JPS63139552A - Reclining bed apparatus - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to an upright bed device used for medical equipment, etc., and in particular, it is designed to reduce the required installation space in the vertical and horizontal directions as much as possible. This invention relates to an upright bed device.

(Prior Art) In the case of a tilting bed device generally used for medical equipment, etc., considering the installation space, it is sufficient to rotate the bed around its longitudinal center and raise it up. In this case, the horizontal height of the bed becomes extremely high, necessitating a high step stool, etc., which increases the burden and risk on the patient, and makes it difficult for the doctor to examine the patient. Therefore, it is desirable that the horizontal height of the bed be as low as possible so that the bed can be raised and lowered.

Conventionally, when raising and lowering a bed, the bed is rotated and at the same time, the bed is slid upward in the direction of inclination, thereby preventing interference between the bed and the floor surface when raising and lowering the bed. Various types of raising and lowering bed devices have been developed that allow the height of the bed to be lowered, and one known example of this type of raising and lowering bed device is the one shown in FIG. 7.

As shown in the figure, in this raising/lowering platform system 21, a semicircular large gear 8 with a large diameter is oscillated via a hollow oscillating shaft 6 on a pedestal 4 fixedly provided on a floor surface 2. The large gear 8 is rotatably supported, and a binion gear 12 of a first output shaft 10, which is rotatably supported on a pedestal 4, is meshed with the lower end of the large gear 8.

Further, a bed 14 is supported on the side surface of the large gear 8 so as to be slidable along its longitudinal direction, and a rack 16 is provided on this bed 14 along its longitudinal direction.

A binion gear 20 of a second rotary output shaft 18, which is inserted through the swing shaft 6 and rotatably provided on the same axis, is meshed with the rack 16, and these first and second outputs are connected to the rack 16. The shafts 10 and 18 are configured so that the rotational force of the same motor is transmitted to each of them via a gear transmission mechanism or a chain transmission mechanism (not shown) so that they can freely rotate forward and backward in the same direction at a constant rotation ratio. It has become.

Therefore, the slide movement amount and the tilting angle table of the bed 14 are moved at a constant ratio as shown in FIG. 8(b), and the movement trajectory of the bed 14 is as shown in FIG. It is as shown in (a).

(Problems to be Solved by the Invention) However, in the above-mentioned conventional raising/lowering bed device 1, the amount of sliding movement and the tilting angle of the bed 14 are always constant from the horizontal position to the vertical position of the bed 14. Because it is designed to be moved at a ratio of
It has not yet been possible to lower the horizontal height of the bed 14 sufficiently to raise and lower the bed 14.

In other words, the height of the bed 14 in the horizontal position can be lowered by increasing the slide movement 8J relative to the tilting angle table.1 However, if this is done, the total amount of slide movement of the bed 14 increases. Therefore, when the bed 14 is raised to a vertical position, the bed 14 is slid upward more than necessary, and the locus of movement when the bed 14 is raised and lowered becomes large, requiring a large installation space in the vertical and horizontal directions. The problem was that it became necessary.

For this reason, as shown in FIGS. 8(a) and 8(b), for example, if the installation space of the tilting bed device 1 is Y2 in the vertical direction and ×2 in the horizontal direction, the slide movement opening for the tilting angle of the bed 14 is If the maximum height was set to Y3, the height of the bed 14 at the horizontal position was required to be Yl.

The present invention has been made in view of the above-mentioned circumstances, and its purpose is to enable the bed to be moved up and down according to the amount of the tilting angle of the bed, and to move the bed according to the amount of the tilting angle of the bed. ffl can be varied between the horizontal position and the vertical position of the bed depending on the tilting angle of the bed, thereby preventing interference between the bed and the floor without increasing the total sliding movement of the bed. To provide a raising/lowering bed device capable of raising/lowering the bed by lowering the horizontal height of the bed, and reducing the required installation space in the horizontal and vertical directions as much as possible. be.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention provides a frame that supports a bed so that it can slide back and forth in the longitudinal direction, and a frame that can swing freely in the longitudinal direction of the bed. a pedestal that is pivotally supported by the pedestal; a first gear mechanism provided on the pedestal for swinging the frame; and a first gear mechanism provided in the pedestal and operated in synchronization with the first gear mechanism to slide the bed. In the raising/lowering bed device equipped with a second gear mechanism,
The pedestal is provided with a base that supports the pedestal so as to be movable up and down, and between the base and the frame, there is provided a base that supports the pedestal so as to be movable up and down. The second gear mechanism includes a planetary gear device, and the second gear mechanism includes a planetary gear device. Through the intervention, the Jli! A lever for rotating the planetary frame is integrally provided on the planetary frame of the two-star gear unit and projects outward in the radial direction, and the swinging end of the lever is engaged with the frame to rotate the planetary frame. A tilting bed device is constructed by integrally providing a planetary frame rotating cam that rotates the planetary frame in response to the swinging of the frame to vary the sliding movement m of the bed with respect to the swinging angle of the frame.

(Function) When the first gear mechanism swings the frame to raise the bed from a horizontal position, the second gear mechanism synchronizes with this and causes the bed to slide upward in the direction of inclination. However, at this time, the cam for rotating the planetary frame is also swung integrally with the swiveling of the frame. When the planet frame rotation cam swings, the lever swings along the cam profile, and the planet frame is rotated. At this time, due to the shape of the cam broil, when the planetary frame is rotated in the opposite direction to the sun gear of the planetary gear unit, the output rotational speed of the planetary gear unit is increased, and the bed slides according to the amount of the tilting angle. When the amount increases and the planetary frame is rotated in the same direction as the sun gear, the output rotational speed of the planetary gear portion is reduced, and the amount of slide movement relative to the amount of the tilting angle of the bed becomes smaller.

At the same time, the bed, along with the frame, pedestal, and drive means provided on the pedestal, is susceptible to interference between the bed and the floor during the early stages of rising due to the swinging angle of the frame due to the lifting/lowering drive means. They are moved upward within a predetermined swing angle range, and when a predetermined f:l swing angle is exceeded, they are moved downwardly. For this reason, if the cam profile of the planetary frame rotation cam is formed so that the slide movement speed of the bed is slowed down at the beginning of the bed rising from the horizontal position, the bottom and sides of the bed can be If the cam profile of the cam for rotating the planetary frame is formed so that the amount of overhang to the bed can be suppressed as much as possible, and the slide movement speed of the bed is increased in the initial stage of raising the bed, The initial downward overhang can be further suppressed.

(Example) A preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

FIG. 1 is a front view of the up/down bed device according to the present invention, FIG. 2 is a view taken along the arrow I-II in FIG. 1, and FIG. 3 is a view taken along the arrow FIG.

As shown in the figure, the raising/lowering bed device 21 includes a frame 24 pivotally supported on the upper end of a pedestal 23 so as to be freely swingable, and a bed 25 supported by the frame 24 so as to be slidably movable along the longitudinal direction. The bag stand 2 is provided in the stand 23.
a bed tilting drive mechanism 26 that slides the frame 24 in its longitudinal direction and swings the frame 24; The base 60 and this base 60
and an elevating drive means 65 that is interposed between the frame 24 and the frame 24 and moves the pedestal 23 up and down in response to the swinging of the frame 24.

The frame 24 is composed of a substantially semicircular large-diameter external gear 27, and the rotation center of the external gear 27 is a hollow swing shaft 28.
It is swingably supported at the upper end of the pedestal 23 via the cradle 23. A binion gear 30 of the first output shaft 29 rotatably supported on the pedestal 23 is meshed with the substantially lower end of the semicircular external gear 27.
The frame 24 is configured to be swung by a first gear mechanism 31 consisting of an external gear 27 and an external gear 27 .

An input shaft 33 is connected to the first output shaft 29 via a worm gear 32 (worm gear 32a and worm 32b), and a motor supported on the frame 23 by a bracket 34 is connected to the input shaft 33. 58 are connected via a coupling 59.

Further, on the outer surface 24a of the frame 24 made of the semicircular external gear 27, support members 35 for the bed 25, which are shaped like a rectangular parallelepiped, are protrudingly provided on both left and right sides in parallel with the chord at the upper end of the frame 24. There is.

On the other hand, a slide groove 36 is formed in one side surface 25a along the longitudinal direction of the bed 25 over substantially the entire length thereof, and this slide groove 36 is slidable on the rectangular parallelepiped-shaped support member 35 of the frame 24. It is fitted. Slide groove 36
A rack 37 is formed on the lower end surface 25b of the lower bed 25 and extends over substantially the entire length of the bed 25, and this rack 37 is inserted into a hollow swing shaft 28 that supports the frame 24 and is rotatable. The second output shaft 38 is meshed with a pinion gear 39 of a second output shaft 38 provided in the second output shaft 38 .

By the way, a planetary gear device 40 is connected to this second output shaft 38.
The first output shaft 29 via the second gear mechanism 41 having
The rotational force of the tilting actuator v426 is transmitted to the second gear mechanism 41, the first gear mechanism 31, the first and second output shafts 29, 38, and the second gear mechanism v426. It consists of a pinion gear 39 of an output shaft 38, a rack 37 meshed with the pinion gear 39, an input shaft 33, etc.

The planetary gear device 40 includes a sun shaft 42 that is rotatably supported on a mount 23, a sun gear 43 that is fixed to the sun shaft 42, and a sun gear 43 that is meshed with the outside of the sun gear 43. A very common gear is made up of a plurality of planetary gears 44, a planetary frame 46 that supports the rotating shaft 45 of these planetary gears 44, and an internal gear 47 that meshes with and surrounds each of the planetary gears 44. The planetary frame 46 is rotatably supported on the pedestal 23 on its outer circumferential surface, and rotatably supports the sun shaft 42 on its inner circumferential surface.

The sun shaft 42 is provided with a power extraction spur gear 48 for extracting power from the first output shaft 29, and this power extraction spur gear 48 is located approximately at the center of the first output shaft 29. It meshes with a gear 49 that is integrally formed. Further, external teeth 50 are formed on the outer peripheral surface of the internal gear 47, and a spur gear 51 is meshed with the external teeth 5o. This spur gear 51 is fixed to a rotating shaft 52 that is rotatably supported on the frame 23, and a spur gear 53 is fixed to the shaft end of this rotating shaft 52. This spur gear 53 is the second
A spur gear 54 is fixed to the shaft end of the output shaft 38 of the
The second output shaft 38 is meshed with the first output shaft 2.
The output shaft 9 is rotated in the same direction as the first output shaft 29 by the power taken out from the output shaft 9.

Further, a differential mechanism 54 is connected to the planetary gear device 40 for varying the rotational speed output from the internal gear 47 with respect to the rotational speed input to the sun shaft 42 . The differential mechanism 54 includes a lever 55 that is integrally provided with the planetary frame 46 and protrudes outward in the radial direction, and a lever 55 that is integrally provided with the frame 24 and is formed at a swinging end of the lever 55. 55a is engaged, and a planetary frame surrounding diversion cam 56.

The planetary frame surrounding diversion cam 56 is integrally carved in a groove shape along the entire length of the inner surface 27a of the semicircular external gear 27 constituting the frame 24 along its arcuate portion.
The distance from the swing center 0 of the frame 24 to the groove center 56a is changed depending on the swing angle of the frame 24.

Further, a cam follower 57 fixed to the swinging end 55a of the lever 55 is inserted into the planetary frame surrounding rotation cam 56 substantially directly below the swinging shaft 28 of the external gear 27 (i.e., the frame 24). The frame 2 is slidably engaged with the frame 2.
4 is swung, the cam follower 57 and lever 55 are swung integrally along the cam profile of the planetary frame surrounding diversion cam 56, and the planetary frame 46 is rotated.

That is, when the distance from the groove center 56a of the planet frame surrounding rotation cam 56 to the swing center 0 decreases as the frame 24 swings, the planet frame 46 is rotated counterclockwise in FIG.
Conversely, if the distance from the groove center 56a to the swing center 0 increases, it will rotate clockwise, and if the distance from the groove center 56a remains unchanged, it will come to rest.

In addition, as shown in FIG. 5, the planetary gear device 40 has the number of teeth of the internal gear 47 Za, the number of rotations Na, the number of teeth of the planetary gear 44 Zb1, the number of rotations Nb, and the number of rotations of the planetary frame 46 ( That is, the number of revolutions of the planetary tooth 1 (44 revolutions) is Nr, and the number of teeth of the sun gear 43 is 209 revolutions.

If the diameter of the planetary gear 44 is Da, and the diameter inside the planetary gear support of the planetary frame 46 is da, then the sun gear 43 and the internal gear 47
As is well known, the relationship between the rotation speed and the rotation speed is as follows.

(1) When the planet frame 46 is fixed and stationary, Na--
Nc-(Zc/Za) (2) When the sun wheel 43 is stationary and the planetary frame 46 is rotated by Nr, Nr-(1+Da/dm)xNa/2,'', NaNa-2d Nr/(dm+Da )(3)
When the planetary frame 46 is rotated by Nr in the same direction as the rotation direction of the sun gear 43, Na--Nc-(Zc/Za) + ((2dmNr)/(dm+Da)) (4) The planetary frame 46 is rotated by the sun gear When the sun gear 43 is rotated at Nr in the opposite direction to the rotation direction of the sun gear 43, Na--Ncx (Zc/Za) -12dm-Nr/(dm+Da)) In other words, the rotational speed of the sun gear 43 when the planetary frame 46 is stationary Based on the ratio of the rotational speed of the internal gear 47 and the rotational speed of the internal gear 47, when the planetary frame 46 is rotated in the same direction as the rotational direction of the sun gear 43, the output of the internal gear 47 relative to the input rotational speed to the sun gear 43 is The rotation speed is reduced and conversely the sun tooth 1i43
When the planetary frame 46 is rotated in a direction opposite to the rotational direction, the output rotational speed of the internal gear 47 is increased.

In addition, in the case of this embodiment, FIGS. 1 and 4(a).
As shown in (b), when the frame 24 (external gear 27) is swung clockwise by the first gear mechanism 31 to raise the bed 25 from the horizontal position, the The bed 25 is synchronously moved by the second gear mechanism 41.
is slid toward the left in the figure and upward in the tilting direction, and at this time, the sun gear 43 is rotated clockwise in the same direction as the swinging direction of the frame 24.

Therefore, if the cam profile of the planetary frame surrounding cam 56 is formed so that the planetary frame 46 rotates counterclockwise as the frame 24 swings, the slide movement speed of the bed 25 will be increased, and vice versa. If the cam profile is formed to rotate the planetary frame 46 clockwise, the bed 25
The slide movement speed of is reduced.

By the way, in this embodiment, the amount of the tilting angle of the bed 25 (the amount of swinging angle of the frame 24 ) of the planetary frame surrounding diversion cam 56 to prevent interference as much as possible by reducing the amount of slide movement relative to ), and to increase the amount of slide movement relative to the tilting angle when the interference range is exceeded. Forming a profile.

That is, as shown in FIG. 1, the cam profile of the planetary frame surrounding diversion cam 56 has a different shape on the left side and the right side shown, based on the engagement position with the cam follower 57 when the bed 25 is in a horizontal state. ing.

The left part is an interference area of the swing angle range of the frame 24 from the horizontal position where the bed 25 tends to interfere with the side wall 70 when the bed 25 is raised up to the initial stage of raising up to θ degrees. The distance from the groove center 56a of the planetary frame surrounding diversion cam 56 to the swing center 0 is formed to be shortened at a large rate of change, and the groove center distance L2 of the swing angle position at the terminal θ degree of this initial stage of tilting is formed. is formed the shortest. Also,
This dry! Within the swing angle range (θ) beyond the J area until the bed 25 is vertically erected, the center distance of the groove is formed so as to gradually become longer as the bed 25 is erected. The groove center distance L3 at the moving angle position is set equal to the groove center distance L1 at the reference horizontal position.

On the other hand, on the right side, similarly, in the interference region of the swing angle range of the initial stage of raising and falling up to θ, the distance from the groove center 56a of the planetary frame surrounding diversion cam 56 to the swing center 0 has a large rate of change. The end point θ of this initial section is
The groove center distance L4 at the swing angle position is the longest. Further, within the swing angle range (θ) beyond this interference area until the bed 25 is vertically erected, the groove center distance is formed so as to gradually become shorter as the bed 25 is erected. Groove center path 1 at 90 degree 1st angle position
1L5. is formed to be equal to the groove center distance L1 at the reference horizontal position.

On the other hand, the pedestal 23 is guided and supported by a base 60 fixedly provided on the floor 22 so as to be slidable up and down.

The base 60 consists of a flat plate-shaped leg 61 and two columns 62, 62 that stand vertically from the leg 61.
The pedestal 23 is provided between the book pillars 62 and 62. A guide rail 63 is provided protruding from the opposing inner surfaces of each of the columns 62, 62 to guide the pedestal 23 vertically and slidably from its upper end to its lower end.
On the other hand, the pedestal 23 has the guide rails 63 on both side walls thereof.
A guide groove 64 is cut into the guide groove 64 and is slidably engaged with the guide groove 64 .

Further, between the base 60 and the frame 24, the frame 2
An elevating drive means 65 is interposed for moving the frame 24, the bed 25, and the pedestal 24 integrally up and down in response to the raising and lowering of the bed 25 from the swinging portion of No. 4. The means 65 consists of a lifting drive cam 66 that is integrally provided with the frame 24, and a support 67 that engages with the lifting drive cam 66 and is fixed to the base 60. .

The elevating drive cam 66 is a plate-shaped cam that is integrally provided on the outer surface 27b of the semicircular external gear 27 of the frame 24 on the side of the bed 25 along an arcuate portion thereof. The support body 67 fixedly provided to the base 60 is a support @6 that is slidably engaged with the vertical drive cam 66 directly below the swing shaft 38 of the external gear 27 (namely, the frame 24).
8 and a support member 69 that rigidly fixes the support shaft 68 to the base 60, and the support member 69 is vertically erected from the leg portion 61 of the base 60 and is integrally molded.

The elevating drive cam 66 is formed such that the cam profile of the distance from each part of the sliding surface 66a with the support shaft 68 to the swing center O changes along the circumferential side of the frame 24. The distance to the sliding surface 66a of the engaging portion with the support shaft 68 in the horizontal position is formed to be short, and the distance to the sliding surface 66a on both left and right sides continuously increases until a predetermined swing angle is reached. It is formed so that it is increased in length, and furthermore, when it exceeds a predetermined swing angle, it is formed so that it becomes shorter again.

In this embodiment, when the bed 25 is raised, the interference region is the swing angle range in the initial stage of raising from the horizontal position to approximately θ on both the left and right sides, where the bed 25 and the floor 32 tend to interfere with each other. The sliding surface distance is formed so that it increases at a large rate of change with respect to the amount of swing angle, and the groove center distance L7 at the terminal θ degree position of the initial tilting section is the maximum. ,
In addition, in the 9 range up to 90 degrees beyond the initial stage of tilting, the sliding surface distance is formed so that it becomes shorter at a small rate of change with respect to the swing angle, and the 90 degree position and the horizontal position (i.e. 0 The sliding blood path 11L-L6 is minimized at ' Therefore, in the foldable sleeping bag @21 configured in this way,
As shown in FIG. 1 and FIGS. 4(a) and 4(b), the motor 58 is rotated at a constant speed to swing the frame 24 clockwise from the horizontal position to the vertical position of the bed 25. Then, the frame 24 connects the external gear 27 and the pinion gear 3.
A first gear mechanism 31 and a worm gear 32 consisting of
It is decelerated by and oscillates at a constant speed.

On the other hand, in synchronization with the operation of the first output shaft 29, the rotational force of the first output shaft 29 is reduced by the reduction ratio of a second gear mechanism 41 including a planetary gear device 40 having a differential function. The bed 25 is erected by the swinging of the frame 24, and is also slid to the left in an upward direction of inclination. At this time, the reduction ratio of the second gear mechanism 41 is varied according to the rotational speed and rotation direction of the planetary frame 46, but the reduction ratio in the planetary gear unit 40 is such that the planetary frame 46 described above remains stationary. In terms of the reduction ratio, that is, the number of revolutions (speed), Na--Ncx (Zc/
Za) becomes dominant and becomes the standard.

By the way, when the frame 24 is swung clockwise, the bed 2
5 is raised from the horizontal position, the lever 55 of the planetary frame 46 moves to the planetary frame surrounding rotation cam 56 during the initial stage of raising the bed 25 from the horizontal position to a swing angle range of 30 degrees.
The planetary frame 46 is rotated in the same direction as the rotational direction of the sun gear 43 by being swung downwardly, that is, clockwise.

Therefore, the rotational speed of the internal gear 47 of the planetary gear device 40 is reduced from the above-mentioned reference rotational speed, and if the rotational speed of the planetary frame 46 is Nr, the internal gear 47
The rotational speed Na is Na=-Nc-(Zc/Za)+((2dmNr)/(dm+Da)).

In addition, in the swing angle range (0 to 90 degrees) beyond the initial stage of raising and lowering up to 90 degrees, the lever 55 swings upward, that is, counterclockwise, and the planetary frame 46 becomes the sun gear. rotated in the opposite direction. Therefore, the rotational speed of the internal gear 47 is increased from the above-mentioned reference rotational speed, and if the rotational speed of the planetary frame 46 is Nr, the rotational speed of the internal gear 47 is Na.
becomes Na=-Ncx (Zc/Za)-((2dm-Nr/(dm+Da)).

Also, contrary to the above case, when the frame 24 is swung counterclockwise and the bed 25 is raised from the horizontal position,
The bed 25 is slid to the right in the upward direction of its inclination, and the sun gear 43 is rotated counterclockwise. In the swing angle range of the initial stage of collapse, lever 5
5 is swung upwards counterclockwise, and the planet frame 46
is rotated in the same direction as the sun gear 40, and in the swing angle range beyond θ up to 90 degrees, the lever 55 is swung downward clockwise, and the planetary frame 46 is rotated in the opposite direction to the sun gear 40. be rotated. Therefore, as mentioned above, in the swing angle range of the initial stage of raising and lowering θ from the horizontal position, the rotational speed of the internal gear 47 is decelerated, and the rotational speed Na is: Na−−Ncx (Zc/Za) + ((2dm-Nr/ (dm+Da)), and in the swing angle range exceeding θ to 90fli, the rotational speed of the internal gear 47 is increased and the rotational speed Na is Na--Ncx (Zc/Za) - ((2dm-Nr/ (dm+Da)).

Therefore, when the bed 25 is raised from its horizontal position to θ degrees, which is the end of the initial stage of raising, the sleight movement speed relative to the raising angle speed becomes slower than the reference speed and exceeds θ. When the robot is raised up to 90 degrees, the slide movement speed becomes faster than the reference speed.

Therefore, in the interference region at the initial stage of raising and lowering where the bed 25 interferes with the side wall 70, its slide movement speed becomes slow and the amount of lateral overhang becomes small, and as a result, interference with the side wall 70 is reduced as much as possible. be avoided.

At this time, the total value of the slide movement amount is as shown in FIG. 6(b), and the reference reduction ratio of the second gear v1 structure 41 including the planetary gear device 40 is as shown in FIGS. 7 and 8. If the setting is the same as that of the conventional up/down bed device 1, the total amount of slide movement ω can be made the same as that of the conventional device.

On the other hand, when the frame 24 is swung from the horizontal position of the bed 25, the elevating drive cam 66 is also swung together, and the position of engagement with the support shaft 68 of the support body 67 fixed to the base 60 is adjusted. The sliding surface distance becomes longer in the interference region of the initial stage of raising and lowering, which is the range up to the swing angle θ where the bed 25 and the floor surface 32 interfere easily.

As a result, the frame 24, bed 25, pedestal 23, etc. are rapidly moved (lifted) upward against gravity.

Therefore, the interference with the floor surface 22 is avoided as much as possible during the initial stage of the bed 25 rising from the horizontal position where it is likely to interfere with the floor surface 22, and at this time, the weight of the pedestal 23, etc. is transferred to the support body 67. It is supported by the base 60 through the (Fig. 4(a))
b)).

Moreover, when the swing angle exceeds θ, the sliding surface distance gradually becomes shorter, and the distance between the frame 24, the bed 25, and the pedestal 23 decreases.
etc. were slowly moved downwards, and bed 25 was moved to 90.
When the bed 25 is fully erected, the position of the center of rotation of the bed 25 (1z center of motion O of the frame 24) is the same as the height of the bed 25 when it is horizontal.

In other words, the maximum value (L - 11) of the difference in distance from the sliding surface 66a to the center of oscillation O is the maximum lift distance, and the bed 2
When the bed 25 is raised θ degrees from the horizontal position, the bed 25 is lifted upward to the maximum.

In addition, in the tilting mechanism 26 of the bed 25 described above, the bed 25
At the initial stage of standing up, the amount of slide movement relative to the tilting angle of the bed 25 is made smaller than the standard, so the bed 25 moves slightly closer to the floor 22. It is sufficiently absorbed by the elevating drive means 65.

Therefore, we used a bed 25 whose dimensions, such as length, thickness, and height of the center of rotation, were the same as those of the conventional bed shown in FIGS. 7 and 8. The amount of slide movement is set as shown in the figure 6(b), and the lift distance relative to the raising/lowering angle rim of the bed 25 is set as shown in the solid line B in FIG. 6(b). When the raising/lowering bed device 21 of the embodiment is constructed, the rotation locus of the bed 25 will be as shown in FIG. 6<a). Therefore, as shown in the figure, clearances Y4 and (x2-x3) can be obtained between the bed 25 and the floor 22 and between the bed 25 and the side 170. As a result, the height of the bed 25 in the horizontal position can be lowered by the clearance Y4, and the required space in the vertical and horizontal directions can be reduced by the clearance Y ・(×2−×3)
It will be possible to reduce the amount by that amount.

In this embodiment, the conversion point angle for increasing/decelerating the slide movement speed of the bed corresponding to the swing angle of the frame 24 and the conversion point angle for the vertical movement direction of the bed 25 are set to be the same.
In other words, the predetermined swing angle ranges are set to be the same to form the cam profiles of both the planetary frame rotation cam 56 and the elevating drive cam 66, but the settings of the respective predetermined swing angle ranges are not necessarily the same. It is not necessary to make the settings different, and the settings may be made slightly different.

In addition, in FIG. 1, if the shape of the cam profile of the planetary frame rotation cam 56 is made symmetrical by reversing the left and right sides of the illustrated example, the bed 2
5, the slide movement m relative to the tilting angle of the bed 25 can be increased at the initial stage of rising from the horizontal position of the bed 25.
Since interference with the bed 25 can be avoided, the horizontal height of the bed 25 can be significantly lowered.

Further, in this embodiment, the elevating drive means 36 includes an elevating drive cam 66 and a support body 67 that is engaged with the elevating drive cam 66.
The cam 66 for driving up and down is provided integrally with the external gear 27, the support body 67 is integrally formed with the base 60, and a planet interposed in the second gear mechanism 41. Gearbox! Since the lever 55 of the 40 planetary frame 46 is engaged with the groove-shaped planetary frame surrounding diversion cam 56 formed by integrally carving the external gear 27, the elevating bed device 2
2 can be configured as compactly as possible.

(Effects) To summarize, according to the present invention, depending on the swing angle of the frame, the trestle, frame, and The bed and the bed tilting drive device can be integrally moved upward, and when the predetermined angle range is exceeded, the pedestal etc. can be lowered downward. At the same time, the amount of slide movement relative to the tilting angle of the bed can be varied between the horizontal position and the vertical position of the bed depending on the tilting angle of the bed. As a result, the bed can be raised and lowered while avoiding interference between the bed and the floor and side walls as much as possible without increasing the total amount of slide movement of the bed, and the necessary horizontal and vertical installation Space can be reduced as much as possible.

[Brief explanation of the drawing]

Fig. 1 is a front view showing a preferred embodiment of the present invention, Fig. 2 is a view taken along the line ■-■ in Fig. 1, and Fig. 3 is a view taken along the line I--
4(a) is a diagram showing the horizontal state of the bed, FIG. 4(b) is a diagram showing the state raised up to θ, and FIG. 5 is a diagram showing the differential principle of the planetary gear system. Figure 6 (
(a) is a diagram showing the rotation locus of the bed of the tilting bed device of this embodiment, and FIG. Fig. 7 shows a conventional elevating bed device, Fig. 8 (a) shows the rotation locus of a conventional elevating bed @ position, and Fig. 8 (b) shows the elevating angle and sliding movement of the bed. It is a diagram showing the relationship with m. 21... Lifting sleeper W1 23... Frame 24...
Frame 25... Bed 31... First gear mechanism 40... Planetary gear device 41... Second gear mechanism 46... Planetary frame 55... Lever 56
...Planet frame surrounding diversion cam 56a...Groove center 6
0... Base 65... Elevating drive means 66... Elevating drive cam 66a... Sliding surface 67... Support body 0... Swinging center Patent applicant Sankyo Seisakusho Co., Ltd. Agent Person Patent Attorney - Kensuke Iro Patent Attorney Masatoshi Matsumoto Diagram 5 Procedural Amendment (self-imposed March 20, 1985 Commissioner of the Patent Office Black 1) Akio Tono1, Indication of Case Patent Application No. 286722 of 19862, Title of the invention: Folding bed bag type 3, relationship with the case of the person making the amendment Patent applicant address: 3-37-3 Tabata Shinmachi, Kita-ku, Tokyo Name
Sankyo Seisakusho Co., Ltd. Representative Director Ryohei Ogawa 4, Agent Address: 2-12-7 Shinbashi, Minato-ku, Tokyo Telephone: 508
-0336 (Main) 5. Subject of amendment (1) Column 6 of "Detailed Description of the Invention" of the specification, Contents of amendment (1) "30 degrees from the horizontal position" on page 24, line 13 of the specification Correct the statement to read "θ degrees from the horizontal position."

Claims (1)

[Scope of Claims] A frame that supports the bed so as to be able to slide back and forth in the longitudinal direction, a pedestal that pivotally supports the frame so as to be able to swing freely in the longitudinal direction of the bed, and a frame provided on the pedestal that swings the frame. In the raising/lowering bed device comprising a first gear mechanism to drive the bed, and a second gear mechanism provided on the pedestal and operated in synchronization with the first gear mechanism to slide the bed, the pedestal can be moved. is provided with a base that supports the pedestal in a vertically movable manner, and between the base and the frame, a predetermined position is provided between the base and the frame in accordance with the swing angle of the frame. A lifting drive means is provided to move the pedestal upward within a predetermined angular range and to lower the pedestal downward when the predetermined angular range is exceeded, and a planetary gear device is interposed in the second gear mechanism. and a lever for rotating the planet frame is integrally provided on the planet frame of the planetary gear device and projects radially outward, and a swinging end of the lever is engaged with the frame. A tilting bed characterized by being integrally provided with a planetary frame rotation cam that rotates the planetary frame according to the swinging of the frame to vary the amount of sliding movement of the bed with respect to the swinging angle of the frame. Device. (2) The elevating drive means is provided with an elevating drive cam provided on the frame and integrally swung, and slidably engaged with the elevating drive cam and fixed to the base. A cam profile of a distance from the center of swing of each part of the sliding surface of the elevating drive cam that slides on the support body is such that the cam profile of the distance from the center of rotation of the sliding surface of the elevating drive cam that slides on the support body is engaged with the support body in the horizontal position of the bed. The above-mentioned claim is formed such that the swing angle is increased up to a predetermined swing angle range according to the swing angle of the lifting drive cam, and is decreased when the swing angle exceeds the predetermined swing angle range. The raising/lowering bed device according to item 1. (3) The planet frame rotating cam is a groove-shaped cam that is integrally carved into the frame, and the cam profile of the distance from the center of the groove to the center of swing is from the horizontal position of the bed. When the planetary frame is rotated in the same direction as the rotation direction of the sun gear within a predetermined angular range at the initial stage of standing up, the amount of slide movement of the bed relative to the swinging angle of the frame is reduced, and when the predetermined angular range is exceeded. Claims 1 or 2, wherein the planetary frame is rotated in a direction opposite to the rotational direction of the sun gear to increase the amount of slide movement of the bed relative to the amount of swing angle of the frame. The above-mentioned raising/lowering bed device.