JP5941265B2 - Cable tension adjustment structure for sliding door - Google Patents

Description

  The present invention relates to a cable tension adjustment structure for adjusting the tension and excess length of a cable used for automatically opening and closing a sliding door of a vehicle.

  As shown in FIG. 13, some vehicles 100 such as a wagon car and a one-box car have a slide door 101 attached thereto. The sliding door 101 is opened by sliding backward from the closed state (shown by a solid line in FIG. 13), and moves backward from the open state (shown by a two-dot chain line in FIG. 13). Can be closed by

  As shown in FIG. 14, the slide door 101 is provided with an arm portion 101a extending rearward from the slide door main body. Further, a roller assembly 101b is attached to the rear end portion of the arm portion 101a so as to be rotatable with respect to the arm portion 101a. On the other hand, as shown in FIGS. 13 and 14, a guide rail 102 extending in the longitudinal direction of the vehicle body is provided on the main body side of the vehicle 100. The above-described roller assembly 101b is slidably assembled to the guide rail 102, and the slide assembly 101 slides in the vehicle front-rear direction as the roller assembly 101b moves along the guide rail 102 in the front-rear direction.

  Further, as shown in FIG. 14, the front side portion 102a of the guide rail 102 is gently curved toward the inner side of the vehicle. Due to this curved shape, the sliding door 101 moves toward the inside of the vehicle when the sliding door 101 is closed, and the sliding door 101 is closed with respect to the vehicle 100. On the contrary, when the sliding door 101 opens, the sliding door 101 slides toward the rear of the vehicle after moving from the closed state toward the outside of the vehicle.

  Such an opening / closing operation of the sliding door 101 is realized by the cooperation of the power sliding door unit 103 (hereinafter referred to as the PSD unit 103) and the cable 107 attached to the sliding door 101 (specifically, the arm portion 101a). Is done.

As shown in FIG. 14, the PSD unit 103 includes a front reversing pulley 104 provided on the front end side of the guide rail 102, a rear reversing pulley 105 provided on the rear end side of the guide rail 102, and a guide rail. It is comprised with the drive unit 106 attached to the compartment side rather than 102.
The front reversing pulley 104 and the rear reversing pulley 105 have a function of changing the front-rear direction of the wound cable 107. Further, the drive unit 106 has a function of electrically winding the cable 107 wound around the front reverse pulley 104 and the rear reverse pulley 105.

  The cables 107 to be wound are two cables (one is attached to the slide door 101 from the drive unit 106 through the front reverse pulley 104, and the other is passed from the drive unit 106 through the rear reverse pulley 105. (Attached to the slide door 101) is connected inside the drive unit 106. For this reason, when the drive unit 106 operates, the cable 107 is drawn into the drive unit 106 and simultaneously sent out. Accordingly, the slide door 101 is automatically opened and closed by feeding the cable 107 rearward or frontward using the drive unit 106.

  As shown in FIG. 14, the front reversing pulley 104 described above has a front side portion 102a of the guide rail 102 that is curved toward the inside of the vehicle. It is attached as follows. Similarly, the rear inversion pulley 105 is attached so as to rotate substantially horizontally.

  FIG. 15 is a simplified illustration of the cable tension adjustment structure 108 provided in the drive unit 106. As shown in FIG. 15, the cable 107 is wound around the upper side of a drive pulley 113 that is rotated by a drive motor (not shown). In addition, movable pulleys 109 and 109 for tension adjustment are provided on the lower left and right sides of the drive pulley 113, respectively. As shown in FIG. 15, the cable 107 wound around the drive pulley 113 is wound around the movable pulleys 109 and 109 from the lower side, respectively. Both sides of the cable 107 are routed toward the upper left and the upper right.

  One ends of tension springs 110 and 110 are attached to the left and right movable pulleys 109 and 109, respectively. The other end portions of the tension springs 110 and 110 are attached to the fixing portions 111 and 111 of the drive unit 106, respectively. These tension springs 110 urge the movable pulleys 109 and 109 obliquely downward, respectively. Moreover, the movable pulleys 109 and 109 are attached so as to be movable in an oblique vertical direction 112 (spring expansion / contraction direction). With this configuration, the tension of the cable 107 during the movement of the slide door 101 is adjusted to be substantially constant by the urging force of the tension springs 110 and 110.

  The tension spring 110 also functions to absorb the extra length associated with the change in the movement trajectory of the cable 107. The change in the movement trajectory of the cable 107 means a change in the trajectory of the cable 107 passing through the curved portion of the front side portion 102a of the guide rail 102 as shown in FIG. More specifically, when the roller assembly 101b of the slide door 101 passes, the cable 107 is lifted by the roller 101c and has a locus like a dotted line in FIG. On the other hand, when the roller assembly 101b does not pass, the cable 107 slides along the inner side surface of the guide rail 102 and has a locus like a two-dot chain line in FIG. A surplus length is generated by the change of the two trajectories, and the surplus length is absorbed by the movement of the movable pulleys 109 and 109 described above (see, for example, Patent Document 1).

JP 2008-184880 A

  The opening / closing force at the start of opening / closing of the sliding door 101 is preferably small from the viewpoint of manual operability. However, in the conventional cable tension adjusting structure 108 as shown in FIG. 15, the extra length of the cable 107 is reduced when the sliding door 101 passes through the front side portion 102 a (curved portion) of the guide rail 102. It operates so that 110 is compressed. When the tension spring 110 is compressed, the tension acting on the cable 107 also increases. Therefore, a large force is required for opening and closing the slide door 101 (when the front side portion 102a passes), and the manual operation becomes heavy.

  Further, when the slide door 101 is opened and closed, a large tension at the time of starting the drive motor acts on the cable 107 as an impact force. In addition, during the opening / closing operation of the slide door 101, when an impact such as an object hitting the slide door 101 is received, a larger impact force may be applied to the cable 107 than at the start. However, in the conventional cable tension adjusting structure 108, when a large tension is applied to either the cable 107 extending obliquely upward to the right shown in FIG. 15 or the cable 107 extending obliquely upward to the left shown in FIG. The movable pulley 109 on the side on which the large tension is applied is greatly lifted obliquely upward (the reverse movable pulley 109 moves downward to take up the slack of the cable 107), and the tension spring 110 is The contact height may be completely crushed. Therefore, not only the tension of the cable 107 can be completely removed, but also a large load may act on the drive motor for driving the drive pulley 113 due to the impact of the tension spring 110 being in close contact.

  Conventionally, in order to absorb such a load that cannot be removed, an impact absorbing material is provided, or a small clutch or the like is provided between the drive pulley and the drive motor. However, with this method, the number of parts of the drive unit 106 increases, resulting in high costs. In addition, a space for installing a small clutch or the like is required, and it is difficult to reduce the size and weight of the entire drive unit 106.

  The present invention has been made in view of the above-described circumstances, and is a slide that can absorb an impact force acting on a cable without using an impact absorber or the like and can reduce the size of the entire drive unit. The object is to provide a cable tension adjustment structure for a door.

In order to solve the above-mentioned problems, the present invention is incorporated in a drive unit for driving a cable attached to a slide door, and changes in the tension of the cable and changes in the movement trajectory of the cable caused by opening and closing operations of the slide door. A cable tension adjusting structure of a sliding door provided with a spring for absorbing an impact force generated as a tension in the cable, and a driving drum rotated by a driving motor, and a fixed pulley The cable is wound around the drive drum and the fixed pulley, and the drive drum and the fixed pulley form two support points for the cable, and the cable travels between the two support points. the biasing force of the spring is transmitted to the drive unit Presses directed towards, has a transfer member for changing the traveling path of the cable, said spring is used as a tension spring, the spring is set so as to extend the time to absorb the impact force to the cable It is characterized by.

  Also, the travel length of the cable travel path when absorbing the impact force to the cable is shorter than the travel length of the cable travel path when absorbing the cable tension fluctuation and surplus length. It is trying to become.

  Furthermore, the impact force acting on the cable when the sliding door is opened and closed is absorbed at a position where the travel route of the cable is moved rather than a straight line connecting the two support points.

  On the other hand, the transmission member may be an arm member that has the spring attached to one end thereof and presses the cable while the other end rotates around the one end by the biasing force of the spring.

  Further, the arm member may be rotated so that the longitudinal direction thereof follows the traveling route of the cable.

  Furthermore, the expansion / contraction direction of the spring may be arranged along a straight line connecting the two support points.

  On the other hand, the distance between the two support points can be changed.

  Further, when the distance between the two support points is shortened, a pressing force blocking structure that blocks the pressing force from the transmission member to the cable against the biasing force of the spring may be provided. .

  According to the cable tension adjusting structure for a sliding door according to the present invention, there is provided a transmission member that transmits and presses the urging force of the spring to the cable traveling between two support points to change the traveling path of the cable. The spring is used as a tension spring and is set so that the spring extends when absorbing the impact force on the cable. The compression spring described in 15 is not crushed to the contact height. Therefore, the impact force does not act on the drive motor that drives the drive pulley, for example, and a large load is not applied. As a result, it is not necessary to provide an impact absorbing material or a small clutch for absorbing the impact, and the cost can be reduced. Moreover, since an installation space for attaching these members is not necessary, the entire drive unit can be reduced in size and weight.

  Further, the arm member is rotated so that its longitudinal direction is along the traveling path of the cable, and the expansion and contraction direction of the spring is arranged along a straight line connecting the two support points. When the force is canceled by the angle of the arm member and the spring force is large, the cable can be pressed with a small force. On the other hand, when the spring force is small, the cable can be pressed with a large force.

It is a front view of the drive unit which includes the cable tension adjustment structure of the slide door which concerns on embodiment of this invention. It is a right view of FIG. FIG. 2 is a front view of the drive unit with the upper cover removed from the state of FIG. 1, in which the cable tension is in a normal state. FIG. 2 is a front view of the drive unit with the upper cover removed from the state of FIG. 1, showing a state where the cable tension located on the left side is small and a state where the cable tension located on the right side is high. FIG. 5 is a front view of the drive unit 1 showing a state in which the pulley support section 4 is slid downward from the states of FIGS. 3 and 4. It is a schematic diagram which shows operation | movement of the lever for moving a pulley support part. It is the figure which showed the relationship between cable tension and extra length absorption. It is the enlarged plan view which looked at the front side curve part of the guide rail from the vehicle upper side. It is the expanded side view which looked at FIG. 8 from the vehicle outer side. It is the side view which showed the front pulley alone. It is the side view which removed the side cover from the state of FIG. 10, and showed the locus | trajectory of the cable. It is the top view which looked at FIG. 10 from the upper side. It is a side view of the vehicle to which the sliding door was attached. It is the top view which looked at the conventional PSD unit from the vehicle upper side. It is a general-view figure which simplifies and shows the conventional cable tension adjustment structure. It is an enlarged view of the curved front side part of the conventional guide rail.

  Hereinafter, a cable tension adjusting structure for a sliding door according to an embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is a front view of a drive unit 1 including a cable tension adjustment structure for a sliding door according to an embodiment of the present invention, and FIG. 2 is a right side view of FIG. 3 and 4 are front views of the drive unit 1 with the upper cover removed from the state shown in FIG. 1, and show a state in which the cable tension and extra length are absorbed. Further, FIG. 5 is a front view of the drive unit 1 showing a state in which the pulley support portion 4 is slid downward from the states of FIGS. 3 and 4.

  In the present embodiment, the same components and components as those described in the past will be described with the same reference numerals. Further, the front-rear direction in the following description refers to the depth direction in FIG. 1, and the vertical and horizontal directions refer to the vertical and horizontal directions in FIG. Further, in the drawings described below, the route of the cable 107 is indicated by using a thick two-dot chain line, and similarly denoted by reference numeral 107.

  The drive unit 1 includes a main body 2 that covers the entire rear side of the drive unit 1 and an upper cover 3 that covers an upper front portion of the main body 2. In addition, a pulley support portion 4 that protrudes upward from the upper surfaces of the main body portion 2 and the upper cover 3 is provided on the upper portion of the drive unit 1. In addition, although the main-body part 2 mentioned above is made into the integral structure which covers the whole rear side in a present Example, it can also be comprised by a division structure.

  The upper cover 3 is detachably attached to the main body 2 by four screws 5. When the upper cover 3 is removed, as shown in FIGS. 3 and 4, the entire cable tension adjusting structure 6 provided inside the drive unit 1 is exposed.

  In addition, a spiral groove is formed on the outer peripheral surface several times below the upper cover 3, and a drive drum in which the cable 107 is wound around this spiral groove (in FIGS. 3 to 5, A pitch circle is indicated by reference numeral 7), and a drive motor 14 for sending out the cable 107 by rotating the drive drum is attached. For example, a high-efficiency brushless motor is used as the drive motor 14.

  As shown in FIGS. 3 to 5, the pulley support portion 4 has a flat and substantially rectangular parallelepiped shape, and cable inlets 4 b and 4 b for drawing the cable 107 are provided in the upper left and right ends, respectively. ing. In addition, a fixed pulley (pitch circle is indicated by reference numeral 8) is attached to the center of the pulley support portion 4 so as to be rotatable about a rotation shaft (not shown) and fixed to the cable support portion 4.

  As shown in FIGS. 3 to 5, a cable 107 drawn from the cable inlets 4 b and 4 b of the pulley support portion 4 is wound around the fixed pulley indicated by the pitch circle 8 of the fixed pulley. More specifically, the cable 107 drawn from the upper left side is wound so as to pass through the right side of the fixed pulley 8, and the cable 107 drawn from the upper right side is wound so as to pass through the left side of the fixed pulley 8. It is done. Then, the cable 107 is wound from below on the drive drum 7 positioned below the fixed pulley 8.

  As shown in FIGS. 3 and 4, the wound cable 107 is supported by two pulleys 7 and 8, and the arm members 10 and 10 of the cable tension adjusting structure 6 described later in detail are not functioning. In a state where the tension of the cable 107 is not adjusted, the straight line 9 (shown by a thick dotted line in FIGS. 3 and 4) connecting the two support points T1 and T2 is stretched. . However, although details will be described later, in a state where the arm members 10 and 10 are functioning, the cable 107 does not actually travel on the straight line 9 in a theoretical sense.

  As shown in FIGS. 3 and 4, the cable tension adjustment structure 6 includes arm members (transmission members) 10 and 10 and tension springs (springs) 11 and 11 on both the left and right sides of the pulley support portion 4. Is provided. The arm members 10 and 10 have a function of changing the travel route of the cable 107 by pressing the cable 107 inward of the drive unit 1. The tension springs 11 and 11 are for urging the arm members 10 and 10.

  As shown in FIG. 3, the arm members 10 and 10 and the tension springs 11 and 11 are arranged symmetrically with each other in pairs, and the arm members 10 are formed on the left and right sides. . However, the left and right tension springs 11 and 11 can be extended and contracted independently as shown in FIG. 4, and the arm members 10 and 10 can move differently on the left and right.

  Since the arm member 10 and the tension spring 11 have the same configuration on the left and right, the left arm member 10 and the tension spring 11 will be described below.

  As shown in FIGS. 3 to 5, a rotating shaft 10 b is provided at the lower end of the arm member 10, and a pressing roller 10 a is rotatably attached to the rotating shaft 10 b. The pressing roller 10a is configured to press while being always in contact with the substantially central portion of the cable 107 spanned between the support points T1 and T2 of the pulleys 7 and 8.

  Further, an extension portion 10 c is formed at the upper end portion of the arm member 10 so as to protrude in the outer direction of the arm member 10. A support shaft 10d is attached to the extending portion 10c, and the upper end portion of the tension spring 11 is connected to the support shaft 10d. The support shaft 10d is freely slidable in the extending and retracting direction of the tension spring 11.

  As shown in FIG. 3, the tension spring 11 is a coil spring and is used as a tension spring as a whole. That is, the tension spring 11 is used so that the tension spring 11 extends beyond the natural length when adjusting the tension variation of the cable 107, absorbing the extra length, and absorbing the impact force (details will be described later). It should be noted that the spring 11 is contracted more than the set position 30 (see FIG. 7) at the time of absorbing the extra length 31 (see FIG. 7), which will be described in detail later. Used to be long. Thereby, the tension spring 11 gives the urging | biasing force always pulled down to the support shaft 10d.

  The upper end portion of the tension spring 11 is rotatably attached to the support shaft 10d of the arm member 10 described above. On the other hand, the lower end portion of the tension spring 11 is fixed to a spring receiving portion 12 provided in the main body portion 2. Further, as shown in FIGS. 3 to 5, the tension spring 11 is arranged such that the tension (displacement) direction of the tension spring 11 is substantially parallel along the straight line 9 connecting the two support points T1 and T2. It is arranged to be.

  In the set state shown in FIG. 3, the arm member 10 is installed so that the longitudinal direction thereof is substantially upward and downward. The arm member 10 is attached in such a manner that it is sandwiched between the main body 2 and the upper cover 3 when the main body 2 and the upper cover 3 are assembled, and is not fixed with screws or the like. Therefore, the arm member 10 receives the urging force of the tension spring 11 by the upper support shaft 10d, and rotates downward about the support shaft 10d (one end) at the position where the support shaft 10d moves. The cable 107 is pressed by the pressing roller 10a. In other words, the arm member 10 can change its posture while rotating in accordance with the balance between the urging force of the tension spring 11 and the pressing force to the cable 107.

  Furthermore, as shown in FIGS. 3 and 4, the arm member 10 changes its longitudinal direction by rotating. The direction of the longitudinal direction is along the direction of the travel paths 9A, 9B, and 9C of the cable 107 that are appropriately changed by the pressing force (the travel paths 9A, 9B, and 9C and the arm member 10 are substantially parallel to each other). ), The arm member 10 is configured to rotate.

  On the other hand, as shown in FIGS. 5 and 6, the pulley support portion 4 is configured to be able to slide up and down with respect to the main body portion 2 and the upper cover 3. Thereby, the distance between the center points of the drive drum 7 and the fixed pulley 8 can be changed, and the distance between the support point T1 and the support point T2 can also be changed. The pulley support portion 4 is moved by a lever 13 attached to the main body portion 2.

  FIG. 6 is a cross-sectional perspective view showing a state in which the main body 2 is cut from the center half in order to facilitate explanation, as viewed from the back side of the main body 2. The rotation operation of the lever 13 will be described with reference to FIG.

  As shown in FIG. 6, the lever 13 includes a rotating shaft 13a, an operation portion 13b for an operator to operate the lever 13, and a temporary fixing hole 13c formed in the operation portion 13b. Yes. When the lever 13 is rotated in the rotation direction R1, the pulley support portion 4 protrudes in the upward direction R1A. On the other hand, if the lever 13 is rotated in the rotation direction R2 and the pulley support portion 4 is pushed downward by hand, the pulley support portion 4 moves in the downward direction R2B.

  The rotation shaft 13a is attached to the main body 2 so as to be rotatable. As shown by the solid line in FIG. 6, the operation unit 13 b is in a state in which the pulley support unit 4 is pulled in a state where the operation unit 13 b is horizontal with the front-rear direction of the drive unit 1. Further, as shown in FIG. 6, the distal end portion of the operation portion 13 b protrudes rearward from the back surface of the main body portion 2, and this protruding portion is easily pulled up in the rotation direction R <b> 1.

  Further, the temporary fixing hole 13c formed in the operation portion 13b is adapted to engage with the lever temporary fixing claw of the main body portion 2 in a state where the pulley support portion 4 is retracted. In this engaged state, the pulley support portion 4 is maintained in a retracted state.

  From this state, when the operation portion 13b is rotated in the rotation direction R1, the operation portion 13b is fitted into the operation portion engagement groove 4c of the pulley support portion 4. And this pulley support part 4 comes to push up to upper direction R1A.

  The tension adjustment structure 6 is used in a state where the pulley support portion 4 is pushed upward (see FIGS. 3 and 4). On the other hand, the state in which the pulley support portion 4 is pulled downward (see FIG. 5) is used when the cable 107 is wound around the two pulleys 7 and 8.

  Further, as shown in FIGS. 3 to 5, in the left and right lower corners of the pulley support portion 4, there are recessed roller receiving portions (pressing force blocking structures) 4 a and 4 a for receiving the pressing roller 10 a. Each is provided. The roller receiving portions 4a and 4a do not come into contact with the pressing rollers 10a and 10a when the pulley supporting portion 4 is moved in the upward direction R1A (FIGS. 3 and 4). 10 a is configured to press the cable 107.

  Further, in a state where the pulley support portion 4 is moving in the downward direction R2B (the state of FIG. 5), the roller receiving portions 4a and 4a are in contact with the pressure rollers 10a and 10a or the main body of the arm member 10, and the pressure roller 10a, 10a is moved to the left and right outside directions of the drive unit 1. In this state, as shown in FIG. 5, the pressure rollers 10a and 10a have moved to a position where they do not come into contact with the cable 107 stretched linearly between the support points T1 and T2, and the pressure rollers 10a and 10a The pressing force is cut off.

  Next, the operation and action of the cable tension adjusting structure 6 will be described in detail with reference to FIGS. FIG. 7 is a diagram showing the relationship between cable tension and extra length absorption.

  In FIG. 7, the code | symbol 30 shows the set position (the state which the arm member 10 shows in the left side and the right side of FIG. 3) of surplus length absorption amount.

  At this time, the traveling route 9 </ b> A of the cable 107 is in a position pushed inward from the straight line 9. Here, the travel length of the travel route 9A refers to the pushing length from the straight line 9 to the travel route 9A (indicated by the distance L1 in FIG. 3).

  On the other hand, the positions indicated by reference numerals 31 and 32 in FIG. 7 indicate the extra length max position (the state on the right side in FIG. 4) and the position during shock absorption (the state on the left side in FIG. 4). The state shown in FIG. 4 is when the sliding door 101 is opened and closed. More specifically, when a drive motor (not shown) is started, a large tension is applied to the left cable 107 in FIG. 4, and a large extra length is generated in the right cable 107.

  The travel route 9B of the cable 107 at the extra length max position 31 is a position pushed further inward than the travel route 9A shown in FIG. Here, the travel length of the travel route 9B refers to the pushing length from the straight line 9 to the travel route 9B (indicated by the distance L2 in FIG. 4).

  The travel route 9C of the cable 107 at the position 32 at the time of shock absorption is a position that is pushed outside the travel route 9A and inside the straight line 9. Here, the travel length of the travel route 9C refers to the pushing length from the straight line 9 to the travel route 9C (indicated by the distance L3 in FIG. 4).

  That is, as shown in FIG. 4, the travel length L3 of the travel route 9C is shorter than the travel length L2 of the travel route 9B of the cable 107 when absorbing the tension fluctuation and the extra length.

  In FIG. 7, a curve indicated by reference numeral 35 indicates the displacement amount (elongation amount) of the tension spring 11 with respect to the extra length absorption amount. From this curve 35, it can be seen that the displacement amount of the tension spring 11 increases as the extra length absorption amount decreases and decreases as the extra length absorption amount increases.

  In FIG. 7, a curve indicated by reference numeral 36 indicates a change in the urging force (spring force) of the tension spring 11 with respect to the extra length absorption. From this curve 36, the urging force of the tension spring 11 is not in a proportional relationship, but it increases as the excess absorption amount decreases, and varies depending on the setting, but tends to increase as the excess absorption amount increases. I understand.

  That is, it can be seen from the curves 35 and 36 that, when the tension spring 11 absorbs the impact force, the tension spring 11 is displaced in the extending direction and generates a larger urging force. From this, when absorbing the impact, the impact force is absorbed within the elastic range of the tension spring 11 without being crushed to the contact height unlike the conventional tension spring 11 described in FIG. I understand that I can do it.

  Furthermore, in FIG. 7, the curve shown by the code | symbol 37 has shown the change of the tension | tensile_strength of the cable 107 with respect to surplus length absorption. From this curve 37, it can be seen that the change in the tension acting on the cable 107 is small with respect to the change in the extra length absorption.

  Further, as indicated by a curve 37, the tension acting on the cable 107 does not substantially change when the extra length absorption amount is larger than that at the time of the driving max load shown in FIG. On the other hand, the tension acting on the cable 107 becomes infinitely large as the surplus length absorption amount approaches zero when the surplus length absorption amount is smaller than that at the time of driving max load. This suddenly increases when the traveling route 9C of the cable 107 approaches the straight line 9. At this time, the tension spring 11 applies a large pressing force to the pressing rollers 10a and 10a with a large biasing force as described above. Therefore, it becomes possible to cope with a large impact force with a large pressing force.

  In FIG. 7, the curve indicated by reference numeral 38 indicates the amount of movement of the support shaft 10 d of the arm member 10.

  On the other hand, when the sliding door 101 opens and closes (when the sliding door 101 moves on the front R portion of the guide rail 102), as described above, the position 31 when absorbing the excess length (the state on the right side in FIG. 4). The operation is performed at the position of the route 9B) and the position 32 when absorbing the impact force (the state on the left side in FIG. 4; the position of the travel route 9C). When the sliding door 101 is opened and closed, the tension generation side and the slack side are reversed by the left and right cables 107, so the state shown in FIG. 4 is reversed when the sliding door 101 is opened and closed. Become.

  When the cable 107 passes through the travel route 9C (left side in FIG. 4), a large tension acts on the cable 107 due to the rolling load of the slide door 101. Further, as shown in FIG. 4, the longitudinal direction of the arm member 10 is an angle that is substantially parallel to the expansion / contraction direction of the tension spring 11. At this time, the tension spring 11 extends greatly, and attempts to lower the support shaft 10d of the arm member 10 downward with a large spring force. However, since the pressing roller 10a of the arm member 10 presses the cable 107 at an angle substantially perpendicular to the expansion / contraction direction of the tension spring 11, the pressing force to the cable 107 can be kept small. As described above, the cable tension adjusting structure 6 of the present invention has a structure that can suppress the pressing force from the tension spring 11 when a large tension is applied to the cable 107.

On the other hand, in the structure shown in the prior art, in a state where a large tension is applied to the cable 107 (in FIG. 15, the movable pulley 109 is lifted obliquely upward and the spring force is maximum), the compressed tension spring 110 is compressed. Most of the spring force is a force that pushes down the movable pulley 109 that is pulled up obliquely downward, and gives a greater tension to the cable 107. Therefore, when the slide door 101 is closed (when the slide door 101 moves on the front R portion of the guide rail 102), a large force is required as a manual operation force at the time of opening and closing.
On the other hand, in the structure shown in FIG. 4, the spring force of the tension spring 11 is almost maximum, but the angle of the arm member 10 is almost 90 degrees, so that the force pressing the cable 107 is a component force. It becomes a small power. Therefore, since the tension of the cable 107 is not further increased, the aforementioned opening / closing force can be further reduced.

Further, when the cable 107 passes through the travel route 9B (right side in FIG. 4), the cable 107 is slack for the travel route 9C (left side in FIG. 4). At this time, in the conventional tensioner structure 108 (see FIG. 15), the amount of movement of the movable pulley 109 is proportional to the amount of deflection of the tension spring 110. Therefore, when the amount of deflection of the tension spring 110 is large, the cable 107 The difference between the tension during slack removal MAX and the tension during slack removal MIN becomes large. On the other hand, if the cable 107 is set so that the tension at the time of loosening MAX of the cable 107 does not become zero, the tension of the cable 107 at the R portion of the guide rail 102 increases, and a large manual operation force is required for opening and closing the slide door 101. It may be necessary.
On the other hand, in the configuration of the present invention, the cable tension in the traveling route 9B is made larger than that in the case of using the conventional cable tension adjusting structure 108 described in FIG. The tension is kept small and a small manual operation force is required. More specifically, the angle between the longitudinal direction of the arm member 10 and the expansion / contraction direction of the tension spring 11 is larger than the state shown in FIG. 3 as shown in FIG. At this time, the extension of the tension spring 11 is small, and the support shaft 10d of the arm member 10 tends to be pulled downward with a small spring force. However, since the pressing roller 10a of the arm member 10 presses the cable 107 at a wide angle with respect to the expansion / contraction direction of the tension spring 11, the pressing force to the cable 107 is increased by the component force. As described above, the cable tension adjusting structure 6 of the present invention has a structure capable of increasing the pressing force from the tension spring 11, so that the cable tension in the travel route 9B can be increased and the cable 107 can be increased. The difference between the tension during the slack removal MAX and the tension during the slack removal MIN is prevented from becoming large.

  Further, although not shown in FIGS. 3 and 4, when an impact force greater than that at the time of opening and closing is generated in the cable 107, the operation is performed in the region 41 in FIG. 7. At this time, the tension 37 acting on the cable 107 suddenly increases, but the traveling route of the cable 107 is slightly outside the traveling route 9C (a position slightly closer to the straight line 9 from the traveling route 9C on the left side in FIG. 4). As a result, a large impact force is absorbed.

  The cable tension adjustment structure 6 according to the embodiment of the present invention has been described above. However, the PSD unit according to the present invention has various features in addition to the cable tension adjustment structure 6. Hereinafter, the various features will be described in detail with reference to FIGS. In the following description, the same structures as those shown in the prior art will be described with the same reference numerals.

  FIG. 8 is an enlarged plan view of the front side portion 102a of the guide rail 102 as seen from the vehicle upper side. FIG. 9 is an enlarged side view of FIG. 8 viewed from the vehicle outer side direction. In the following description, the front-rear direction refers to the left-right direction in FIG. 8 (the front-rear direction of the vehicle; the left side is the front side). Further, the vehicle outer side refers to the downward direction in the drawing of FIG. 8, and the vehicle inner side refers to the upward direction of the drawing in FIG.

  As shown in FIG. 8, the front side portion 102a of the guide rail 102 is gently curved toward the inside of the vehicle in the same manner as the guide rail 102 shown in the prior art (see FIG. 14). When the door is closed, the slide door 101 is guided toward the inside of the vehicle. In addition, a roller assembly 101 b provided on the arm portion 101 a of the slide door 101 is attached to the guide rail 102 so as to be movable along the extending direction of the guide rail 102.

  A cable locus adjusting member 50 is attached to the front side portion 102a of the guide rail 102 as shown in FIG. The cable trajectory adjusting member 50 is provided on the inner peripheral surface 102b of the front side portion 102a (more specifically, a particularly curved portion of the front side portion 102a) according to the curved shape of the front side portion 102a. . The length of the cable trajectory adjusting member 50 is continuously provided at least from the R-shaped start end to the end of the curved portion of the front side portion 102a.

  As shown in FIG. 9, the cable trajectory adjusting member 50 includes a sliding surface 50a on which the sliding cable 107 abuts and side wall surfaces 50b located on both sides of the sliding surface 50a. . The sliding surface 50a is a surface on which the cable 107 slides while abutting when the roller assembly 101b described above does not pass through the curved portion (when the sliding door 101 is not in a closed state). The sliding surface 50 a is located on the radially outer side with respect to the inner peripheral surface 102 b of the curved portion of the guide rail 102.

  Moreover, the side wall surface 50b is provided in the both right and left sides in the advancing direction of the cable 107, and is formed in the aspect which protrudes toward a radial outer side rather than the sliding surface 50a, respectively. The side wall surface 50b has a function of preventing the sliding cable 107 from deviating outward from the sliding surface 50a.

  By attaching the cable trajectory adjusting member 50, the trajectory of the cable 107 draws a trajectory 107A as shown by a thick two-dot chain line in FIGS. On the other hand, when the cable locus adjusting member 50 is not provided (conventional structure), the locus of the cable 107 draws a locus 107C indicated by a thin two-dot chain line in FIG. The locus of the cable 107 when the roller assembly 101b passes through the curved portion (when the slide door 101 is closed) draws a locus 107B.

  Comparing the trajectory lengths of the trajectories 107A, 107B, and 107C, the trajectory length of the trajectory 107B is the longest, the trajectory 107A is the longest, and the trajectory 107C is the shortest. The extra length to be adjusted by the cable tension adjusting mechanism 6 of the drive unit 1 varies depending on the length of the locus. That is, as in the prior art, in the combination of the trajectories 107B and 107C, the trajectory length difference is the largest and a large extra length is generated. On the other hand, in the combination of the trajectories 107B and 107A, the trajectory length difference is smaller than in the above-described combination, and the extra length to be adjusted can be reduced.

  In other words, the cable for correcting the trajectory of the cable 107 on the inner peripheral surface 102b of the curved portion of the front side portion 102a of the guide rail 102 so that the trajectory 107A is as close as possible to the trajectory 107B. Since the locus adjusting member 50 is provided, the extra length to be adjusted by the cable tension adjusting structure 6 in the drive unit 1 can be reduced. Thereby, the adjustment amount of surplus length can be made small and the slide movement amount of the pulley support part 4 for adjusting surplus length within the cable tension adjustment structure 6 can be restrained small. As a result, the cable tension adjustment structure 6 itself can be reduced, and the drive unit 1 can be further downsized.

Next, the structure of the front reversing pulley 60 (which differs in structure from the front reversing pulley 104 described in FIG. 14 of the prior art but has the same function to change the direction of the cable 107) will be described with reference to FIGS. To do. FIG. 10 is a side view showing a single front reversing pulley 60 used in the PSD unit. FIG. 11 is a side view in which the inner cover 62 is removed from the state of FIG. 10 and the locus of the cable 107 is indicated by a thick two-dot chain line. Further, FIG. 12 is a plan view of FIG. 10 viewed from above.
10 to 11 are views when viewed from the inside of the vehicle, and the right side of FIG. 10 is the front side of the vehicle, and the left side of FIG. 10 is the rear side of the vehicle. Therefore, in the direction described below, the right side in FIG. 10 is referred to as the front direction, and the left side in FIG. 10 is referred to as the rear direction.

  The front reversing pulley 60 is disposed on an extension line of the cable 107 that is linearly drawn from the front side portion 102a of the guide rail 102, and functions to reverse the direction of the cable 107 in the front-rear direction.

  As shown in FIG. 10, the front reversing pulley 60 includes a main body portion 61, an inner cover 62 positioned on the front side of the paper surface of FIG. 10, and an outer cover 68 positioned on the back side of the paper surface of the main body portion 61. ing.

  As shown in FIG. 10, the main body 61 is formed with three mounting holes 61a for mounting on the vehicle main body side. Further, the front side portion of the main body 61 is covered with an inner cover 62. The inner cover 62 is detachably attached to the main body 61 with two screws 63 and 63. Further, an outlet 69 of the cable 107 that is drawn out to the drive unit 1 side is provided at the upper part of the main body 61.

  As shown in FIG. 11, a longitudinally rotating pulley 64 is attached to the inside from which the inner cover 62 is removed. As shown in FIGS. 11 and 12, the vertical rotation type pulley 64 is supported by a pulley rotation shaft 65 extending substantially horizontally from the inside to the outside of the vehicle, and is configured to rotate in the vertical direction.

  As shown in FIGS. 11 and 12, the outer cover 68 is formed with a cable lead-in port 67. The cable lead-in port 67 is open toward the guide rail front side portion 102a in a state where the front-side reversing pulley 60 is attached to the vehicle body side. More specifically, the cable lead-in port 67 is opened toward the vehicle rear oblique outer side so that the cable 107 routed from the front side portion 102a of the guide rail 102 is drawn into the cable lead-in port 67 linearly. It has become.

  Further, as shown in FIG. 11, the outer cover 68 is formed with a guide surface 66 for turning the cable 107 drawn from the cable drawing port 67 toward the longitudinal rotation type pulley 64. The guide surface 66 is formed in a curved shape so that a large bending load does not act on the cable 107 that slides along the curved surface.

  With these structures, as shown in FIGS. 11 and 12, the cable 107 drawn from the cable lead-in port 67 is wound around the longitudinal rotation type pulley 64 through the guide surface 66 and pulled out from the cable lead-out port 69 as it is. After that, it is routed linearly to the drive unit 1.

  In this way, the pulley rotation shaft 65 of the front reversing pulley 60 is arranged so as to be parallel to the vehicle width direction, and the cable 107 is reversed using the vertical rotation type reversing pulley 64 that rotates vertically, thereby having the conventional structure. Thus, the thickness in the vehicle width direction of the front reversing pulley 60 can be reduced as compared with the case where the reversing pulley rotating in the horizontal direction is used. By reducing the thickness, when the front reversing pulley 60 is attached to the vehicle, the front reversing pulley 60 does not protrude to the vehicle interior side, and the vehicle interior can be configured wider than the conventional structure.

  According to the cable tension adjustment structure of the sliding door according to the embodiment of the present invention, the urging force of the tension spring 11 is transmitted to the cable 107 that travels between the two support points T1 and T2, and the travel path 9 ( 9A, 9B, 9C), and the tension spring 11 is used as a tension spring and is set so that the tension spring 11 is extended when absorbing the impact force to the cable 107. Even if a large impact force acts on the slide door 101 and a large tension acts on the cable 107, it is not crushed to the contact height like the spring 110 used in the structure shown in FIG. 15 of the prior art. . Therefore, the impact force does not act on, for example, the drive motor that drives the drive drum 7 to apply a large load. As a result, it is not necessary to provide an impact absorbing material or a clutch for absorbing the impact, the cost can be reduced, and the entire drive unit 1 can be reduced in size and weight.

Further, the travel path 9C of the cable 107 when absorbing the force to the cable 107 at the time of driving max is larger than the moving length L2 of the travel path 9B of the cable 107 when absorbing the tension fluctuation and the extra length of the cable 107. Since the moving length L3 is shorter, when the slide door 101 passes through the front side portion 102a of the guide rail 102, the traveling route 9C (the state in which the route is short) is changed from the traveling route 9A (the state in FIG. 3). ). Therefore, when the sliding door 101 is opened / closed, the longitudinal direction of the arm member 10 is substantially parallel to the expansion / contraction direction of the tension spring 11, and the tension applied to the cable 107 in the travel path 9C is suppressed, and the closing operation is performed. Manual operation with is lightened.
Further, since the cable 107 changes from the travel route 9A to the travel route 9C, the cable 107 is not greatly bent. Therefore, the running resistance of the cable 107 can be kept small, and the tension acting on the cable 107 can be further reduced.

  Furthermore, a larger impact force than when the sliding door 101 is opened and closed is absorbed at a position on the inner side of the straight line 9 connecting the two support points T1 and T2 and slightly outside the traveling route 9C. Therefore, even when a larger impact is received than when the sliding door 101 is opened and closed, the greater impact can be absorbed between the straight line 9 and the travel route 9C. Therefore, the reliability and safety of the cable tension adjustment structure 6 can be further improved.

On the other hand, the arm member 10 has a tension spring 11 attached to the support shaft 10d side, which is one end portion thereof, and the pressing roller 10a side, which is the other end portion, rotates around the one end portion by the urging force of the tension spring 11. Since the cable 107 is pressed, the direction of the urging force of the tension spring 11 can be effectively changed to the direction of the pressing force of the cable 107. Therefore, the degree of freedom in designing when the tension spring 11 and the arm member 10 are arranged in the drive unit 1 is increased. As a result, the cable tension adjustment structure 6 can be configured in a compact manner, and further, the entire drive unit 1 can be reduced in size.
Further, by canceling the spring force of the tension spring 11 at the angle of the arm member 10, the cable 107 can be pressed with a small force when the spring force is large. On the other hand, when the spring force is small, the cable 107 can be pressed with a large force.

  Moreover, since the arm member 10 rotates so that the longitudinal direction thereof follows the travel path 9A (9B, 9C, 9D) of the cable 107, the space in which the arm member 10 rotates can be made compact. Therefore, the cable tension adjusting structure 6 can be formed in a compact manner, and further, the entire drive unit 1 can be reduced in size.

  Further, the tension spring 11 is disposed so that the expansion / contraction direction (displacement direction) of the tension spring 11 is substantially parallel along the straight line 9 connecting the two support points T1 and T2. These arrangement spaces can be made compact as compared with the case where they are arranged so as to intersect with 9. Therefore, the cable tension adjusting structure 6 can be formed in a compact manner, and further, the entire drive unit 1 can be reduced in size.

  On the other hand, the pulley support portion 4 is configured to be movable, and the distance between the two support points T1 and T2 can be changed by changing the distance between the fixed pulley 8 and the drive drum 7. When the work is wound around the drive drum 7, the distance between the support points T 1 and T 2 is made shorter than that at the time of setting to ensure an extra length at the time of work, and no tension is applied to the cable 107. Can be. Therefore, even if the cable tension adjustment structure 6 as in the present invention is adopted, the work for assembling the cable 107 can be easily performed as in the conventional case.

  Further, when the distance between the two support points T1 and T2 is shortened, the pressing roller 10a of the arm member 10 is received against the urging force of the tension spring 11, and the pressing roller 10a presses the cable 107. Since the roller receiving portion 4a for cutting off the pressure is provided, the pressing force from the pressing roller 10a does not act on the cable 107 when the cable 107 is wound around the pulleys 7 and 8 of the drive unit 1. can do. Therefore, the work can be easily performed without receiving the tension of the cable 107.

  Furthermore, since the pulley support part 4 is separated from the main body part 2 and the upper cover 3 and the pulley support part 4 is configured to be slidable, the main body part 2 and the upper cover 3 are larger than necessary for tension adjustment. There is no need to make it bigger. Further, since the distance between the two support points T1 and T2 is shortened, a space larger than the space for adjusting the tension (the space shown in FIGS. 3 and 4) when the cable 107 is wound. Do not need. Therefore, the whole drive unit 1 can be reduced in size.

As described above, the cable tension adjusting structure of the sliding door according to the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications and changes are made based on the technical idea of the present invention. It can be changed.
For example, although the tension spring 11 is a coil spring in the present embodiment, it may be composed of another spring. For example, any spring that applies a pressing force to the cable 107 by elasticity, such as a spiral spring or a leaf spring, may be used.

DESCRIPTION OF SYMBOLS 1 Drive unit 2 Main-body part 2a Claw for temporary latching of lever 3 Upper cover 4 Pulley support part 4a Roller receiving part (pressing force interruption structure)
4b Cable inlet 4c Operation part engaging groove 5 Screw 6 Cable tension adjustment structure 7 Pitch circle of driving drum 8 Pitch circle of fixed pulley 9 Straight line connecting two support points 9A, 9B, 9C, 9D Changed travel path 10 Arm member (transmission member)
10a Pressing roller 10b Rotating shaft 10c Extension part 10d Support shaft 11 Tension spring (spring)
DESCRIPTION OF SYMBOLS 12 Spring receiving part 13 Lever 13a Rotating shaft 13b Operation part 13c Temporary fixing hole 14 Drive motor 20 Set direction 20a Projection direction 30 Set release direction 20b Retraction direction 30 Cable tension adjustment structure set position 31 Absorption position 32 Shock absorption position of cable tension adjustment structure 35 Displacement amount of tension spring 36 Energizing force of tension spring 37 Cable tension 38 Movement amount of arm member support shaft 50 Cable trajectory adjustment member 50a Sliding surface 50b Side wall surface 60 Front side Reversing pulley 61 Main body 62 Inner cover 63 Mounting screw 64 Vertically rotating pulley 65 Pulley rotating shaft 66 Guide surface 67 Cable inlet 68 Outer cover 69 Cable outlet 100 Vehicle 101 Slide door 101a Arm 101b Roller assembly 102 Guide rail 102a Front side portion of guide rail 102b Inner peripheral surface of guide rail 103 Power slide door unit (PSD unit)
104 Front reversing pulley 105 Rear reversing pulley 106 Drive unit 107 Cable 107A, 107B, 107C Cable trajectory 108 Cable tension adjustment structure 109 Movable pulley 110 Tension spring 111 Fixing part 112 Diagonal vertical direction 113 Drive pulley T1, T2 Support point R1, R2 Rotation direction R1A Up direction R2B Down direction

Claims (8)

The cable is incorporated in a drive unit for driving a cable attached to the slide door, and absorbs extra length caused by a change in the tension of the cable and a change in the movement trajectory of the cable caused by the opening and closing operation of the slide door, and the cable A cable tension adjusting structure of a sliding door provided with a spring for absorbing impact force generated as tension in
A driving drum that is rotationally driven by a driving motor; and a fixed pulley. The cable is wound around the driving drum and the fixed pulley, and the driving drum and the fixed pulley constitute two support points for the cable. And
The two runs between supporting points to transmit the biasing force of the spring to the cable is pressed toward the interior of the driving unit, has a transfer member for changing the traveling path of the cable,
A structure for adjusting a cable tension of a sliding door, wherein the spring is used as a tension spring and is set so that the spring extends when absorbing an impact force to the cable.   The travel length of the cable travel path when absorbing the impact force to the cable is shorter than the travel length of the cable travel path when absorbing the tension variation and the extra length of the cable. The cable tension adjusting structure for a sliding door according to claim 1, wherein   The shock force acting on the cable when the sliding door is opened and closed is absorbed at a position where the travel route of the cable is moved rather than a straight line connecting the two support points. The cable tension adjusting structure for a sliding door according to claim 1 or claim 2.   The transmission member is an arm member that has the spring attached to one end thereof and the other end is an arm member that presses the cable while rotating around the one end by the biasing force of the spring. The cable tension adjusting structure for a sliding door according to any one of claims 1 to 3.   5. The cable tension adjustment structure for a slide door according to claim 4, wherein the arm member rotates so that a longitudinal direction thereof is along a travel route of the cable.   6. The cable tension adjusting structure for a sliding door according to claim 1, wherein the direction of expansion and contraction of the spring is arranged along a straight line connecting the two support points. .   The cable tension adjusting structure for a sliding door according to any one of claims 1 to 6, wherein the distance between the two support points is changeable.   A pressing force blocking structure that blocks a pressing force from the transmission member to the cable against a biasing force of the spring when the distance between the two support points is shortened. Item 8. A cable tension adjustment structure for a sliding door according to Item 7.