Patent Abstract:
A gear pair for a motor vehicle climate control system door drive mechanism includes a drive gear and a driven gear. The drive gear and the driven gear cooperate to form a gear pair, wherein the gear pair is constructed so that a gear ratio of the gear pair transitions from a linear gear ratio to a non-linear gear ratio. The non-linear gear ratio may be proportional to an exponential function. The gear pair is applied to linearly control a climate control door rotation speed when there is a need to meet temperature door linearity performance, and is applied to increase the climate control door rotation speed to meet total temperature door rotation time performance.

Full Description:
CROSS REFERENCE TO RELATED APPLICATION 
       [0001]    This application claims the benefit under 35 U.S.C. §119(e) of U.S. Provisional Patent Application No. 61/666,292, filed on Jun. 29, 2012, the content of which is incorporated by reference herein in its entirety. 
     
    
     FIELD OF THE INVENTION 
       [0002]    The present invention relates to a door drive mechanism of a climate control system for a vehicle, and more particularly, relates to a door drive mechanism of the climate control system that actuates doors for heating, ventilating, and air conditioning applications using a gear mechanism. 
       BACKGROUND OF THE INVENTION 
       [0003]    A motor vehicle typically includes a climate control system to maintain a temperature within a passenger compartment of the vehicle at a comfortable level by providing heating, cooling, and ventilation. Comfort can be maintained in the passenger compartment by an integrated system, referred to as a heating, ventilating, and air conditioning (HVAC) air-handling system. The HVAC air-handling system conditions air flowing therethrough and distributes the conditioned air throughout the passenger compartment. 
         [0004]    The design of an HVAC air-handling system can include features that control air flow volume, air temperature, and one or more air flow paths, for example. Performance of the HVAC air-handling system may be designed to comply with particular targets including temperature linearity, wherein linearity is a predictable rate of change in temperature. For all operating states, it can be desirable to manipulate hot air streams and cold air streams to produce the proper temperatures and a predictable rate of change in temperature. 
         [0005]    To comply with the desired linearity targets, HVAC air-handling systems can include features such as baffles, conduits, mixing plates, and/or climate control doors, or the like, to facilitate mixing of hot air streams with cold air streams. Undesirably, addition of these features and/or components can reduce airflow, degrade flow efficiency, increase noise, and increase the cost and weight of the system. Further issues can arise with a rate at which one or more ventilation conduits or climate control doors are opened and closed in the HVAC air-handling system. For example, mixing and delivery of air streams of various temperatures can be controlled by adjusting the rate at which a climate control door within a ventilation conduit is rotated throughout a range between a fully opened position and a fully closed position. 
         [0006]    An issue with HVAC air-handling systems is that certain designs do not have the ability to rotate a climate control door at a rate of speed (deg/s) that is less than a rate of speed (deg/s) of a drive gear mechanism that is rotating a gear set attached to the climate control door without increasing the total time of rotation beyond a desired target. One way to address this issue is by using a linear pitch gear set with a constant gear ratio that reduces the rate of door rotation relative to the rate of actuator or motor rotation. While this method is effective, it requires additional actuator rotation and additional rotation time. 
         [0007]    Another way to address this issue is by using a cam mechanism (kinematics) that involves a cam and pin interface that reduces the rate of door rotation relative to the rate of actuator or motor rotation. While this method is effective, it requires additional actuator rotation, additional rotation time, extra package space and, sometimes, extra components. Accordingly, improvements in ways to provide HVAC door rotation are desirable to optimize HVAC air-handing system operation. 
       SUMMARY OF THE INVENTION 
       [0008]    Concordant and consistent with the present invention, an improved mechanism for a climate control system door drive mechanism for a vehicle that minimizes actuator rotation and rotation times to optimize air-handling system operation has surprisingly been discovered. 
         [0009]    According to the invention, a gear pair for a motor vehicle climate control system door drive mechanism includes a drive gear and a driven gear. The drive gear and the driven gear cooperate to form a gear pair, wherein the gear pair is constructed so that a gear ratio of the gear pair transitions from a linear gear ratio to a non-linear gear ratio. The non-linear gear ratio may be proportional to an exponential function. In one embodiment, the driven gear includes a first toothed portion having a substantially linear pitch radius and a second toothed portion having a pitch radius derived from an exponential function. 
         [0010]    In another embodiment, a door drive mechanism for a vehicle climate control system includes an actuator rotatably coupled to an actuator gear about an actuator axis of rotation. The actuator gear includes a toothed portion having a first plurality of teeth. A door gear includes a toothed portion having a second plurality of teeth intermeshed with the first plurality of teeth, the door gear rotatably connected to a vehicle climate control door about a door axis of rotation to drive the door upon rotation of the actuator. A first portion of the first plurality of teeth is arranged having a first constant pitch radius from the actuator axis of rotation and a second portion of the first plurality of teeth is arranged having a first variable pitch radius from the actuator axis of rotation. The variable pitch radius may be non-linear, and may further be derived from an exponential function. Additionally, the variable pitch may include a first portion having a substantially linear pitch and a second portion having a substantially non-linear pitch. 
         [0011]    The present invention therefore provides a climate control door drive mechanism that has the ability to slowly rotate climate control doors at a rate of speed necessary to meet design requirements while also providing the ability to still meet total rotation time requirements. As a result, a climate control door rotation speed may be linearly or non-linearly controlled when there is a need to meet temperature door linearity performance, and the climate control door rotation speed may also be increased to meet total temperature door rotation time performance. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0012]    The above, as well as other advantages of the present invention will become readily apparent to those skilled in the art from the following detailed description, particularly when considered in the light of the drawings described herein. 
           [0013]      FIG. 1  is a perspective view of a prior art mechanism having a gear set with a constant linear pitch. 
           [0014]      FIG. 2  is a perspective view of a prior art cam mechanism. 
           [0015]      FIG. 3  is a perspective view of a non-linear, variable pitch gear set in a first door position according to an embodiment of the invention. 
           [0016]      FIG. 4  is a perspective view of the non-liner, variable pitch gear set of  FIG. 3  in a second door position according to an embodiment of the invention. 
           [0017]      FIG. 5  is a graphical depiction of certain non-linear, variable pitch gear profiles according to an embodiment of the invention. 
       
    
    
     DETAILED DESCRIPTION 
       [0018]    The following detailed description and appended drawings describe and illustrate various embodiments of the invention. The description and drawings serve to enable one skilled in the art to make and use the invention, and are not intended to limit the scope of the invention in any manner. 
         [0019]    A prior art mechanism  100  using a linear pitch gear set having a constant gear ratio is shown with reference to  FIG. 1 . An actuator gear  112  includes an actuator gear hub  114  that is configured to receive an output shaft of an actuator mechanism (not shown). It is understood that the actuator mechanism may include a manually rotatable shaft, a motor, or other device having a rotational output. The actuator gear hub  114  is typically integrally attached to the actuator gear  112  so that a rotational force applied in the actuator gear hub  114  is translated directly to the actuator gear  112 . The actuator gear  112  includes a plurality of teeth  116  located on a predetermined portion of the circumference  118 . As shown in  FIG. 1 , the actuator gear  112  has a fan shape that has an arcuate outer peripheral part  120  corresponding to a portion of the circumference  118 . A door gear  122  having a plurality of teeth  124  meshed with the plurality of teeth  116  of the actuator gear  112  is secured to a rotatable shaft  126 . The rotatable shaft  126  is attached to a gear door (not shown) that rotates integrally with the rotatable shaft  126 . The plurality of teeth  124  of the door gear  122  is included along an outer circumference  128  of the door gear  122 . Additionally, as shown in  FIG. 1 , the outer circumference  128  of the door gear  122  may be less than  360  degrees. 
         [0020]    The actuator gear hub  114  defines an axis of rotation  130  about which the actuator gear  112  rotates. The outer circumference  118  of the actuator gear  112  is a fixed distance, or constant radius, R 1  from the axis of rotation  130  of the actuator gear  112 . The constant radius R 1  of the actuator gear  112  results in the actuator gear  112  having a fixed pitch radius from the axis of rotation  130 . 
         [0021]    Similarly, the rotatable shaft  126  of the door gear  122  defines an axis of rotation  132  about which the door gear  122  rotates. The outer circumference  128  of the door gear is a fixed distance, or constant radius, R 2  from the axis of rotation  132  of the door gear  122 . The constant radius R 2  of the door gear  122  results in the door gear  122  having a fixed pitch radius from the axis of rotation  132 . 
         [0022]    As a non-limiting example, in one configuration the door gear  122  may have a constant radius R 2  equal to about 60 mm, while the actuator gear  112  may have a constant radius R 1  equal to about 20 mm. When intermeshed as shown in  FIG. 1 , the mechanism  100  develops a 3:1 gear ratio, meaning that for every 3 degrees of rotation of the actuator gear  112 , the door gear  122  rotates 1 degree. Due to the fixed pitch radii of both the actuator gear  112  and the door gear  122 , the rate of rotation by the door gear  122  is fixed in the 3:1 ratio. In this example, therefore, the actuator gear  112  must rotate 270 degrees to achieve a total rotation of 90 degrees by the door gear  122  (and by the gear door, not shown). The prior art design shown in  FIG. 1  therefore provides for linear control of the gear door and the ability to rotate an air door at a rate of speed (deg/s) that is less than a rate of speed (deg/s) of an actuator, but only by adding considerable rotation distance and time to the mechanism  100 . 
         [0023]    Another known mechanism that provides the ability to rotate an air door at a rate of speed less than a rate of speed of a drive gear mechanism attached to a rotating gear door without increasing the total time of rotation beyond a desired target is shown in  FIG. 2 . A cam drive mechanism  200  includes a cam  210  attached to a door lever  212 . The cam  210  includes an actuator hub  214  integrally formed thereon that is configured to receive an output shaft of an actuator mechanism (not shown). It is understood that the actuator mechanism may include a manually rotatable shaft, a motor, or other device having a rotational output. The actuator hub  214  is typically integrally attached to the cam  210  so that rotational force applied in the actuator hub  214  is translated directly to the cam  210 . The door lever  212  is attached to an air door (not shown) proximate a first end  216 , while a second end  218  of the door lever  212  is coupled to the cam  210 . A separate cam bracket  220  is used to mount the cam  210  to the actuator (not shown), and may further be useful to retain the cam  210  and the door lever  212  in proper alignment. As a non-limiting example, the cam  210  shown in  FIG. 2  may be rotated by the actuator (not shown) through approximately 120 degrees of rotation, translating approximately 70 degrees of rotation to the air door (not shown) through the door lever  212 . The cam mechanism  200  therefore is able to provide effective temperature linearity control, but it may require additional actuator rotation and additional rotation time. The cam mechanism  200  also requires the extra cam bracket  220 , increasing the part count while adding weight, package volume, and cost. 
         [0024]    A door opening mechanism  300  is shown in  FIGS. 3 and 4  that addresses the shortcomings of the prior art. In particular,  FIG. 3  demonstrates the door opening mechanism  300  in a starting position, or a full hot door position, while  FIG. 4  demonstrates the door opening mechanism  300  in an ending position, or a full cold door position. The door opening mechanism  300  includes an actuator gear  312  and a door gear  322 . The actuator gear  312  includes an actuator gear hub  314  that is configured to receive an output shaft of an actuator mechanism (not shown). It is understood that the actuator mechanism may include a manually rotatable shaft, a motor, or other device having a rotational output. The actuator gear hub  314  is typically integrally attached to the actuator gear  312  so that a rotational force applied in the actuator gear hub  314  is translated directly to the actuator gear  312 . The actuator gear  312  includes a plurality of teeth  316  located on a predetermined portion of the circumference  318  of the actuator gear  312 . As shown in  FIG. 3 , the actuator gear  312  has a fan shape that has an arcuate outer peripheral part  320  corresponding to at least a portion of the circumference  318 . It is understood that the actuator gear  312  may have any desired shape that presents the arcuate outer peripheral part  320 . 
         [0025]    The door gear  322  includes a plurality of teeth  324  meshed with the plurality of teeth  316  of the actuator gear  312  and is secured to a rotatable shaft  326 . The rotatable shaft  326  is attached to a gear door (not shown) that rotates integrally with the rotatable shaft  326 . The plurality of teeth  324  of the door gear  322  is included along an outer circumference  328  of the door gear  322 . Additionally, as shown in  FIGS. 3 and 4 , the door gear  322  has a fan shape that has an arcuate outer peripheral part  330  corresponding to at least a portion of the circumference  328 . The outer circumference  328  of the door gear  322  may be less than  360  degrees, and it is understood that the door gear  322  may have any desired shape that presents at least the arcuate outer peripheral part  330  that includes the plurality of teeth  324  intermeshed with the plurality of teeth  316  of the actuator gear  312 . 
         [0026]    The actuator gear  312  and the door gear  322  may be made from any suitable material, without limitation. Typically one gear material can be polyoxymethylene (POM) and the other gear material can be 40% mineral filled Nylon. However, it is understood that other materials and combinations of materials can be used. 
         [0027]    The actuator gear hub  314  defines an axis of rotation  332  about which the actuator gear  312  rotates. Similarly, the rotatable shaft  326  of the door gear  322  defines an axis of rotation  334  about which the door gear  322  rotates. Further, the axis of rotation  332  of the actuator gear  312  is separated from the axis of rotation  334  of the door gear  322  by a fixed center-to-center distance CD. It is understood that the actuator gear  312  and the door gear  322  are sized and shaped so that the actuator gear  312  rotates about the axis of rotation  314  and the door gear  322  rotates about the axis of rotation  334  while maintaining intermeshing of the plurality of teeth  316  of the actuator gear  312  with the plurality of teeth  324  of the door gear  322 , and while maintaining the fixed center-to-center distance CD. 
         [0028]    The exemplary door opening mechanism  300  of  FIGS. 3 and 4  may be distinguished from the prior art, however, by an ability to provide a non-linear predefined variable gear pitch in at least a portion of the gear pair travel. As non-limiting examples, the door opening mechanism  300  may provide a transition from a linear to a non-linear gear pitch near the start of gear travel. The door opening mechanism may also be configured to provide a transition from a non-linear gear pitch to a linear gear pitch near the start of gear travel. Also, the door opening mechanism may be configured to provide both transitions from linear to non-linear gear pitch and from non-linear to linear gear pitch at any point of the gear travel. 
         [0029]    A variable gear pitch is provided in the door opening mechanism  300  by providing a predefined variable gear pitch for both the actuator gear  312  and the door gear  322 . With reference to the actuator gear  312 , the arcuate outer peripheral part  320  includes a first actuator gear arcuate portion  340  and a second actuator gear arcuate portion  342 . In  FIGS. 3 and 4 , the first actuator gear arcuate portion  340  includes that portion of the arcuate outer peripheral part  320  closest to the axis of rotation  332  of the actuator gear hub  314  having a constant pitch radius R ac , while the second actuator gear arcuate portion  342  includes that portion of the arcuate outer peripheral part  320  farthest away from the axis of rotation  332  of the actuator gear hub  314  having a variable pitch radius R av . It is understood, however, that other configurations of the arcuate outer peripheral part  320  may be used, as desirable. With reference to the door gear  322 , the arcuate outer peripheral part  330  includes a first door gear arcuate portion  350  and a second door gear arcuate portion  352 . In  FIGS. 3 and 4 , the first door gear arcuate portion  350  of the door gear  322  includes that portion of the arcuate outer peripheral part  330  farthest away from the axis of rotation  334  of the door gear  322  having a constant pitch radius R dc , while the second door gear arcuate portion  352  of the door gear  322  includes that portion of the arcuate outer peripheral part  330  closest to the axis of rotation  334  of the door gear  322  having a variable pitch radius R dv . It is understood, however, that other configurations of the arcuate outer peripheral part  330  may designed, as desirable 
         [0030]      FIG. 3  shows the door opening mechanism in a starting position corresponding to a full hot mixing position of the gear door. The first actuator gear arcuate portion  340  of the actuator gear  312  having constant pitch radius R ac  corresponds to approximately the first 30 degrees of rotation by the actuator gear  312  in the clockwise direction. The first door gear arcuate portion  350  of the door gear  322  having a constant pitch radius R dc  corresponds to approximately the first 10 degrees of rotation by the door gear  322  in the counter-clockwise direction. It is understood that other degrees of rotation can be used as desired. As the actuator gear  312  rotates through the first actuator gear arcuate portion  340  that also corresponds to the first door gear arcuate portion  350 , the door gear  322 , fixed to the air door (not shown), rotates at a constant speed of 1 degree for every 3 degrees of rotation by the actuator gear  312 , corresponding to a 1:3 gear ratio. 
         [0031]    The second actuator gear arcuate portion  342  of the actuator gear  312  having variable pitch radius R av  corresponds to approximately the next 130 degrees of rotation by the actuator gear  312  in the clockwise direction as shown in  FIG. 3 . The second door gear arcuate portion  352  of the door gear  322  having a variable pitch radius R dv  corresponds to approximately the next 80 degrees of rotation by the door gear  322  in the counter-clockwise direction. It is understood that other degrees of rotation can be used as desired. Thus, for the next 130 degrees of actuator gear rotation, the pitch between the two gears changes until the door rotates an additional 80° of rotation. In the embodiment shown in  FIGS. 3 and 4 , the variable pitch radius R av  of the actuator gear  312  and the variable pitch radius R dv  of the door gear  322  change exponentially to achieve the example door gear movement. 
         [0032]    Using the non-linear, variable pitch gear pair, for example, a user can operate a temperature control knob for an HVAC air-handling system that is coupled to the actuator gear. A rotation of the knob throughout a portion of a temperature range may provide a corresponding movement of the door gear, while rotation of the knob throughout another portion of the temperature range may provide an increase or decrease in the corresponding movement of the door gear. 
         [0033]    The door opening mechanism  300  may include corresponding non-linear, variable pitch actuator gears  312  and door gears  322  (gear pairs) having a multitude of variable profiles. For example, Table 1 shows two exemplary gear profiles. According to Example 1, a first arcuate portion of the gear pair may include a constant 2(actuator):1(door) linear profile gear ratio in the direction rotating from full hot to full cold, a second arcuate portion of the gear pair may include a non-linear profile until the gear pitch reaches a 1.5:1 gear ratio, after which a third arcuate portion of the gear pair maintains the 1.5:1 linear profile gear ratio. The total amount of Example 1 temperature actuator rotation is approximately 155 degrees, while the total amount of door rotation is approximately 90 degrees. 
         [0034]    According to the Example 2 of Table 1, a gear pair may be designed having a first arcuate portion with a constant 3(actuator):1(door) linear profile gear ratio in the direction rotating from full hot to full cold, and a second arcuate portion having a non-linear variable pitch gear profile until the end, at which the gear profile may specify, for example a 0.8:1 gear ratio. The total amount of the variant of Example 2 temperature actuator rotation is approximately 160 degrees. The total amount of door rotation is approximately 94 degrees. 
         [0000]    
       
         
               
             
               
               
               
               
               
             
           
               
                 TABLE 1 
               
             
             
               
                   
               
               
                 Pitch Definition 
               
             
          
           
               
                 Example 
                 Start (FH) 
                 Middle 
                 End (FC) 
                 reason 
               
               
                   
               
               
                 1 
                 constant: 2:1 
                 variable 
                 constant: 1.5:1 
                 Packaging and improve- 
               
               
                   
                   
                   
                   
                 ment of temp. linearity 
               
               
                   
                   
                   
                   
                 while maintaining the 
               
               
                   
                   
                   
                   
                 rotation time require- 
               
               
                   
                   
                   
                   
                 ment. 
               
               
                 2 
                 constant: 3:1 
                 variable 
                 variable: 0.8:1 
                 Improvement of temp. 
               
               
                   
                   
                   
                   
                 linearity while maintain- 
               
               
                   
                   
                   
                   
                 ing the rotation  
               
               
                   
                   
                   
                   
                 time requirement. 
               
               
                   
               
             
          
         
       
     
         [0035]    Several reference non-linear profiles for exemplary gear pairs are also shown graphically in  FIG. 5 . In particular,  FIG. 5  shows a slope of the gear profile as the pitch radius changes from start to finish over 130° of rotation. The function that defines the slope in this case is an exponential function, but it is understood that any applicable function may be utilized to establish appropriate gear pair profiles. The curve  360  closest to the origin (X,Y of 0,0) in  FIG. 5  shows a first minor exemplary profile. The second closest curve  362  to the origin shows a base exemplary profile. The third closest curve  364  to the origin shows an exemplary actuator pitch profile. The fourth closest curve  366  to the origin shows an exemplary major profile. The curve  368  furthest from the origin shows a reference circle. 
         [0036]    According to one embodiment, the gear pitch radius curves in  FIG. 5  may be derived using exponential functions. For example, the actuator gear variable pitch radius R av  and rotation angle Θ may have the form of Equation 1: 
         [0000]      R av =Ae kθ   Equation 1
 
         [0000]    where R av  is the pitch radius of the actuator gear, θ is the angle of actuator rotation and A and k are chosen constants. Similarly, for a given center-to-center distance CD, a corresponding door gear variable pitch radius Rdv may have the form of Equation 2: 
         [0000]        R   dv   =CD−R   av    Equation 2
 
         [0000]    where R dv  is the pitch radius of the door gear. Equation 3 may then be used to determine a door gear rotation angle Ø, where: 
         [0000]      Ø=1 /k*In [( CD−Ae   kΘ )/ A]   Equation 3
 
         [0037]    In Equations 1-3, CD, k, A and Θ are inputs and R av , R dv  and Ø are outputs. 
         [0038]    According to the invention, the non-linear, variable pitch gear pair design can be used with climate control door drives in a motor vehicle air-handling system. Using this non-linear gear technology, it is possible to reduce the rate of speed of the climate control door rotation relative to the rate of speed of the actuator output shaft rotation in those locations where the climate control door is sensitive to temperature control curve linearity. Then, at other climate control door locations, where the climate control door position is less sensitive to temperature linearity, the rate of the climate control door rotational speed relative to that of the actuator output shaft speed can be increased to a speed that reduces a time necessary to completely rotate the door. Furthermore, by reducing the rate of speed of the door rotation at the sensitive end of rotation, it is possible to reduce the need for ventilation conduits or shades. The reduction in shade use can thereby increase the amount of cross section for airflow. Therefore, improved temperature linearity can be achieved with an increased cross section in airflow without increasing the time needed to rotate the door from one end of rotation to the other. 
         [0039]    While certain representative embodiments and details have been shown for purposes of illustrating the invention, it will be apparent to those skilled in the art that various changes may be made without departing from the scope of the disclosure, which is further described in the following appended claims.

Technology Classification (CPC): 1