CN102092618A - Double-deck elevator - Google Patents
Double-deck elevator Download PDFInfo
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- CN102092618A CN102092618A CN2010105838144A CN201010583814A CN102092618A CN 102092618 A CN102092618 A CN 102092618A CN 2010105838144 A CN2010105838144 A CN 2010105838144A CN 201010583814 A CN201010583814 A CN 201010583814A CN 102092618 A CN102092618 A CN 102092618A
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Abstract
The invention provides a double-deck elevator using a screw mechanism in a storey height adjusting mechanism, and the double-deck elevator inhibits a maximum load effected on the screw mechanism, and makes load uniform, thereby prolonging service lifetime. Cross slide block shaft couplers (7) performing transmission of rotary power around a shaft and allowing relative movement in a shaft direction are used to connect a plurality of screw shafts (4a, 4c) driving an upper part elevator car and a plurality of screw shafts (4b, 4d) driving a lower elevator car, a support load equalization mechanism (8) making a larger-thrust part descend along the shaft direction and the smaller-thrust part ascend along the shaft direction according to thrust sizes is used to support the screw shafts (4b, 4d) driving the lower elevator car, thereby inhibiting the maximum load of the screw mechanism generated by eccentric load of the elevator car, and equalizing load to prolong service lifetime of the screw mechanism.
Description
Technical field
The present invention relates to a kind of double-deck elevator, especially relate to a kind of improvement mechanism with double-deck elevator of floor height adjusting mechanism, wherein this floor height adjusting mechanism uses screw mechanism to carry out the adjustment of floor height.
Background technology
Based on improving transporting power and the consideration that reduces aspects such as occupied area, use the situation of double-deck elevator constantly increasing.Double-deck elevator can be divided into the double-deck elevator with floor height adjustment function and not have the double-deck elevator that floor height is adjusted function.A lot of buildings are for the consideration of appearance and modeling aspect, be arranged to the story height of a part of floor (for example hall of one deck etc.) different with the story height of other floors, when in this building, double-deck elevator being set, need to be provided with double-deck elevator with floor height adjustment function.
Adjust the double-deck elevator of function as having floor height, a kind of scheme is for example disclosed in patent documentation 1, in the scheme of patent documentation 1, adjust distance between the car (lower car) of the car (upper car) of upside and downside by using screw mechanism.Support the screw shaft of upper car and support the hand of spiral that the screw shaft of lower car is configured to separately opposite, for example one to right-hand screw, and one to left-hand screw, so that the moment that acts on the screw shaft by the weight of car is up and down cancelled out each other.Thus, can reduce and carry out floor height and adjust required propulsive effort, thereby can realize the miniaturization and the brownout of drive motor.
The patent documentation 1 open patent 2000-344448 of Japan communique
As described in patent documentation 1, using screw mechanism to carry out the floor height adjustment is a kind of effective method.But because the replacing operation of screw shaft and nut member etc. is relatively more difficult, if the service life of screw mechanism is short, the burden of then maintaining operation will increase.Therefore, become very important problem the service life that how to prolong screw mechanism.
As prolonging screw mechanism a kind of method in service life, can consider to increase the diameter of screw shaft, just use more large-scale screw mechanism, but when this method of employing, exist the weight of screw mechanism to increase and needs are bigger that problem such as space is set.In order when using the screw mechanism identical, to prolong the service life of screw mechanism, can consider to make the support load that acts on a plurality of screw shafts that support lift car to realize equalization with the prior art size.Act on some screw shaft only and having under the situation of bigger support load, the burden that this part screw shaft is born is big, thereby can cause its reduction in service life.
When making the support load equalization of the screw mechanism that supports a lift car, can consider to use differential gear train etc.But, in double-deck elevator, if screw mechanism is set respectively in upper car and lower car, and when two screw shafts are set respectively in each screw mechanism, service life of screw shaft of wherein bearing the maximum support load is the shortest, therefore, this maximum support load will determine the service life of the whole floor height adjusting mechanism in the double-deck elevator.
Summary of the invention
The present invention makes in view of the particularity of the double-deck elevator with the floor height adjusting mechanism that uses screw mechanism, first purpose of the present invention is to provide a kind of double-deck elevator, described double-deck elevator can suppress the maxim of the support load of screw mechanism, thereby can develop towards the direction in service life of further raising floor height adjusting mechanism.
Second purpose of the present invention is to provide a kind of makes the support load of screw mechanism realize equalization energetically, thereby can satisfy the double-deck elevator of long life needs.
The 3rd purpose of the present invention is to provide a kind of power that can save significantly when adjusting floor height, thereby can realize the double-deck elevator of long lifeization.
Other purposes of the present invention are described in detail in following embodiment.
In order to realize above-mentioned first purpose of the present invention, first of double-deck elevator of the present invention is characterised in that, two lift cars with upper and lower settings, and can adjust the interval between upper car and the lower car, in described double-deck elevator, described upper car and described lower car are driven by screw mechanism respectively, a plurality of screw shafts that described upper car is driven are connected by bindiny mechanism with a plurality of screw shafts that described lower car is driven, described bindiny mechanism transmits the rotary power around axle of screw shaft, and allows described axial relatively moving.
Thus, when the required rotary power around axle of driving lift car is delivered to lower car, the transmission of the axial thrust between the car obtains relaxing up and down, so, even Eccentric Load is for example arranged on upper car, also can make the Support Position of upper car that small moving takes place by the micro-displacement (distortion) of screw shaft, make this eccentric load obtain relaxing, thus, can the maximum load of inhibit function on screw mechanism.And, utilization can be in the transmission this point that relaxes above-mentioned axial thrust up and down between the car, can reduce and following carry out equalization floor height required power when adjusting, thereby can make double-deck elevator towards increasing the service life and the direction of saving in power develops to supporting load.
In order to realize above-mentioned second purpose, on the basis of first feature of the invention described above, second of double-deck elevator of the present invention is characterised in that, the described screw mechanism of upper car or lower car has the load of support equalization mechanism, described support load equalization mechanism is according to the magnitude relationship of thrust, the screw shaft that makes the big side of thrust is along axial decline, and the screw shaft that makes the little side of thrust is along axial rising.
Thus, utilization can be in this first feature of transmission that relaxes up and down axial thrust between the car, under the effect of above-mentioned support load equalization mechanism, makes the support load equalization on the screw mechanism that acts on upper car or lower car energetically.
In order to realize above-mentioned the 3rd purpose, on the basis of first feature of the invention described above or second feature, the 3rd of double-deck elevator of the present invention is characterised in that, the described screw mechanism of upper car and lower car is made of the rolling screw mechanism that carries out load transfer by rolling body between nut member that supports lift car and screw shaft.
Thus, by the service life that prolongs screw mechanism, that utilizes above-mentioned rolling screw mechanism is used for reducing frictional loss, raising will rotatablely move when being transformed to motion of translation mechanical efficiency forward efficiency (positive efficiency) and motion of translation is transformed to mechanical efficiency adverse efficiency (reverse efficiency) when rotatablely moving, thus, at the screw shaft of the screw mechanism that will drive upper car with to drive the hand of spiral that the screw shaft of the screw mechanism of lower car is configured to separately opposite, for example one to right-hand screw, one under the situation of left-hand screw, the weight of upper car and lower car is cancelled out each other, the required power of difference weight lifting between the load weight that required power when adjusting floor height is become make upper car and the load weight of lower car, thus can saving in power.
Except above-described feature, in the embodiment of the following stated, also disclose and realized the required scheme of practicability, these features are described in detail in embodiment described later.
The invention effect
According to the present invention, in double-deck elevator with the floor height adjusting mechanism that uses screw mechanism, the maxim that can suppress the support load of screw mechanism, thereby can prolong the service life of floor height adjusting mechanism, in addition, support the load equalization by making up to make energetically with support load equalization mechanism, and by screw mechanism being arranged to rolling screw mechanism, can also improve drive efficiency, so can alleviate the intensity of maintenance examination operation, thereby can realize and to increase the service life, again the double-deck elevator that can raise the efficiency.
Description of drawings
What Fig. 1 had been to use elevator of the present invention is provided with near the place a part of wall and the scheme drawing of floor.
Fig. 2 is the scheme drawing that the floor height of expression double-deck elevator involved in the present invention is adjusted overview.
Fig. 3 is the double-deck elevator of one embodiment of the invention and the block diagram of floor height adjusting mechanism.
Fig. 4 is the partial enlarged drawing of the floor height adjusting mechanism of Fig. 3.
Fig. 5 is the constructional drawing of the Hooke's coupling mechanism (gimbal mechanism) of Fig. 3.
Fig. 6 is the constructional drawing of the sliding cross coupling (Oldham coupling) of Fig. 3.
Fig. 7 is the front view of the support load equalization mechanism of Fig. 3.
Fig. 8 is the partial perspective view of the support load equalization mechanism of Fig. 3.
Fig. 9 is the expansion drawing of the anti-locking mechanism of eccentric load of Fig. 3.
Figure 10 is the block diagram of the drive part of the related differential gear train of second embodiment of the present invention.
Figure 11 is the block diagram of the connecting bridge of the related screw shaft of second embodiment of the present invention.
Figure 12 is the block diagram of the related support load equalization mechanism of second embodiment of the present invention.
Nomenclature
1 double-deck elevator
2 floor height adjusting mechanisms
3 Hooke's coupling mechanisms
4 screw shafts
5 eccentric loads are prevented locking mechanism
6 nut members
7 sliding cross couplings
8 support load equalization mechanism
The wall of 9 buildings and the part of floor
11 main guide rails
12 external frame
13 lift cars
14 floors
Side rails in 15
16 guide boots
17 guide rollers
18 upper frame portion
19 central frame parts
21 drive motors
31 Hooke's coupling mechanism frameworks
32 Hooke's coupling mechanism frameworks
33 intermediate members
34 S. A.s
51 intermediate members
52 sliding components
53 connecting pin members
71,72 fastened components
73 intermediate members
81 Hooke's coupling mechanisms
The support of 82 L word shapes
83 load-carrying elements
84,85 axostylus axostyles
The support of 86 T word shapes
87 bar members
The floor of 91 buildings
The floor side elevator door of 92 buildings
The specific embodiment
Followingly embodiments of the present invention are described with reference to accompanying drawing.In the embodiment of the following stated, to except that having used first feature of the present invention, the double-deck elevator of also having used second feature and the 3rd feature is illustrated.Certainly, each feature of the present invention can realize independently, and the present invention is not limited in these embodiment.
Embodiment 1
Fig. 1 to Fig. 9 is one embodiment of the invention, represents first embodiment.
Fig. 1 illustrates near a part of wall and the floor the elevator lobby of the building that is provided with double-deck elevator of the present invention.Building 9 has floor 91 at each floor, and has for taking advantage of the floor side elevator door of using into lift car 92 at each floor.1 layer story height of building 9 is than the story height height of other floor, for example the lower car of double-deck elevator rests in one deck, upper car when upper car rests in two layers and the interval between the lower car rest in five layers with lower car, upper car when upper car rests in six floors and the interval difference between the lower car.
Fig. 2 illustrates building shown in Figure 19 and the double-deck elevator 1 that is arranged in this building 9.Double-deck elevator 1 among Fig. 2 has external frame 12, upper car 13a, lower car 13b and guide roller 17, and wherein guide roller 17 is arranged on the external frame 12.Main guide rail 11 in the guide roller 17 of double-deck elevator 1 and the hoist trunk that is arranged on building 9 engages, thereby makes lift car carry out lifting along this main guide rail 11 in hoist trunk.
The lower car 13b of Fig. 2 (a) expression double-deck elevator 1 rests in the 1st building, and the situation of upper car 13a when resting in the 2nd buildings.The lower car 13b of Fig. 2 (b) expression double-deck elevator 1 rests in the 5th buildings, the situation when upper car 13a rests in the 6th buildings.As shown in Figure 2, when double-deck elevator 1 rests in the different floor of story height, need adjust the distance between upper car 13a and the lower car 13b.
Fig. 3 illustrates the double-deck elevator 1 as first embodiment of the present invention.Fig. 3 (a) represents double-deck elevator 1, the floor height setting device 2 in Fig. 3 (b) expression double-deck elevator 1.Double-deck elevator 1 mainly has external frame 12, upper car 13a, lower car 13b, be arranged on guide boot 16a on the upper car 13a, be arranged on guide boot 16b on the lower car 13b, be arranged on the external frame 12 be used for to upper car 13a channeling conduct interior side rails 15a, be arranged on the external frame 12 be used for to lower car 13b channeling conduct interior side rails 15b, be arranged on guide roller 17 and floor height setting device 2 on the external frame 12. Guide boot 16a and 16b engage with interior side rails 15a and 15b respectively, and thus, upper car 13a and lower car 13b can externally carry out moving of above-below direction in the framework 12 along interior side rails 15a and 15b.
Shown in Fig. 3 (b), floor height setting device 2 has: respectively with screw shaft 4a that constitutes the screw mechanism that supports upper car 13a and nut member 6a and the 6c (Fig. 4) that 4c screws togather, respectively with screw shaft 4b that constitutes the screw mechanism that supports lower car 13b and nut member 6b and the 6d (Fig. 4) that 4d screws togather, be arranged on the Hooke's coupling mechanism 3 of the upper end of screw shaft 4a and 4c, be separately positioned on the floor 14a and the 14b of the bottom of upper car 13a and lower car 13b, be separately positioned on the anti-locking mechanism 5 of eccentric load between nut member and the floor, be arranged on the sliding cross coupling 7 between screw shaft 4a and the 4b and between screw shaft 4c and the 4d, thereby the drive motor 21a that screw shaft 4a and 4b is rotated lift car is driven up and down by gear, thereby the load equalization mechanism 8 of the support load equalization of drive motor 21b that screw shaft 4c and 4d is rotated car is driven up and down by gear and the screw mechanism that will support lower car 13b.
Floor height setting device 2 makes the screw shaft rotation by drive motor 21a and 21b, so that floor 14a and the 14b to coupling nut's member drives at above-below direction, at above-below direction upper car 13a and the lower car 13b that is respectively arranged with floor 14a and 14b driven thus, the distance between the car is up and down adjusted.Thus, constitute double-deck elevator with floor height adjustment function.
Fig. 4 is the partial enlarged drawing of floor height setting device 2, and Fig. 4 (a) represents front view, and Fig. 4 (b) represents left side view.The hand of spiral that screw shaft 4a and 4b and screw shaft 4c and 4d are configured to respectively separately is opposite, makes one of them screw axial right-hand screw, another screw axial left-hand screw.Therefore, make screw shaft when rotation by drive motor 21a and 21b, upper car 13a overcome gravity and towards above under driven situation, lower car 13b under the effect of gravity along with screw shaft 4b, the rotation of 4d and descending.At this moment, screw shaft 4b, the hand of rotation of 4d with by screw shaft 4a, the hand of rotation when 4c drives upper car 13a towards the top is identical.Therefore, lower car 13b makes screw shaft 4b under the effect of gravity, the 4d rotation, and this rotation becomes the part of the propulsive effort that upper car 13a is driven towards the top.Therefore, the propulsive effort that drive motor 21a, the propulsive effort that 21b produced can be when driving upper car 13a separately is littler, and its result does not need to use large-scale drive motor.Lower car 13a by towards above when driving too, upper car 13a makes screw shaft 4a under the effect of gravity, the 4c rotation, this rotation becomes the part of the propulsive effort that drives lower car 13b.According to said structure, can pass through drive motor 21a, 21b make up and down car mutually near or mutually away from, can adjust the distance between the car up and down.Thus, can constitute double-deck elevator by floor height setting device 2 with floor height adjustment function.
The propulsive effort that is produced by drive motor 21a and 21b is passed on screw shaft 4a and the 4c by gear and Hooke's coupling mechanism 3.The propulsive effort of screw shaft 4a and 4c is delivered on the 14a of floor by nut member 6a and 6c and the anti-locking mechanism 5 of eccentric load, thereby the upper car 13a that is provided with floor 14a is driven.In addition, the propulsive effort that is delivered to screw shaft 4a and 4c also is passed to sliding cross coupling 7 when being passed to nut member 6a and 6c.The propulsive effort that is delivered to sliding cross coupling 7 is passed to screw shaft 4b and 4d by supporting load equalization mechanism 8, thereby drives by nut member 6b and 6d and the anti-5 couples of floor 14b of locking mechanism of eccentric load and the lower car 13b that is arranged on the 14b of floor.
Fig. 5 illustrates Hooke's coupling mechanism 3, and Fig. 5 (a) is an assembly drawing, and Fig. 5 (b) is an expansion drawing.Hooke's coupling mechanism 3 has 2 groups of S. A.s 34,35 that intersect vertically, and each S. A. 34,35 is supported on respectively on the intermediate member 33.In addition, the framework 31 of Hooke's coupling mechanism is supported by S. A. 34, and the framework 32 of Hooke's coupling mechanism is supported by S. A. 35, thereby makes that the framework 31 and 32 of Hooke's coupling mechanism can be relatively towards direction inclination arbitrarily.By on the framework 31 of Hooke's coupling mechanism, connecting turning cylinder, connecting screw rod axle 4a (perhaps 4c) on the framework 32 of Hooke's coupling mechanism, screw shaft 4a can be that swing at the center with the imaginary intersection point of S. A. 34 and 35 these 2 groups of axles with respect to turning cylinder.
Fig. 6 illustrates sliding cross coupling 7.Sliding cross coupling 7 comprises the fastened component 71,72 that has the intermediate member 73 that is arranged on 2 groups of recesses on the direction that intersects vertically and have the protuberance that engages with 2 groups of recesses of intermediate member 73 respectively.When fastened component 71 pivoted, the recess of the protuberance of fastened component 71 and intermediate member 73 came in contact, and made intermediate member 73 be rotated too.When intermediate member 73 was rotated, the protuberance of the recess of intermediate member 73 and fastened component 72 came in contact, and made fastened component 72 be rotated too.In addition, the recess of the protuberance of fastened component 71,72 and intermediate member 73 has the gap in the axial direction, thus can transmitter shaft to power.Therefore, fastened component 71 and fastened component 72 only be configured to can transferring rotational motion and can transmitter shaft to power, just can not transmit thrust.And fastened component 71,72 can be with respect to intermediate member moving on radial direction along the form of recess, and also can transferring rotational motion under situation movably.Thus, even skew has appearred in the S. A. of fastened component 71 and 72 on radial direction, also can transferring rotational motion.
Be connected with the screw shaft 4a (perhaps 4c) of the screw mechanism that drives upper car 13a on the fastened component 71, be connected with the screw shaft 4b (perhaps 4d) of the screw mechanism that drives lower car 13b on the fastened component 72, and screw shaft 4a (perhaps 4c) and screw shaft 4b (perhaps 4d) are supported on rotatably on the upper frame portion 18 and central frame part 19 of external frame by thrust baring respectively.According to this structure, the support load that acts on the screw shaft 4a (perhaps 4c) is born by upper frame portion 18, the support load that acts on the screw shaft 4b (perhaps 4d) is then born by central frame part 19, therefore, screw shaft 4a (perhaps 4c) and screw shaft 4b (perhaps 4d) can transmitter shaft to the support load, and only can transmit moment of rotation around screw shaft.In addition, the Hooke's coupling mechanism 3 on the top by being connected screw shaft 4a (perhaps 4c), screw shaft 4a (perhaps 4c) can be that the center is swung the bottom with top.And screw shaft 4a (perhaps 4c) and these two S. A.s of screw shaft 4b (perhaps 4d) are owing to the small skew that this swing produces can absorb by sliding cross coupling 7.
Fig. 7 and Fig. 8 illustrate supporting load equalization mechanism 8.Fig. 7 represents to support the front view of load equalization mechanism 8.Support support 82, load-carrying element 83, axostylus axostyle 84 that load equalization mechanism 8 has Hooke's coupling mechanism 81, L word shape, 85, the support 86 of T word shape and bar member 87, except bar member 87, other member is divided into two groups of two ends that are arranged on bar member 87 symmetrically.Load-carrying element 83 is arranged on the central frame part 19 of external frame 12, supports the support 82 of L word shape by axostylus axostyle 84.The support 82 of L word shape has three holes rotatably supporting axostylus axostyle, and three holes are respectively as force, fulcrum and point of action performance function.The hole of inserting for axostylus axostyle 84 has the function of fulcrum, and its support 82 that is constructed such that the L word shape is that the center is rotated with axostylus axostyle 84.Hole as the force performance function of the support 82 of L word shape is connected with Hooke's coupling mechanism 81, and this Hooke's coupling mechanism 81 supports the screw shaft 4b (perhaps 4d) (omission illustrates) that lower car 13b is driven by thrust baring.Therefore, making masterpiece be used on the force of support 82 of L word shape by acting on support load on the screw shaft 4b (perhaps 4d), is the power of center rotation thereby produce with the fulcrum.But, because the support 86 of bar member 87 by axostylus axostyle 85 and T word shape is connected in the hole as the point of action performance function of the support 82 of L word shape, and be connected with the support 82 of L word shape symmetrically at the two ends of bar member 87, therefore, the point of action of the support 82 by bar member 87 bonded assembly L word shapes suffers restraints, make these point of actions each other not can away from.Its result, the support 82 of L word shape makes the power of support 82 rotations that impel the L word shape finally keep balance by bar member 87, so the rotation of the support 82 of L word shape is prevented from.
Fig. 8 is the partial perspective view that load equalization mechanism 8 is supported in expression.In Fig. 8,, show its a part of partial cross section in order to represent the inner case of Hooke's coupling mechanism 81.Hooke's coupling mechanism 81 has inboard Hooke's coupling mechanism framework 811, outside Hooke's coupling mechanism framework 812, S. A. 813 and 814.Inboard Hooke's coupling mechanism framework 811 is by thrust baring and radial bearing studdle axle 4b (perhaps 4d) (illustrating among the figure).S. A. 813 connects inboard Hooke's coupling mechanism's framework 811 and outside Hooke's coupling mechanism framework 812 by rotation to (revolute pairs), and S. A. 814 is by rotating connecting the support 82 of outside Hooke's coupling mechanism's framework 812 and L word shape.In addition, the S. A. that is installed into separately of S. A. 813 and S. A. 814 intersects vertically.Thus, the support 82 of L word shape and inboard Hooke's coupling mechanism framework 811 can be relatively tilt towards direction arbitrarily, and the screw shaft 4b (perhaps 4d) that is installed on the inboard Hooke's coupling mechanism framework 813 can be that swing at the center with the imaginary intersection point of the S. A. of S. A. 813 and S. A. 814.
Below the function that supports load equalization mechanism 8 is described.In the support load of screw shaft 4b that drives lower car 13b and screw shaft 4d not simultaneously, this support load is dwindled according to certain ratio by the support 82 of each L word shape, and the point of action of the support 82 of each L word shape is held the equilibrium of forces of bar member 87 and broken.Therefore, the force of the support 82 of each L word shape is subjected to displacement at above-below direction.For example, during greater than the support load of screw shaft 4d, screw shaft 4b is along axial decline in the support load of screw shaft 4b, and screw shaft 4d is along axial rising.After axial decline, the support load that acts on the screw shaft 4b reduces at screw shaft 4b, and on the contrary, after axial rising, the support load that acts on the screw shaft 4d increases at screw shaft 4d.This is because the inclination of lower car 13b is limited by interior side rails 15b, and has only the screw shaft 4b of the weight that supports lower car 13b, the cause that 4d moves up and down.Its result equates and on the position of keeping in balance, the displacement of the above-below direction of screw shaft stops in the support load separately of screw shaft 4b and screw shaft 4d.That is to say, by the screw shaft 4b of the 8 feasible driving lower car 13b of support load equalization mechanism and the support load equalization automatically of screw shaft 4d.
Fig. 9 illustrates the anti-locking mechanism 5 of eccentric load, and Fig. 9 (a) represents assembly drawing, and Fig. 9 (b) represents expansion drawing.Component part as the anti-locking mechanism 5 of eccentric load comprises 4 sliding components 52 and intermediate member 51, described 4 sliding components are made of the peaceful face portion of convex surface part, be shaped as and roughly be semi-cylindrical form and partly have sliding surface at convex surface, described intermediate member 51 in the form of a ring, offer the cylinder-shaped hole that passes for screw shaft, and the convex curved surface that has with sliding component 52 divides corresponding concave curved surface branch.In addition, the connecting pin member 53 that is used for coupling nut's member 6a (perhaps 6b) and floor 14a (perhaps 14b) is installed in the sliding component 52.The anti-locking mechanism 5 of eccentric load is configured to make the concave curved surface phase-splitting mutual connection of the convex surface part of sliding component 52 and intermediate member 51 to touch and slides, and carries out wobbling action by these contact portions are slided at the circumferencial direction of semicircle.In addition, the concave curved surface of intermediate member 51 partly is respectively formed at the upper surface and the lower surface of intermediate member 51, is respectively arranged with sliding component 52 on upper surface and lower surface.Oscillating axle when sliding component 52 carries out wobbling action is constituted as the oscillating axle that makes the upper surface that is separately positioned on intermediate member 51 and the sliding component on the lower surface 52 and is being positioned on the direction that intersects vertically when axially looking.Thus, with the upper surface that is arranged on intermediate member 51 on sliding component 52 bonded assembly floor 14a (perhaps 14b) with the lower surface that is arranged on intermediate member 51 on sliding component 52 bonded assembly nut member 6a (perhaps 6b) being connected towards any direction bevelled mode.In addition, sliding component 52 is connected by connecting pin member 53 with floor 14a (perhaps 14b) and nut member 6a (perhaps 6b), and nut member 6a (perhaps 6b) is prevented from respect to the rotation of floor 14a (perhaps 14b).Therefore, by make screw shaft 4a (perhaps 4b, 4c, 4d) rotation, nut member 6a (perhaps 6b) carries out motion of translation at above-below direction, can drive upper car 13a (perhaps lower car 13b) thus when driving floor 14a (perhaps 14b).
By the anti-locking mechanism 5 of eccentric load is inserted between nut member 6a (perhaps 6b) and the floor 14a (perhaps 14b), even inclination has taken place in nut member 6a (perhaps 6b) and floor 14a (perhaps 14b), nut member 6a (perhaps 6b) can not produce edge load (edge load) yet, can prevent that therefore nut member 6a (perhaps 6b) from producing eccentric load.In addition, the anti-locking mechanism 5 of eccentric load have with can be by two S. A.s intersecting vertically with posture bevelled Hooke's coupling mechanism identical functions arbitrarily, but owing to adopted is not that shear-loaded is acted on the S. A., but make compressive load act on structure on the S. A., so more favourable aspect intensity.In addition, by S. A. being arranged to half-terete sliding component, can realize slimming.
Fig. 1 to first embodiment shown in Figure 9 owing to having adopted said structure to have following feature.
At first, allowing to drive up and down, the screw shaft of car relatively moves in the axial direction.Owing to drive the screw shaft 4a of upper car 13a, the end portion of 4c connects by sliding cross coupling 7, therefore can with the screw shaft 4b that drives lower car 13b, relatively move in the axial direction between the 4d, can cut off or relax the transmission of thrust thus.Therefore, under the eccentric load of upper car 13a makes the situation on load centralization some in the nut member 6a of screw shaft 4a and 4c and 6c of supporting, the elongation difference that produces by the distortion because of screw shaft 4a or 4c etc. makes the Support Position of nut member 6a or 6c etc. that micro displacement take place, thereby can relax load centralization in specific nut member 6a or the phenomenon on the 6c.In addition, screw shaft 4a that drives upper car 13a or 4c and drive the screw shaft 4b of lower car 13b or 4d between do not carry out under the situation that thrust transmits, the load equalization can be between screw shaft 4a that drives upper car 13a and 4c, realized supporting, the load equalization can also be between screw shaft 4b that drives lower car 13b and 4d, realized supporting simultaneously.If thrust is transmitted between screw shaft, then be difficult to driving between two screw shafts of upper car and driving the equalization that realizes supporting load between two screw shafts of lower car simultaneously.
The second, avoid car is up and down carried out excessive constraint.In screw shaft 4a and 4b and screw shaft 4c and 4d, no matter be used to drive the screw shaft of upper car 13a or the screw shaft that is used to drive lower car 13b, its upper part is by Hooke's coupling mechanism supports (screw shaft 4a, 4c is supported by Hooke's coupling mechanism 3, screw shaft 4b, 4d is supported by Hooke's coupling mechanism 81).In addition, as mentioned above, drive the screw shaft 4a of upper car 13a, the end portion of 4c connects by sliding cross coupling 7, so also be not activated the screw shaft 4b of lower car 13b, the constraint of 4d in the axle right angle orientation.Screw shaft 4b, the end portion of 4d is fully freely towards the mobile of axle right angle orientation.That is to say that all screw shafts all can be that fulcrum is gone up swing in any direction with the Hooke's coupling mechanism that is installed in the upper part.
Therefore, with each nut member 6a that each screw shaft screws togather, 6b only is subjected to the constraint of car position up and down on the axle right angle orientation.So, in the horizontal direction, side rails 15a in car only is subjected to up and down, the constraint of 15b, and be not subjected to the constraint of screw mechanism.Therefore, can avoiding up and down, car is exceedingly retrained.
If car is subjected to guide rail and the constraint of screw mechanism two-fold in the horizontal direction up and down, then can cause having excessive load to act on the screw mechanism in the horizontal direction, and the service life that will reduce screw mechanism if this occurs widely.According to this structure, car is exceedingly retrained owing to avoided up and down, acts on the screw mechanism so can prevent the load of horizontal direction, thereby descends the service life that can prevent screw mechanism.As not allowing the load of horizontal direction act on method on the screw mechanism, also can adopt with nut member and up and down car be mounted in the horizontal direction can displacement structure, if employing said structure, then nut member and up and down the contact portion of car have sliding surface, nut member is by sliding to carry out displacement with respect to car up and down on sliding surface.
At this moment, the friction of sliding surface is big more, and then friction drag is also big more, and big friction drag component acts directly on the nut member as the load of horizontal direction.In contrast to this, it is not to allow up and down car and nut member carry out displacement that this structure has adopted, but nut member is connected up and down on the car, make whole screw mechanism carry out the structure of displacement in the horizontal direction, sliding surface is the periphery of the S. A. of Hooke's coupling mechanism.In addition, by Hooke's coupling mechanism is installed in the upper end of screw shaft, and makes and have fully big distance between Hooke's coupling mechanism and the nut member, therefore, even displacement has taken place nut member in the horizontal direction, also the pivot angle of screw shaft can be remained on very little angle.Therefore, it is minimum that sliding distance becomes, and friction drag is also little.Therefore, can reduce the load that is created in the horizontal direction on the nut member.
The 3rd, prevent the eccentric load that acts on the screw mechanism.When car generation eccentric load up and down, because car (restriction occurs in the loosening scope to bevelled at interior side rails) run-off the straight up and down, relative tilt takes place in also run-off the straight of floor 14a (perhaps 14b), so floor 14a (perhaps 14b) simultaneously and nut member 6a (perhaps 6b).If floor and nut member be direct contact under the state that relative tilt takes place, then produce the edge load in contact part branch, make on nut member, to produce eccentric load, may cause shorten significantly service life.In this structure, between floor and nut member, insert the anti-locking mechanism 5 of eccentric load, absorb the inclination of floor and nut member by the anti-locking mechanism 5 of this eccentric load, so can prevent the generation of edge load.In addition, even do not produce eccentric load up and down on the car, also might swing because of Hooke's coupling mechanism causes screw shaft, make floor and nut member run-off the straight, but in this structure, because tilting, this is also absorbed, so can prevent from nut member, to produce eccentric load by the anti-locking mechanism 5 of eccentric load.
The 4th, make the support load that acts on the screw mechanism that each car is up and down driven respectively realize equalization energetically.Under the effect of supporting load equalization mechanism 8, act on the screw shaft 4b of the screw mechanism that drives lower car 13b and the support load on the 4d by equalization.And, in the driving of screw shaft 4a and 4b and in the driving of screw shaft 4c and 4d, using identical induction motor (IM) respectively, the voltage of these two induction motor (IM) green phase same frequencys is driven.
According to this structure, drive the skidding of skidding of the induction motor (IM) of the big screw shaft of load power greater than the induction motor (IM) that drives the little screw shaft of load power, therefore, the rotation of the induction motor (IM) of the screw shaft that driving load power is big is slack-off, and the rotation of the opposing party's induction motor (IM) accelerates.Therefore, be supplied to screw shaft 4a and 4b propulsive effort and be supplied to the propulsive effort of screw shaft 4c and 4d to become equal.And, by being connected with sliding cross coupling 7 between screw shaft 4a and the 4b and between screw shaft 4c and the 4d respectively, thereby formed the structure of only rotary power being transmitted and the thrust of screw axial not being transmitted.
Therefore, the support load that acts on the screw shaft 4a (perhaps 4c) can not have influence on the screw shaft 4b (perhaps 4d), and the support load that acts on the screw shaft 4b (perhaps 4d) can not have influence on the screw shaft 4a (perhaps 4c) yet.At this, because under the effect of supporting load equalization mechanism 8, the propulsive effort of screw shaft 4b and screw shaft 4d also becomes equal, therefore, its result makes the propulsive effort of screw shaft 4a and screw shaft 4c also become equal.So, by using two induction motor (IMies, support load equalization mechanism 8 and sliding cross coupling 7 simultaneously by the voltage driving of same frequency, can make the propulsive effort of two screw mechanisms that drive upper car 13a realize equalization, can also make the propulsive effort of two screw mechanisms that drive lower car 13b also realize equalization simultaneously.By making the propulsive effort equalization that acts on the screw mechanism, can prevent that only acting on the phenomenon that heavy load is arranged on a side screw mechanism occurs, and the load that acts on the screw mechanism can be controlled in the required Min., so can prolong the service life of screw mechanism.
At last, using the rolling screw mechanism that is provided with rotor aspect nut member that supports lift car and the load transfer between the screw shaft, making and when increasing the service life, reduce frictional loss.The screw shaft 4a and the 4c that support upper car 13a are opposite with the hand of spiral that screw shaft 4b and the 4d of support lower car 13b are configured to separately, thereby can offset mutual weight.At this moment,, then be difficult to rely on the weight of lift car that nut member is pressed, thereby be difficult to make the screw shaft rotation by the weight of lift car if the adverse efficiency of screw mechanism is low.
In the floor height adjusting mechanism of present embodiment, when floor height is adjusted, the lift car of decline side under the effect of gravity towards below descend, make nut member carry out motion of translation by this decline, thus screw shaft is rotated driving.Become the part of propulsive effort of the lift car of upthrow side by the power that the rotation of this screw shaft is produced, can dwindle and be used to make the required propulsive effort of lift car rising, its result can dwindle required motor capacity.
Wherein, if the adverse efficiency of screw mechanism is low, the lift car of the side that then descends can't be rotated driving to screw shaft, thereby can't the propulsive effort of the lift car of upthrow side be compensated.Therefore, screw mechanism preferably adopts the high rolling screw mechanism of adverse efficiency.
But, when adopting rolling screw mechanism, because rolling body bears compressing stress repeatedly during rolling between screw shaft and the nut member, because of fatigue of material the problem that layering is peeled off takes place so exist easily.The service life (life-span is peeled off in layering) of decision rolling screw mechanism is peeled off in layering, and 3 powers (when rolling body is spheroid) or 10/3 power (when rolling body is roller) that life-span and the load of effect are generally speaking peeled off in known this layering are inversely proportional to.That is to say, be 2 times if support load, then will be reduced to about 1/10 service life.
As mentioned above, can sharply descend the service life of rolling screw mechanism when supporting the load increase, and therefore, the increase of supporting load will produce unfavorable result.But as described in present embodiment, act on maximum load on the nut member, perhaps form unitized construction, can in the power that reduces when adjusting floor height, prolong the service life of screw mechanism with equalization mechanism by reduction.
Figure 10 to Figure 12 represents second embodiment of the present invention.Second embodiment has been compared following difference with first embodiment, in second embodiment, use differential gear train to replace two induction motor (IMies, use two Hooke's coupling mechanisms and slide key to replace sliding cross coupling, and use scale mechanism to be used as supporting load equalization mechanism or the like, but the function of second embodiment is identical with the function of first embodiment.Following is that the center describes with reference to accompanying drawing with the part different with first embodiment.
Figure 10 illustrates the drive part that adopts differential gear train.Drive part has drive motor 210 and differential gear train 211, and the moment of rotation that drive motor 210 is produced is passed through to distribute equably about differential gear train 211 quilts, and is passed to turning cylinder 212 by cone gear.Turning cylinder 212 is connected (omitting diagram) by Hooke's coupling mechanism with screw shaft.Because moment of rotation distributed equably by differential gear train 211,, can make the propulsive effort equalization of screw shaft 4a and 4b and screw shaft 4c and 4d so the occasion of two induction motor (IMies that drive with the voltage that uses same frequency is the same.Its result, the enough differential gear trains of energy replace two induction motor (IMies of the voltage driving of green phase same frequency.
Figure 11 illustrates the connecting bridge of the screw shaft that uses two Hooke's coupling mechanisms and slide key.Connecting bridge at screw shaft 4a (perhaps 4c) and screw shaft 4b (perhaps 4d) has two Hooke's coupling mechanisms 3 and slide key 70, replaces sliding cross coupling thus.Under the effect of two Hooke's coupling mechanisms 3, screw shaft 4a (perhaps 4c) and screw shaft 4b (perhaps 4d) can be at the enterprising line displacements of axle right angle orientation, and under the effect of slide key 70, screw shaft 4a (perhaps 4c) and screw shaft 4b (perhaps 4d) can also axially carry out displacement, therefore, the same with the occasion of sliding cross coupling, can absorb screw shaft 4a (perhaps 4c) that the swing owing to the screw shaft 4a (perhaps 4c) that drives upper car produces and the skew of screw shaft 4b (perhaps 4d).And, because the rotation around axle suffers restraints under the effect of slide key 70, so can form the structure of axial thrust not being transmitted and only moment of rotation being transmitted.Its result, enough two Hooke's coupling mechanisms of energy and slide key replace sliding cross coupling.
Figure 12 illustrates the support load equalization mechanism in second embodiment.Support mechanism loading in second embodiment has Hooke's coupling mechanism 810, balance bracket 820, load-carrying element 830 and axostylus axostyle 840.Be used to drive the screw shaft 4b of lower car, 4d is connected (omitting diagram) by thrust baring with Hooke's coupling mechanism 810 with crosshead shoe bearing (Oldham bearing).The center of balance bracket 820 is connected with axostylus axostyle 840, and axostylus axostyle 840 is supported by load-carrying element 830.According to said structure, it is the effect of the balance of fulcrum that balance bracket 820 plays with axostylus axostyle 840.Thus, when the support laod unbalance of screw shaft 4b and 4d, balance bracket 820 is towards supporting the big side's run-off the straight of load, and the feasible screw shaft that supports the big side of load is along axial decline, and the screw rod that supports the little side of load is along axial rising.Support load equalization mechanism in this structure and first embodiment has identical functions, its result, and the support load equalization mechanism in enough second embodiments of energy replaces the support load equalization mechanism in first embodiment.
Except with the upper type, can also carry out suitable change to the position of the support load equalization mechanism in first embodiment etc., for example should not support load equalization mechanism to be arranged on lower car 13b side and be arranged on upper car 13a side etc., and can when keeping its function, carry out suitable application and change thus.
Claims (10)
1. double-deck elevator, described double-deck elevator has two lift cars of upper and lower settings, and can adjust the interval between upper car and the lower car, described double-deck elevator is characterised in that, described upper car and described lower car are driven by screw mechanism respectively, a plurality of screw shafts that described upper car is driven are connected by bindiny mechanism with a plurality of screw shafts that described lower car is driven, described bindiny mechanism transmits the rotary power around axle of screw shaft, and allows axial relatively moving.
2. double-deck elevator as claimed in claim 1, it is characterized in that, the described screw mechanism of upper car or lower car has the load of support equalization mechanism, described support load equalization mechanism is according to the magnitude relationship of thrust, the screw shaft that makes the big side of thrust is along axial decline, and the screw shaft that makes the little side of thrust is along axial rising.
3. as claim 1 or 2 described double-deck elevators, it is characterized in that the described screw mechanism of upper car and lower car is made of the rolling screw mechanism that carries out load transfer by rolling body between nut member that supports lift car and screw shaft.
4. double-deck elevator as claimed in claim 2, it is characterized in that, be set at two separately with driving described a plurality of screw shafts of upper car and described a plurality of screw shafts of driving lower car, described support load equalization mechanism is configured to support support section with each screw shaft of thrust support by the bar member that has fulcrum respectively, thrust on the support section of the screw shaft by acting on a side makes the bar member be rotated around fulcrum, the support section of screw shaft that makes a described side under the effect of the rotation of this bar member is along axial decline, and makes support section with thrust support the opposing party's screw shaft along axial rising.
5. double-deck elevator as claimed in claim 4, it is characterized in that, described two screw shafts are connected with the force part of the bar member with these three points of force, fulcrum and point of action respectively in the mode that can pivot separately, described each bar member be arranged on when screw shaft be that the center is rotated during along axial decline with this fulcrum, the point of action that makes each bar member by this rotation mutually away from direction on, the point of action of a plurality of bar members suffers restraints, and makes point of action distance each other can not become big.
6. double-deck elevator as claimed in claim 2, it is characterized in that, be set at two separately with driving described a plurality of screw shafts of upper car and described a plurality of screw shafts of driving lower car, described support load equalization mechanism has the bar member that has fulcrum at the center of gravity place of two point of actions, and described screw shaft is connected on this point of action in the mode that can pivot separately.
7. double-deck elevator as claimed in claim 1 is characterized in that, the described screw shaft that drives upper car is connected by sliding cross coupling with the described screw shaft that drives lower car.
8. double-deck elevator as claimed in claim 1 is characterized in that, the described screw shaft that drives upper car is connected by slide key with the described screw shaft that drives lower car.
9. double-deck elevator as claimed in claim 1 is characterized in that, the described a plurality of screw shafts that drive upper car are by the power driven that distributes by differential gear train.
10. double-deck elevator as claimed in claim 1 is characterized in that, the described a plurality of screw shafts that drive upper car are driven by induction motor (IM) respectively, and described each induction motor (IM) is driven by the voltage of same frequency.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009-280243 | 2009-12-10 | ||
| JP2009280243A JP5325753B2 (en) | 2009-12-10 | 2009-12-10 | Double deck elevator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102092618A true CN102092618A (en) | 2011-06-15 |
| CN102092618B CN102092618B (en) | 2014-06-11 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010583814.4A Expired - Fee Related CN102092618B (en) | 2009-12-10 | 2010-12-07 | Double-deck elevator |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5325753B2 (en) |
| CN (1) | CN102092618B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102167251A (en) * | 2010-02-25 | 2011-08-31 | 株式会社日立制作所 | Double-deck elevator |
| CN102295211A (en) * | 2011-08-08 | 2011-12-28 | 吴国辉 | Elevator-car ropeless-elevating mechanism for vertical elevator |
| CN103496624A (en) * | 2013-09-09 | 2014-01-08 | 费传华 | Novel efficient vertical energy-saving elevator |
| CN107879222A (en) * | 2017-10-30 | 2018-04-06 | 黄丽贤 | A kind of multistation elevator structure |
| CN113800362A (en) * | 2021-10-29 | 2021-12-17 | 重庆迈高电梯有限公司 | Double-lifting elevator for port |
| US11332344B2 (en) | 2018-05-16 | 2022-05-17 | Otis Elevator Company | Elevator car frame assembly |
| CN113800362B (en) * | 2021-10-29 | 2024-05-31 | 重庆迈高电梯有限公司 | Port double-lifting elevator |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20220364380A1 (en) * | 2019-08-27 | 2022-11-17 | Mitsubishi Electric Corporation | Conveying device |
| WO2021063611A1 (en) * | 2019-09-30 | 2021-04-08 | Inventio Ag | Elevator car for a double-deck elevator |
| CN110980586B (en) * | 2019-12-30 | 2023-11-24 | 郑州宇通重工有限公司 | Lifting device with self-adaptive load balancing function |
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| JP4107858B2 (en) * | 2002-03-22 | 2008-06-25 | 東芝エレベータ株式会社 | Double deck elevator |
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| CN1225332A (en) * | 1998-04-09 | 1999-08-11 | 奥蒂斯电梯公司 | Adjustable double-deck elevator |
| CN1176003C (en) * | 1999-06-07 | 2004-11-17 | 株式会社东芝 | Double decker cage for elevator |
| JP2001278569A (en) * | 2000-03-30 | 2001-10-10 | Otis Elevator Co | Story height variable double deck elevator |
| US20030024772A1 (en) * | 2001-07-03 | 2003-02-06 | Otis Elevator Company | Double deck elevator with adjustable floor height |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102167251A (en) * | 2010-02-25 | 2011-08-31 | 株式会社日立制作所 | Double-deck elevator |
| CN102295211A (en) * | 2011-08-08 | 2011-12-28 | 吴国辉 | Elevator-car ropeless-elevating mechanism for vertical elevator |
| CN103496624A (en) * | 2013-09-09 | 2014-01-08 | 费传华 | Novel efficient vertical energy-saving elevator |
| CN107879222A (en) * | 2017-10-30 | 2018-04-06 | 黄丽贤 | A kind of multistation elevator structure |
| US11332344B2 (en) | 2018-05-16 | 2022-05-17 | Otis Elevator Company | Elevator car frame assembly |
| CN113800362A (en) * | 2021-10-29 | 2021-12-17 | 重庆迈高电梯有限公司 | Double-lifting elevator for port |
| CN113800362B (en) * | 2021-10-29 | 2024-05-31 | 重庆迈高电梯有限公司 | Port double-lifting elevator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011121693A (en) | 2011-06-23 |
| CN102092618B (en) | 2014-06-11 |
| JP5325753B2 (en) | 2013-10-23 |
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