JP3409847B2 - 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. 24 shows, for example, Japanese Patent Laid-Open No. 8-15086.
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 a load is placed (shown by a two-dot chain line on the right side) and folded (folded) when stored. Shown with 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 210 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.

[0003]

SUMMARY OF THE INVENTION In the conventional loading platform lifting device as described above, the loading platform 20 is centered around the pin 210.
6 (see the chain double-dashed line portion), the rotating end portion of the load receiving base 206 is moved to the vehicle body 201 due to a difference in vehicle height or the like.
There was a case where it could not be stored because it hit the rear part of the. Therefore, in order to avoid interference with the vehicle body 201, the cargo receiving table 206
I had no choice but to limit the depth (front-back direction) of the car. Therefore, a large baggage cannot be loaded, and the loading tray 2
There was a problem that the work space on 06 was small.
In view of the above-mentioned conventional problems, an object of the present invention is to provide a load receiving platform elevating device that prevents a load receiving platform from interfering with a vehicle body while securing a load receiving surface of a predetermined size. Another object of the present invention is to provide a load receiving platform elevating / lowering device that can be stored compactly while securing a load receiving surface of a predetermined size.

[0004]

SUMMARY OF THE INVENTION A cargo platform raising / lowering device of the present invention comprises a support base supported by a vehicle body, an arm supported by the support base to form a parallel link for raising and lowering the arm. Lifting drive mechanism, a link body that is connected to the tip side of the arm and forms a part of the load receiving surface, a main plate that is rotatably connected to the link body, and a main plate that rotates to the tip side of the main plate. A sub-plate that is movably connected to the main plate and is foldable. The sub-plate is foldable to the link body as a whole in a folded state, and constitutes a load receiving surface together with the link body when unfolded. and the receiving platform which,
Having a fulcrum of rotation for the link body at one end side
Has a rotation fulcrum at the other end for rotating the load receiving base.
A hinge, and in a state in which the main plate and the sub plate are folded with respect to the link body via the hinge, a tip portion of the sub plate is between a base portion of the main plate and an upper surface of the link body. It is introduced into the gap formed in (1) (claim 1).

In the load receiving platform elevating device thus constructed, the load receiving surface is constituted by the link body, the main plate and the sub plate, and a predetermined size is secured.
Since the load receiving tray with the sub-plate folded can be folded with respect to the link body, the turning radius at the time of folding does not include the dimension corresponding to the link body. Therefore,
The turning radius becomes smaller accordingly. The front end of the sub-plate is formed between the base of the main plate and the upper surface of the link body in a state where the main plate and the sub-plate are folded with respect to the link body via a hinge. Opportunity
Since it introduced between, or can reduce the overall length of the longer or the full length of the sub-plate so as to correspond to its introduction length, or the main plate.

[0006] In the load receiving platform elevating device, an elastic member for restricting vertical movement of the main plate and the sub plate is arranged between the main plate and the link body in a state of being folded with respect to the link body. It is preferable that it is (claim 2). In this case, the elastic member can regulate the vertical movement of the sub plate while the vehicle is traveling.

[0007]

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 described later (FIG. 16 and FIG. 17 (b))).
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.

A switch box 7 containing the operation switches, control circuit, etc. of the load receiving platform elevating 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. The pair of left and right substantially linear lower arms 9 are each rotatable within a predetermined range around a pin 10 provided at the left end in FIG.
Is attached to a support portion 11 fixed to the connecting pipe 6. 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 within a predetermined range around a pin 15 provided at the left end, 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. A predetermined gap is formed between the base portion of the main plate 30 and the upper surface 13a of the link body 13 in the state where the load receiving table 29 is stored (see FIG. 1).
The tip of the sub plate 31 is introduced into this gap. Therefore, the depth (length in the vehicle front-rear direction) of the sub-plate 31 is increased by the length corresponding to the amount of introduction of the tip portion.

FIG. 9 is a view of the load receiving table 29 in the unfolded state (see FIG. 7) viewed from the back side (the surface on which the load is placed is the front side). 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 vehicle width direction, 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 as 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 / lowering 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 (entry prevention device). 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. Furthermore, since the link body 13 is a member that is continuous in the vehicle body width direction, it has the effect of preventing twisting between the left and right pairs of the upper arm 14 and 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 load receiving platform elevating device 1 will be described. FIG. 15 is a hydraulic circuit diagram. The hydraulic circuit includes a pair of left and right lift cylinders 20, a slide cylinder 42, a hydraulic pump 81 driven by a motor 80,
Four solenoid valves 82 to 85 that are two-position valves, a pair of solenoid valves 86 that perform the same operation, a reservoir tank 87, and a pressure reducing valve 88.
Other components are shown. 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 if 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)
[Fig. 3] is a horizontal sectional view of a main part of the slide lock device 60, and (b) is a vertical 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 tapered portion 64a is provided in the slide rail 3 in a storage position hole 3b (see FIGS. 3 and 4) and a pull-out position hole 3a (see FIGS. 16 and 16). (See FIGS. 1 and 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 17 show a 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 rotated like this,
The handle 66 is held in the position directly above by being biased by the tension spring 67 again. When the handle 66 is right above, the direction of the taper portion 64a of the engaging pin 64 is opposite to that of FIG. 17A (the lower side of the drawing is the taper portion). Therefore, the handle 66 is operated depending on whether the sliding operation is the storing direction or the pulling direction.
Turn to. 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 receiving table 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 engagement (fixing), 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 elevating mechanism of the loading tray 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.

When the pin 18 is set to the point A, the pin 15 is set to the point B, and the pin 21 is set to the point C, the tilting operation of the load receiving table 29 (an operation from the tilt to the horizontal or vice versa) is below the point A. 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 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 raising / 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 "down".
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.

Then, 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 deployed, a linearly continuous load receiving surface is formed from the upper surface 13a of the link body 13, and the load can be placed. Here, the backing plates 34 and 35
Serves as a cushion between the ground and the cradle 29, and stabilizes the cradle 29. Further, since the load receiving surface in the unfolded state is constituted not only by the main plate 30 and the sub plate 31 but also by the upper surface 13a of the link body 13, a sufficient size can be secured.

When the load is completely loaded on the load receiving table 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.

When the loading platform raising / lowering device 1 is to be stored, the configuration shown in FIG.
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 contraction 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 in the vertical direction is suppressed.

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.

As shown in FIG. 23, the sub-plate 31 may have its tip end portion sandwiched by elastic members 91 and 92 such as rubber in a state where the load receiving table 29 is stored. In this case, for example, the elastic member 91 is attached to the lower surface of the tip portion of the sub-plate 31, and the elastic member 92 is attached to the lower surface of the main plate 30 on the base side, and the former elastic member 91 is attached to the upper surfaces of the sub-plate 31 and the link body 13. 13a and the latter elastic member 92 may be interposed between the sub-plate 31 and the main plate 30 without any gap, thereby more reliably preventing the sub-plate 31 from rattling in the vertical direction. can do.
However, when the tip end portion of the sub plate 31 is directly placed on the upper surface 13a of the link body 13, the lower elastic member 92 can be omitted.

In the above embodiment, the total length of the sub plate 31 is increased by the length of the sub plate 31 introduced into the gap between the main plate 30 and the link body 13. Alternatively, the total length of the main plate 30 may be shortened by the length introduced, and in this case, the load receiving table 29 can be made compact while ensuring a load receiving surface of a predetermined size. Further, in the above-described embodiment, the load receiving platform elevating / lowering device 1 has been described as being pulled out to the rear of the vehicle body 101, but it can be similarly applied to a configuration in which it is pulled out to the side.

[0058]

The present invention constructed as described above has the following effects. According to the load-bearing platform lifting device of claim 1, the load-bearing surface of a predetermined size is configured by the link body, the main plate, and the sub-plate, and the load-bearing platform in which the sub-plate is folded with respect to the link body. Since it can be folded, the turning radius at the time of folding does not include the dimension corresponding to the link body, and the turning radius becomes smaller accordingly. Therefore, it is possible to prevent interference with the vehicle body of the load receiving base while ensuring a predetermined size of the load receiving surface. Also Hin
Link the main plate and sub-plate via the
The front end of the sub-plate is formed between the base of the main plate and the upper surface of the link body in the folded state.
Since it is introduced into the gap, the total length of the sub-plate can be lengthened or the total length of the main plate can be shortened according to the length of the introduction. Therefore, in the former case, the load receiving surface can be further effectively enlarged, and in the latter case, the load receiving surface can be compactly stored while ensuring a predetermined size of the load receiving surface.

According to the loading platform raising / lowering device of the second aspect,
The elastic member can prevent the sub-plate from rattling up and down while the vehicle is traveling.

[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 of a main part showing another embodiment.

FIG. 24 is a side view showing a schematic structure of a conventional load receiving platform lifting device.

[Explanation of symbols]

1 Lifting device 2 Mounting member 3 slide rails 4 First support plate 5 Second support plate 6 connecting pipes 9 Lower arm 10, 15 pin (rotation fulcrum) 12,17 pin (point of action) 13 link body 14 Upper arm 20 lift cylinder 29 Receiving platform 30 main plate 31 sub plate 42 slide cylinder 91,92 Elastic member 102 car body 104 chassis

Claims (2)

(57) [Claims] 1. A support base portion supported by a vehicle body, an arm which is supported by the support base portion, and which constitutes a parallel link for performing an ascending / descending operation, an elevation drive mechanism for driving the arm, and a tip end side of the arm. A link body that constitutes a part of the load receiving surface, a main plate that is rotatably connected to the link body, and a pivotally connected end of the main plate that is foldable on the main plate. A sub-plate, which is foldable with respect to the link body as a whole in a folded state of the sub-plate, and when unfolded, forms a load receiving surface that forms a load receiving surface together with the link body , and one end side is provided with a rotation for the link body. Having an fulcrum
Has a rotation fulcrum at the other end for rotating the load receiving base.
A hinge, and the main plate and the sub-plate are folded with respect to the link body through the hinge, and the tip of the sub-plate is between the base of the main plate and the upper surface of the link body. A loading platform raising / lowering device, which is introduced into a gap formed in the . 2. An elastic member for restricting the vertical movement of the sub-plate in a state where the main plate and the sub-plate are folded with respect to the link body is arranged between the main plate and the link body. 1. The loading platform lifting device according to 1.