JP6607067B2 - Auxiliary drive belt tension adjusting device - Google Patents

Description

  The present invention relates to an accessory drive belt tension adjusting device and an accessory drive belt tension adjusting device.

  In recent years, demands for reducing the environmental load of automobiles are increasing, and there is a demand for stricter fuel consumption regulations (reduction of CO2 emissions). In response to such environmental conservation and resource saving demands, there is an increasing need for items that improve fuel consumption, and idling stop mechanisms are being installed and hybridized. In automobile internal combustion engines, a belt drive system is driven by mechanically connecting auxiliary machinery such as water pumps, compressors, and radiator fans required to operate the main engine and air conditioner with an auxiliary belt. The auxiliary drive belt system (hereinafter referred to as “auxiliary drive system”) is generally used. In the accessory drive system, a driving force is transmitted through an accessory belt wound around a crank pulley that is a main machine pulley and each accessory pulley. In this auxiliary machine drive system, there is an increasing need for loss reduction.

  In the auxiliary drive system that transmits the driving force by the belt, it is necessary to apply tension to the belt so that slip does not occur between each pulley and the belt. It is common to use. This tensioner has a function of keeping the tension of the belt in a section provided with the tensioner constant. The tension applied to the belt increases on the side pulled by the drive pulley (hereinafter also referred to as “tension side”) and decreases on the side pushed by the drive pulley (hereinafter also referred to as “relaxation side”). For example, when an alternator is provided as an auxiliary machine, an engine crank pulley that is a main machine pulley serves as a drive pulley, and an alternator pulley that serves as an auxiliary machine pulley serves as a driven pulley.

  The tension required to drive the belt increases in proportion to the transmission torque transmitted by the belt. That is, the appropriate value of the tension required to drive the belt varies depending on the load state of the driven pulley. Specifically, for example, the tension required to drive the belt changes according to the power generation amount of the alternator. When the power generation amount of the alternator is large and the transmission torque is large, the rotational resistance of the auxiliary pulley connected to the rotor of the alternator increases compared to the case where the power generation amount of the alternator is small and the transmission torque is small. In order to obtain torque, a larger tension is required than in the case of obtaining a small transmission torque. For this reason, for example, the tensioner is designed to prevent slippage between each pulley and the belt in advance even if the power generation amount of the alternator is maximized and the rotation resistance of the auxiliary pulley of the alternator is maximized. It is set so that a tension corresponding to the maximum power generation amount of the alternator can be obtained.

  Here, when a tensioner is provided on the tension side, even if the load on the driven pulley becomes maximum, the tension on the loose side where the tension applied to the belt is small causes slippage between each pulley and the belt. It is necessary to set a tension applied to the tension side of the belt (hereinafter referred to as “tension-side tension”) so that the tension does not occur. In other words, when the load on the driven pulley becomes maximum, it is necessary to set the tension side tension as the initial tension so as to obtain the slack side tension so that no slip or the like occurs between each pulley and the belt. In this way, when the tensioner is provided on the tension side, it is necessary to set the tension side tension required at the maximum load of the driven pulley as the initial tension, so it is not necessary when the load on the driven pulley is small and the transmission torque is small The tension is applied to the belt, and the transmission efficiency of the driving force by the belt is lowered.

  On the other hand, when a tensioner is provided on the slack side, the initial tension of the tension applied to the slack side of the belt (hereinafter referred to as “relaxation side tension”) may be the slack side tension required at the maximum load of the driven pulley. . That is, when the tensioner is provided in the accessory drive system, the initial tension applied to the belt can be made smaller when the tensioner is provided on the loose side of the belt than when the tensioner is provided on the belt tension side. For this reason, the tensioner is preferably provided on the loose side of the belt.

  In vehicles equipped with an idling stop mechanism and vehicles equipped with a hybrid system, ISG-equipped engines that employ a generator with starter function (ISG: Integrated Starter Generator) are becoming popular in place of conventional alternators. In such an ISG-equipped engine, the driving side and the driven side are switched between when the driving force by the engine is transmitted to the ISG for regeneration and when the driving force by the ISG is transmitted to perform engine start and driving assist. . That is, at the time of regeneration, the crank pulley becomes a drive pulley and the ISG pulley becomes a driven pulley, and at the time of engine start or drive assist, the ISG pulley becomes a drive pulley and the crank pulley becomes a driven pulley. In this way, in an accessory drive system in which the drive side and the driven side are switched, the tension side and the loose side are switched depending on which pulley is the drive pulley, and transmission torque is generated from one to the other. For this reason, for example, Patent Document 1 describes a belt tension adjusting device that adjusts the tension applied to the belt by swinging the auxiliary machine according to the operation state of the auxiliary machine.

JP 2009-180177 A

  However, since the one described in Patent Document 1 has a structure that swings the auxiliary machine (motor generator) itself, there is a possibility that the wiring of the motor generator may be disconnected due to fatigue deterioration due to repeated swinging. It can be a factor of lowering reliability in the machine drive system.

  The present invention has been made in view of the above, and an object of the present invention is to provide an accessory drive belt tension adjusting device capable of achieving both high reliability and loss reduction of an accessory drive system.

  In order to solve the above-described problems and achieve the object, an auxiliary machine driving belt tension adjusting device includes a roller that applies tension to a loose side section of a belt that transmits driving force between a first pulley and a second pulley. An arm that supports the roller, and a rocking mechanism that rocks the arm with a rotation axis of the second pulley as a rotation axis, and the rocking mechanism is fixed to the shaft of the second pulley. A first housing, a second housing which is provided on the outer side in the circumferential direction of the first housing and is supported so as to be rotatable in the circumferential direction with respect to the first housing, and the first housing or the second housing Rotation-linear motion conversion for converting a circumferential phase difference caused by the rotational motion between the first housing and the second housing, which changes according to the torque applied to the shaft, into an axial linear motion Mechanism, Linear converts the linear motion of the serial axial to the rotation movement of the arm - and includes a rotation conversion mechanism.

  With the above-described configuration, the slack side tension proportional to the transmission torque can be applied to the belt, and the loss of the accessory drive system can be reduced.

  Further, as a desirable aspect, the belt transmits a driving force bidirectionally from one to the other between the first pulley and the second pulley, and the roller transmits the second pulley from the second pulley of the belt. It is preferable to include a first roller that applies tension to a feeding section to one pulley and a second roller that applies tension to a feeding section from the first pulley to the second pulley of the belt.

  With the above configuration, in an auxiliary drive system in which the drive side and the driven side are switched, it is possible to apply a slack side tension proportional to the transmission torque generated in both directions to the belt, and the auxiliary drive in which the drive side and the driven side are switched. It becomes possible to reduce the loss of the system.

  In the above configuration, the rotation-linear motion conversion mechanism is provided between a protrusion provided on the outer peripheral surface of the first housing and a protrusion provided on the inner peripheral surface of the second housing. And a first annular member provided between the first housing and the second housing via a screw portion.

  Further, in the above configuration, the rotation-linear motion conversion mechanism is an annular first cam that is disposed with the rolling elements interposed therebetween and cam surfaces facing each other in the axial direction, and an urging force is applied in the axial direction by an elastic member. A first annular member provided between the first housing and the second housing, wherein the first cam plate is positioned circumferentially with respect to the first housing. The second cam plate is arranged with its circumferential position and axial position fixed with respect to the second housing, and the first annular member is axially disposed on the first cam plate. One end may be in contact with each other.

  Further, in the above configuration, a base member fixed in a circumferential direction with respect to the rotation axis of the second pulley is provided, and the base member has a base annular portion centered on the rotation axis of the second pulley. And the arm is provided on the inner side in the circumferential direction of the base annular portion, and has an arm annular portion that is supported so as to be rotatable in the circumferential direction with respect to the base annular portion. The rotation conversion mechanism may include a second annular member provided via a screw portion between the inner circumferential surface or the outer circumferential surface of the arm annular portion.

  Moreover, the said structure WHEREIN: The said 2nd annular member may be connected with the said 1st annular member via the bearing.

  ADVANTAGE OF THE INVENTION According to this invention, the auxiliary machine drive belt tension | tensile_strength adjustment apparatus which can make high reliability and loss reduction of an auxiliary machine drive system compatible can be provided.

FIG. 1 is a diagram illustrating an example of an auxiliary machine drive system. FIG. 2 is a conceptual diagram showing the relationship between the transmission torque in the drive pulley and the tension on the tension side and the loose side. FIG. 3 is a diagram showing the relationship between transmission torque and tension in an accessory drive system in which a belt is wound around two pulleys. FIG. 4 is a structural conceptual diagram of an accessory drive system to which the accessory drive belt tension adjusting device according to the first embodiment is applied. FIG. 5 is a schematic cross-sectional view of the accessory drive belt tension adjusting device according to the first embodiment. 6 is a cross-sectional view taken along line AA shown in FIG. FIG. 7 is a diagram illustrating a circumferential phase difference caused by a rotational movement between the first housing and the second housing when the second pulley generates a driving force. FIG. 8 is a diagram illustrating a circumferential phase difference caused by a rotational movement between the first housing and the second housing when the first pulley generates a driving force. FIG. 9 is a diagram illustrating a state change of the rotation-linear motion conversion mechanism and the linear motion-rotation conversion mechanism when the second pulley generates a driving force. FIG. 10 is a diagram illustrating a state change of the rotation-linear motion conversion mechanism and the linear motion-rotation conversion mechanism when the first pulley generates a driving force. FIG. 11 is a diagram illustrating an operation example of the accessory drive belt tension adjusting device according to the first embodiment when the second pulley generates a driving force. FIG. 12 is a diagram illustrating an operation example of the accessory driving belt tension adjusting device according to the first embodiment when the first pulley generates the driving force. FIG. 13 is a structural conceptual diagram of an accessory drive system to which an accessory drive belt tension adjusting device according to a modification of the first embodiment is applied. FIG. 14 is a schematic cross-sectional view of the accessory drive belt tension adjusting device according to the second embodiment. FIG. 15 is a view of the first cam plate, the rolling element, and the second cam plate as seen in the direction indicated by the arrow A in FIG. 16 is a view of the first cam plate, the rolling element, and the second cam plate as viewed in the direction indicated by the arrow B in FIG. FIG. 17 is a diagram illustrating a state change of the rotation-linear motion conversion mechanism and the linear motion-rotation conversion mechanism when the first pulley generates a driving force. FIG. 18 is a diagram illustrating an operation example of the accessory driving belt tension adjusting device according to the second embodiment when the first pulley generates the driving force.

  DESCRIPTION OF EMBODIMENTS Embodiments (embodiments) for carrying out the present invention will be described in detail with reference to the drawings. The present invention is not limited by the contents described in the following embodiments. The constituent elements described below include those that can be easily assumed by those skilled in the art and those that are substantially the same. Furthermore, the constituent elements described below can be appropriately combined.

(Embodiment 1)
FIG. 1 is a diagram illustrating an example of an auxiliary machine drive system. The auxiliary drive system shown in FIG. 1 is a machine that uses auxiliary belts to connect auxiliary equipment such as a water pump, a compressor, and a radiator fan necessary for operating an engine, an air conditioner, etc. Is an auxiliary drive belt system of a belt drive system that is connected and driven in an integrated manner, and a crank pulley 101 provided on a crankshaft of an engine that is a main machine, and auxiliary pulleys 201 to 201 provided on a shaft of each auxiliary machine The belt 301 is wound around the belt 205, and the driving force is transmitted to each auxiliary machine via the belt 301.

  In this embodiment, when transmitting the driving force generated by the engine to each auxiliary machine in the example shown in FIG. 1, the crank pulley 101 of the engine is referred to as a drive pulley, and the auxiliary pulleys 201 to 201 of each auxiliary machine are used. 205 is called a driven pulley. In addition, in an auxiliary machine drive system provided with a starter function generator (ISG: Integrated Start Generator) as an auxiliary machine, when an engine start or drive assist is performed by transmitting a drive force by the ISG, an ISG shaft The ISG pulley provided in the shaft is a driving pulley, and the crank pulley 101 is a driven pulley.

  FIG. 2 is a conceptual diagram showing the relationship between the transmission torque in the drive pulley and the tension on the tension side and the loose side. FIG. 3 is a diagram showing the relationship between transmission torque and tension in an accessory drive system in which a belt is wound around two pulleys. In the example shown in FIGS. 2 and 3, the relationship between the tension side tension T1 and the slack side tension T2 when the driving pulley 100 generates a driving force in the direction of the arrow is shown. FIG. 3 (a-1) shows an example in which the tensioner 400 is not provided on either the tension side or the loose side, and FIG. 3 (a-2) shows that the tensioner 400 is provided on either the tension side or the loose side. It shows the relationship between the transmission torque and tension when not. 3 (b-1) shows an example in which the tensioner 400 is provided on the tension side, and FIG. 3 (b-2) shows the relationship between the transmission torque and the tension when the tensioner 400 is provided on the tension side. Yes. 3 (c-1) shows an example in which a tensioner 400 is provided on the loose side, and FIG. 3 (c-2) shows the relationship between transmission torque and tension when the tensioner 400 is provided on the loose side. Yes. Moreover, the broken line described in FIG. 3 (a-2) thru | or FIG. 3 (c-2) shows the ideal characteristic of tension | tensile_strength side tension | tensile_strength T1, and it describes in FIG. 3 (a-2) thru | or FIG. The alternate long and short dash line indicates the ideal characteristic of the slack side tension T2.

  As shown in FIG. 2, when the driving pulley 100 rotates in the direction indicated by the arrow to generate a driving force, the transmission torque N transmitted by the belt is the radius r of the driving pulley 100, the tension on the tension side T1, the loose side. It represents with the following formula | equation using tension | tensile_strength T2.

  N = r × (T1-T2)

  As shown in the above equation, the transmission torque N is proportional to the tension difference T1-T2 between the tension side tension T1 and the loose side tension T2. That is, the driving force generated by the driving pulley 100 can be transmitted to the driven pulley by giving the tension difference T1-T2 necessary for transmitting torque without causing slip in the accessory driving system.

  As shown in FIG. 3 (a-1), even when the tensioner 400 is not provided on either the tension side or the loose side, the initial tension T0 applied to the belt 300 is set as shown in FIG. 3 (a-2). If set appropriately, the maximum transmission torque Nmax in the accessory drive system can be obtained. Here, when the slack side tension T2 becomes equal to or less than the minimum value T2min of the slack side tension T2 for obtaining the maximum transmission torque Nmax, slip of the belt 300 occurs in the maximum transmission torque Nmax or a transmission torque region below the maximum transmission torque Nmax. . Accordingly, it is necessary to set the initial tension T0 so that the slack side tension T2 does not fall below the minimum value T2min when the maximum transmission torque Nmax to be achieved in the accessory drive system is generated. In the example shown in FIG. 3, when the maximum transmission torque Nmax is generated, the maximum value of the tension side tension T1 when the loose side tension T2 becomes the minimum value T2min is T1max.

  As shown in FIG. 3 (b-1), when the tensioner 400 is provided on the tension side and the maximum transmission torque Nmax is achieved by keeping the tension side tension T1 constant, the tension is shown in FIG. 3 (b-2). Thus, it is necessary to set the tensioner 400 so that the initial tension T0 is equal to or greater than T1max. In this case, excessive tension that is not necessary in the transmission torque region below the maximum transmission torque Nmax is applied to the belt 300, and a large load is applied to the driving pulley 100 and the driven pulley 200, so that the transmission efficiency of the driving force is improved. descend.

  On the other hand, as shown in FIG. 3 (c-1), when the tensioner 400 is provided on the slack side and the slack side tension T2 is kept constant, the maximum transmission torque Nmax is to be achieved. As shown in -2), the tensioner 400 may be set so that the initial tension T0 is T2 min or more. However, even when the tensioner 400 is provided on the loose side (see FIG. 3 (c-1)), it is necessary to always apply a tension of T2 min or more to the loose side regardless of the magnitude of the transmission torque (FIG. 3 (c). -2)). In an internal combustion engine such as an automobile, the loss in a low torque region such as idling or high-speed running is made smaller, and the loose side tension T2 is brought closer to the ideal characteristic, that is, the loose side tension T2 proportional to the magnitude of the transmitted torque. It is expected that fuel efficiency will be further improved.

  FIG. 4 is a structural conceptual diagram of an accessory drive system to which the accessory drive belt tension adjusting device according to the first embodiment is applied. In the accessory drive system shown in FIG. 4, a belt 3 that transmits a driving force is wound between a first pulley 1 and a second pulley 2. FIG. 4 shows an example of the structural concept in the initial state of the accessory drive system to which the accessory drive belt tension adjusting device according to the present embodiment is applied, that is, in the stopped state of the accessory drive system.

  In the accessory drive system shown in FIG. 4, the first pulley 1 is, for example, a crank pulley provided on the crankshaft of an engine that is an internal combustion engine of an automobile, and the second pulley 2 is provided on, for example, an ISG shaft. ISG pulley. That is, in the auxiliary drive system shown in FIG. 4, the drive side and the driven are driven in the case where the driving force by the engine is transmitted to the ISG for regeneration, and in the case where the driving force by the ISG is transmitted for engine start and drive assist. The side changes. That is, during regeneration, the crank pulley that is the first pulley 1 is a drive pulley and the ISG pulley that is the second pulley 2 is a driven pulley. The crank pulley which is the pulley 1 is a driven pulley. In this way, in the auxiliary drive system in which the drive side and the driven side are switched, the tension side and the loose side are switched depending on which pulley is the drive pulley, so depending on which pulley is the drive pulley. Bidirectional transmission torque is generated. That is, in the auxiliary drive system in which the drive side and the driven side are switched, the belt 3 is driven bidirectionally from one to the other between the crank pulley as the first pulley 1 and the ISG pulley as the second pulley 2. Transmit power.

  As described above, in the accessory drive system, it is preferable to apply the slack side tension proportional to the magnitude of the transmission torque. The auxiliary machine drive belt tension adjusting device 10 according to the present embodiment can provide the belt 3 with a loose side tension T2 proportional to the transmission torque generated in both directions in an auxiliary machine drive system in which the drive side and the driven side are switched. It has a possible configuration. Hereinafter, the configuration of the accessory drive belt tension adjusting device 10 according to the present embodiment will be described. In the following description, it is assumed that the belt 3 advances in the direction indicated by the arrow shown in FIG.

  FIG. 5 is a schematic cross-sectional view of the accessory drive belt tension adjusting device according to the first embodiment. 6 is a cross-sectional view taken along line AA shown in FIG.

  As shown in FIG. 5, the accessory drive belt tension adjusting device 10 according to this embodiment includes a first roller 11, a second roller 12, an arm 13, a base member 14, and a swing mechanism 4. I have.

  The first roller 11 applies tension to the feeding section from the second pulley 2 to the first pulley 1 of the belt 3 that transmits the driving force bidirectionally from one to the other between the first pulley 1 and the second pulley 2. give. The second roller 12 applies tension to the delivery section of the belt 3 from the first pulley 1 to the second pulley 2.

  The arm 13 supports the first roller 11 and the second roller 12.

  The base member 14 is fixed in the circumferential direction with respect to the rotation axis of the second pulley 2.

  The swing mechanism 4 swings the arm 13 with the rotation axis AX of the second pulley 2 as the pivot axis.

  As shown in FIG. 5, the swing mechanism 4 of the accessory drive belt tension adjusting device 10 according to the present embodiment includes the components of the second pulley 2. Specifically, the swing mechanism 4 includes a first housing 41, a second housing 42, a rotation-linear motion conversion mechanism 6, and a linear motion-rotation conversion mechanism 7.

  The first housing 41 is a cylindrical member fixed to the shaft 5 of the second pulley 2.

  The second housing 42 is a cylindrical member that is provided on the outer side in the circumferential direction of the first housing 41 via a first bearing 81 and is supported so as to be rotatable in the circumferential direction with respect to the first housing 41. The first bearing 81 is constituted by, for example, a ball bearing, but the present invention is not limited by the configuration or type of the first bearing 81.

  The rotation-linear motion conversion mechanism 6 is configured to change the circumferential phase difference between the first housing 41 and the second housing 42 that changes according to the torque applied to the first housing 41 or the second housing 42 in the axial direction. Convert to linear motion.

  The linear motion-rotation conversion mechanism 7 converts the axial linear motion into the rotational motion of the arm 13.

  The rotation / linear motion conversion mechanism 6 includes an elastic member 61 and a first annular member 63.

  As shown in FIG. 6, the elastic member 61 is provided between a protruding portion 411 provided on the outer peripheral surface of the first housing 41 and a protruding portion 421 provided on the inner peripheral surface of the second housing 42. . The elastic member 61 may be, for example, a leaf spring or a coil spring, or may be a solid member such as elastic rubber. The present invention is not limited by the configuration, material, and shape of the elastic member 61.

  As shown in FIG. 5, the first annular member 63 is provided between the first housing 41 and between the second housing 42 via screw portions 62.

  The screw portion 62 is provided on the outer peripheral surface of the first annular member 63 because the male screw provided on the inner peripheral surface of the first annular member 63 and the screw are provided on the inner peripheral surface of the first housing 41. Since the male screw is provided on the inner peripheral surface of the second housing 42, the screw is engaged with the male screw. In addition, the screw part 62 can also be comprised, for example with a ball screw or a slide screw. The present invention is not limited by the configuration or type of the screw portion 62.

  As shown in FIG. 5, the base member 14 has an annular base annular portion 141 centering on the rotation axis AX of the second pulley 2.

  As shown in FIG. 5, the arm 13 has an annular arm ring portion 131 provided on the inner peripheral surface of the base ring portion 141 via a second bearing 82. In addition, although the 2nd bearing 82 is comprised with a ball bearing, for example, this invention is not limited by the structure or kind of this 2nd bearing 82. FIG.

  As shown in FIG. 5, the linear motion-rotation conversion mechanism 7 includes a second annular member 72 provided via a screw portion 71 between the inner annular surface of the arm annular portion 131. Yes. In the example shown in FIG. 5, the example which comprised the thread part 71 with the ball screw is described. In this case, the arm ring portion 131 functions as a ball screw nut, the second ring member 72 functions as a screw shaft, and is provided between the arm ring portion 131 and the second ring member 72. The linear motion of the second annular member 72 is converted into the rotational motion of the arm annular portion 131 by the rolling elements. In addition, the screw part 71 may be comprised by the slide screw, for example, and this invention is not limited by the structure or kind of this screw part 71. FIG. In the example illustrated in FIG. 5, the example in which the screw portion 71 is configured between the inner peripheral surface of the arm annular portion 131 and the outer peripheral surface of the second annular member 72 is illustrated. A thread portion 71 may be formed between the outer peripheral surface of the second annular member 72 and the inner peripheral surface of the second annular member 72.

  As shown in FIG. 5, the second annular member 72 is connected to the first annular member 63 via a third bearing 83. The second annular member 72 needs to prevent direct rotation with the third bearing 83 and linearly move in the axial direction. For this reason, for example, the base member 14 is provided with an annular protrusion facing the inner peripheral surface of the second annular member 72, and splines are formed on the outer peripheral surface of the protrusion and the inner peripheral surface of the second annular member 72. The spline provided on the inner peripheral surface of the second annular member 72 and the spline provided on the outer peripheral surface of the protruding portion of the base member 14 are fitted, and the second annular member 72 is provided on the base member 14. The structure which suppresses the rotational motion of the 2nd annular member 72 may be sufficient by being supported by the projected part which cannot rotate. Moreover, the 3rd bearing 83 is comprised, for example with a thrust needle bearing. The present invention is not limited by the support structure of the second annular member 72 and the configuration or type of the third bearing 83.

  As shown in FIG. 5, the first roller 11 is provided on a shaft 132 extending from the arm 13 via a bearing 112 and a bearing 113, and a cylindrical roller housing 111 supported rotatably around a rotation axis BX. It is composed. As shown in FIG. 5, the second roller 12 is provided on a shaft 133 extending from the arm 13 via a bearing 122 and a bearing 123, and is a cylindrical roller housing that is rotatably supported around a rotation axis CX. 121 is comprised. The bearing 112, the bearing 113, the bearing 122, and the bearing 123 are constituted by ball bearings, for example, but the present invention is not limited by the configuration or type of the bearing 112, the bearing 113, the bearing 122, or the bearing 123. .

  Next, the operation of the accessory drive belt tension adjusting apparatus 10 according to the present embodiment configured as described above will be described with reference to FIGS.

  FIG. 7 is a diagram illustrating a circumferential phase difference caused by a rotational movement between the first housing and the second housing when the second pulley generates a driving force. FIG. 8 is a diagram illustrating a circumferential phase difference caused by a rotational movement between the first housing and the second housing when the first pulley generates a driving force. FIG. 9 is a diagram illustrating a state change of the rotation-linear motion conversion mechanism and the linear motion-rotation conversion mechanism when the second pulley generates a driving force. FIG. 10 is a diagram illustrating a state change of the rotation-linear motion conversion mechanism and the linear motion-rotation conversion mechanism when the first pulley generates a driving force. FIG. 11 is a diagram illustrating an operation example of the accessory drive belt tension adjusting device according to the first embodiment when the second pulley generates a driving force. FIG. 12 is a diagram illustrating an operation example of the accessory driving belt tension adjusting device according to the first embodiment when the first pulley generates the driving force.

  In the accessory drive belt tension adjusting apparatus 10 according to the present embodiment, the rotation-linear motion conversion mechanism 6 includes the first housing 41 and the first housing 41 that change according to the torque applied to the first housing 41 or the second housing 42. The circumferential phase difference caused by the rotational movement between the two housings 42 is converted into the axial linear motion shown in FIG. 5, and the linear motion-rotation conversion mechanism 7 is axially linear. The motion is converted into a rotational motion of the arm 13 shown in FIG.

  When the second pulley 2 generates a driving force, that is, when the second pulley 2 is a driving pulley and the first pulley 1 is a driven pulley, as shown in FIG. The phase difference Δθ is generated between the rotation angle θ1 of the first housing 41 and the rotation angle θ2 of the second housing 42 by the rotational movement between the two housings 42. At this time, as shown in FIG. 9, the first annular member 63 constituting the rotation-linear motion conversion mechanism 6, the third bearing 83, and the second annular member constituting the linear motion-rotation conversion mechanism 7. 72 moves in the direction of the arrow. At this time, as shown in FIG. 11, the arm 13 swings in the direction of the arrow, and the first roller 11 pushes the loose side of the belt 3 to apply tension.

  When the first pulley 1 generates driving force, that is, when the first pulley 1 is a driving pulley and the second pulley 2 is a driven pulley, as shown in FIG. A phase difference Δθ ′ is generated between the rotation angle θ1 ′ of the first housing 41 and the rotation angle θ2 ′ of the second housing 42 by the rotational movement between the two housings 42. At this time, as shown in FIG. 10, the first annular member 63, the third bearing 83, and the second annular member constituting the linear-rotational conversion mechanism 7 that constitute the rotational-linear motion converting mechanism 6. 72 moves in the direction of the arrow. At this time, as shown in FIG. 12, the arm 13 swings in the direction of the arrow, and the second roller 12 pushes the loose side of the belt 3 to apply tension.

  In the present embodiment, the torque applied to the first housing 41 or the second housing 42 and the circumferential position generated by the rotational movement between the first housing 41 and the second housing 42 that changes according to the torque. The phase difference, the amount of movement of the first annular member 63, the third bearing 83, and the second annular member 72 caused by the rotation-linear motion conversion mechanism 6 due to this phase difference in the linear motion direction, and the linear motion direction The amount of swing of the arm 13 generated by the linear motion-rotation conversion mechanism 7 according to the amount of movement is proportional to each other. That is, in the auxiliary machine drive belt tension adjusting device 10 according to the present embodiment, by using the configuration as described above, in the auxiliary machine drive system in which the drive side and the driven side are switched, it is proportional to the transmission torque generated in both directions. The slack side tension T2 thus obtained can be applied to the belt 3.

(Modification)
In the above-described example, the auxiliary machine drive belt tension adjusting device 10 according to the present embodiment is applied to an auxiliary machine drive system in which the drive side and the driven side are switched. For example, the second pulley 2 is an alternator. The present invention can also be applied to an accessory drive system having a configuration of a driven pulley provided on the shaft.

  FIG. 13 is a structural conceptual diagram of an accessory drive system to which an accessory drive belt tension adjusting device according to a modification of the first embodiment is applied. In the example shown in FIG. 13, the auxiliary drive belt tension adjusting device 10 a according to the modification of the first embodiment is applied to an auxiliary drive system in which the second pulley 2 is a driven pulley and the second pulley 2 cannot be a drive pulley. The example of a structure in the case of applying is shown. In this case, it can be easily realized by adopting a configuration in which the first roller 11 is not provided in the auxiliary machine drive belt tension adjusting device 10 described above.

  In addition, since the auxiliary drive belt tension adjusting devices 10 and 10a according to the present embodiment do not have a structure for swinging auxiliary equipment such as ISG and alternator, the wiring of the auxiliary equipment is disconnected due to fatigue deterioration. Since there is no factor, it is possible to realize the auxiliary drive belt tension adjusting devices 10 and 10a with high reliability.

  As described above, the accessory driving belt tension adjusting device 10 according to the first embodiment is configured to adjust the belt 3 that transmits the driving force bidirectionally from one to the other between the first pulley 1 and the second pulley 2. A first roller 11 for applying tension to a delivery section from the second pulley 2 to the first pulley 1; a second roller 12 for applying tension to a delivery section from the first pulley 1 to the second pulley 2 of the belt 3; An arm 13 that supports the roller 11 and the second roller 12, and a swing mechanism 4 that swings the arm 13 about the rotation axis AX of the second pulley 2 as a pivot axis.

  The swing mechanism 4 is provided on the outer side in the circumferential direction of the first housing 41 fixed to the shaft 5 of the second pulley 2, and is supported so as to be rotatable in the circumferential direction with respect to the first housing 41. And the circumferential position generated by the rotational movement between the first housing 41 and the second housing 42, which changes according to the torque applied to the first housing 41 or the second housing 42. A rotation-linear motion conversion mechanism 6 that converts the phase difference into an axial linear motion, and a linear motion-rotation conversion mechanism 7 that converts the axial linear motion into the rotational motion of the arm 13 are included. Has been.

  In this configuration, a base annular portion 141 centered on the rotation axis of the second pulley 2 is provided, and a base member 14 fixed in the circumferential direction with respect to the rotation axis AX of the second pulley 2 is provided. An elastic member 61 provided between the protrusion 411 provided on the outer peripheral surface of the first housing 41 and the protrusion 421 provided on the inner peripheral surface of the second housing 42, the motion-linear motion conversion mechanism 6, The first annular member 63 provided between the first housing 41 and the second housing 42 via the screw portion 62, and the arm 13 includes the base annular portion 141. The arm-ring portion 131 is provided on the inner side in the circumferential direction and is supported so as to be rotatable in the circumferential direction with respect to the base annular portion 141. Between the inner peripheral surface (or outer peripheral surface) of 131, the thread portion 71 The second annular member 72 provided via the second annular member 72 and the second annular member 72 and the first annular member 63 are connected to each other in the axial direction via the third bearing 83 so that the drive side and the driven member are driven. In the auxiliary drive system in which the side is switched, a slack side tension T2 proportional to the transmission torque generated in both directions from one to the other can be applied to the belt 3, and the auxiliary drive system in which the drive side and the driven side are switched. Loss can be reduced.

  Further, the second pulley 2 is a driven pulley, and the second pulley 2 can be applied to an accessory driving system in which the second pulley 2 cannot be a driving pulley. The accessory driving belt according to the modification of the first embodiment can be easily obtained. The tension adjusting device 10a can be realized.

  In addition, the auxiliary machine driving belt tension adjusting devices 10 and 10a according to the present embodiment do not cause the breakage of the wiring of the auxiliary machines due to fatigue deterioration, and realize the highly reliable auxiliary machine driving belt tension adjusting devices 10 and 10a. can do.

  Thus, by applying the accessory drive belt tension adjusting devices 10 and 10a according to the present embodiment to the accessory drive system, it is possible to achieve both high reliability and loss reduction of the accessory drive system. .

(Embodiment 2)
FIG. 14 is a schematic cross-sectional view of the accessory drive belt tension adjusting device according to the second embodiment. FIG. 15 is a view of the first cam plate, the rolling element, and the second cam plate as seen in the direction indicated by the arrow A in FIG. 16 is a view of the first cam plate, the rolling element, and the second cam plate as viewed in the direction indicated by the arrow B in FIG. FIG. 16A shows an initial state in which the first pulley 1 does not generate a driving force, and FIG. 16B shows the first housing 41 when the first pulley 1 generates a driving force. The circumferential phase difference produced by the rotational movement between the second housing 42 is shown. FIG. 17 is a diagram illustrating a state change of the rotation-linear motion conversion mechanism and the linear motion-rotation conversion mechanism when the first pulley generates a driving force. FIG. 18 is a diagram illustrating an operation example of the accessory driving belt tension adjusting device according to the second embodiment when the first pulley generates the driving force. In addition, the same code | symbol is attached | subjected to the same component as Embodiment 1 mentioned above, and the overlapping description is abbreviate | omitted.

  As shown in FIG. 14, the accessory drive belt tension adjusting device 10 b according to the present embodiment applies tension to the loose side section of the belt 3 that transmits the driving force between the first pulley 1 and the second pulley 2. The roller 12, the arm 13 supporting the roller 12, the base member 14 fixed in the circumferential direction with respect to the rotational axis AX of the second pulley 2, and the arm 13 pivoting about the rotational axis AX of the second pulley 2 And a swing mechanism 4 that swings as an axis.

  As shown in FIG. 14, the swing mechanism 4 is configured to include the components of the second pulley 2. Specifically, the swing mechanism 4 includes a first housing 41, a second housing 42, a rotation-linear motion conversion mechanism 6 a, and a linear motion-rotation conversion mechanism 7.

  The first housing 41 is a cylindrical member fixed to the shaft 5 of the second pulley 2.

  The second housing 42 is a cylindrical member that is provided on the outer side in the circumferential direction of the first housing 41 via a first bearing 81 and is rotatably supported with respect to the first housing 41.

  The rotation-linear motion conversion mechanism 6 a is a circumferential direction generated by a rotation motion between the first housing 41 and the second housing 42 that changes according to the torque applied to the first housing 41 or the second housing 42. Is converted into a linear motion in the axial direction.

  The linear motion-rotation conversion mechanism 7 converts the axial linear motion into the rotational motion of the arm 13.

  The rotation-linear motion conversion mechanism 6a includes a first cam plate 66 and a second cam plate 67, and a first annular member 68.

  As shown in FIGS. 14 to 16, the first cam plate 66 and the second cam plate 67 are disposed with a plurality of roller-shaped or ball-shaped rolling elements 64 sandwiched therebetween and the cam surfaces facing each other in the axial direction. This is an annular member that is given an urging force in the axial direction by the elastic member 65. The rolling element 64 may have a structure in which, for example, a plurality of rolling elements 64 are supported by an annular rolling element support member. In the example shown in FIG. 15, the example in which the four rolling elements 64 are arranged at positions shifted by 90 degrees in the circumferential direction is shown, but the number and positions of the rolling elements 64 are not limited to this, and three or more. The rolling elements 64 may be arranged at equal intervals in the circumferential direction. Further, the elastic member 65 is constituted by, for example, an annular disc spring, but may be a leaf spring or a coil spring, or may be a solid member such as elastic rubber. The present invention is not limited by the configuration, material, and shape of the elastic member 65.

  The first annular member 68 is an annular member provided between the first housing 41 and the second housing 42.

  As shown in FIG. 14, the first cam plate 66 is restricted in movement in the axial direction by the elastic member 65 locked by the ring stopper member 93, and is positioned circumferentially with respect to the first housing 41 by the fixing member 91. Is fixed and arranged. In the example shown in FIG. 14, the ring stopper member 93 is configured by two annular members, but the present invention is not limited by the configuration of the ring stopper member 93. In the example shown in FIG. 14, the circumferential position of the first cam plate 66 relative to the first housing 41 is fixed by the fixing member 91, but the circumferential position of the first cam plate 66 relative to the first housing 41 is used. The structure for fixing is not limited to this, and the present invention is not limited to this structure.

  As shown in FIG. 14, the second cam plate 67 is arranged with the circumferential position and the axial position fixed to the second housing 42 by the fixing member 92, and the fixing member 91 via the fourth bearing 84. Connected with. The fourth bearing 84 suppresses the displacement of the axial position of the second cam plate 67 with respect to the second housing 42 by the fixing member 91, and the circumferential phase difference between the first housing 41 and the second housing 42. However, the structure for fixing the axial position of the second cam plate 67 with respect to the second housing 42 is not limited to this, and the present invention is not limited to this structure. Absent. Moreover, although the 4th bearing 84 is comprised with a thrust needle bearing, for example, this invention is not limited by the structure or kind of this 4th bearing 84.

  As shown in FIG. 14, the first annular member 68 is disposed such that one end in the axial direction is in contact with the first cam plate 66 and is connected to the second annular member 72 via the third bearing 83. .

  Next, the operation of the accessory drive belt tension adjusting device 10b according to the present embodiment configured as described above will be described with reference to FIGS. In the above-described first embodiment, the configuration applicable to the accessory drive system in which the drive side and the driven side are interchanged has been described. However, the accessory drive belt tension adjusting device 10b according to the present embodiment includes, for example, the first The 2 pulley 2 is a driven pulley provided on the shaft of the alternator, and the second pulley 2 can be applied to an accessory drive system that cannot be a drive pulley.

  In the accessory drive belt tension adjusting device 10b according to the present embodiment, the rotation-linear motion conversion mechanism 6a is formed between the first housing 41 and the second housing 42 that change according to the torque applied to the second housing 42. The phase difference in the circumferential direction generated by the rotation motion between the two is converted into the linear motion in the axial direction shown in FIG.

  As described above, the first cam plate 66 and the second cam plate 67 are biased in the axial direction by the elastic member 65. The first cam plate 66 and the second cam plate 67 are periodically different in thickness in the circumferential direction. For this reason, when the first pulley 1 does not generate a driving force, the axial force of the first cam plate 66 and the rolling elements are caused by the reaction force applied by the elastic member 65 as shown in FIG. The sum of the diameter of 64 and the thickness of the second cam plate 67 in the axial direction is the thinnest D1. At this time, the rolling element 64 is in a position where the circumferential position C1 on the first cam plate 66 and the circumferential position C2 on the second cam plate 67 coincide with each other in the example shown in FIG.

  When the first pulley 1 is generating a driving force, a torque that shifts the first cam plate 66 and the second cam plate 67 in the circumferential direction due to the torque applied to the second housing 42 is generated, and FIG. ), The rolling element 64 moves between the first cam plate 66 and the second cam plate 67. At this time, the sum of the axial thickness of the first cam plate 66, the diameter of the rolling element 64, and the axial thickness of the second cam plate 67 increases, and thrust is generated in the axial direction. A first housing 41 in which the first cam plate 66 is fixed in the circumferential direction and a second housing 42 in which the second cam plate 67 is fixed in the circumferential direction so that the thrust and the reaction force by the elastic member 65 are balanced. In the meantime, a phase difference Δθ corresponding to the deviation of the circumferential position C1 on the first cam plate 66 and the circumferential position C2 on the second cam plate 67 is generated. At this time, the total D2 of the thickness of the first cam plate 66 in the axial direction, the diameter of the rolling element 64 and the thickness of the second cam plate 67 in the axial direction, as shown in FIG. By deforming, the first pulley 1 becomes thicker by ΔD than when the driving force is not generated (D2 = D1 + ΔD). As a result, as shown in FIG. 17, the first annular member 68 constituting the rotation-linear motion conversion mechanism 6 a, the third bearing 83, and the second ring constituting the linear motion-rotation conversion mechanism 7. The member 72 moves in the direction indicated by the arrow. At this time, as shown in FIG. 18, the arm 13 swings in the direction of the arrow, and the roller 12 applies a tension by pushing the loose side of the belt 3.

  In the present embodiment, the torque applied to the second housing 42, the circumferential phase difference caused by the rotational movement between the first housing 41 and the second housing 42 that changes according to this torque, The first ring member 68, the third bearing 83, and the second ring member 72, which are generated by the rotation-linear motion conversion mechanism 6a due to the phase difference, move in the linear motion direction, and move linearly by the movement amount in the linear motion direction. The amount of rocking of the arm 13 generated by the rotation conversion mechanism 7 is proportional to each other. That is, in the auxiliary machine drive belt tension adjusting device 10b according to the present embodiment, by adopting the above-described configuration, it is possible to apply the slack side tension T2 proportional to the transmission torque to the belt 3.

  In addition, since the auxiliary machine drive belt tension adjusting device 10b according to the present embodiment does not have a structure for swinging auxiliary machines such as an alternator, there is no cause for the wiring of the auxiliary machines to be disconnected due to fatigue deterioration. Therefore, it is possible to realize the auxiliary drive belt tension adjusting device 10b with high reliability.

  As described above, the auxiliary machine drive belt tension adjusting device 10b according to the second embodiment is arranged so that the cam surfaces are opposed to each other in the axial direction with the rolling element 64 interposed therebetween, and an urging force is applied in the axial direction by the elastic member 65. The first and second cam plates 66 and 67, and the first annular member 68 provided between the first housing 41 and the second housing 42, are configured to rotate. By including the linear motion conversion mechanism 6a, for example, the second pulley 2 is a driven pulley provided on the shaft of the alternator, and the auxiliary pulley drive system in which the second pulley 2 cannot be a driving pulley is proportional to the transmission torque. The slack side tension T2 can be applied to the belt 3, and the loss of the accessory drive system can be reduced.

  In addition, in the auxiliary machine drive belt tension adjusting device 10b according to the present embodiment, there is no factor that the wiring of the auxiliary machines is disconnected due to fatigue deterioration, and a highly reliable auxiliary machine drive belt tension adjusting device 10b can be realized. .

  Thus, by applying the accessory drive belt tension adjusting device 10b according to the present embodiment to the accessory drive system, it is possible to achieve both high reliability and loss reduction of the accessory drive system.

  As described above, by using the accessory drive belt tension adjusting devices 10, 10a, and 10b according to the present embodiment, a slack side tension proportional to the transmission torque can be applied to the belt. The adjusting devices 10, 10a, and 10b are suitable for achieving both high reliability and loss reduction of the auxiliary machine drive system.

DESCRIPTION OF SYMBOLS 1 1st pulley 2 2nd pulley 3 Belt 4 Oscillating mechanism 5 Shaft (2nd pulley)
6, 6a Rotation-linear motion conversion mechanism 7 Linear motion-rotation conversion mechanism 10, 10a, 10b Auxiliary machine drive belt tension adjusting device 11 First roller 12 Second roller (roller)
13 Arm 14 Base member 41 First housing 42 Second housing 61 Elastic member 62 Screw part 63, 68 First annular member 65 Elastic member 66 First cam plate 67 Second cam plate 71 Screw part 72 Second annular member 81 First bearing 82 Second bearing 83 Third bearing 84 Fourth bearing 91, 92 Fixing member 93 Ring retaining member 100 Drive pulley 101 Crank pulley 111, 121 Roller housing 112, 113, 122, 123 Bearing 131 Arm ring portion 132, 133 Shaft 141 Base annular part 200 Driven pulley 201-205 Auxiliary machine pulley 301 Belt 400 Tensioner 411 Projection part 421 Projection part AX Rotation axis (second pulley)
BX Rotating shaft (first roller)
CX Rotating shaft (second roller, roller)
T0 Initial tension T1 Tension side tension T2 Loose side tension

Claims (2)

A roller for applying tension to the loose side section of the belt for transmitting driving force between the first pulley and the second pulley;
An arm for supporting the roller;
A rocking mechanism for rocking the arm with the rotation axis of the second pulley as a pivot axis;
With
The swing mechanism is
A first housing fixed to the shaft of the second pulley;
A second housing provided on the outer side in the circumferential direction of the first housing and supported so as to be rotatable in the circumferential direction with respect to the first housing;
An axial linear motion is obtained by converting a circumferential phase difference caused by a rotational motion between the first housing and the second housing, which changes according to a torque applied to the first housing or the second housing. A rotation-linear motion conversion mechanism that converts to
A linear-rotation conversion mechanism for converting the linear linear motion into the rotational motion of the arm;
Including,
Auxiliary drive belt tension adjuster. The belt transmits a driving force bidirectionally from one to the other between the first pulley and the second pulley,
The roller is
A first roller that applies tension to a delivery section of the belt from the second pulley to the first pulley;
A second roller that applies tension to a delivery section of the belt from the first pulley to the second pulley;
Including,
The auxiliary machine drive belt tension adjusting device according to claim 1.

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