CN102311060B - Elevating device - Google Patents
Elevating device Download PDFInfo
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- CN102311060B CN102311060B CN201110176318.1A CN201110176318A CN102311060B CN 102311060 B CN102311060 B CN 102311060B CN 201110176318 A CN201110176318 A CN 201110176318A CN 102311060 B CN102311060 B CN 102311060B
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Abstract
The invention provides an elevating device. The elevating device comprises a pair of upright columns having guide rails extending along the plumb direction, a lifting stand configured between the upright columns and applied for elevation; guide mechanisms equipped on the lifting stand and capable of being clamped on the corresponding guide rail of each upright column in a rolling way, and an elevation driving mechanism supplying elevation driving force to the lifting stand. The lifting stand comprises a pedestal module and a pair of side modules. The guide mechanisms are linearly-moving guide pieces which are connected on the side modules through a spherical bearing.
Description
Technical field
The present invention relates to jacking system article being elevated for tower crane etc.The application to the Japanese patent application 2010-149278 CLAIM OF PRIORITY applied on June 30th, 2010, and quotes its content at this.
Background technology
As the jacking system for tower crane etc., known such jacking system: bay-lift is configured between the column that configures dividually, this bay-lift is suspended to column and makes it be elevated.The both ends of bay-lift are supported on the column of both sides by this jacking system by cable or chain, by making bay-lift oscilaltion by motor traction cable or chain.Such jacking system is provided with the multiple deflector rolls rolled in the side of each column mostly at the both ends of bay-lift, utilize the guide function of these deflector rolls to limit the runout of bay-lift.
In addition, in the prior art, propose the jacking system (for example, referring to Japanese Patent No. 2571013 publication, Japanese Patent No. 3982562 publication and Japanese Patent No. 4013991 publication) of the function of the deviation of the separating distance possessing absorption two column.This jacking system be provided with between the deflector roll maintaining part and the body of bay-lift of bay-lift allow both column between the slide mechanism of slip movement in direction.Thus, even if the separating distance of two columns is uneven a little, moved the lifting action smoothly that also can carry out bay-lift relative to body via slide mechanism by deflector roll maintaining part.
, sometimes such jacking system is equipped on tower crane etc., in order to carry out article transport and use in clean room etc.In such purposes, the dust produced along with action becomes problem, and each parts thus for jacking system expect to be the structure more not easily producing dust.
For such expectation, now, discuss and study adopts dust and the less direct acting guiding element of vibrating noise as the guiding mechanism of bay-lift.In direct acting guiding element, in module, be accommodated with the rolling elements such as multiple roller or ball, these multiple rolling elements always closely contact with multiple spigot surfaces of guide rail.Therefore, the omnidirectional movement orthogonal with the bearing of trend of this guide rail by guide rail of direct acting guiding element is restricted, and the bearing of trend along guide rail carries out action swimmingly.
But the omnidirectional movement orthogonal with this guide rail by guide rail of direct acting guiding element is restricted.Therefore, when the guiding mechanism of jacking system adopts direct acting guiding element, when the parallelism of two guide rails (two columns) and straightness accuracy etc. exist error, the stress of these errors of resulting from can concentrate on direct acting guiding element and guide rail.Especially when under the state that the parallelism of two guide rails and straightness accuracy etc. also exist error, bay-lift carries out lifting action, due to the warpage or crooked and produce elastic deformation at bay-lift self of rail-sides.Large counteraction when producing the elastic deformation reset of this bay-lift acts on the problem of direct acting guiding element and guide rail sharp.And, in large-scale jacking system, the error of the parallelism of two columns and straightness accuracy etc. can not be eliminated completely, thus in fact be difficult to adopt direct acting guiding element.
The present invention considers that such situation is made, and its object is to, and provides a kind of direct acting guiding element that can adopt as the dust of the guiding mechanism of bay-lift or the few jacking system of vibrating noise.
Summary of the invention
The present invention is in order to solve above-mentioned problem and reach described object and adopt following mode.Jacking system of the present invention possesses: a column with the guide rail extended along vertical; Be configured at the bay-lift of lifting between a described column; Be installed on described bay-lift and rollably can be sticked in the guiding mechanism of the guide rail of the correspondence of described each column; And described bay-lift is provided to the lift drive mechanism of lifting propulsive effort.Described bay-lift possesses: extend along direction between described column and in the pedestal module of top mounting article; And a pair side form block at the both ends of bearing of trend between the described column being configured at this pedestal module, the lower end of this each side form block is rotatably linked to the end of the bearing of trend between the described column of described pedestal module.Described each guiding mechanism be multiple rolling element with multiple guide face contacts of corresponding guide rail and the direct acting guiding element that the omnidirectional movement orthogonal with the bearing of trend of described guide rail is restricted, this direct acting guiding element is linked to described each side form block via globe bearing.
According to the jacking system of the invention described above, if bay-lift is subject to propulsive effort from lift drive mechanism, then each direct acting guiding element being linked to the both sides module of bay-lift rolls along the guide rail of each column, lifting of lifting table.Now, when the parallelism of the guide rail due to both sides and straightness accuracy etc. error and produce between two guide rails local warpage or crooked, limited by guide rail and each direct acting guiding element of movement relative to the side form block of the correspondence of bay-lift via globe bearing relatively yaw.Accompany therewith, the side form block of both sides automatically regulates relative to the link angle of the pedestal module of bay-lift.
According to the jacking system of the invention described above, the direct acting guiding element being sticked in the guide rail of each column is linked to the side form block of the correspondence of bay-lift via globe bearing, and the lower end of each side form block and the end of pedestal module of bay-lift can link rotationally.That is, even if due to the error of parallelism and straightness accuracy etc. of the guide rail of both sides and the posture of two guide rails or alteration of form, also allow the yaw of direct acting guiding element by globe bearing, relatively rotating of side form block and pedestal module is also allowed.As a result, can prevent large effect of stress in advance between direct acting guiding element and guide rail.
Especially, in bay-lift, the lower end of side form block is rotatably linked to the both ends of pedestal module.Even if when making lifting of lifting table there is the warpage of local or crooked situation between the guide rails in the error due to the parallelism of two guide rails and straightness accuracy etc. under, to be rotated at the both ends of pedestal module by side form block and also can prevent from producing elastic deformation at bay-lift self.Therefore, it is possible to prevent the large load counteraction of the elastic deformation due to bay-lift caused from acting on direct acting guiding element and guide rail sharp in advance.So, direct acting guiding element can be adopted as the guiding mechanism of bay-lift without undesirable condition, the generation of dust or vibrating noise can be suppressed by direct acting guiding element.
In the jacking system of the invention described above, also can be the lower end of described each side form block be rotatably linked to described pedestal module via globe bearing described column between the end of bearing of trend.
In this case, the rotation of the lower end of side form block relative to the three-dimensional of pedestal module is allowed by globe bearing.
In the jacking system of the invention described above, also can be the lower end of described each side form block be rotatably linked to described pedestal module via fulcrum pin described column between the end of bearing of trend.
In this case, the rotation of the lower end of side form block relative to the two dimension of pedestal module is allowed by rest pin.
In the jacking system of the invention described above, also can be link the direct acting guiding element of stud sides of one and the described globe bearing of described side form block possesses slide mechanism, the relative movement in direction between its column of allowing the column of described bay-lift and one.
In this case, when direct acting guiding element is along the lifting rail of each column, even if the distance variation in direction between the column of two guide rails, the variation of the distance between guide rail is also absorbed by slide mechanism.In addition, between column, the position of the bay-lift in direction is maintained certain with the column with the opposition side of the direct acting guiding element of slide mechanism for benchmark.
In the jacking system of the invention described above, also at two places left up and down of described each side form block, respectively described direct acting guiding element can be set via described globe bearing.
In this case, each side form block of bay-lift follows guide rail via upper and lower direct acting guiding element, automatically regulates the link angle of each side form block and pedestal module.
Accompanying drawing explanation
Fig. 1 is the block diagram of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 2 is the cutaway view in the A-A cross section along Fig. 1 of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 3 is the cutaway view in the B-B cross section along Fig. 2 of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 4 is the block diagram of the car (bay-lift) of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 5 is the amplification view in the C-C cross section along Fig. 2 of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 6 is the amplification view in the D-D cross section along Fig. 2 of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 7 is the enlarged drawing in the E portion of Fig. 3 of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 8 A is the schematic isometric of the car (bay-lift) of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 8 B is the diagrammatic side view of the car (bay-lift) of the tower crane of the jacking system adopting an embodiment of the invention.
Fig. 9 is the diagrammatic side view of the tower crane of the jacking system adopting an embodiment of the invention.
Detailed description of the invention
Below, based on accompanying drawing, one embodiment of the present invention is described.Jacking system of the present invention is applied to tower crane SC by present embodiment.Tower crane SC is used for such as clean room etc., travels being laid on ground track.In the following description, using the moving direction of the track along tower crane SC as X-direction, using the direction orthogonal with X-direction of horizontal direction as Y direction, be described using the vertical orthogonal with X-Y plane as Z-direction.
Fig. 1 is the block diagram of tower crane SC, and Fig. 2, Fig. 3 are the cutaway views of tower crane SC.As shown in these figures, tower crane SC possesses column 20A, 20B for the prism-shaped extended along Z-direction, the bottom of each column 20A, 20B is installed on rectangular box-like base framework 10, and the upper end of each column 20A, 20B is linked by the upper frame 30 extended along the X direction each other.On base framework 10, being provided with the wheel support of rail running is rotatable wheel mounting portion 11.Leave along X-direction between column 20A, 20B, be lifting freely configured with car 40 (bay-lift), on car 40, be provided with shifting apparatus 100 (such as, fork device).
In the lower end of each column 20A, 20B, be respectively provided with one group of drive sprocket 21 (lift drive mechanism), in the upper end of each column 20A, 20B, be respectively provided with one group of driven sprocket 22 (lift drive mechanism).The chain 23 (lift drive mechanism) of supporting car 40 is set up in drive sprocket 21 corresponding on the above-below direction of each column 20A, 20B and driven sprocket 22.In addition, in the lower end of each column 20A, 20B, be provided with the motor 24 (lift drive mechanism) integrated with reductor 25 (with reference to Fig. 3), two (one group) drive sprockets 21 are connected to the outgoing side of reductor 25.In addition, in the present embodiment, the motor 24, drive sprocket 21, driven sprocket 22, chain 23 etc. that are arranged at each column 20A, 20B form lift drive mechanism car 40 (bay-lift) being provided to lifting propulsive effort.In addition, in the present embodiment, two motors 24 being arranged at each column 20A, 20B are controlled as by not shown controller and carry out synchronization action.
In addition, in the mutually opposing side of two column 20A, 20B, be fixedly installed guide rail 26A, 26B of extending along Z-direction (vertical).The guiding mechanism being configured at car 40 side described later is sticked in these each guide rail 26A, 26B.
Fig. 4 is the block diagram representing car 40 and guide rail 26A, 26B, and Fig. 5, Fig. 6 are the cutaway views of the engagement section of car 40 and each guide rail 26A, 26B, and Fig. 7 is the cutaway view of a part for car 40.Car 40 possesses: a pair side form block 28A, the 28B at the both ends of the pedestal module 27 being set with shifting apparatus 100 on top and the X-direction being linked to pedestal module 27.
Pedestal module 27 possesses a pair main frame 27a of the cross section I shape extended along X-direction, is fixedly installed shifting apparatus 100 on the top of these main frames 27a.Therefore, a pair main frame 27a becomes the integrated module of rigidity.In addition, a pair main frame 27a also can replace shifting apparatus 100 and be combined with each other by cross frame and improve intensity.In addition, in each end of the X-direction of main frame 27a, be provided with the connecting part with side form block 28A, 28B.
The frame material of square-section is assembled into roughly triangular shape and forms side form block 28A, 28B.These side form blocks 28A, 28B are (following with one side of roughly triangular shape, being called " following 31 ") on even keel extends and the mode that the across corner on this limit is divided into top sides (hereinafter referred to as " top sides 32 ") is linked to pedestal module 27.At the both ends of following 31 of each side form block 28A, 28B, arrange support 33 with extending downwards, the axle portion 34 of being supported by this each support 33 is rotatably linked to each end of the main frame 27a of pedestal module 27 via globe bearing 35 described later.
In following 31 and the top sides 32 of each side form block 28A, 28B, be respectively equipped with the fulcrum pin 41 outstanding to the direction opposed with guide rail 25A, 25B.Direct acting guiding element 42 (guiding mechanism) is linked to this each fulcrum pin 41 via globe bearing 43 (with reference to Fig. 5, Fig. 6).The globe bearing 43 supported by each fulcrum pin 41 is except be configured at column 20B side following 31, and globe bearing 43 has identical structure.The globe bearing 43 being configured at following 31 of column 20B side carries out distinguishing with other globe bearings 43 and marks the symbol of 43S.
As shown in Figure 5, Figure 6, on each guide rail 26A, 26B, be provided with a pair guide groove 45 along Z-direction, in each guide groove 45, be provided with a pair spigot surface 46a, the 46b with cross one another leaning angle.On the other hand, each direct acting guiding element 42 can be provided with multiple roller (not shown) in the module 48 of general square shape shape loopy moving, and this module 48 is sticked in the outside face of corresponding guide rail 26A, 26B.Multiple rollers in module 48 rollably can be connected to the leaning angle of guide rail 26A, 26B different each spigot surface 46a, 46b.By guide rail 26A, 26B, the omnidirectional movement orthogonal with Z-direction is restricted direct acting guiding element 42, and, along action swimmingly on the direction (Z-direction) of guide rail 26A, 26B.
In addition, in globe bearing 43, as shown in Figure 5, the housing 50 of module 48 bolted joint with direct acting guiding element 42 is provided with cylindric maintaining part 51, in this maintaining part 51, the foreign steamer 52 with the inner peripheral surface caving in into dome shape is installed.Thus, spherical bushing 53 is held in the inner peripheral surface of foreign steamer 52 sliding freely.Spherical bushing 53 is fixed on the outside face of fulcrum pin 41.But, in the globe bearing 43S of following 31 being configured at column 20B side, as shown in Figure 6, at the inner peripheral surface of spherical bushing 53, roughly cylindric slide bushing 54 is installed.Thus, slide bushing 54 axially can slide on fulcrum pin 41.In the present embodiment, this slide bushing 54 and fulcrum pin 41 are slide mechanisms of the relative movement of the X-direction of allowing car 40 (side form block 28B) and column 20B.
The globe bearing 35 adopted at the main frame 27a of aforesaid car 40 and the connecting part of side form block 28A, 28B is structures roughly the same with the globe bearing 43 being installed on direct acting guiding element 42.The connecting part of main frame 27a and side form block 28A is amplified the cutaway view represented by Fig. 7.As shown in the drawing, on the support 33 of side form block 28A (with reference to Fig. 3), axle portion 34 is installed extended, at the outside face in this axle portion 34, spherical bushing 57 is installed.In the end of main frame 27a (with reference to Fig. 3), be provided with the flange part 58 extended upward, this flange part 58 is provided with via hill holder 60 foreign steamer 59 of the inner peripheral surface with dome shape.Spherical bushing 57 in axle portion 34 is held in the inner peripheral surface of foreign steamer 59 sliding freely.
In addition, as depicted in figs. 1 and 2, be set up in the drive sprocket 21 of each column 20A, 20B and be linked to the both ends of the chain 23 of driven sprocket 22 the direct acting guiding element 42 be connected with the upper end of each side form block 28A, 28B and bottom respectively.
Fig. 8 A is the block diagram schematically representing above-mentioned car 40, the lateral plan of action when Fig. 8 B is the lifting schematically representing car 40.Below, with reference to these figure, the lifting action of car 40 is described.Such as, when the car 40 making to be positioned at most lowering position rises, make the motor 24 of the lower end of two column 20A, 20B to a direction rotary actuation, by chain 23 by being connected to both sides module 28A, the direct acting guiding element 42 of upper end of 28B draws high upward.Thus, car 40 is directed and rise to set height along two guide rail 26A, 26B by direct acting guiding element 42.
In addition, when making car 40 decline, motor 24 contrarotation is driven.Thus, car 40 is directed and drop to set height along two guide rail 26A, 26B by direct acting guiding element 42.
Now, the omnidirectional movement that each direct acting guiding element 42 of the both sides of the X-direction of car 40 is orthogonal with the bearing of trend of guide rail 26A, 26B is limited, and moves along guide rail 26A, 26B.But, when the error of the parallelism and straightness accuracy etc. of existence two guide rail 26A, 26B, by the globe bearing 43, the 43S that are clipped between each direct acting guiding element 42 and car 40 (side form block 28A, 28B), suitably bend between each direct acting guiding element 42 and car 40 and allow the relative yaw of each direct acting guiding element 42 relative to car 40.And, in car 40 side, according to the posture of two guide rail 26A, 26B and the change of shape by globe bearing 35 automatically adjusting side mould block 28A, 28B relative to the link angle of pedestal module 27.And, by the axial slip of the slide bushing 54 in globe bearing 43S relative to fulcrum pin 41, allow the relative movement leaving the direct acting guiding element 42 of configuration in the X-axis direction of the variation of the separating distance along with two guide rail 26A, 26B.
As described above, in this tower crane SC, the direct acting guiding element 42 being sticked in each guide rail 26A, 26B is via globe bearing 43,43S and be linked to side form block 28A, 28B of the correspondence of car 40.And each lower end of side form block 28A, 28B and the end of pedestal module 27 can link rotationally via globe bearing 35.Therefore, even if produce warpages or crooked etc. attitude change and alteration of form due to the error of the parallelism of two guide rail 26A, 26B and straightness accuracy etc. at two guide rail 26A, 26B, also can realize the yaw of the direct acting guiding element 42 based on globe bearing 43,43S allow with the lower end of side form block 28A, 28B with the allowing of the rotation of pedestal module 27.Thereby, it is possible to prevent large effect of stress in direct acting guiding element 42 with between guide rail 26A, 26B in advance.
In addition, in this tower crane SC, in the globe bearing 43S of the lower end of car 40, be provided with slide bushing 54 (slide mechanism).Therefore, when the separating distance variation of two guide rail 25A, 26B, slide mechanism absorbs the variation of this distance, and N/R effect of stress can be prevented in direct acting guiding element 42.
In addition, in this tower crane SC, car 40 entirety is not the integrated module of rigidity.This car 40 is made up of the pedestal module 27 of mounting shifting apparatus 100 and point body component that carries out by motor 24 side form block 28A, the 28B being elevated the both sides driven via chain 23, and each lower end of side form block 28A, 28B and the end of pedestal module 27 link via globe bearing 35.Therefore, when making car 40 carry out lifting action there is the warpage of local or crooked situation between guide rail 26A, 26B in the error due to the parallelism of two guide rail 26A, 26B and straightness accuracy etc. under, N/R effect of stress also can be prevented in advance in car 40.
With reference to Fig. 9, concrete example is described.Fig. 9 schematically represents that guide rail 26A, 26B of both sides bend the figure of the action of when (warpage) becomes arcuation, car 40 and direct acting guiding element 42 at the middle section of above-below direction with leaving most.As shown in the solid line in this figure, when car 40 is positioned at more than the middle section of guide rail 26A, 26B, the direct acting guiding element 42 being connected to the top of side form block 28A, 28B follows outside the bending and move in outward direction of guide rail 26A, 26B.As a result, each side form block 28A, 28B are outward-dipping centered by globe bearing 35 relative to pedestal module 27.In addition, as shown in the imaginary line in this figure, when car 40 is positioned at more top than the middle section of guide rail 26A, 26B, the direct acting guiding element 42 being connected to the top of side form block 28A, 28B follows the inside bending of guide rail 26A, 26B and to inward side to movement.As a result, each side form block 28A, 28B slope inwardly centered by globe bearing 35 relative to pedestal module 27.So when car 40 is elevated along guide rail 26A, 26B, side form block 28A, 28B flexibly fascinate the bending part absorbing guide rail 26A, 26B, thus do not produce N/R stress in each portion of car 40.Namely, in this tower crane SC, do not produce at car 40 elastic deformation that stress causes along with the lifting action of car 40, the large load that thus can prevent the counteraction of elastic deformation from causing in advance acts on direct acting guiding element 42 and guide rail 26A, 26B sharp.In addition, in this case, when the lifting action of car 40, side form block 28A, 28B follow guide rail 26A, 26B warpage or crooked and fascinate time, the slide bushing 54 (slide mechanism) being connected to the globe bearing 43 of the bottom of car 40 automatically regulates the separation width of both sides module 28A, 28B.This function also contributes to the lifting action obtaining car 40 smoothly.
So, according to this tower crane SC, N/R effect of stress can be suppressed in the situation of direct acting guiding element 42.Therefore, it is possible to do not adopt dust or the few direct acting guiding element 42 of vibrating noise with not causing the lower degradation undesirable condition in life-span.
In addition, in this tower crane SC, only slide mechanism (slide bushing 54) is set at the globe bearing 43S of the end side of the X-direction of car 40.Therefore, it is possible to by the position of the shifting apparatus 100 on car 40 apart from not having the column 20A of the side of slide mechanism (guide rail 26A) to be maintained certain distance all the time.That is, the position of the shifting apparatus 100 being arranged at car 40 can correctly be managed all the time.
In addition, in this tower crane SC, the upper end of side form block 28A, 28B of car 40 and bottom are sticked in corresponding guide rail 26A, 26B respectively via direct acting guiding element 42.Therefore, it is possible to make side form block 28A, 28B of both sides flexibly follow guide rail 26A, 26B all the time, the pedestal module 27 of car 40 can be made stably to be held in guide rail 26A, 26B.
In addition, when this tower crane SC, linked in the mode that can bend by globe bearing 43,43S between car 40 and each direct acting guiding element 42.Therefore, when tower crane SC mobile starts and the action of mobile when stopping, shifting apparatus 100 time etc., can easily and correctly calculate the load acting on direct acting guiding element 42.This is because, when tower crane SC mobile starts and the load of the mobile X-direction produced when stopping and the load of Y direction that producing when the action of shifting apparatus 100 act on globe bearing 43,43S part without moment.So, the intensity etc. of direct acting guiding element 42 and guide rail 26A, 26B can be set rightly.
In addition, the present invention is not limited to above-mentioned embodiment, can carry out various design modification in the scope not departing from its main idea.Such as, in the above-described embodiment, jacking system of the present invention is applied to the tower crane SC of movement on running rail, but also jacking system can be fixedly installed on floor.In addition, in the above-described embodiment, the lower end of side form block 28A, 28B is linked to the both ends of the X-direction of pedestal module 27 via globe bearing 35, but this connecting part must be not necessarily globe bearing 35.Such as, also pedestal module 27 and side form block 28A, 28B can be linked by the fulcrum pin along Y direction.
Claims (4)
1. a jacking system, possesses:
One column, has the guide rail extended along vertical;
Bay-lift, is configured between a described column and is elevated;
Guiding mechanism, is installed on described bay-lift, rollably can be sticked in the guide rail of the correspondence of each column; And
Lift drive mechanism, provides lifting propulsive effort to described bay-lift, wherein,
Described bay-lift is,
Possess:
Pedestal module, extends along the direction between described column, at top mounting article; With
A pair side form block, the both ends of the bearing of trend between the described column being configured at this pedestal module,
The lower end of each side form block is rotatably linked to the end of the bearing of trend between the described column of described pedestal module via the 1st globe bearing,
Each guiding mechanism is direct acting guiding element, and multiple rolling element is with multiple guide face contacts of corresponding guide rail and the omnidirectional movement orthogonal with the bearing of trend of described guide rail is restricted,
This direct acting guiding element is linked to described each side form block via the 2nd globe bearing,
The lower end of described side form block is made to be linked to described 2nd globe bearing of the described direct acting guiding element of the stud sides of a side and this side form block possesses slide mechanism, the relative movement in direction between the column that this slide mechanism allows the column of described bay-lift and one,
Above-mentioned slide mechanism has: the fulcrum pin arranged highlightedly from the lower end of above-mentioned side form block to the direction opposed with above-mentioned guide rail and the slide bushing that can arrange slidably on above-mentioned fulcrum pin above-mentioned 2nd globe bearing.
2. jacking system according to claim 1, is characterized in that, the lower end of described each side form block replaces the 1st globe bearing and is rotatably linked to the end of the bearing of trend between the described column of described pedestal module via fulcrum pin.
3. jacking system according to claim 1, is characterized in that, at two places left up and down of described each side form block, arranges described direct acting guiding element respectively via described 2nd globe bearing.
4. jacking system according to claim 2, is characterized in that, at two places left up and down of described each side form block, arranges described direct acting guiding element respectively via described 2nd globe bearing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-149278 | 2010-06-30 | ||
| JP2010149278A JP5644213B2 (en) | 2010-06-30 | 2010-06-30 | lift device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102311060A CN102311060A (en) | 2012-01-11 |
| CN102311060B true CN102311060B (en) | 2015-04-01 |
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ID=45424681
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110176318.1A Active CN102311060B (en) | 2010-06-30 | 2011-06-28 | Elevating device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5644213B2 (en) |
| CN (1) | CN102311060B (en) |
| TW (1) | TWI465384B (en) |
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| CN102556891B (en) * | 2011-12-21 | 2013-12-11 | 中汽昌兴（洛阳）机电设备工程有限公司 | Slide lifter |
| JP5920475B2 (en) * | 2012-09-04 | 2016-05-18 | 村田機械株式会社 | Stacker crane |
| CN103803228B (en) * | 2012-11-08 | 2015-11-18 | 沈阳新松机器人自动化股份有限公司 | Jacking system |
| TWI488798B (en) * | 2013-02-01 | 2015-06-21 | Ming Lurn Prec Machine Co Ltd | Vehicle lift transmission mechanism and vehicle lift comprising the same |
| CN103879895A (en) * | 2014-02-21 | 2014-06-25 | 合肥市神雕起重机械有限公司 | Special bridge crane for hoisting aluminum profile |
| CN104444742B (en) * | 2014-10-30 | 2016-08-24 | 浙江吉利控股集团有限公司 | A kind of hoisting tooling |
| JP2018070304A (en) * | 2016-10-26 | 2018-05-10 | 村田機械株式会社 | Stacker crane and method of assembling the same |
| CN111606239A (en) * | 2020-06-28 | 2020-09-01 | 河南卫华特种车辆有限公司 | Heavy type lifting machine with guiding and locking functions |
| CN112405454A (en) * | 2020-10-22 | 2021-02-26 | 东风汽车股份有限公司 | Mechanical type area helping hand goes up and down to install and assists utensil |
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| JP2006036522A (en) * | 2004-07-30 | 2006-02-09 | Hitachi Kiden Kogyo Ltd | Stacker crane |
| JP4013991B1 (en) * | 2006-09-28 | 2007-11-28 | 株式会社Ｉｈｉ | Stacker crane |
| JP4884937B2 (en) * | 2006-11-22 | 2012-02-29 | 株式会社日立プラントテクノロジー | Support structure of linear motion bearing in lifting mechanism |
| JP2009001406A (en) * | 2007-06-25 | 2009-01-08 | Ihi Corp | Stacker crane |
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- 2011-06-29 TW TW100122790A patent/TWI465384B/en active
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| CN2196613Y (en) * | 1993-11-30 | 1995-05-10 | 沈阳飞机制造公司 | Revolving stereo garage |
| JP2571013B2 (en) * | 1994-01-24 | 1997-01-16 | 株式会社ダイフク | Crane lifting carriage guidance device |
| CN1768392A (en) * | 2003-06-27 | 2006-05-03 | 喜开理株式会社 | Supporting unit, and moving table device and linear-motion guiding device using the supporting unit |
| CN2915768Y (en) * | 2006-06-22 | 2007-06-27 | 成都市三极机械有限公司 | Turn over warehouse |
Also Published As
| Publication number | Publication date |
|---|---|
| TW201208970A (en) | 2012-03-01 |
| JP5644213B2 (en) | 2014-12-24 |
| TWI465384B (en) | 2014-12-21 |
| CN102311060A (en) | 2012-01-11 |
| JP2012012152A (en) | 2012-01-19 |
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