JP3409840B2 - Loading platform lifting device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an apparatus for lifting and lowering a cradle which is mounted on a rear portion or a side portion of a lorry and is used for loading and unloading luggage.

[0002]

2. Description of the Related Art FIG.
It is a side view of the conventional loading platform raising / lowering apparatus described in the 9th publication. In the figure, a main frame 202 of a load receiving platform elevating device is attached to a rear portion of a vehicle body 201 so as to be slidable in the vehicle longitudinal direction. This mainframe 202
To the main arm 203 and the sub arm 2 via a pin or the like.
04, and a lifting hydraulic cylinder 205 are attached. The loading tray 206 includes a main plate 207 and a foldable sub-plate 208. The sub-plate 208 is unfolded when loading a load (shown by a chain double-dashed line) and folded when stored (shown by a solid line). .). The load receiving base 206 is connected to the main arm 203 and the pin 210 at a bracket 209 provided at the base of the main plate 207. Therefore, the load receiving base 206 rotates together with the bracket 209 about the pin 210. The link body 211 that shares the pin 209 with the bracket 209 is the other pin 21.
2 is connected to the sub arm 204. The tip of the lifting hydraulic cylinder 205 is connected to the main arm 203 by a pin 213.

The main arm 203 and the sub arm 20
4 constitutes a parallel link, and the lifting hydraulic cylinder 20
By expanding and contracting 5, the load receiving base 206 is moved up and down while being kept horizontal. When loading and unloading of luggage is completed, the loading tray 206
The sub-plate 208 of is folded. Next, when the folded load receiving table 206 is further tilted to the position shown by the chain double-dashed line in FIG. 23, the main arm 203 and the sub arm 204 are raised to predetermined positions, and the state shown in FIG. 24 is obtained. This state is the pull-out position of the load receiving platform lifting device. From here, when the sliding hydraulic cylinder (not shown) is slid in the storage direction, the loading platform elevating device is retracted and stored under the vehicle body.

[0004]

In the conventional load receiving platform raising / lowering device as described above, the hydraulic cylinder for sliding is used to move to the predetermined storage position or the pulling out position. Not provided. Therefore,
If oil leaks from the slide hydraulic cylinder, it is expected that the movable member of the device will be pulled out due to vibration during traveling. Further, in the case where a vehicle body is loaded and unloaded on a slope in a state where the vehicle body is lowered forward, if oil leakage similarly occurs, there is a possibility that the drawn movable side member may move in the storage direction due to gravity. In view of the above-mentioned conventional problems, it is an object of the present invention to provide a load platform elevating / lowering device that prevents an unintentional sliding operation in the storage position or the withdrawal position.

[0005]

SUMMARY OF THE INVENTION A cargo platform raising / lowering device according to the present invention includes a fixed side member attached to a vehicle body, a support base supported slidably in the horizontal direction by the fixed side member, and the support base. A slide drive mechanism that slides to a predetermined position, two arms that are supported by the support base and that form a parallel link that moves up and down, a lift drive mechanism that drives the arm, and a pivotable end side of the arm. The load-bearing platform elevating device including a load-bearing platform connected to the fixed-side member, the fixed-side member including a slide rail having holes corresponding to a storage position and a withdrawal position, and the support base to the slide-rail. An engaging pin that is movably supported in the intersecting direction, has a tapered portion at a portion of its tip, and the tip portion including the tapered portion can be inserted into and removed from the hole, and the engagement pin. A slide lock device including an elastic member for urging the slider toward the slide rail, and an operation portion connected to the engagement pin for changing the direction of the taper portion (claim 1). .

In the load receiving platform raising / lowering device configured as described above, the taper portion is moved in the direction in which it is slid by the operating portion from the initial state in which the engaging pin is fitted into the hole of the slide rail in the retracted position or the retracted position. By orienting, the engaging pin can be brought out of the hole of the slide rail, and the sliding operation becomes possible. At the slide end, the engagement pin fits into the hole and locks the slide movement in the reverse direction. To slide in the opposite direction, the tapered portion is directed in the direction in which it is slid by the operating portion, so that the engagement pin can be removed from the hole of the slide rail, and the sliding operation becomes possible. Even at this sliding end, the engaging pin fits into the hole, and the sliding operation in the reverse direction is locked. In this way, in the retracted position or the retracted position, which is the slide end, the engagement pin fits into the hole and the sliding operation in the reverse direction is automatically locked. Unlocking requires the act of operating the operation unit, and is not naturally released.

[0007] In the load receiving platform raising / lowering device (claim 1), a plurality of the holes corresponding to the pulling position may be provided in the sliding direction (claim 2). In this case, the slide lock position can be adjusted by selecting the hole into which the engagement pin fits.

[0008]

1 to 22 are views relating to an apparatus for lifting and lowering a cradle according to an embodiment of the present invention. FIG.
It is a side view which shows the goods receiving platform raising / lowering apparatus 1 attached below the luggage box 102 in the rear part of the vehicle body 101 of a lorry.
First, in FIG. 1, the chassis 1 behind the rear wheel 103 is shown.
An angle-shaped mounting member 2 is vertically mounted on each of both side surfaces of 04, and a slide rail 3 made of I-shaped steel is horizontally fixed to the mounting member 2. The slide rail 3 supports a movable side member of the load receiving platform elevating / lowering device 1 which will be described later, and horizontally guides the sliding movable side member. The supporting bases of these movable-side members are the first supporting plate 4, the second supporting plate 5 having a thick wall (about 25 mm), and the rectangular tubular connecting pipe 6.

The first support plate 4 arranged adjacent to the slide rail 3 is mounted on the slide rail 3 via a sliding member (a side pad 69 (FIG. 16 and FIG. 17B) which will be described later).
And is slidable in the horizontal direction along the slide rail 3. The first support plates 4 provided on the left and right (both sides) of the vehicle body are welded to the outer peripheral portion of the connecting pipe 6 which is horizontally arranged in the width direction of the vehicle body. The second support plate 5 is externally inserted into the connecting pipe 6 and welded to the outer periphery of the connecting pipe 6 at a predetermined position outside the first supporting plate 4 in the vehicle width direction. Therefore, the left and right pair of the first support plate 4, the second support plate 5, and the connecting pipe 6 form a structurally integral support base.

The switch box 7 containing the operation switches, control circuit, etc. of the load receiving platform lifting device 1 is provided only on the left side of the vehicle body. The switch box 7 is fixed to the second support plate 5 and projects most outward in the vehicle width direction. When the cover 7a is opened to the front, the key switch S1
An elevating switch S2 is arranged. Key switch S
1 has three positions of "OFF", "ON" and "ST", and in the "OFF" and "ON" positions, the key can be held at that position even if the hand is released.
At the "ST" position, the key returns to "ON" when the hand is released. The elevating switch S2 is a neutral position automatic return type toggle switch, and has three positions of "up" and "down" across the neutral position. The elevating switch S2 is connected to a retractor type cable, and can be operated by pulling it out of the switch box 7. On the other hand, a power unit box 8 (shown by a broken line) containing a hydraulic pump, a valve and the like is provided only on the right side of the vehicle body and is fixed to the second support plate 5 on the right side surface.

FIG. 2 shows the switch box 7 from FIG.
FIG. 3 is a diagram mainly showing a structure relating to a slide mechanism and an elevating mechanism of the load receiving platform elevating / lowering device 1 while omitting illustration of the power unit box 8. 3 to 6 are side views sequentially showing a process of pulling out and deploying the load receiving platform elevating device 1 in the state of FIG. In FIG. 2, the substantially linear lower arm 9 is rotatable about a pin 10 provided at the left end within a predetermined range.
It is attached to the support portion 11 fixed to the. The right end of the lower arm 9 is connected to a link body (vertical link body) 13 via a pin 12.

The upper arm 14 forming a parallel link together with the lower arm 9 is rotatable about a pin 15 provided at the left end within a predetermined range, and the pin 15 is a vertically elongated auxiliary link 16. It is installed. Upper arm 1
The right end of 4 is connected to the link body 13 via a pin 17. The upper arm 14 is composed of a side trunk portion 14a such as a long sword and a substantially L-shaped tip portion 14b. The root portion 14a is the second support plate 5
A pair of steel plates having the same shape are provided with the hydraulic cylinder (hereinafter referred to as a lift cylinder) 20 as a lifting drive mechanism arranged between the pair of steel plates.

The auxiliary link 16 is rotatable about a pin 18 within a predetermined range, and the pin 18 is attached to the second support plate 5. A stopper 19 including a bolt, a nut, and the like is attached to the lower left end side of the auxiliary link 16, and the head of the stopper 19 (head of the bolt) abuts on the second support plate 5 so that the auxiliary link 1
The clockwise rotation of 6 is restricted. Both ends of the lift cylinder 20 are connected to the auxiliary link 16 and the upper arm 14 by pins 21 and 22, respectively.
The pair of left and right upper arms 14 are connected to each other at a tip portion 14b by a connecting pipe 23 that is horizontally arranged in the width direction of the vehicle body. In addition, the root portion 14 of the upper arm 14
A short angle member 24 is welded to the upper end surface of a, and a stopper 25 composed of a bolt, a nut and the like is attached to the angle member 24. This stopper 2
The upper arm 1 is brought into contact with the head of No. 5 by contacting the second support plate 5.
4 is prevented from rotating counterclockwise beyond the allowable rotation range.

A hinge 27 that rotates about a pin 26 is attached to the link body 13. The hinge 27 is also connected to a load receiving platform (platform) 29 via another pin 28, and is a double hinge having two pivot points. Therefore, the load receiving table 29 can rotate about the pin 28 and also about the pin 26. The receiving tray 29 is a main plate 30.
And the sub-plate 31. The main plate 30 and the sub plate 31 are connected to each other by a hinge 32 which is a double hinge similar to the hinge 27 described above.

FIG. 9 is a view of the load receiving table 29 in the unfolded state (see FIG. 7) viewed from the back surface side (the surface on which the load is placed is the front surface). In FIG. 2 or 9, a pair of “U” -shaped guides 33 are provided on the back surface side of the main plate 30 so that their opening sides face inward and correspond to the slide rails 3 (rear). See also Figure 11 above). The pair of guides 33 engage with the corresponding slide rails 3 to support the load receiving table 29 when the load receiving platform elevating device 1 is stored, and also have a function as a reinforcing member for the main plate 30. Further, a pair of contact plates 34 made of an elastic member (rubber or the like) are provided on the back surface side of the main plate 30.
When the load receiving tray 29 is unfolded, the contact plate 34 comes into contact with the ground to serve as a cushion (see FIGS. 5 and 6) and stabilizes the load receiving tray 29. Similarly, a pair of backing plates 35 are also provided on the back surface of the sub plate 31. In addition, the sub plate 31
49 is attached to one side surface.

Next, in FIG. 4, a switch mounting plate 36 is provided so as to project slightly upward from the upper end surface of the lower arm 9, and a detection switch 37 is mounted on the switch mounting plate 36. Dog 3 to operate the detection switch 37
8 is provided adjacent to the backing plate 35 of the sub plate 31. When the folded load receiving tray 29 is stacked on the upper arm 14 (see FIG. 3), the contact plate 35 contacts the switch mounting plate 36 to serve as a stopper, and the dog 38 operates the detection switch 37.

An angle 39 is horizontally mounted between the left and right slide rails 3 in the width direction of the vehicle body, and a mounting plate 40 is fixed to the center of the angle 39. A hydraulic cylinder (hereinafter referred to as a slide cylinder) as a slide drive mechanism is mounted on the mounting plate 40 via a pin 41.
The tip of the piston rod 42a of 42 is supported.
The cylinder support member 43, which houses the cylinder portion of the slide cylinder 42, is horizontally arranged in the front-rear direction of the vehicle body.
It is welded to the connecting pipe 6 at a position intersecting with the connecting pipe 6.

A lock member 44 having a plurality of holes 44a is attached to the right end portion of the cylinder support member 43. In addition, the triangular guide roller support member 45 is
A pin 46 attached to the right end of the cylinder support member 43
Is rotatable about a vertical plane, and a guide roller 48 is rotatably supported by a pin 47 provided on the right end side. The hole 44a of the lock member 44 is formed on a circumferential orbit drawn with the pin 46 as a center, the hole 45a provided on the left end side of the guide roller support member 45. Therefore, the hole 45a of the guide roller support member 45 is replaced with the arbitrary hole 4a.
The guide roller support member 45 can be attached at a desired attachment angle by bolting together with 4a.

The connecting cylinder 6 slides with respect to the pin 41 when the slide cylinder 42 expands and contracts as the hydraulic pressure is supplied and discharged. Therefore, the connecting pipe 6
All the members directly or indirectly supported by the movable member are movable members. That is, the mounting member 2, the slide rail 3, the angle 39, the mounting plate 40, and the pin 41 are fixed-side members of the load receiving platform elevating / lowering device 1, and include a piston rod 42a that serves to connect with the fixed-side members. The remaining members are movable members. The loading platform elevating device 1 is manufactured separately from the vehicle body, and is mounted as one unit by fixing the mounting member 2 to the chassis 104 of the completed vehicle. Therefore, the mounting is easy.

FIG. 14 is a view of the load receiving platform elevating device 1 folded and stored, as seen from the rear of the vehicle body. Link body 13
Has a rear end face that is substantially vertical and continuous in the vehicle width direction,
It can also be used as a rear bumper. Therefore, it is not necessary to separately provide a rear bumper, and a rear bumper mounting member is also unnecessary. Further, since it is not necessary to provide a rear bumper separately, it is possible to secure a sufficient dimension of the load receiving table 29 in the vehicle front-rear direction. Further, since the link body 13 is a member that is continuous in the vehicle body width direction, the upper arm 14
And, there is an effect of preventing twisting between each pair of left and right in the lower arm 9. If a rear bumper needs to be provided a little higher, a metal plate can be attached to the rear end surface 30a of the main plate 30 above the hinge 27 shown in FIG. 2 to form a rear bumper.

Next, the detailed structure of the folding portion of the cargo receiving table 29 will be described. As shown in FIG. 9, a pair of hinges 32 connecting the main plate 30 and the sub plate 31.
A torsion bar 50 is attached to each.
FIG. 10 is a side view of the connecting portion, which shows the main plate 3
The sub plate 31 is upright with respect to 0. FIG. 11 shows the hinge 3 of the load receiving tray 29 in the folded state.
It is the figure which looked at 2 circumference from the back (for example, the back of Drawing 5).
As shown in FIG. 11, four torsion bars 50 are attached to one hinge 32, and the upper two of the torsion bars 50 are fixed to the sub-plate 31 at one bent end, and the other bent end is a central portion of the hinge 32. It is inserted and fixed slightly above. The lower two are fixed to the main plate 30 at one bent end and the hinge 32 at the other bent end.
It is inserted and fixed slightly below the center of the.

The torsion bar 50 is mounted in the upright state of the sub plate 31 shown in FIG. That is, the torsion bar 50 is free in this state. Therefore, when the sub plate 31 is rotated from this state, the four torsion bars 50 uniformly apply a force to the back surface of the hinge 32. As a result, the hinge 32 always follows the sub plate 31 with the rotation corresponding to half the rotation angle amount of the sub plate 31. For example, in the state shown in FIG. 10, the rotation amount of the sub plate 31 from the folded state or the unfolded state is 90 degrees, whereas the hinge 3
The rotation amount of 2 is 45 degrees.

If the torsion bar 50 as described above is not used, the sub-plate 31 rotates around only one pin of the hinge 32, so that the so-called hinge 32 is bent and a smooth rotation occurs. Movement is disturbed. Therefore, by using the torsion bar 50 in this way, waist bending can be prevented and the side plate 31 can be smoothly rotated. In both the expanded state shown in FIG. 9 and the folded state shown in FIG. 11, the torsion bar 50 is in the maximum twisted state, and the sub-plate 31 is returned to the state shown in FIG. 10 with respect to the main plate 30. Being energized. Therefore, the force required to erect the sub-plate 31 from the folded state or the unfolded state of the load receiving table 29 can be reduced.

Next, the link body 13 and the main plate 30
The detailed structure of the connection portion with and will be described. 12 and 13 are cross-sectional views of the connection portion (the upper arm 14 and the lower arm 9 are shown in phantom lines). In the figure, the torsion spring 51 is provided so as to be wound around the pin 28 of the hinge 27 (see also FIG. 9). One end of the torsion spring 51 is fixed to the main plate 30, and the other end is fixed to the hinge 27. The torsion spring 51 is in a free state in the folded state (the state shown in FIGS. 2 and 3) of the load receiving table 29 in which the main plate 30 is in a positional relationship of 90 degrees with respect to the hinge 27.

When the load receiving table 29 is lifted from the folded state, the main plate 30 is pin 2 of the hinge 27.
There is a possibility of turning around 6 or pin 28. However, while the rotation about the pin 26 is not limited, the rotation about the pin 28 is limited because the load of the torsion spring 51 is received. As a result, the hinge 27 rotates about the pin 26 following the rotation of the main plate 30 until the main plate 30 is lifted to the upright state shown in FIG. Therefore, so-called hinge bending of the hinge does not occur and the main plate 30
Can be smoothly rotated.

When the main plate 30 stands upright, the hinge 27 hits the link body 13 and further rotation is restricted. Therefore, after this, the main plate 30 is pin 2
The torsion spring 51 is rotated around 8 while accumulating energy. In the expanded state of the main plate 30 shown in FIG. 13, the torsion spring 51 is in the maximum twisted state. On the contrary, when the main plate 30 is folded from the unfolded state, the main plate 30 remains in the pin 2 until the upright state.
It rotates about 8 and rotates about the pin 26 from the upright state to the folded state.

Next, the hydraulic system of the loading platform lifting device 1 will be described. FIG. 15 is a hydraulic circuit diagram. The hydraulic circuit includes a pair of lift cylinders 20 and slide cylinders 4.
2, hydraulic pumps 81, 2 driven by a motor 80
It is composed of four electromagnetic valves 82 to 85 which are position valves, a pair of electromagnetic valves 86 which perform the same operation, a reservoir tank 87, a pressure reducing valve 88 and other elements shown in the figure. The elements except the lift cylinder 20 and the slide cylinder 42 are mainly housed in the power unit box 8 (FIG. 1). The operation of the hydraulic circuit is four modes corresponding to the extension (drawing) / contraction (storing) of the slide cylinder 42 and the extension (raising) / contraction (falling) of the lift cylinder 20.

First, when the slide cylinder 42 is extended, the hydraulic pump 81 is driven and all the solenoid valves 82 to 86 are in the non-excited state. As a result, hydraulic pressure is supplied to the piston rod side chamber 42r of the slide cylinder 42, and also hydraulic pressure is supplied to the piston head side chamber 42h via the electromagnetic valve 84. Here, the hydraulic pressure P supplied to the piston rod side chamber 42r and the hydraulic pressure P supplied to the piston head side chamber 42h are equal to each other. However, depending on the presence or absence of the piston rod 42a, the piston pressure receiving area Sr of the piston rod side chamber 42r is smaller than the piston pressure receiving area Sh of the piston head side chamber 42h. Therefore, the driving force applied to both sides of the piston head is P ・ (S
(h-Sr) difference is generated, and this becomes the driving force for the piston rod 42a in the extension direction.

Further, by receiving the driving force based on the pressure receiving area difference as described above, even when excessive resistance is applied to the extension of the slide cylinder 42, an excessive compression force is applied to the piston rod 42a. Never join. Therefore, buckling of the piston rod 42a can be reliably prevented. Since the solenoid valve 83 is in the non-excited state, hydraulic pressure is not supplied to the lift cylinder 20 due to the internal check valve.

When the slide cylinder 42 is contracted, the hydraulic pump is driven and only the solenoid valves 84 and 85 are excited. Therefore, the hydraulic pressure is supplied only to the piston rod side chamber 42r, and the oil liquid in the piston head side chamber 42h is stored in the reservoir tank 87 via the electromagnetic valve 85 in the communicating state.
Returned to. As a result, the piston rod 42a receives the driving force in the returning direction and the slide cylinder 42 contracts.
The driving force in this case is approximately represented by P · Sr. Usually Sr
Is about 1/2 of Sh, so this driving force P · Sr is almost equal to the driving force P · (Sh−Sr) at the time of extension. Therefore, the speed at the time of extension and the speed at the time of contraction are substantially the same. As described above, according to the configuration in which the slide cylinder 42 is expanded and contracted by utilizing the pressure receiving area difference, the two solenoid valves 84 and 85 necessary for the operation are both 2-position valves, so that an expensive 3-position valve is used. It is economical because there is no need to use it.

On the other hand, when the lift cylinder 20 is extended after the extension operation of the slide cylinder 42, the hydraulic pump 81 is driven and only the solenoid valve 83 is excited. By exciting the solenoid valve 83, hydraulic pressure is supplied to the lift cylinder 20 via the solenoid valves 83 and 86, and the lift cylinder 20 extends. At this time, the hydraulic pressure is continuously supplied to the slide cylinder 42. on the other hand,
Even if the hydraulic pump 81 is stopped after the lift cylinder 20 is extended, the check valve action of the solenoid valve 86 causes the lift cylinder 2 to move.
The oil in 0 does not return. Therefore, the lift cylinder 20
Are held in the extended state. In addition, the lift cylinder 20
, The hydraulic pump 81 is stopped and only the solenoid valves 82 and 86 are excited. Therefore, the oil liquid in the lift cylinder 20 moves from the solenoid valve 86 in the communicating state to the solenoid valve 8
3 through the solenoid valve 82 in the communication state and then returned to the reservoir tank 87.

Next, the slide lock device will be described. Although not shown in FIGS. 1 to 7 for simplification of the drawings, a slide lock device 60 shown in FIG. 16 is provided near the connecting pipe 6. 17 (a)
6C and 6C are horizontal cross-sectional views of the main part of the slide lock device 60, and FIG. 9B is a vertical cross-sectional view. 16 and 17, the lock rod 61 penetrates through the second support plate 5 and is attached to the second support plate 5 by the attachment plate 62 so as to be rotatable about its axis. An engagement pin 64 is attached to the tip end side of the lock rod 61 via a compression spring 63 so as to be movable in the axial direction. The tip of the engagement pin 64 is tapered, and the tip including the taper portion 64a is stored in the storage position hole 3b provided in the slide rail 3 (see FIG.
4) and pull-out position hole 3a (see FIGS. 16 and 1,
(See FIG. 2). The pull-out position holes 3a are provided at a plurality of positions so that the pull-out position can be adjusted according to the rear overhang (the distance from the center of the rear wheel to the rear surface of the vehicle body). A lock slide pad 68 having tapered portions 68a at both ends is attached between the storage position hole 3b and the pull-out position hole 3a.

A side pad 69, which is a sliding member, is attached to the first support plate 4 facing the slide rail 3 (see FIGS. 16 and 17 (b)). The side pad 69 serves as a stopper 3 provided on the slide rail 3.
The position corresponding to c (FIG. 16) is the pull-out position. Figure 1
When the side pad 69 attached at the position shown in 6 hits the stopper 3c, the engagement pin 64 engages with the rightmost pull-out position hole 3a in the figure. The mounting position of the side pad 69 can be shifted to the right from the position shown in the figure. By shifting the mounting position of the side pad 69 according to the rear overhang, the central pull-out position hole 3a or the leftmost position. The engagement pin 64 can be engaged with the pull-out position hole 3a.

A handle 66 is attached to the lock bar 61 via a connecting handle 65. The rotation range of the lock bar 61 and the handle 66 is 180 degrees.
17 and the solid line portions of FIGS. 17A and 17B show the state in which the handle 66 is lowered right below. One end of the tension spring 67 is locked to a part of the handle 66, and the other end is attached to the attachment plate 62. Therefore, in order to rotate the handle 66 located right below, the handle 66 is rotated counterclockwise against the tension spring 67. When the handle 66 is rotated in this manner, it is biased by the tension spring 67 again and the handle 66 is held at the position immediately above (the two-dot chain line portion in FIG. 16 and the two-dot chain line portion in FIG. See c)). Handle 66
When is right above, the direction of the tapered portion 64a of the engaging pin 64 is opposite to that of (a) as shown in FIG. 17C (the lower side of the drawing is the tapered portion).

When the taper portion 64a is oriented as shown in FIG. 17A, when the first support plate 4 and the second support plate 5 slide in the direction of the arrow, the presence of the taper portion 64a causes the engagement pin 64a to move. 64 can be pulled out from the slide rail 3. On the contrary, even if the first support plate 4 and the second support plate 5 try to move in the direction opposite to the arrow direction, the engagement pin 64 cannot be pulled out from the slide rail 3 and therefore cannot be moved. On the other hand, the tapered portion 64a
Is in the direction shown in FIG. 17 (c), the first support plate 4
When the second support plate 5 and the second support plate 5 slide in the arrow direction, the engagement pin 64 can be pulled out from the slide rail 3 due to the presence of the tapered portion 64a. On the contrary, even if the first support plate 4 and the second support plate 5 try to move in the direction opposite to the arrow direction, the engagement pin 64 cannot be pulled out from the slide rail 3 and therefore cannot be moved. Therefore, the handle 66 is operated depending on whether the sliding operation is the storage direction or the withdrawal direction, and the taper portion 64a is oriented in the storage direction during storage. Further, when pulling out, the taper portion 64a is oriented in the pulling direction.

When the slide operation is started after the handle 66 is set to the pull-out position or the storage position, the slide lock device 60 starts to slide together with the second support plate 5 and the like, and the taper portion 64a of the engagement pin 64 is pressed. It As a result, the engagement pin 64 pushes the compression spring 63 and removes the pull-out position hole 3a or the storage position hole 3b, thereby enabling the slide lock device 60 to move. Engagement pin 6
4 further slides on the lock slide pad 68.

In the case of sliding in the storage direction, the engagement pin 64 engages with the storage position hole 3b at the end of the contraction operation of the slide cylinder 42 (FIGS. 1 to 7). Once engaged,
Unless the tapered portion 64a is oriented in the pull-out direction, the engaging pin 64 does not come out naturally. Therefore, it is possible to prevent the movable side member of the load receiving platform elevating device 1 from being pulled out by vibration while the vehicle is traveling. On the other hand, in the case of sliding in the pull-out direction, the side pad 69 comes into contact with the stopper 3c to stop the sliding operation, and the engagement pin 6
4 is engaged with the corresponding pull-out position hole 3a. Once engaged, the engagement pin 64 will not come out naturally unless the tapered portion 64a is oriented in the storage direction. Therefore, when loading and unloading the vehicle body in a front-down direction on a slope, it is possible to avoid the risk of falling of the luggage due to the movable member pulled out moving in the storage direction due to gravity.

Next, the lashing device for the loading tray 29 will be described. The loading tray 29 is provided with a lashing device for holding the folded state. FIG. 18 shows the receiving stand 2
9 is a diagram showing only the portion 9 in which a male side engaging portion 70 is attached to the main plate 30 and a female side engaged portion 73 is attached to the sub plate 31. FIG. Receiving stand 29
In the state before () is folded ((a) in the figure), the engaging portion 70 slightly projects from the upper surface of the main plate 30. In the state where the sub plate 31 is folded ((b) in the figure), the engaging portion 70 and the engaged portion 73 are engaged and held with each other, and the sub plate 31 becomes the main plate 3
It is held at 0.

FIG. 19 is a sectional view showing the details of the fastening device. In the figure, the engaging portion 70 includes a mounting seat 71 and a mushroom-shaped pin 72 at the tip. The engaged portion 73 on the female side includes a housing 74, an engaging piece 75 with the pin 72, a compression spring 76, one spring bearing 77, and the other spring bearing 7.
8 and a push button 79 (see also FIG. 9) integrally attached to the spring receiver 78. Engaging piece 75
Is composed of a combination of three split members, and the upper and lower ends of the engagement piece 75 housed in the housing 74 are naturally inwardly recessed. In the state of FIG. 19,
The lower end portion of the engagement piece 75 is pushed open by the spring receiver 77, and the opening 75a has a size capable of receiving the pin 72. Further, the upper end side of the engagement piece 75 is recessed inward. The shape of the engagement piece 75 at this time as viewed from the bottom surface on the engagement side with the pin 72 is shown in FIG.

When the pin 72 is relatively pushed into the engaged portion 73 by folding the sub plate 31 on the main plate 30, the spring receiver 77 is pushed up by the pin 72. Further, as shown in FIG. 20, the pin 72 pushes up the spring bearing 78 via the compression spring 76, so the upper side of the spring bearing 78 is pushed out from the housing 74, and the push button 79 projects. As a result, the engagement piece 75 is pushed open in such a manner that the upper end portion of the engagement piece 75 is externally inserted in the large diameter portion of the spring receiver 78. On the other hand, the lower end portion of the engagement piece 75 is released from the push-opening by the spring receiver 77 and is in a recessed state (see FIG. 21 (b)). As a result, the head of the pin 72 is held in a state of being engaged with the engaging piece 75. Further, the pin 72 is stably held by receiving the bias of the compression spring 76.
Therefore, the sub-plate 31 is fixed to the main plate 30 and is in a state in which it does not come off naturally.

To release the above-mentioned engagement (locking), the push button 79 is pushed. When the push button 79 is pressed,
The engagement piece 75 is disengaged from the large diameter portion of the spring receiver 78, and the state in which the engagement piece 75 is pushed open is released. As a result, the upper end of the engagement piece 75 is recessed inward. Therefore, it becomes easy to spread at the lower end. Further, the pressing force of the push button 79 pushes the spring bearing 77 downward via the compression spring 76, and the engaging piece 7
The lower end of 5 is pushed open to enlarge the opening 75a. In this state, if the sub-plate 31 is lifted while the push button 79 is being pushed, the pin 72 will come out of the engagement piece 75 and the secured state will be released.

Next, the lifting mechanism of the load receiving table 29 will be described in detail. FIG. 8 is a side view showing only the main parts involved in the lifting operation, and the reference numerals of the respective parts are common to those in FIGS. In FIG. 8, (a) shows a state in which the load receiving table 29 is raised so as to be flush with the floor surface of the cargo box of the vehicle body,
(B) shows a state in which the load receiving table 29 is horizontal on the ground, and (c) shows a state in which the load receiving table 29 is inclined on the ground. Here, the pin 18 is a rotation fulcrum of the auxiliary link 16 and a fixed point in the movable member. On the other hand, the pins 15 and 21 are movable points that move according to the rotation of the auxiliary link 16. The pin 10 is a fixed point that is fixed regardless of the auxiliary link 16. Other pins 12, 1
7, 22 and 28 move according to the raising / lowering operation.

First, the ascending operation from the state (c) to the state (a) will be described. In (c), the lift cylinder 20 is in a contracted state, and the auxiliary link 16 is shown in (b).
Assuming that the state shown in (1) is vertical, it is in a free state in which it is rotated slightly counterclockwise. When the lifting operation is performed from this state and the lift cylinder 20 begins to extend, the auxiliary link 16 slightly rotates in the clockwise direction via the pin 21. By this rotation, the pin 15 also slightly rotates in the same direction. Therefore, the pin 17 is slightly pulled to the left side of the drawing via the upper arm 14. On the other hand, since the pin 10 is a fixed point, the pin 12 is also stationary and fixed at this point. Therefore, the link body 13 and the load receiving base 29 are rotated counterclockwise with the pin 12 as a fulcrum, and the upper surface 13a of the link body 13 and the load receiving base 29 are horizontal as shown in (b). At this time, the position of each pin is designed so as not to rotate further than horizontal, and the stopper 1
9 (see FIG. 7) is adjusted.

The above-described tilting operation of the loading tray 29 (from tilting to horizontal or vice versa) is performed below the point A when the pin 18 is at the point A, the pin 15 is at the point B, and the pin 21 is at the point C. To B
There is a point, and further, there is a point C below the point B, which is a positional relationship. Further, the distance AC is larger than the distance AB. Accordingly, the rotation distance of the point B with respect to the stroke amount of the lift cylinder 20 is
It becomes almost AB / AC, and the tilt operation becomes slower than the operation of the lift cylinder 20. In addition, pin 17 is point D,
When the pin 12 is the point E, the angle at which the line segment AB and the line segment BD intersect is slightly larger than 90 degrees in the state of (c),
In the state of (b), it is slightly smaller than 90 degrees. That is,
In the state change from (c) to (b), the angle is 9
It changes before and after 0 degree. This brings about the effect that the rotational speeds of the points B and D are almost constant from the start to the end of the rotation. For example, when loading luggage on the receiving tray 29,
If the tilting operation is accelerated or decelerated from the state (c) to the state (b), a situation may occur in which the luggage swings or falls with excessive force. According to the operation, there is no such fear.

When the auxiliary link 16 reaches the state shown in (b), the stopper 19 comes into contact with the second support plate 5 and the auxiliary link 16 cannot rotate any more. Where pin 1
When 0 is the F point, between the points B, D and E,
The line segment BF and the line segment DE are parallel to each other, and the line segment BD and the line segment FE are parallel to each other. That is, the quadrangle BDEF is a parallelogram, and the upper arm 14
The lower arm 9 and the lower arm 9 constitute a parallel link with the points B and F as pivotal fulcrums and the points D and E as points of action. This parallel relationship is then maintained up to the raised position. Therefore, the upper surface 13a of the link body 13 and the load receiving table 29 maintain the horizontal state.

When the lift cylinder 20 is further extended from the state of (b), the driving force is applied to the pin 22 in the parallelogram with the pin 21 located below the parallelogram as a fulcrum, so that the parallel link is performed. Rotates counterclockwise around points B and F, and the cradle 29 rises. When the floor surface of the luggage box, the upper surface 13a of the link body 13, and the cargo receiving table 29 are flush with each other, the stopper 25 (see FIG. 7) comes into contact with the second support plate 5 to stop the rotation of the upper arm 14. Then
The ascending of the receiving tray 29 stops. After stopping the rise, the hydraulic pressure generated by the hydraulic pump 81 rises, but this hydraulic pressure is released by the pressure reducing valve 88 (see FIG. 15).

It is also possible to stop the rise of the load receiving table 29 by applying the link body 13, the upper arm 14, etc. to a part of the load box 102. However, the packing box 102 is generally made of aluminum, and the link body 13 and the upper arm 14 are
Is an iron-based metal such as iron or stainless steel, and therefore, if the iron-based metal having a hardness higher than that of aluminum is applied to the load box 102 to stop the rise of the load receiving table 29, the load box 102 is damaged. Therefore, it is troublesome because it is necessary to provide additional reinforcement to the contact portion of the luggage box 102. In that respect, the configuration in which the stopper 25 is applied to the second support plate 5 as described above is simple and sturdy.

Next, the descending operation from the state (a) to the state (c) will be described. In the state of (a),
When the lowering operation is performed and the lift cylinder 20 begins to contract, the operation reverse to that at the time of raising is performed, and the state shown in (b) is reached. Here, the tip of the lower link 9 lands and stops rotating.
At this time, the total weight of the link body 13, the load receiving table 29, and the load placed on the link body 13 acts as a force in the direction of rotating the pin 17 in the clockwise direction around the pin 12. Here, when the lift cylinder 20 further contracts,
The auxiliary link 16 slightly rotates about the pin 18 in the counterclockwise direction. As a result, the pin 15 rotates counterclockwise around the pin 18. By the rotation of the pin 15, the pin 17 rotates in the clockwise direction around the pin 12, and the load receiving table 29 tilts so as to lower its tip. Similar to the case of ascending, the tilting motion is about AB / AC turning distance with respect to the contraction of the lift cylinder 20,
And, it is performed at almost constant speed. Therefore, the loading platform 29 slowly inclines at a substantially constant speed. Therefore, the situation in which the luggage swings or falls too fast does not occur.

Next, a series of operations and operations (storage / drawing and raising / lowering) in the load receiving platform elevating / lowering device 1 configured as described above will be described with reference to FIGS. First, after stopping the vehicle and pulling the parking brake, the occupant gets off the vehicle and sets the handle 66 (FIGS. 16 and 17) to the "drawer". Next, switch box 7 (Fig. 1)
The key switch S1 provided at is turned from "OFF" to "ON", and further turned to the "ST" position where the slide operation is performed and held. As a result, the slide cylinder 42 extends and the movable-side member of the load receiving platform elevating / lowering device 1 slides to the right in the figure (FIG. 3). By this slide, the switch box 7 also moves to the right together, so that the operator follows the gait. It is rather preferable that the operator walks in this manner from the viewpoint of operability and safety such as backward confirmation. When the side pad 69 attached to the first support plate 4 comes into contact with the stopper 3c (see FIG. 16), the slide stops, and at the same time, the slide lock device 6
Since the engagement pin 64 of 0 engages with the corresponding hole 3a, it is in a locked state with respect to both directions of withdrawal and storage.

Next, the operator operates the elevating switch S2 provided on the switch box 7 to "fall".
As a result, the lift cylinder 20 begins to contract, and the upper arm 14 and the lower arm 9 rotate clockwise. Figure 4
As shown in, since the rotation is stopped when the lower arm 9 lands on the ground, the lowering operation is stopped. Along with this operation, the load receiving table 29 is relatively pushed by the guide rollers 48 to be separated from the link body 13, and is in a slightly erected state so as not to be vertical.

Next, the operator grasps 49 (FIG. 9) and manually raises and further rotates the load receiving tray 29 to lay it down on the ground (FIG. 5). As a result, the main plate 30 of the load receiving table 29 is in a fully expanded state with respect to the link body 13. Since the load receiving table 29 is slightly raised in advance as described above when the load receiving table 29 is tilted down, the load of the force required by the operator is small. Subsequently, the operator pushes the push button 79 (FIG. 19) to release the securing state of the load receiving table 29 and opens the sub plate 31 (FIG. 6).
In this way, when the load receiving table 29 is unfolded, a load receiving surface of a predetermined size that is linear and continuous from the upper surface 13a of the link body 13 is formed, and a state in which a load can be placed is ready. Here, the backing plates 34 and 35 serve as a cushion between the ground and the load receiving tray 29, and stabilize the load receiving tray 29.

When the load is completely loaded on the load receiving tray 29, the user operates the lift. As a result, the above-described tilting operation is first performed, and the link body 13 and the load receiving table 29 are horizontal (see FIG. 7).
Is indicated by a two-dot chain line. ). Further, when the lift cylinder 20 extends, the link body 13 and the load receiving table 29 are kept horizontal and rise to a height corresponding to the floor surface of the load box 102 (FIG. 7). Here, the operator transfers the luggage to the luggage box 102. When the luggage is unloaded from the luggage box 102, the above operation is performed in the reverse order from the state of FIG. 7 to the state of FIG.

FIG. 6 shows the case where the loading platform raising / lowering device 1 is stored.
After the state shown in FIG. 5, the operator takes 49 (FIG. 9) and folds the sub-plate 31. Upon folding, the sub-plate 31 is automatically secured and remains folded (FIG. 5) unless the push button 79 (FIG. 20) is pressed. Next, the operator lifts the folded load receiving tray 29 and leans it against the guide roller 48 (FIG. 4). As a result, the cargo receiving table 29 as a whole has the link body 1
It is folded to some extent with respect to 3. That is, the load receiving surface which is a flat surface continuous from the link body 13 is in a folded state even at the connection portion between the link body 13 and the load receiving base 29. In addition, the loading tray 29 in the state shown in FIG.
The force required to lift the
It is assisted by (Figs. 12 and 13) and becomes slightly lighter than the actual weight. Therefore, it is possible to easily stand up with a force of holding 49 with one hand.

When the state shown in FIG. 5 is changed to the state shown in FIG. 4 as described above, the load receiving base 29 includes the hinge 27 and the load receiving base 29.
And are rotated about the pin 28 until they are in a positional relationship of about 90 degrees with respect to each other, and then about the pin 26. The pin 26 is in a position separate from the pin 17 and the pin 12, which are the working points of the parallel link. Therefore, the rotating load carrier 2
The turning radius when 9 comes closest to the rear part of the vehicle body 102 and reaches the state of FIG. 4 does not include the depth of the upper surface 13a of the link body 13 (the length in the vehicle front-rear direction), and the pin 26 extends from the load receiving base. It is the length up to the turning tip of 29. This allows
The turning radius is compact, and the turning tip of the load receiving table 29 does not interfere with the vehicle body 101. Here, to supplement the degree of compactness, it is assumed that the load receiving base 29 shown in FIG. 5 is integrated with a member similar to the link body 13 around the pin 17 which is an action point of the parallel link (foldable). If it rotates (without), the radius of rotation becomes extremely large, and the difference from the above configuration is obvious.

Next, the handle 66 of the slide lock device 60 is operated to set it to "stored". Then, while the key switch S1 is kept "ON", the ascending operation is performed. As a result, the upper arm 14 and the lower arm 9 rotate in the counterclockwise direction, and the load receiving table 29 tilts in the counterclockwise direction while rollingly contacting the guide roller 48. Falling cradle 2
The contact plate 35 of 9 is a switch mounting plate 36 as a stopper.
When it comes into contact with, the detection switch 37 is activated by the dog 38 (FIG. 3). When the detection switch 37 is actuated, the lift is stopped, and the lift cylinder 20 moves to the solenoid valve 86 (see FIG.
By the non-return action of 5), the oil liquid supply state at that time is maintained. Subsequently, the retracting operation of the slide cylinder 42 is automatically performed.

When the slide cylinder 42 reaches the contracted end and the movable member of the load receiving platform elevating device 1 reaches the predetermined storage position, the engagement pin 64 (FIG. 17) is moved to the storage position hole 3b.
The movable member is automatically locked by engaging (FIG. 3). Further, the guide 33 provided on the load receiving table 29 engages with the slide rail 3. Thus, the storage of the load receiving platform elevating / lowering device 1 is completed and the vehicle is ready to travel. The engagement of the engagement pin 64 prevents the situation where the load receiving platform elevating device 1 is unintentionally pulled out even with vibration during traveling. Also,
Even if there is an oil leak in the lift cylinder 20 due to the engagement between the guide 33 and the slide rail 3, the load carrier 2
There is no possibility that movable members such as 9 and the arms 9 and 14 will descend. Further, since the contact plate 35 made of an elastic body is in contact with the switch mounting plate 36 attached to the lower arm 9, the load receiving platform 29 is stably supported by the lower arm 9 and the load receiving platform 29 in the storage position. Rattling is prevented.

Next, the position adjustment of the guide roller 48 will be described with reference to FIGS. Guide roller 4
As described above, the position of 8 is the same as the position of the guide roller support member 45.
It is possible to adjust by rotating.
FIG. 22 shows a vehicle height H1 higher than the vehicle height H0 of the vehicle shown in FIG.
It shows the case of a vehicle having. In this case, the hole 45a of the guide roller support member 45 is fixed to the lock member 44 by shifting in the clockwise direction from the position shown in FIG. As a result, the guide roller 48 rotates in the clockwise direction around the pin 46, and is below the case of FIG. 4 and on the left side (front side).
Move to. As a result, the inclination erection angle of the load receiving table 29 leaning against the guide roller 48 with respect to the ground becomes almost the same as in the case of FIG. That is, the guide roller 4
By adjusting the position of 8, it is possible to maintain the tilted standing postures of the load receiving table 29 substantially the same regardless of the vehicle height. Therefore, regardless of the vehicle height, it is possible to make the force required to fall the load receiving table 29 from the inclined standing state substantially constant, and the work is easy. On the contrary, even when the loading tray 29 is erected and leans against the guide roller 48, it can be leaned stably regardless of the vehicle height. By rotating the guide roller 48 as described above, position adjustment in both the horizontal direction and the vertical direction is performed at the same time. If the inclination standing angle is maintained only by adjusting the horizontal direction, the tip end of the load receiving table 29 may interfere with the rear part of the vehicle body 101 during the operation of retracting the load receiving table 29 from the state shown in the figure. It is preferable to perform the vertical adjustment simultaneously.

In the above embodiment, the load receiving platform elevating / lowering device 1 is described as being pulled out to the rear of the vehicle body 101, but the same can be applied to a configuration in which it is pulled out to the side.

[0059]

The present invention constructed as described above has the following effects. According to the loading platform elevating / lowering device of claim 1, in the retracted position or the retracted position which is the slide end
The engaging pin fits in the hole and the sliding operation in the opposite direction is automatically locked, and the unlocking requires an action of operating the operating portion, which is not naturally released. Therefore, the sliding operation is not performed unintentionally from the storage position or the withdrawal position, and the safety is improved.

According to the loading platform raising / lowering device of the second aspect, since the slide lock position can be adjusted, the slide lock can be performed at the position suitable for the rear overhang of the vehicle body.

[Brief description of drawings]

FIG. 1 is a side view of a loading platform lifting device according to an embodiment of the present invention.

FIG. 2 is a side view in which a part of FIG. 1 is omitted.

FIG. 3 is a side view showing the load receiving platform elevating device in a state of being pulled out rearward.

FIG. 4 is a side view showing the load receiving platform elevating device in a state where the tip of the lower arm lands and the load receiving platform leans against a guide roller and stands up.

FIG. 5 is a side view showing the load receiving platform elevating device in a state where the tip of the lower arm lands and the load receiving platform is lying down in a folded state.

FIG. 6 is a side view showing the load receiving platform elevating device in a state where the load receiving platform is completely deployed and is along the ground.

FIG. 7 is a side view showing an elevating operation of the load receiving platform elevating device.

FIG. 8 is a diagram showing in detail an elevating operation of the load receiving platform elevating device.

FIG. 9 is a bottom view of the unfolded cargo cradle in the cargo cradle lifting device.

FIG. 10 is a side view showing a hinge portion of the load receiving platform in the load receiving platform lifting device.

FIG. 11 is a view of the hinge portion of the folded load carrier in the load carrier lifting device as viewed from the rear side of the vehicle.

FIG. 12 is a cross-sectional view showing a hinge structure of a base portion of the load carrier in the load carrier lifting device, showing a standing state of the load carrier.

FIG. 13 is a cross-sectional view showing a hinge structure of a base portion of the load carrier in the load carrier lifting device, showing a collapsed state of the load carrier.

FIG. 14 is a view of a part of the load receiving platform elevating device seen from the rear of the vehicle.

FIG. 15 is a hydraulic system diagram of the load receiving platform lifting device.

FIG. 16 is a side view showing a slide lock device of the load receiving platform elevating device.

FIG. 17 is a horizontal sectional view and a vertical sectional view of the slide lock device.

FIG. 18 is a side view showing a lashing structure of the load receiving table in the load receiving table lifting device.

FIG. 19 is a cross-sectional view showing details of the securing structure, showing a state before securing.

FIG. 20 is a cross-sectional view showing details of the securing structure, showing a state after securing.

FIG. 21 is a bottom view showing an engagement piece in the securing structure.

FIG. 22 is a side view similar to FIG. 4, showing a state in which the position of the guide roller is adjusted according to the vehicle height.

FIG. 23 is a side view showing a schematic structure of a conventional load receiving platform elevating device.

FIG. 24 is a side view showing a state before storage in the conventional load receiving platform lifting device.

[Explanation of symbols]

1 Lifting device 2 Mounting member 3 slide rails 3a Draw-out position hole 3b Storage position hole 4 First support plate 5 Second support plate 6 connecting pipes 9 Lower arm 14 Upper arm 20 lift cylinder 29 Receiving platform 42 slide cylinder 60 Slide lock device 61 Rock Stick 63 compression spring 64 engagement pin 64a taper part 66 handle 102 car body 104 chassis

─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) B60P 1/44

Claims (2)

(57) [Claims] 1. A fixed-side member attached to a vehicle body, a support base supported slidably in the horizontal direction by the fixed-side member, a slide drive mechanism for sliding the support base to a predetermined position, and the support base. Supported by the two arms constituting a parallel link for raising and lowering, a raising and lowering drive mechanism for driving the arms, and a loading and unloading platform that is rotatably connected to a tip side of the arms. In the device, the fixed-side member includes a slide rail having holes corresponding to a retracted position and a retracted position, and is supported by the support base so as to be movable in a direction intersecting with the slide rail, and has one end thereof. An engaging pin having a tapered portion, and a tip portion including the tapered portion can be inserted into and removed from the hole; and an elastic member that urges the engaging pin toward the slide rail. Member and is connected to the engaging pin, receiving platform lifting apparatus comprising the slide lock device and an operating unit for changing the orientation of the tapered portion. 2. The load receiving platform elevating device according to claim 1, wherein a plurality of the holes corresponding to the pull-out positions are provided in the sliding direction.