JP3435119B2 - Table lift equipment - Google Patents

Description

Description: BACKGROUND OF THE INVENTION [0001] 1. Field of the Invention [0002] The present invention relates to a table lift apparatus for moving a table up and down in parallel with a base. 2. Description of the Related Art A table lift apparatus of this type has a substantially X-shaped telescopic arm formed by connecting an inner arm and an outer arm so as to be rotatable between a table and a base. The two telescopic arms are arranged in parallel, and the two telescopic arms are vertically expanded and contracted by a telescopic operation of a cylinder having a rod end pivotally supported on the inner arm side or the outer arm side, so that the table is moved up and down in parallel. In the case of such a table lift device, it is more desirable that the height of the lowermost end of the table is as low as possible in consideration of its usability (easiness of the transfer operation). However, in order to reduce the height of the lowering end of the table as much as possible, when the rotation fulcrum of the telescopic arm is positioned on the rod axis of the cylinder when the table is at the lowering end, the thrust of the cylinder is reduced. Does not act as a torque for rotating the inner arm or the outer arm, so that the telescopic arm cannot be raised (the cylinder is locked), and as a result, the table cannot be raised. For this reason, in the table lift device having the above configuration (hereinafter, referred to as a first conventional device), there is a limit to reducing the height of the lower end of the table. [0004] Conventionally, as a table lift device which has solved this problem, there has been a device disclosed in WO88 / 5759 (International Publication No. WO) (hereinafter referred to as a second conventional device).
Although not shown, the second conventional device does not rotatably support the rod end of the cylinder on the inner arm or the outer arm of the telescopic arm as in the first conventional device,
The inner roller and the outer roller are rotatably attached to the tip of the rod, and the cylinder is rod-mounted while rolling the outer roller on the cam surface provided on the outer arm and rolling the inner roller on the cam surface provided on the inner arm. By operating to the protruding side, the telescopic arm is rotated upward to raise the table. According to this configuration, the component of the thrust of the cylinder in the direction normal to the cam surface acts as a torque for rotating the inner arm and the outer arm, so that when the table is located at the lower end. Even if the rotation center of the telescopic arm is positioned on the axis of the rod of the cylinder, the telescopic arm can be raised, and as a result, the first
The height of the lower end of the table can be set lower than in the conventional device. [0006] However, the second conventional device has a problem to be further improved. That is, since one of the inner cam surface and the outer cam surface for rolling the inner and outer rollers attached to the tip of the rod of the cylinder is not a circular arc but a straight line (flat surface), the extension speed of the cylinder is constant. Even
The ascending and descending speed of the table increases as it reaches the rising end, and as a result, there is a problem that, for example, a person who has moved onto the table with a wheelchair may feel uneasy. The present invention has been made in view of this problem, and it is possible to raise the table even when the rotation fulcrum of the lifting arm is positioned on the rod axis of the cylinder. As a result, the height of the lower end of the table can be reduced. It is an object of the present invention to provide a table lift device that can be set at a lower position and that can raise and lower a table at a substantially constant speed. [0008] [Means for Solving the Problems] Therefore, the present invention is, before
Serial claims and a table lift device constructed as described in section.
According to the table lift device of the first aspect, the rotation fulcrum of the outer and inner arms (the rotation fulcrum of the telescopic arm; hereinafter, on the line of action of the component force in the normal direction perpendicular to the cam surface) of the thrust of the cylinder. ) Is not located, and this component acts as a torque for rotating the outer and inner arms. For this reason, if the cylinder is operated to the extension side while the rotation fulcrum of the outer and inner arms is positioned on the rod axis of the cylinder, the outer and inner arms are rotated to extend the telescopic arm upward. Yes, so you can raise the table. As described above, the table can be raised by extending the cylinder while the rotation fulcrum of the telescopic arm is positioned on the rod axis of the cylinder.
The lower end position of the table can be made lower than before, thereby improving the convenience when moving to the table. Moreover, since both the outer cam surface on which the outer wheel rolls and the inner cam surface on which the inner wheel rolls have an arc shape, the table can be moved up and down at substantially constant speed, Thereby, the person on the table does not feel uneasy. In addition, since the pair of right and left telescopic arms extend and contract integrally, the rigidity of the table lift device can be increased, for example, the inclination of the table can be suppressed when an eccentric load is applied to the table. Even when a person gets on a position off the center of the table, the table moves up and down in a horizontal state without tilting, so that the person does not feel uneasy. [0011] The table lift device according to claim 1
The outer arm side connection member and the inner arm side connection
The members are located near the rotation fulcrum and both ends of each arm.
It can be placed at a location. According to this configuration, the rigidity of the telescopic arm can be increased. Claim 1
On the head side of the cylinder
To be rotatably supported by the inner arm connecting member.
Can be. According to this configuration, the cylinder can be arranged compactly. FIG. 1 shows an embodiment of the present invention.
This will be described with reference to FIG. FIG. 1 shows a table lift device 10 of the present embodiment. The table lift device 10 includes a base 11, a table 12 that is moved up and down in parallel with the base 11, a table 12 and the base 1
1 is provided with a pair of left and right telescopic arms 20 and 30 interposed between the two arms. In FIG. 3, the upper telescopic arm 20 has an inner arm 21 and an outer arm 2 having substantially the same length.
Two. The two arms 21 and 22 are connected via a connecting shaft 13 so as to be mutually rotatable substantially at the center in the longitudinal direction. In addition, the lower telescopic arm 30 in FIG. 3 also has an inner arm 31 and an outer arm 32 having substantially the same length as each other. These two arms 31, 32
Are also rotatably connected to each other via the connection shaft 13. The connection shaft 13 is disposed between the left and right telescopic arms 20 and 30. The left and right outer arms 22 and 32 are fixed to both ends of the connecting shaft 13. Therefore, the left and right outer arms 22 and 32 rotate and move integrally. On the other hand, the left and right inner arms 21 and 31 are inserted into the through holes 21a and 31a provided substantially at the center in the longitudinal direction thereof.
Is inserted, and is supported rotatably with respect to the connection shaft 13. Thus, the pair of right and left telescopic arms 20, 30
Is the axis of one connecting shaft 13 (hereinafter referred to as the telescopic arm 20,
30 (referred to as 30 rotation fulcrum C). The left and right outer arms 22 and 32 are integrally connected to each other also by the connecting plate 16 having a flat plate shape. The connecting plate 16 is attached to a position near the center of rotation of the outer arms 22 and 32 (near the connecting shaft 13).
The connecting plate 16 has its width direction defined by the outer arms 22 and 3.
The outer arms 22 and 32 are connected around the connecting shaft 13 with high rigidity. Next, inner arm side cam plates 23, 33 are attached to the inner side surfaces (surfaces facing each other) of the inner arms 21, 31, respectively. The inner arm side cam plates 23 and 33 are connected to the inner arm 2.
The entire surface is fixed to the inner surfaces of the first and the first 31. Inner arm side cam surfaces 23a, 33a each having a substantially semicircular shape are formed on the lower surfaces of the distal ends (left end side in FIG. 1) of both inner arm side cam plates 23, 33. Both inner arm side cam plates 23, 33
Are formed substantially in the center with insertion holes 23b and 33b coaxial with the insertion holes 21a and 31a.
The connection shaft 13 is also rotatably inserted into b and 33b. Both inner arm side cam plates 23, 3
The rear end portions 3 are integrally connected by a connecting member 14. A square pipe material is used for the connecting member 14. The two inner arms 21,
The inner arm 31 and the inner arm side cam plates 23 and 33 rotate and move together. Thus, the outer arms 22, 32 are provided between the pair of right and left telescopic arms 20, 30.
Are vertically rotated integrally by the connecting shaft 13 and the connecting plate 16, and the inner arms 21 and 31 are vertically rotated integrally by the right and left via the connecting member 14. The arms 20 and 30 extend and contract vertically. The rotation base ends (left ends in FIGS. 1 to 3) of the left and right outer arms 22 and 32 are vertically rotatable via support shafts 24 and 34 provided at the left end of the base 11, respectively. Supported. Both support shafts 24 and 34 are arranged coaxially. On the other hand, the rotating front ends (the right ends in FIGS. 1 to 3) of the outer arms 22 and 32 are connected via a connecting shaft 15. Guide rollers 15 are provided at both ends of the connection shaft 15.
a and 15a are rotatably mounted. As shown in FIG. 1, both guide rollers 15 a, 15 a roll on the lower surface of the table 12 in the horizontal direction in FIG. The base ends (left ends in FIGS. 1 to 3) of the left and right inner arms 21 and 31 are turned up and down to the left end of the table 12 via a common support shaft 17 and an auxiliary connecting bar 17a. Supported as possible. On the other hand, the rotating front ends (the right ends in FIGS. 1 to 3) of the inner arms 21 and 31 are connected via a connecting shaft 18. Guide rollers 18a, 18a are rotatably attached to both ends of the connecting shaft 18. The two guide rollers 18a, 18a are rolled along the left and right edges of the base 11 with the extension and retraction of the two extension arms 20, 30. Next, a connecting member 19 is attached to the left and right outer arms 22, 32 near the turning base end in a bridging manner. Further, as shown in FIG.
The center of the connecting plate 16 in the width direction (the vertical direction in the drawing) and the center of the connecting plate 16 in the width direction are connected by an auxiliary connecting plate 16a.
The connecting member 19 includes two hydraulic cylinders 40 and 41.
Is attached. Both hydraulic cylinders 40, 41
It is vertically rotatably supported by the connecting member via rotating shafts 40a and 41a attached to the head end thereof. Rods 40b, 41b of both hydraulic cylinders 40, 41
Are connected to a common operating shaft 42 having a rectangular cross section. That is, the operating shaft 42 is
It is attached in a bridging manner between the tips of b and 41b. Inner arm side cam wheels 43, 44 and outer arm side cam wheels 45, 46 are rotatably attached to both ends of the operation shaft 42, respectively. The inner arm side cam wheels 43 and 44 and the outer arm side cam wheels 45 and 46 are rotatably supported independently of each other. The left and right inner arm side cam wheels 43,
44 is the inner arm side cam plate 23, 3
3 and rolls on the inner arm side cam surfaces 23a and 33a by the extension operation of the hydraulic cylinders 40 and 41. As shown in FIG. 1, the cam surfaces 23 of the inner arm side cam plates 23, 33
a and 33a have a substantially semicircular shape as described above. On the other hand, the left and right outer arm side cam wheels 45, 4
Reference numeral 6 designates 2 attached to the connection shaft 13 and the connection plate 16.
Cam surface 2 of the outer arm side cam plates 25 and 35
5a, 35a, and the hydraulic cylinder 4
0, 41, the outer arm side cam surface 2
Roll on 5a, 35a. Outer arm side cam surface 25
a and 35a are formed on the upper surface side of the outer arm side cam plates 25 and 35, and are provided to face the cam surfaces 23a and 33a of the inner arm side cam plates 23 and 33 when viewed from the side. However, as shown in FIG. 3, the inner arm side cam plates 23, 33 and the outer arm side cam plates 25, 35 are aligned with the axial displacement between the inner arm side cam wheels 43, 44 and the outer arm side cam wheels 45, 46. And its thickness direction (connection shaft 13
In the axial direction). The cam surfaces 25a and 35a of the outer arm side cam plates 25 and 35 have a gentle arc shape as shown in FIG. The hydraulic control circuits for the two hydraulic cylinders 40 and 41 are configured so as to extend and retract in synchronization. When the two hydraulic cylinders 40 and 41 extend, the operating shaft 42 is moved.
1 to 3 move rightward in FIGS. 1 to 3, whereby the inner arm side cam wheels 43 and 44 respectively move the cam surfaces 23 a and 33 a of the inner arm side cam plates 23 and 33.
The upper arm-side cam wheels 45, 46 roll on the upper arm-side cam plates 25, 35.
a, 35a, thereby causing the inner arm side cam plates 23, 33 and the outer arm side cam plates 2
The space between 5, 35 is expanded. The cam surfaces 23a, 33 of the thrust of the two hydraulic cylinders 40, 41 generated at this time.
a, 25a, 35a, the component forces F1, F2 in the normal direction (FIG. 1
0) is the inner arm 21, 31 and the outer arm 2
Acts as a torque for rotating the second and second arms 32 and 32 in the upright direction, whereby the telescopic arms 20 and 30 extend upward, and the table 12 rises in parallel. FIG. 1 shows a state in which the table 12 is raised most. When both hydraulic cylinders 40 and 41 operate in the retracting direction, the two telescopic arms 20 and 30 move their own weight of the table 12 or the table 1.
2 contracts downward due to the load applied thereto, whereby the table 12 descends in parallel. FIG. 2 shows a state where the table 12 is lowered most. According to the table lift apparatus 10 of the present embodiment, the inner arm acting on the inner arm side cam wheels 43, 44 of the thrust P of the cylinders 40, 41 as shown in FIG. Side cam surface 25
a, the component force F1 in the normal direction of the inner arm 21;
Acts as a torque for rotating 31 to the upright side,
The component force F2 in the normal direction of the outer arm side cam surfaces 25a, 35a acting via the outer arm side cam wheels 45, 46 acts as a torque for rotating the outer arms 22, 32 to the upright side. Each component F1, F1, F
The rotation fulcrum C (the axis of the connecting shaft 13) of the telescopic arms 20 and 30 is not located on the line of action of F2 and F2, and the distance L
1, L2. Therefore, when the table 12 is located at the lower end as shown in FIG.
Even if the rotation fulcrum C of 0, 30 is set to be located on the rod axis of the cylinders 40, 41, the respective arms 21, 31, 22 by the respective component forces F1, F2 generated by the thrust P of the cylinders 40, 41. , 32 to rotate (F
1 × L1 and F2 × L2), whereby the telescopic arms 20, 30 can be extended upward and the table 12 can be raised, so that the lower end position of the table 12 is set to a lower position than before. Therefore, the convenience at the time of transferring to the table 12 can be improved. Each of the cam plates 23, 33, 25, 3
Since the cam surfaces 23a, 33a, 25a, and 35a of the No. 5 are formed in an arc shape, the table 12 can be moved up and down at a substantially constant speed in a range from the lower end to the upper end. Hereinafter, the relationship between the strokes of the cylinders 40 and 41 and the elevation distance of the table 12 is disclosed in the case of using the above-described upper and lower cam plates 23, 33, 25, and 35 (circular cams) and in, for example, WO88 / 05759. A comparison will be made between a case where the cam surface of one (lower) cam plate is simply a linearly inclined surface as in the table lift device according to the second related art. The cylinder 4
The formulas for calculating the strokes 0 and 41 and the vertical distance of the table 12 can be obtained by using, for example, XY coordinates with the origin at the pivot point C of the telescopic arms 20 and 30. Alternatively, a mathematical method is sufficient, and thus will not be described in detail. Needless to say, conditions other than the shape of the cam surface (conditions such as the mounting position of the cylinder and the distance between the fulcrum of the telescopic arm) are compared under the same condition. Hereinafter, only the results are shown. (1) The arc cam surfaces 23a, 25a (33
a, 35a) (in the case of this embodiment) The height of the table 12 is increased from 50 mm near the lower end to 100 mm.
mm, the cylinders 40, 41
When the stroke is 1.29mm, cylinder 4
The amount of change in the height of the table 12 per unit stroke of 0.41 is 4.43 mm. On the other hand, when the cylinders 40 and 41 are stroked by 10.45 mm to change the height of the table 12 from 350 mm near the rising end to 400 mm, the amount of change in the table height per unit stroke of the cylinders 40 and 41 Is 4.78 mm
It becomes. For this reason, the arc-shaped cam surfaces 23a, 25
a (33a, 35a), the ratio of the rising speed near the falling end of the table 12 to the rising speed near the rising end is
4.78 / 4.43 = 1.08, so that the table 12 moves up and down at a substantially constant speed. (2) When a straight cam surface is used for the lower cam surface as in the second prior art, similarly, in order to change the height of the table 12 from 50 mm near the lower end to 100 mm, the cylinder 40, 4
When 1 is moved by 2.84 mm, the amount of change in the height of the table 12 per unit stroke of the cylinders 40 and 41 is 17.6 mm. On the other hand, table 12
When the cylinders 40, 41 are stroked by 1.49 mm in order to change the height of the cylinder from 350 mm near the rising end to 400 mm, the amount of change in the height of the table 12 per unit stroke of the cylinders 40, 41 is 33 .
6 mm. From this, the ratio of the rising speed near the falling end of the table 12 to the rising speed near the rising end when the linear cam is used is 33.6 / 17.9 = 1.91, and
Therefore, the table 12 does not move up and down at a constant speed. As described above, the inner arm side cam plates 23 and 33 and the outer arm side cam plate 2
If the cam surfaces 23a, 33a, 25a, and 35a of the fifth and the 35th do not all have an arc shape, but, for example, one (or both) of the cam surfaces on the inner arm side or the outer arm side has a linear shape, Near the ends, the arm push-out angle per unit stroke of the cylinders 40 and 41 becomes large, and a large speed difference occurs between the vicinity of the descending end and the vicinity of the ascending end. If the table 12 does not move up and down at a substantially constant speed, the rider will feel anxious,
According to the table lift device 10 of the present embodiment, such a problem does not occur because the table 12 moves up and down at a substantially constant speed in the entire range from the rising end to the falling end. The load Wkg applied to the table 12
Is required to be raised by 50 mm, the energy Ew required is E
w = 50 Wkg · mm, which corresponds to cylinders 40 and 4
1 is balanced with the energy Ec generated by
The following can be said. (3) All arc cam surfaces 23a, 33a, 25a, 35a
(In the case of the present embodiment) When the table 12 is changed from 50 mm near the lower end to 100 mm, the strokes of the cylinders 40 and 41 are 11.29 mm as described above.
29P = 50W, so the cylinder thrust P is P = 4.43
W (kg). On the other hand, when the table 12 is raised from 350 mm near the rising end to 400 mm, the stroke of the cylinders 40 and 41 is 10.45 mm, so that P = 4.78 W (kg). Comparing the two, the required thrust of the cylinders 40 and 41 near the lower end and the upper end is almost the same (1.08 times).
It becomes. (4) When a straight cam surface is used for the lower cam surface as in the second related art, the cylinder thrust P required for raising the table 12 by 50 mm near the lower end is P = 50W / 2.84.
= 17.6 W (kg), and the cylinder thrust P required for raising the table 12 by 50 mm near the rising end is P = 50 W / 1.49 = 33.6 W (kg). Therefore, in the case of the linear cam, 33.6 / 17.6 = 1.91 times the cylinder thrust is required near the rising end than near the falling end. As described above, when the linear cam is used, the cylinder thrust near the ascending end is about twice as large as that near the descending end. Therefore, it is necessary to prepare a large-sized cylinder suitable for the vicinity of the ascending end. In order to raise the table 12 by the same distance with a relatively small stroke, it is necessary to prepare a cylinder having a larger thrust.
On the other hand, as illustrated, the cam surface 23 having the arc shape is used.
By using a, 33a, 25a, and 35a, the required thrusts P of the cylinders 40 and 41 near the lower end and near the upper end are substantially the same, and the same thrust is larger with a larger stroke than in the case of the linear cam. Since the configuration is such that the table 12 is raised by a distance, the required thrust P of the cylinders 40 and 41 may be smaller, and the cost can be reduced. Next, as shown in FIGS. 1 and 10, at the rising end of the table 12, the inner arm side cam wheels 43, 44 are connected to the vertices T of the inner arm side cam surfaces 23a, 33a (points at which the displacement amount S is the largest). ), It is possible to prevent the table 12 from being inadvertently dropped (stopper function of the inner arm side cam plates 23, 33). That is, the inner arm side cam wheel 4
In a state in which the upper and lower ends of the inner and outer cam surfaces 23a and 33a are at the apex T (the rising end position of the table 12), the weight of the table 12 and the load applied to the table 12 are reduced by the cylinders 40 and 41. To act in the direction of extension, the table 12 is locked in the raised end position unless the cylinders 40, 41 are actively activated in the contraction direction. Further, a pair of right and left telescopic arms 20, 30
The outer arms 22 and 32 are connected by a connecting plate 16 having a flat plate shape in the vicinity of the rotation fulcrum C so as to rotate integrally up and down.
The connecting members 14 and 31 are also located near the rotation fulcrum C.
(Square pipe) so as to rotate integrally up and down, the left and right telescopic arms 20,
High rigidity between 30 can be obtained. In addition, since the turning end sides of the outer arms 22 and 32 are integrally connected by the connecting shaft 15, and the turning end sides of the inner arms 21 and 31 are integrally connected by the connecting shaft 18, the telescopic arm is also provided in this respect. The rigidity of 20, 30 is increased. Further, since the left and right telescopic arms 20 and 30 are integrally extended and retracted, an eccentric load is applied to the table 12 because, for example, a person seated in a wheelchair rides off the center of the table 12. Even if the table 12 is moved, the table 12 moves up and down while maintaining a horizontal state without tilting, so that a person on the table 12 does not feel uneasy. Further, in the table lift device 10 of the present embodiment, the table 12 is raised when the hydraulic cylinders 40, 41 operate to the extension side, and the extension sides of both hydraulic cylinders 40, 41 are set to the table elevation side. This is the configuration used. In this respect, for example, Japanese Patent Application Laid-Open No.
As disclosed in Japanese Unexamined Patent Publication No. 597 or No. 63-35795, there has been provided a table lift device having a structure in which a contraction side of a cylinder as a driving source is used on a table ascending side. However, in general, in a cylinder, the pressure receiving area on the head side is larger than the pressure receiving area on the rod side of the piston by the integral of the cross-section of the rod. From this, the table lift device 1 of the present embodiment
According to 0, the load can be set higher than that of the conventional table lift device (a configuration in which the contraction side of the cylinder is used as the table lift side), and if the load is set to be equal. A cylinder one size smaller can be used, so that the table lift device 10 can be made compact. Various modifications can be made to the embodiment described above. For example, two hydraulic cylinders 40, 4
Although the configuration using 1 has been illustrated, a configuration in which the left and right telescopic arms 20 and 30 are extended and retracted by one hydraulic cylinder may be used.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a table lift device according to an embodiment of the present invention. In this figure, the table at the rising end is shown by a solid line, and the table at the falling end is shown by a two-dot chain line. FIG. 2 is a longitudinal sectional view of the table lift device when the table is located at a lower end. FIG. 3 is a plan view of the table lift device according to the present embodiment. In the figure, the table is indicated by a two-dot chain line. FIG. 4 is a sectional view taken along line (4)-(4) of FIG. 2; FIG. 5 is a sectional view taken along line (5)-(5) of FIG. 2; FIG. 6 is a sectional view taken along line (6)-(6) of FIG. 2; FIG. 7 is a sectional view taken along line (7)-(7) of FIG. 2; FIG. 8 is a sectional view taken along line (8)-(8) of FIG. 2; FIG. 9 is a sectional view taken along line (9)-(9) of FIG. 2; FIG. 10 is a side view of the vicinity of the cam plate and the cam wheel when the table is located at a lower end. In this drawing, a state is described in which the thrust of the cylinder acts on the cam plate via the cam wheel. DESCRIPTION OF SYMBOLS 10 ... Table lift device 11 ... Base, 12 ... Table 13 ... Connection shaft, 14 ... Connection member 15 ... Connection shaft, 15a ... Guide roller 16 ... Connection plate, 16a ... Auxiliary connection plate 18 ... Connection shaft , 18a ... guide roller 19 ... connecting members 20, 30 ... telescopic arms 21, 31 ... inner arms 22, 32 ... outer arms 23, 33 ... inner arm side cam plates 23a, 33a ... inner arm side cam surfaces 25, 35 ... outer arm side Cam plates 25a, 35a: Outer arm side cam surfaces 40, 41 ... Hydraulic cylinder 42 ... Operating shafts 43, 44 ... Inner arm side cam wheels 45, 46 ... Outer arm side cam wheels P: Thrusts F1, F2 of cylinders 40, 41 ... Cylinder Force in the direction normal to the cam surface of the thrust P

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) B66F 7/08

Claims (1)

(57) [Claims 1] A pair of left and right telescopic arms having an outer arm and an inner arm rotatably connected to each other between a base and a table; A left and right telescopic arm is provided at the left and right ends of a single connecting shaft.
And the outer arm is fixed to an end of the connecting shaft.
And the inner arm is rotatable about the connection shaft.
The outer arm and the inner arm are
If it is provided so that it can rotate mutually about the connecting shaft
Between the left and right outer arms and the left and right inner arms.
Each of the arms is connected integrally by a connecting member, and a single operating shaft is attached to the rod end of the cylinder,
It ends of the actuation shaft in response to the left and right telescopic arm
Each one rotatably mounting the outer arm side wheel and the inner arm wheel to each other, the inner arm side cam surface of the respective circular arc shape on the left and right inner arms provided, said to correspond to the inner arm side cam surface of the left and right Linking
Provided outer arm side cam surface of the arc-shaped axis, from <br/> parallel movement of the actuating shaft by extending action of the cylinder, along the outer arm side wheel on the outer arm side cam surface, said inner arm each Rukoto is rolled along the wheel to the inner arm side cam surface
The common drive of the left and right telescopic arms
A table lift device having a configuration in which the telescopic arm is extended upward integrally with the left and right sides as a source to raise the table in parallel to a rising end.