JPH11303503A - Window regulator carrier plate - Google Patents

Abstract

PROBLEM TO BE SOLVED: To lessen rotational rattle between a carrier plate and a guide rail as retaining smooth elevating motion of the carrier plate and restrain rotational rattle from increasing after a a long period of use. SOLUTION: This carrier plate 1 is provided with a substrate made of a metal plate, hard synthetic resin made sliding parts 7, 8 provided on the substrate so as to sandwich a guide rail 2 between them, and an elastic boss protruding from both sides of the sliding parts 7, 8 guiding surfaces 7b, 8b sliding with the guide rail 2. The elastic boss is composed of a protrusion from the guiding surfaces 7b, 8b of an urethane made elastic body 16 integrally provided in a cylindrical hole provided on the sliding parts 7, 8 by two-layer forming.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a carrier plate for a window regulator. More specifically, the present invention relates to an improvement of a carrier plate in a window regulator for elevating a window glass of an automobile or the like.

[0002]

2. Description of the Related Art A window regulator 100 as shown in FIG. 11 has conventionally been used to raise and lower a window glass such as a door of an automobile. In FIG.
Reference numeral 1 denotes a guide rail attached to the inner surface of the door panel, and reference numeral 102 denotes a carrier plate slidably provided on the guide rail 101. Carrier plate 1
The lower end of the window glass G is attached to 02. The carrier plate 102 has a locking portion 103 protruding therefrom, and two inner cables (inner cable) 104, 1
05 is locked. One inner cable 104 extends upward from the locking portion 103 and is connected to the guide rail 1.
Guide pulley 1 rotatably attached to the upper end of 01
06, changed direction, outer casing (conduit)
It is guided by 107 and wound around the drum 109 in the actuator 108 and locked.

[0003] The other inner cable 105 is
It extends downward from 03, is turned by a guide pulley 110, is guided by an outer casing 111, is wound around the drum 109 of the actuator 108 in the opposite direction, and is locked. Reference numeral M is a motor for rotating the drum 109 forward and backward.

The guide rail 101 is, for example, shown in FIG.
As shown in FIG. 2, a bent portion 113 is formed at one end of one steel sheet, and a ridge 114 is provided near the other end. In order to increase rigidity and thickness accuracy, the protruding ridges 114 are formed by being once raised and then double-folded. The carrier plate 102 includes a substrate 115 made of a steel plate and a sliding portion (slider) 116 made of synthetic resin which is insert-molded on the substrate.
A guide groove 117 that slides on the protrusion 114 of the guide rail is formed in the sliding portion. Hard engineering plastic such as polyacetal is used for the sliding portion 116. Reference numerals 118 and 119 are guide rails 1.
01 is an inverted L-shaped side guide that is in sliding contact with the side edge and the upper surface of No. 01.

[0005] The fitting between the guide groove 117 and the ridge 114 is usually provided with a clearance of about 0.1 to 0.5 mm, so that the window glass G attached to the carrier plate 102 is ± 0.1 to 0 mm. .Rotation of about 2 ° (FIG. 11)
Play in the direction of rotation in the paper plane). Further, due to the elastic deformation of the sliding portion 116, the play in the rotation direction of the window glass G is further increased, which causes problems such as rattling when the window glass is moved up and down and a bottom contact with the run channel.

In view of the above problem, the present applicant has proposed a metal plate 11 for a carrier plate as shown by a broken line in FIG.
5, convex part 116a by drawing and raising
The sliding portion 116 is formed by outsert molding a synthetic resin so as to cover the projecting portion 116a and the projecting portion 116b. (See Japanese Patent Application Laid-Open No. 8-13912).

[0007] This is a sliding part 116 and side guide 1
The pinching rigidity of the guide rail 101 by 18, 18 is high. Therefore, it is possible to reduce the rotational play due to the elastic deformation. However, the sliding portion 116
However, in order to slide on the guide rail 101, the clearance cannot be eliminated, and the rotational play based on this clearance does not decrease. Further, since the sliding portion 116 slides on the guide rail 101 when the window glass G is raised and lowered, the guide surface which is the inner surface of the guide groove 117 is worn. Therefore, if the raising / lowering operation of the window glass G is repeatedly performed, the clearance between the sliding portion 116 and the ridge 114 of the guide rail 101 increases, and the rotational play is also, for example, ± 0.3 to
It increases to about 0.5 °.

[0008]

SUMMARY OF THE INVENTION The present invention aims at minimizing the rotational play between the carrier plate and the guide rail while maintaining the smooth sliding of the carrier plate. The technical task is to suppress the increase as much as possible.

[0009]

According to the present invention, there is provided a carrier plate comprising: a substrate; a synthetic resin sliding portion provided on the substrate so as to sandwich a guide rail;
The sliding portion includes a guide rail and an elastic projection made of an elastic polymer material provided on a sliding guide surface. In the carrier plate according to the second aspect, the elastic projections are further provided on the guide surfaces on both sides of the guide rail, and the size of the gap between the elastic projections on both sides is larger than the size of the sliding portion of the guide rail. It is characterized by being narrow.

According to a third aspect of the present invention, the sliding portion is made of a hard synthetic resin integrally formed on a metal substrate, and the elastic projection is formed in two layers on the sliding portion. It is characterized by being a protrusion of an elastic body made of a molecular material. The carrier plate according to a fourth aspect is characterized in that the elastic projection has a form of a ridge extending transversely to a sliding direction of the carrier plate. The carrier plate according to claim 5 is characterized in that at least two of the sliding portions are provided at intervals in the longitudinal direction of the guide rail.

[0011]

Since the carrier plate of the present invention has elastic projections on the guide surface, the contact pressure can be reduced even when the carrier plate strongly contacts the guide rail. Therefore, even if the clearance with the guide rail is reduced, the sliding resistance of the carrier plate does not increase so much. Therefore, the clearance can be reduced as compared with the related art, and the backlash in the front-rear direction of the windowpane when the windowpane moves up and down can be reduced. Therefore, since the rotation angle of the windowpane is small, problems such as bottoming of the windowpane into the run channel are reduced.
In addition, this makes it possible to reduce the setting of the gap between the glass and the run channel, thereby increasing the degree of freedom in door design.

In the carrier plate of the present invention, since the dimension of the gap between the elastic projections sandwiching the guide rail is smaller than the dimension of the sliding portion of the guide rail, the elastic projection is elastic so as to retract with respect to the sliding surface. It comes into contact with the guide rail in a deformed state and slides on its surface. Therefore, the clearance becomes substantially zero, and the backlash in the front-back direction of the window glass can be almost eliminated. Further, even if there is a change with time such as wear, the state of zero clearance can be maintained while the elastically deformed elastic projection returns to its shape and follows.

In the carrier plate according to the third aspect, the sliding portion made of a hard synthetic resin is integrally formed on a metal substrate, and the elastic portion is formed in two layers on the sliding portion, so that the fixing strength is improved. High and easy to mold. In addition, since the elastic deformation of the protrusion extends to the portion embedded in the sliding portion, local deformation of the protrusion is suppressed. In the carrier plate according to the fourth aspect, since the elastic projection has a shape of a ridge extending in the horizontal direction, the elastic projection is easily deformed and has a large sliding contact area. In the carrier plate according to the fifth aspect, since two or more sliding portions are provided at intervals, the rotational play of the carrier plate is further reduced.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of a carrier plate according to the present invention will be described with reference to the drawings. 1 is a front view showing an embodiment of the carrier plate of the present invention, FIG. 2 is a perspective view thereof, FIG. 3a is an enlarged view of a main part thereof, FIG. 3b is a sectional view taken along line III-III of FIG. 3a, FIG. 4b is an explanatory view illustrating the operation of the carrier plate of the present invention, FIGS. 5a and 5b are perspective views showing other embodiments of the sliding portion according to the present invention, and FIGS. 6a and 6b are respectively related to the present invention. Perspective view showing still another embodiment of the sliding portion,
FIG. 7 is a front view of a main part showing another embodiment of the carrier plate of the present invention, FIG. 8 is a schematic front view of a device for measuring the rotational play of the carrier plate of the example and the comparative example, and FIGS. It is a graph which shows the rotation backlash of the carrier plate of an Example and a comparative example.

The carrier plate 1 shown in FIG. 1 has almost the same overall configuration as a conventional carrier plate, and slides on a guide rail 2. The guide rail 2 is the same as the conventional one, and as shown in FIG. 2, one end of a strip-shaped metal plate such as a steel plate is bent at a right angle to form a bent portion 3.
And a ridge 4 having a double bending structure is provided near the other end. Note that the guide rail 2 is curved so as to protrude outward from the automobile according to the curvature of the window glass.

The carrier plate 1 comprises a substrate 5 made of a metal plate such as a steel plate, and a synthetic resin portion integrally formed with the substrate by insert molding. The synthetic resin portion includes a cable locking portion 6 provided at the center of the substrate 5, sliding portions 7 and 8 provided at the top and bottom, and side guides 9 and 10 provided at the left and right.
Etc. Reference numeral 12 denotes a stopper rubber holding portion for stopping the carrier plate 1 at the lower end of the guide rail 2. Hard engineering plastics such as polyacetal, polyamide, and polyethylene terephthalate are used as the synthetic resin for insert molding.

The above-mentioned cable locking portion 6 has a box-down configuration, and an opening 6b for passing a cable end fitting of a cable is provided at the center of the upper surface 6a.
A groove 6d through which the cable passes is formed over 6c. Each of the side guides 9 and 10 has an inverted L-shape, and slides on a side edge and an upper surface of the guide rail 2 to restrict the carrier plate 1 from falling in the left-right direction. On the lower surface of the upper end of the right side guide 10, a small protrusion is formed which slides while engaging with a groove 4a which appears on the back side of the ridge 4 of the guide rail 2.

FIG. 3a is an enlarged view of the lower sliding portion 8 of the upper and lower sliding portions 7 and 8 in FIG. As shown in detail in FIG. 3A, the sliding portion 8 is a block having a guide groove 8a extending vertically in the center. As shown in FIG. 3B, the guide groove 8a has a substantially U-shaped cross-sectional shape that is in sliding contact with the ridge 4 of the double bent structure of the guide rail 2. The sliding portion 8 extends to the rear surface of the substrate 5 through an opening (not shown) formed in the substrate 5, and is thereby fixed to the substrate 5. Between the guide groove 8a and the ridge 4, a clearance equivalent to that of the related art is provided.

The sliding portion 8 is provided with a total of four elastic projections 15 projecting somewhat from the inner surface (guide surface) 8b of the guide groove 8a, two pairs of upper and lower portions on the left and right. In this embodiment, the elastic projections 15 are provided with the guide grooves 8a.
And a portion protruding from the inner surface of the elastic body 16 embedded in the cylindrical hole or groove 8d formed in the above. The elastic body 16 is made of a polymer material having elasticity and high abrasion resistance, such as synthetic rubber such as polyurethane or chloroprene rubber, natural rubber, or synthetic resin having high elasticity. The hardness of the material constituting the elastic body 16 is determined according to JIS.
K 6301-5, about 50 to 90, especially 60 to 8
About 0 is preferable. The elastic body 16 can be manufactured separately from the sliding portion 8 and then embedded and fixed with an adhesive. However, the elastic member 16 is formed on the sliding portion 8 by molding two layers of synthetic resin such as polyurethane. It is preferable to integrally mold the notch into a cylindrical hole or groove 8d. Note that FIG.
As shown in the figure, the lower part of the columnar elastic body 16 penetrates through the substrate 5 and extends to the rear surface thereof in the same sectional shape. Although this configuration is for convenience in molding, it also has the advantage of increasing the fixing strength to the substrate 5.

The protrusion of the elastic body 16 having an arcuate cross section, that is, the protrusion height (h in FIG. 4A) of the elastic protrusion 15 may be set to an appropriate size according to the hardness and shape of the elastic body 16. However, usually about 0.2 to 0.8 mm, especially 0.3
About 0.4 mm is preferable. The width w of the protrusion is 1 to 5 mm
It is preferably about 2 to 4 mm. When the protrusion height h and the width w are reduced, the ridge 4 of the guide rail 2 directly contacts the sliding portion 8 when the elastic body 16 is pressed. Thereby, the maximum value of the rotation angle of the carrier plate 1 is regulated, and the sliding portion 8 shares the load based on the torque, and the load on the elastic body 16 is reduced. However, if it is too small, the inner surface 8b of the guide groove 8a tends to be worn. When the protruding height h and the width w are large, it is possible to prevent the ridge 4 of the guide rail 2 from directly slidingly contacting the inner surface 8b of the guide groove 8a. However, if it is too large, the rotation angle with respect to the torque load becomes large. The portion of the elastic body 16 embedded in the sliding portion 8 serves to fix the elastic projection 15 to the sliding portion 8 and also elastically deforms together according to the load applied to the elastic projection 15, Plays a role in increasing the amount of displacement of the protrusion height h while reducing the local deformation of.

In this embodiment, as shown in FIG. 4A, a part of the inner surface 8b of the guide groove 8a is inclined or formed in an arc shape. The inclination is made so that a lubricant such as grease easily enters the sliding portion. Accordingly, the protrusion height h of the upper elastic body 16 is larger than the protrusion height h of the lower elastic body. The gap between the left and right elastic bodies 16 is smaller than the thickness of the ridge 4 of the guide rail 2 by about 0.2 to 1.2 mm, preferably about 0.3 to 0.7 mm. That is, a negative tolerance is set.
Thereby, when the ridge 4 is inserted into the gap of the elastic body 16,
The elastic body 16 is somewhat deformed, and the repelling force elastically presses the ridge 4. Therefore, the mechanical clearance becomes zero, and the rotational play of the carrier plate 1 is reduced.
That is, there is no rotation play at the time of no load unlike the conventional one. However, when a load is applied, it tilts back and forth according to the amount of elastic deformation. Further, by pressing the ridge 4 with the elastic body 16, there is an effect of preventing dust from being mixed into the sliding portion.

In the present embodiment, the sliding portions 7 and 8 are
And guide grooves 7 of the respective sliding portions 7 and 8
Elastic body 16 is provided on a and 8a. Therefore, when a counterclockwise torque in FIG. 1 is applied to the carrier plate 1, the right elastic body 16 of the upper sliding part 7 and the left elastic body 16 of the lower sliding part 8 are pressed, respectively. The elastic body 16 facing them is restored to the original shape. In this case, as shown in FIG. 4B, when the amount of deformation of the elastic body 16 on the torque supporting side exceeds the amount of return of the elastic body 16 on the opposite side, a gap is formed between the ridge 4 and the elastic body on the opposite side. S
There is a possibility that there will be. Such a gap S is not particularly obstructive unlike the rotation play at the time of no load, but can be avoided by setting the elastic coefficient of the elastic body 16 in an appropriate range according to the assumed torque. Further, the interval P between the tip of the elastic body 16 on the returning side (right side) and the inner surface 8b of the guide groove 8a on the pressed side (left side) may be made smaller than the thickness of the ridge 4. . In this case, even if the ridge 4 abuts on the inner surface 8b of the guide groove 8a, the zero clearance state in which the distal end of the elastic body 16 on the return side abuts on the ridge 4 is maintained.

The carrier plate 1 shown in FIG. 1 is manufactured by pressing a steel plate to produce a substrate 5, setting the substrate 5 in a mold having a predetermined cavity, and injection molding a hard synthetic resin such as polyacetal. Then, the synthetic resin portion excluding the elastic body 16 is outsert formed, and after cooling, a synthetic resin such as polyurethane is injection-molded to form the elastic body 16 into two layers. However, it can also be manufactured by fixing the separately formed sliding portion 8 and side guides 7 and 8 to the substrate 5 by bonding or the like, or by crimping through a metal shaft.

In the above-described embodiment, a columnar elastic body is employed. However, the elastic body may be a prismatic one, or a columnar elastic body 16 in which a cylinder and a prism are combined as shown in FIG. 5A. When the columnar elastic body 16 is employed irrespective of the cross-sectional shape, the sliding portions 7 and 8 having the holes or grooves 8d for receiving the elastic body 16 and the injection molding of the elastic body 16 become easy, respectively. Furthermore, the elastic projections are in the form of ridges extending laterally with respect to the guide rails 2 and exhibit a so-called line contact state. Therefore, there is an advantage that the elastic projection 16 can be easily deformed and has a relatively large sliding contact area, so that a large pressing force can be received and the sliding resistance is low. However, the present invention is not limited to this. For example, FIG.
An elastic body 16 exhibiting a point contact state as shown in FIG.

Further, in the above-described embodiment, a part of the elastic body 16 is used as an elastic projection. However, as shown in FIG. 6A, a cylindrical ridge 16 is formed on the inner surface 8b of the guide groove 8a.
The plate-like elastic body 16 provided with a may be fixed by bonding or the like. Also, the sliding portions 7 and 8 and the side guides 9
In the same manner as in the prior art (see FIG. 12), a protrusion 10 or a protrusion is formed from the metal plate substrate 4 by cutting or drawing, and a synthetic resin is outsert-molded on the surface. In such a case, the rigidity of the sliding portion 8 can be increased. Further, as shown in FIG.
8 can also be manufactured by directly outsert molding the elastic body 16.

In the above-described embodiment, the guide grooves 7a and 8a are formed in each of the sliding portions 7 and 8, however, as shown in FIG.
A sliding portion 19 that slides from one side with respect to the guide rail 2,
20, 21, and 22 may be alternately arranged in three or four or more staggered shapes. Also in this case, the distal end of the elastic body 16 of the left sliding parts 19 and 21 and the right sliding part 2
It is preferable that the interval t (the interval in the direction perpendicular to the sliding direction) t between the distal ends of the elastic members 16 of 0 and 22 is smaller than the thickness of the ridge 4 of the guide rail. The “gap” in claim 2 includes such an interval t.

[0027]

Next, the effects of the carrier plate of the present invention will be described with reference to examples and comparative examples. Example 1 A cold-rolled steel plate (SPCC) was press-formed to produce a substrate 5 having the form shown in FIG. 1, and polyacetal was insert-molded to form sliding parts 7 and 8, and then polyurethane 2 was formed. The elastic body 16 is formed by layer forming, and FIG.
Was manufactured. This carrier plate is referred to as Example 1. The width of the guide grooves 7a, 8a is 2.5 mm, the diameter of the elastic body 16 is 3 mm, the distance between the centers of the upper and lower elastic bodies is 6 mm, the hardness of the elastic body is 70 Hs,
8 was 90 mm. Comparative Example 1 A conventional product similar to that of Example 1 except that the elastic body 16 was not provided was used as a carrier plate of Comparative Examples 1 and 2.

A measurement bar 30 as shown in FIG. 8 was attached to the obtained carrier plate 1 and fitted to the guide rail 2, and a displacement gauge 31 was installed on the lower surface of the tip of the measurement bar 30. The distance L from the center of the guide rail at the tip of the measurement bar 30 was 500 mm. The measurement bar 30
Was directly attached to the guide rail 2 and the elastic displacement of the measurement bar 30 and the guide rail 2 was measured in advance. However, the displacement was 0.1 mm, which was sufficiently smaller than the displacement 10 mm based on the rotational play of the carrier plate 1. , Ignored in the following data.

The load F applied to the carrier plate 1 while gradually applying a large load to the tip of the measurement bar 30 described above.
And the amount of displacement of the tip of the measurement bar 30 was determined. FIG. 9 shows the result. In the graph of FIG. 9, the load torque (Nm) is obtained from the load and the length of the measurement bar,
The rotation angle (゜) is obtained from the length of
The vertical axis and the horizontal axis are shown respectively.

Next, each carrier plate and the guide rails are set on the door of the actual vehicle, and a durability test is performed in which 15,000 times of lifting and lowering operations are performed. I asked. The result is shown in FIG.

According to FIG. 9, when the torque was increased, the rotation angle of the carrier plate of Example 1 was larger than that of the carrier plates of Comparative Examples 1 and 2. It is considered that this is because the elastic deformation of the elastic body increases proportionally.
However, in a no-load state, in Comparative Examples 1 and 2, 0.1 to 0.2.
In the first embodiment, the rotational play was zero, while the angle was about 2 °. Also, the range where the load torque is small (15 Nm in FIG. 9)
It can be seen that even in the case of (−35 Nm), the inclination angle of the carrier plate of Example 1 is smaller than those of Comparative Examples 1 and 2. Here, the torque on the “+” side is defined as clockwise torque, and the torque on the “−” side is defined as counterclockwise torque.

Further, according to the measurement results after the durability test shown in FIG. 10, in the carrier plates of Comparative Example 1 and Comparative Example 2, the rotational play under no load greatly increased to 0.3 to 0.4 °. On the other hand, in the carrier plate of the first embodiment, a state in which there is no rotation play is maintained. In addition, even when a load is applied, it can be seen that the rotational play of the carrier plate of Example 1 is much smaller than that of Comparative Examples 1 and 2.

Note that the sliding resistance of the carrier plate of the first embodiment is 12 N even though the elastic body is always pressing.
Met. This value was only slightly increased as compared with the sliding resistance 10N of Comparative Example 1 and the sliding resistance 9N of Comparative Example 2.

[Brief description of the drawings]

FIG. 1 is a front view showing an embodiment of a carrier plate of the present invention.

FIG. 2 is a perspective view of the carrier plate of FIG.

FIG. 3a is an enlarged view of a main part thereof, and FIG. 3b is a sectional view taken along line III-III of FIG. 3a.

4a and 4b are explanatory views illustrating the operation of the carrier plate of the present invention.

5a and 5b are perspective views showing other embodiments of the sliding portion according to the present invention.

6A and 6B are perspective views showing still another embodiment of the sliding portion according to the present invention.

FIG. 7 is a main part front view showing another embodiment of the carrier plate of the present invention.

FIG. 8 is a schematic front view of an apparatus for measuring rotational play of a carrier plate according to an example and a comparative example.

FIG. 9 is a graph showing the backlash of the carrier plates of the example and the comparative example.

FIG. 10 is a graph showing the backlash of the carrier plates of the example and the comparative example.

FIG. 11 is a front view showing an example of a window regulator using the carrier plate of the present invention.

FIG. 12 is a perspective view showing an example of a conventional carrier plate and guide rail.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Carrier plate 2 Guide rail 4 Protrusion 5 Substrate 7 Sliding part 8 Sliding part 15 Elastic projection 16 Elastic body 19 Sliding part 20 Sliding part 21 Sliding part 22 Sliding part

Claims (5)

[Claims] 1. A carrier plate that slides on a guide rail, comprising: a substrate; a synthetic resin sliding portion provided so as to sandwich the guide rail on the substrate; and a guide for the sliding portion. A carrier plate for a window regulator, comprising: a rail; and an elastic projection made of an elastic polymer material provided on a sliding guide surface. 2. The method according to claim 1, wherein the elastic projections are provided on guide surfaces on both sides of the guide rail, and a gap between the elastic protrusions on both sides is smaller than a thickness of a sliding portion of the guide rail. The described carrier plate. 3. An elastic body made of an elastic polymer material, wherein said sliding portion is made of a hard synthetic resin integrally formed on a metal substrate, and said elastic projection is formed on said sliding portion in two layers. The carrier plate according to claim 1, wherein the carrier plate is a protrusion. 4. The carrier plate according to claim 1, wherein said elastic projection has a form of a ridge extending transversely to a sliding direction of the carrier plate. 5. The carrier plate according to claim 1, wherein at least two sliding portions are provided at intervals in a longitudinal direction of the guide rail.