifically,
Check pads 402, 404 can be preformed and subsequently attached to connector link 350 or, in the alternative, they can be formed on top and bottom plates 352, 354 via an over-molding process. At least one of check pads 402, 406 and check retainers 406, 408 can be made of a resilient material to allow camming movement during swinging movement of the vehicle door. While not specifically shown, a spring-loaded retention member, such as a ball bearing, can be installed in apertures formed in check retainers 406, 408 and extend through check lugs 406A, 408A and provide the biasing function required to mechanically hold the vehicle door in each available position, while permitting such biasing to be overcome via actuation of electric motor 302 and/or mechanically via manual door movement. The actual number of detents and the specific configuration of check pads 402, 404 are not limited to that shown. As such, the shape and path of the detent pads can be optimized for each particular application (i.e. linear, spline, etc.). This allows power swing door actuator 300A to be used on many different vehicle door systems with only minimal changes while also permitting the conventional mechanical check mechanism associated with the hinged connections to be eliminated. While two identical pads are shown, it is contemplated that only one pad can be used or two pads having differing profiles to provide a larger number of detent door check positions.
Referring now to
Upon continued movement of the vehicle door in its opening direction, it will be located and held in a second intermediate door check position (
Referring now to
The pair of oppositely-extending pivot posts 360 formed on, or fixed to, drive nut 334 are retained in upstanding tubular bosses 362A, 362B respectively formed in top plate 352 and bottom plate 354. A pair of aligned apertures 364, 366 formed in top and bottom plates 352, 354 of connector link 350 are again configured to receive pivot post 370 for pivotably connecting the second end of link 350 to body-mounted bracket 344.
Drive housing 326′ is shown to include a pair of elongated checklink guide channels 604A, 604B. Each guide channel 604A, 604B is contoured, in this non-limiting example, to define a fully-closed door detent (Position “X”), an intermediate door check detent (Position “Y”), and a fully-open door detent (Position “Z”).
The foregoing description of the embodiments has been provided for purposes of illustration and description. It is not intended to be exhaustive or to limit the disclosure. Individual elements or features of a particular embodiment are generally not limited to that particular embodiment, but, where applicable, are interchangeable and can be used in a selected embodiment, even if not specifically shown or described. The same may also be varied in many ways. Such variations are not to be regarded as a departure from the disclosure, and all such modifications are intended to be included within the scope of the disclosure.
This application is a continuation of U.S. application Ser. No. 15/473,727, filed on Mar. 30, 2017, which claims the benefit of U.S. Provisional Application No. 62/319,560 filed Apr. 7, 2016 and U.S. Provisional Application No. 62/372,502 filed Aug. 9, 2016. The entire disclosure of each of the above applications is incorporated herein by reference.
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| Number | Date | Country | |
|---|---|---|---|
| 20200300022 A1 | Sep 2020 | US |
| Number | Date | Country | |
|---|---|---|---|
| 62319560 | Apr 2016 | US | |
| 62372502 | Aug 2016 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 15473727 | Mar 2017 | US |
| Child | 16898752 | US |
