CN209942310U

CN209942310U - Chain plate length-variable circulating type stereo garage transmission system

Info

Publication number: CN209942310U
Application number: CN201920012687.9U
Authority: CN
Inventors: 赵巍
Original assignee: Yunya Space (beijing) Technology Co Ltd
Current assignee: Yunya Space (beijing) Technology Co Ltd
Priority date: 2019-01-04
Filing date: 2019-01-04
Publication date: 2020-01-14
Anticipated expiration: 2029-01-04

Abstract

The utility model relates to a variable circulating stereo garage transmission system of link joint length adopts the link joint that comprises link joint fixed arm and link joint digging arm, through the flexible connection of link joint fixed arm and link joint digging arm and the appearance setting of hanging beam axle guide rail, stretches out the link joint digging arm in the gyration region, can obtain the car frame longitudinal separation that carries than prior art under the same car frame transverse separation, has reduced circulating stereo garage volume, has improved circulating stereo garage's space utilization; the transmission system of the circulating type stereo garage with the chain plates of variable length realizes that two vehicle carrying frames are parked at the position close to the ground under the vertical type circulating type stereo garage through the shape arrangement of the hanging beam shaft guide rail, thereby increasing the number of vehicles simultaneously stored and taken in the vertical type circulating type stereo garage and reducing the waiting time of users.

Description

Chain plate length-variable circulating type stereo garage transmission system

Technical Field

The utility model relates to a stereo garage field especially relates to changeable circulating stereo garage transmission system of link joint length.

Background

A circulating stereo garage, for example, a vertical circulating stereo garage disclosed in Chinese patent CN105672712A [1], a vertical circulating fork transmission mechanism and garage disclosed in Chinese patent CN102041911A [2], and a stereo circulating double-layer garage disclosed in Chinese patent CN106285109A [3], includes a vertical circulating stereo garage and a horizontal circulating stereo garage.

See fig. 1-4; the transmission system of the circulating type stereo garage adopts a conveyor belt principle, and two groups of transmission wheels 200 are used for driving two pairs of chains 300 to rotate circularly; a plurality of chain plates 400 are arranged on the chain 300 at equal intervals; the hanging beam shaft 500 is hinged with the chain plate 400 through a steering device; the carriage frame 800 is hung on the hanging beam shaft 500 and driven by the chain 300 to reciprocate circularly.

The transmission system of the circulating stereo garage comprises a linear area 1000 and a rotary area 1001; in the linear region 1000, the chain 300 drives the chain plate 400, the hanging beam shaft 500 and the vehicle-carrying frame 800 to make linear motion along the vertical direction of the vertical type circulating stereo garage or the horizontal direction of the horizontal type circulating stereo garage, i.e. the longitudinal axis 900 direction of the circulating stereo garage; in the rotation area 1001, the chain 300 drives the chain plate 400, the hanging beam shaft 500 and the load-carrying frame 800 to rotate to complete rotation from one movement direction to the opposite direction, and the rotation radius of the load-carrying frame 800 is equal to the sum of the length 404 of the chain plate and the radius 201 of the driving wheel; the included angle between the connecting line from any point in the plane of the driving wheel 200 to the axle center of the driving wheel 200 and the longitudinal axis 900 of the circulating type stereo garage is called the revolution angle of the point, and the revolution angle is in the range of-90; the link plate length 404 of the prior art circulating stereo garage, i.e. the distance between the link plate top center 406 and the link plate bottom center 405, remains constant.

The type of a driving wheel 200 of the transmission system of the circulating stereo garage comprises a chain wheel [3] and a shifting fork wheel [1] [2 ]; when a chain wheel type driving wheel 200 is adopted, a chain 300 rotates 180 degrees around the axis of the driving wheel 200 in a rotation area 1001, and a motion track 407 of the top center of each chain plate is a semicircle with the radius equal to the sum of the radius 201 of the driving wheel and the length 404 of each chain plate; when a driving wheel 200 of a fork wheel type is adopted, under the guidance of a guide rail of a chain 300, the chain 300 also rotates 180 degrees around an axis vertical to a plane where the chain 300 is located in a rotation area 1001, a movement track 407 of the top center of each chain plate is also semicircular, the axis is called as a rotation axis of the chain 300, and the radius of the semicircle is called as the rotation radius of the chain 300; in the circulating stereo garage transmission system who adopts fork wheel type drive wheel 200, the effect of fork wheel is the same with drive wheel 200 that the axis is located chain 300 axis of rotation, radius and equals chain 300 radius of rotation's sprocket type, and is succinct for the narration, the utility model discloses in drive wheel 200 axis indicates chain 300 axis of rotation, drive wheel radius 201 indicates chain 300 radius of rotation.

The appearance of the vehicle carrying frame 800 is similar to a cube, the vehicle carrying frame 800 and a loaded vehicle are always kept in a horizontal direction in the movement, and the length direction of the vehicle is parallel or vertical to the axis of the driving wheel 200; on a plane vertical to the axis of the driving wheel 200, the length of the vehicle carrying frame 800 in the horizontal direction is called the width of the vehicle carrying frame 800 and is marked as w; the height of the carriage frame 800 is denoted as h; the cross section of the carriage frame 800, viewed along the axis of the drive wheel 200, is approximately rectangular with a width w and a height h.

Recording the length 404 of the chain plate as L and the radius 201 of the driving wheel as r; in the linear region 1000, the linear velocity of the carriage frame 800 is equal to the average linear velocity of the chain 300; in the gyration region 1001, the vehicle-carrying frame 800, the chain plate 400 and the chain 300 synchronously rotate around the transmission wheel 200, the angular velocity of the vehicle-carrying frame 800 is equal to the average angular velocity of the chain 300, and the linear velocity of the vehicle-carrying frame 800 is (L + r)/r times of the linear velocity of the vehicle-carrying frame 800 in the linear region 1000 because the gyration radius of the vehicle-carrying frame 800 is equal to the sum of the length L of the chain plate and the radius r of the transmission wheel; in order to shorten the speed of parking and taking vehicles, the linear speed of the chain 300 of the circulating stereo garage is relatively high, generally more than 0.4 m/s; at the moment the link plate 400 moves from the linear region 1000 to the turning region 1001 and at the moment the link plate 400 moves from the turning region 1001 to the linear region 1000, the linear speeds of the link plate 400, the suspension beam shaft 500, the vehicle carrier 800 and the load thereof greatly change in a short time; the larger the ratio of the length 404 of the chain plate to the radius 201 of the driving wheel is, the larger the linear velocity variation is, and the larger the corresponding acceleration absolute value is; the larger the absolute value of the acceleration is, the larger the impact force applied to the chain 300 and the link shaft 301 by the power system of the circulating stereo garage through the transmission wheel 200 is; the excessive absolute value of the acceleration of the carriage frame 800 will cause the reliability of the chain 300 to be reduced, and cause the stability of the carriage frame 800 and the load thereof to be reduced; for the reasons mentioned above, there is an upper limit Km, K = L/r < = Km — (1), typically Km greater than 0.4 and less than 1.0, to the ratio K of the link plate length 404 to the drive wheel radius 201.

The gap width of two adjacent rows of vehicle-carrying frames 800 of the circulating stereo garage is called as the transverse distance 802 of the vehicle-carrying frames and is marked as L2; generally, the transverse distance 802 between the vehicle carrying frames of the horizontal type circulating stereo garage and the vertical type circulating stereo garage is not more than 0.5h and not more than 0.5w respectively, otherwise, the circulating stereo garage is too large in size and low in space utilization rate.

The chain plates 400 of the circulating stereo garage are arranged on the chain 300 at equal intervals, and the chain 300 between every two adjacent chain plates 400 has the same length, which is marked as D'; for a circulating stereo garage with a certain transmission wheel radius r, chain plate length L, vehicle carrying frame 800 width w and vehicle carrying frame 800 height h, a minimum value D'm exists in D'; if the length D '< D'm of the chain 300 between two adjacent chain plates 400 of the circulating stereo garage is set, the vehicle carrying frame 800 collides, and the circulating stereo garage cannot normally run; if D ' = D'm is set, two adjacent vehicle-carrying frames 800 are close to meet at some positions in the operation process, and the gap width between the vehicle-carrying frames 800 in the linear region 1000 reaches the minimum value, which is called the longitudinal spacing 801 of the circulating stereo garage and is denoted as L1 '; if D ' > D'm is arranged, the gap width between the adjacent vehicle carrying frames 800 in the linear region 1000 is larger than L1', and the efficiency of the circulating stereo garage is not fully utilized; thus, the circulating stereo garage typically operates with a carriage longitudinal spacing 801, L1 'being determined by the minimum chain 300 length D' between two adjacent carriages 800 that keeps the carriages 800 from colliding.

When two adjacent vehicle carrying frames 800 are close to meet, the positions of the vehicle carrying frames respectively comprise three combinations of a linear region 1000 and a linear region 1000, a linear region 1000 and a rotation region 1001, a rotation region 1001 and the like; in the turning region 1001, the vehicle-carrying frame 800 rotates along a 180-degree arc with the radius equal to the sum of the length L of the chain plate and the radius r of the driving wheel, the turning space of the vehicle-carrying frame 800 is semi-cylindrical, and the size of the turning space is determined by the turning radius L + r; when the turning radius L + r is large, the turning space of the carriage frame 800 is large, and the adjacent carriage frames 800 may appear in the turning area 1001 at the same time; when the turning radius L + r is small, adjacent vehicle-carrying frames 800 which are positioned in the turning region 1001 at the same time are not close to meet; in the linear region 1000, the gap widths between the adjacent carriage frames 800 are equal to each other, and the carriage frames 800 do not collide even if the gap width of the carriage frames 800 is close to zero; therefore, in the case where only the adjacent carriage frames 800 in the linear region 1000 meet, L1' = 0; at smaller turning radii L + r, if L1'>0, there must be a near-meeting of a carriage frame 800 in the turning region 1001 with an adjacent carriage frame 800 in the straight region 1000, and therefore L1' is determined by the length of the chain 300 between the two carriage frames 800 that meet near-meet.

The smaller the volume of the circulating type stereo garage accommodating the same number of vehicle carrying frames 800 is, the more vehicle carrying frames 800 are loaded into the circulating type stereo garage under the same volume, and the higher the space utilization rate is; the volume of the circulating stereo garage is in direct proportion to the longitudinal length and the transverse length of the circulating stereo garage; the transverse length of the circulating three-dimensional garage depends on the transverse distance 802 of the vehicle carrying frames, and the smaller the transverse distance 802 of the vehicle carrying frames is, the smaller the volume of the circulating three-dimensional garage is; the longitudinal length of the circulating stereo garage is equal to the length of a linear area 1000 plus 2 times of the longitudinal length of a rotary area 1001; because the circulating stereo garage contains more vehicle carriers 800, generally more than 6 vehicle carriers, the longitudinal length of the circulating stereo garage is mainly determined by the longitudinal distance 801 of the vehicle carriers; under the condition of containing the same number of vehicle carriers 800, the smaller the longitudinal distance 801 of the vehicle carriers is, the smaller the volume of the circulating type stereo garage is.

The main defects of the transmission system of the circulating type stereo garage in the prior art are that the longitudinal distance 801 of the vehicle carrying frames and the transverse distance 802 of the vehicle carrying frames are mutually restricted and cannot be small at the same time, and under the condition of containing the same number of the vehicle carrying frames 800, the circulating type stereo garage is large in size, the number of the vehicle carrying frames 800 which are arranged in the circulating type stereo garage under the same size is small, and the space utilization rate is low; according to the document [1], when the longitudinal distance 801 of the vehicle carrying frames of the circulating type stereo garage is small, the transverse distance 802 of the vehicle carrying frames is large, according to the observation of the inventor on the use site of the vertical type circulating type stereo garage of the patent [1], the longitudinal distance 801 of the vehicle carrying frames can reach the minimum value allowed by engineering technology and can be considered to be equal to zero, and the transverse distance 802 of the vehicle carrying frames is large and is close to 1.4 meters; on the other hand, when the vehicle frame lateral pitch 802 is small, the vehicle frame longitudinal pitch 801 is large, as shown in document [3 ].

The reason that the longitudinal distance 801 of the vehicle-carrying frames and the transverse distance 802 of the vehicle-carrying frames are restricted mutually is explained below by taking a horizontal circulating type stereo garage transmission system as an example, and the longitudinal distance 801 of the vehicle-carrying frames is larger when the transverse distance 802 of the vehicle-carrying frames is smaller.

The longitudinal spacing 801 of the vehicle carrying frames of the horizontal circulating type stereo garage is L1', L1' = D '-w- (2)', the transverse spacing 802 of the vehicle carrying frames of the horizontal circulating type stereo garage is L2, and L2= 2 x (L + r) -h- (3); since L2 is not more than 0.5h in general, L + r < = 0.75h according to formula (3); for the same height h of the vehicle carrier 800, L2 is determined by the sum of the chain plate length 404 and the radius 201 of the transmission wheel; the transverse distance L2 of the vehicle carrying frame is positively correlated with the sum L + r of the length 404 of the chain plate and the radius 201 of the driving wheel, namely L2 is increased when L + r is increased, and L2 is reduced when L + r is decreased.

When the turning radius L + r of the carriage frame 800 is small, the process of the carriage frame 800 approaching the other carriage frame 800 adjacent to the turning region 1001 is analyzed as follows.

See fig. 4; the vehicle-carrying frames 800 of the horizontal circulating type stereo garage shown in fig. 4 run at a longitudinal distance 801 of the vehicle-carrying frames, the vehicle-carrying frames 800 rotate clockwise around the driving wheel 200 with the axis at O', and the vehicle-carrying frames 800-1 are adjacent to the vehicle-carrying frames 800-2 and in front of the vehicle-carrying frames 800-2; the moment the carriage frame 800-1 enters the turning region 1001 from the linear region 1000, the horizontal distance between the carriage frame 800-2 is L1'; in the gyration region 1001, the distance between the load-carrying frame 800-1 and the load-carrying frame 800-2 in the horizontal direction changes along with the change of the gyration angle theta' of the top center 406 of the chain plate connected with the load-carrying frame 800-1; when the truck frame 800-1 is in the linear region 1000, the linear velocity is v 1; when the carriage frame 800-1 is in the rotation region 1001, the linear speed is (L + r) × v1/r, the horizontal direction speed is v2, v 2= v1 × (L + r) × sin (theta')/r — (4); in the initial stage of the rotation of the truck frame 800-1, the horizontal distance between the truck frame 800-1 and the truck frame 800-2 behind the truck frame is increased continuously because L is greater than 0 and sin (theta') is larger and v2 is greater than v 1; the vehicle carrying frames 800-1 continue to rotate, when theta 'reaches a certain angle theta' 0, the horizontal speeds of the two vehicle carrying frames 800 are equal, the horizontal distance stops increasing, the horizontal distance reaches the maximum value, and the larger L + r is, the larger the maximum value of the horizontal distance is; from v1 = v2, sin (θ'0) = r/(L + r) — (5) can be obtained; according to the formula (5), the larger the L/r is, the smaller the theta' 0 is, the larger the angle rotated by the carriage frame 800-1 is, and the larger the maximum value of the horizontal distance between the carriage frame 800-1 and the carriage frame 800-2 is; according to the formula (4), the larger L + r is, the larger v2 is, and the larger the maximum value of the horizontal distance between the carriage frame 800-1 and the carriage frame 800-2 is.

After the vehicle carrying frame 800-1 reaches the rotation angle theta' 0, the vehicle carrying frame continues to rotate, and the horizontal distance between the vehicle carrying frame 800-1 and the vehicle carrying frame 800-2 begins to decrease; at a certain moment, two adjacent vertex angles of the rectangular cross sections of the two carriage frames 800 are infinitely close to each other and meet each other at a point P; since L + r < = 0.75h, as can be seen from fig. 4, when the carriage frame 800-1 and the carriage frame 800-2 are close to meet, the axis O' of the driving wheel 200 is located at the right side of the chain plate 400 connected with the carriage frame 800-2 above the carriage frame 800-1; therefore, the meeting of the adjacent vehicle-carrying frames 800-1 and 800-2 occurs in the range of (-pi/2-0) of the revolving angle theta' of the vehicle-carrying frame 800-1, and the vehicle-carrying frame 800-2 is always positioned in the straight line region 1000 when and before the event occurs; after the adjacent meeting of the vehicle carrying frame 800-1 and the vehicle carrying frame 800-2 occurs, the vehicle carrying frame 800-1 continues to move below the vehicle carrying frame 800-2, the distance between the vehicle carrying frame 800-1 and the vehicle carrying frame 800-2 in the horizontal direction is increased again until the vehicle carrying frame is rotated out of the rotation area 1001, and the adjacent meeting with the vehicle carrying frame 800-1 does not occur all the time.

Similarly, the process of the adjacent meeting of the carriage 800-1 in the turning region 1001 and the adjacent, preceding, another adjacent carriage 800, and the process of the adjacent meeting of the carriage 800-1 and the carriage 800-2 following the same carriage are completely the same except for the opposite movement directions; when the vehicle-carrying frame 800-1 and another adjacent vehicle-carrying frame 800 before the vehicle-carrying frame are close to meet at a point P ', the meeting point P' is within the range of (0-pi/2) of the revolution angle theta 'of the vehicle-carrying frame 800-1, and the meeting point P' and the point P are in mirror symmetry relative to the longitudinal axis 900 of the circulating type stereo garage; thus, in the turnaround region 1001, the carriage frame 800-1 meets the adjacent carriage frame 800 at the rear or front only in close proximity at point P or point P', respectively.

Therefore, when the vehicle carrying frames 800-1 and 800-2 meet each other near the point P, the length D ' of the chain 300 between the vehicle carrying frames 800 is the minimum value of D ' for ensuring that the vehicle carrying frames 800 do not collide with each other in the circulating stereo garage, and D ' determines the longitudinal distance L1' between the vehicle carrying frames, as shown in the formula (2) '.

Through the analysis, it can be seen that if the ratio of the turning radius r + L or the L/r of the vehicle-carrying frame 800 is increased, the maximum value of the horizontal distance between the vehicle-carrying frame 800-1 and the vehicle-carrying frame 800-2 is increased before the meeting is approached, the meeting approaching event cannot occur, the initial horizontal distance L1 'between the vehicle-carrying frame 800-1 and the vehicle-carrying frame 800-2 can be reduced, and the longitudinal distance L1' between the vehicle-carrying frames is also reduced; therefore, the longitudinal spacing 801 of the vehicle carriers is negatively correlated with the turning radius r + L of the vehicle carriers 800, and the longitudinal spacing 801 of the vehicle carriers is negatively correlated with the L/r ratio.

Generally, to obtain a smaller longitudinal spacing 801 of the carriage, the L/r ratio is set near its upper limit Km, not greater than Km, and therefore the longitudinal spacing 801 of the carriage is only related to the turning radius r + L of the carriage 800; because the turning radius r + L of the vehicle-carrying frame 800 is positively correlated with the transverse distance 802 of the vehicle-carrying frame, when the sum of the length 404 of the chain plate and the radius 201 of the driving wheel is small, the longitudinal distance 801 of the vehicle-carrying frame is also negatively correlated with the transverse distance 802 of the vehicle-carrying frame, and when the transverse distance 802 of the vehicle-carrying frame is small, the longitudinal distance 801 of the vehicle-carrying frame is large; for example, the horizontal type circulating stereo garage parameters of w =2.4 meters, h =1.8 meters, r =0.6 meters and L =0.5 meters, L2=0.4 meters and L1' =0.51 meters.

Similarly, the vertical type circulating stereo garage and the horizontal type circulating stereo garage are basically the same except that the working directions are different, and the same conclusion as the above can be obtained by analyzing the transverse distance 802 of the vehicle carrying frames and the longitudinal distance 801 of the vehicle carrying frames of the vertical type circulating stereo garage.

The vertical circulating stereo garage is provided with a vehicle entrance at the bottom of a rotary area 1001 below and at a position close to the ground; when the vehicle is stored and taken out, the vehicle carrying frame 800 is moved to a vehicle entrance and exit, and then a user stores the vehicle in the vehicle carrying frame 800 parked in the vehicle entrance and exit or takes the vehicle out of the vehicle carrying frame 800 parked in the vehicle entrance and exit; the time interval between the access of two consecutive vehicles, comprising the movement time of the carriage frame 800 plus the time of the user operating the vehicle, is typically between 1 and 2 minutes; when a plurality of users request to access the vehicle, the users need to wait in line, the waiting time is longer, the more the number of the vehicle carrying frames 800 contained in the vertical circulating type stereo garage is, and the longer the waiting time is.

In the turning region 1001, when the turning radius of the carriage frame 800 is small, only one carriage frame 800 is located in the turning region 1001 at the same time, and only one vehicle can be stored or taken out; when the turning radius of the carriage frame 800 is large, there is a case where the adjacent carriage frames 800 are simultaneously in the turning region 1001; because the two carriage frames 800 move along a semicircle and only one lowest point is close to the ground, when two adjacent carriage frames 800 respectively move to two sides of the lowest point of the rotation area 1001 and reach the same height, the included angle between the top center 406 of the chain plate connected with the two carriage frames 800 and the axle center of the driving wheel 200 is larger, therefore, the distance between the two carriage frames 800 and the ground is larger, and the situation that the two carriage frames 800 are close to the ground at the same time does not exist; the vertical circulating stereo garage in the prior art only has one vehicle entrance and exit, and only one vehicle can be stored or taken out at the same time, so that a plurality of users need to wait in a queue when requesting to store or take the vehicle at the same time, and the waiting time is longer.

In summary, when the turning radius r + L of the vehicle-carrying frame 800 is smaller, the circulating stereo garage has the situation that the vehicle-carrying frame 800 in the turning region 1001 meets the adjacent vehicle-carrying frame 800; the movement process of the vehicle-carrying frame 800 in the rotation area 1001 determines that the longitudinal spacing 801 of the vehicle-carrying frames is negatively correlated with the transverse spacing 802 of the vehicle-carrying frames, and when the transverse spacing 802 of the vehicle-carrying frames is smaller, the longitudinal spacing 801 of the vehicle-carrying frames is larger; therefore, the circulating type stereo garage in the prior art is large in size, the number of the vehicle carrying frames 800 accommodated under the same size is small, and the space utilization rate is low; the vertical circulating stereo garage can only store or take out one vehicle, and a plurality of users can wait for a long time when requesting to store or take out the vehicle.

SUMMERY OF THE UTILITY MODEL

In view of this, the present invention provides a technical solution for a transmission system of a circulating stereo garage, and firstly, according to the technical solution, under the condition of accommodating the same number of car carrying frames 800, the volume of the circulating stereo garage is reduced, so as to accommodate more car carrying frames 800 under the same volume of the circulating stereo garage, thereby improving the space utilization rate of the circulating stereo garage; and secondly, the number of vehicles simultaneously stored and taken by the vertical circulating stereo garage is increased, and the waiting time for storing and taking the vehicles by a user is reduced.

In order to achieve the above object, the present invention is achieved according to the following technical solutions.

A chain plate length variable circulating type stereo garage transmission system comprises a front group of transmission wheels and a rear group of transmission wheels, wherein the axes of the transmission wheels are parallel to each other and drive a chain to rotate;

two pairs of chains which respectively rotate around the two groups of driving wheels and are parallel to each other;

a plurality of chain plates which are fixed on the two pairs of chains at equal intervals and correspondingly in position;

a hanging beam shaft for hanging the loading frame is connected with the chain plate through a steering device;

in the rotation area, the front and rear groups of hanging beam shaft guide rails are respectively arranged on the support frames at the corresponding positions to support and guide the hanging beam shaft;

the chain plate is composed of a chain plate fixing arm and a chain plate movable arm, the chain plate fixing arm of the chain plate is fixed on the chain, and the chain plate movable arm of the chain plate is in telescopic connection with the chain plate fixing arm; the suspension beam shaft guide rail in the rotation area is an n-shaped arc continuous change curve; through the connection and matching of the chain plate movable arm and the chain plate fixed arm, the chain plate movable arm of the hanging beam shaft guide rail constraint chain plate is subjected to telescopic change in the length direction of the chain plate along with the position change of the hanging beam shaft guide rail.

As a further technical scheme, two ends of the bottom of the fixed arm of the chain plate are respectively fixed on two adjacent link shafts of the chain; the steering device is a bearing, and the chain plate movable arm is hinged with the hanging beam shaft through the bearing; the left end and the right end of the hanging beam shaft are provided with hanging beam shaft rollers; the hanging beam shaft roller rolls in the hanging beam shaft guide rail.

As a further technical scheme, the chain plate lifting device further comprises a chain plate lifting rod and a lifting wheel disc, wherein the top of a chain plate fixing arm is fixedly provided with the chain plate lifting rod parallel to the axis of the driving wheel; the poking wheel disc is coaxially arranged on one side of the driving wheel or is concentrically fixed on the driving wheel, and the poking wheel disc is matched with the chain plate poking rod through a catching device arranged on the outer edge of the poking wheel disc to drive the chain plate poking rod to rotate.

As a further technical scheme, the engaging device is a wheel disc tooth groove on a shifting wheel disc, and the shifting wheel disc is meshed with a chain plate shifting rod through the wheel disc tooth groove.

As a further technical scheme, in the range of the rotation angle interval of the hanging beam shaft guide rail (34-40) and-40-34 in the rotation region, the distance from the hanging beam shaft guide rail to the axle center of the driving wheel is 1.2-1.65 times of the sum of the length of the chain plates in the linear region and the radius of the driving wheel.

As a further technical scheme, in the range of a rotation angle interval of a hanging beam shaft guide rail (28-34) and-34-28 in a rotation region, the distance from the hanging beam shaft guide rail to the axle center of a driving wheel is 1.2-1.6 times of the sum of the length of a chain plate in a linear region and the radius of the driving wheel.

As a further technical scheme, in the range of [ 22-28 ] and [ -28-22 ] rotation angles of a hanging beam shaft guide rail in a rotation region, the distance from the hanging beam shaft guide rail to the axis of a driving wheel is 1.15-1.45 times of the sum of the length of a chain plate in a linear region and the radius of the driving wheel.

As a further technical scheme, the curvature radius within the range of-30 rotation angle of a hanging beam shaft guide rail in a rotation region below a link plate length-variable transmission system of the circulating type stereo garage is more than 2 times of the sum of the length of the link plate in the linear region and the radius of a transmission wheel, and the distance from the 0-degree rotation angle of the hanging beam shaft guide rail to the axis of the transmission wheel is 1.0-1.2 times of the sum of the length of the link plate in the linear region and the radius of the transmission wheel.

As a further technical scheme, the transmission system of the circulating type stereo garage with the variable chain plate length is positioned in the range of a turning angle between 65-90 degrees and-90-65 degrees of a hanging beam shaft guide rail in a turning region below the transmission system of the circulating type stereo garage, and the hanging beam shaft guide rail is linear.

The beneficial effect of adopting above-mentioned technical scheme is: a chain plate length-variable circulating type stereo garage transmission system is characterized in that chain plate movable arms are extended out within a certain rotation angle range of a rotation area through the adoption of length-variable chain plates and the arrangement of a hanging beam shaft guide rail, so that the longitudinal distance of vehicle carrying frames is smaller than that of the circulating type stereo garage transmission system in the prior art under the condition of the same transverse distance of the vehicle carrying frames, and the volume of the circulating type stereo garage is reduced; therefore, under the same volume of the circulating stereo garage, the chain plate length-variable circulating stereo garage transmission system can accommodate more vehicle-carrying frames, and the space utilization rate of the circulating stereo garage is improved; the utility model discloses a changeable circulating stereo garage transmission system of link joint length, through the adoption of variable length link joint and the appearance setting of hanging beam axle guide rail, realized that two year car racks parking in being close ground position have been carried to gyration region occasionally in perpendicular type circulating stereo garage below, perpendicular type circulating stereo garage deposits and gets car quantity simultaneously and increases to two, has reduced the waiting time when a plurality of users deposit and take the car simultaneously.

Drawings

Fig. 1 is a structural schematic view of a vertical type circulating stereo garage in the prior art.

Fig. 2 is a structural schematic view of a horizontal type circulating stereo garage in the prior art.

Fig. 3 is a schematic view of an installation structure of a link plate in the prior art.

Fig. 4 is a schematic diagram of a carriage frame spacing calculation in the prior art.

Fig. 5 is a schematic diagram of the calculation of the pitch of the vehicle carrying frames of the present invention.

Fig. 6 shows the relationship curve between the longitudinal distance of the vehicle carrying frame and the transverse distance of the vehicle carrying frame.

Fig. 7 is a schematic structural view of the dial wheel disc and the driving wheel of the present invention.

Fig. 8 is a schematic structural diagram of the link plate of the present invention.

Fig. 9 is a schematic sectional view taken along the line a-a in fig. 8.

Fig. 10 is a schematic top view of the structure of fig. 8.

Fig. 11 is a schematic view of the whole structure of the embodiment of the horizontal type circulating stereo garage of the present invention.

Fig. 12 is a schematic view of an assembly structure of the link plate and the chain in fig. 11.

Fig. 13 is a cross-sectional side view of the structure of fig. 12.

Fig. 14 is a schematic top view of the structure of fig. 12.

Fig. 15 is a partial cross-sectional structural view of fig. 11.

Fig. 16 is a schematic structural view of an embodiment of the vertical type circulating stereo garage including two vehicle entrances and exits according to the present invention.

In the figure, the position of the upper end of the main shaft,

100 support frames;

the radius of 200 driving wheels and 201 driving wheels;

300 chains, 301 link shafts;

400 chain plates, 401 chain plate fixed arms, 402 chain plate movable arms, 403 chain plate deflector rods, 404 chain plate length, 405 chain plate bottom center, 406 chain plate top center and 407 chain plate top center motion tracks;

500 hoisting beam shafts and 501 hoisting beam shaft rollers;

600 hoisting beam shaft guide rails;

700 stirring the wheel disc and 701 the wheel disc tooth groove;

800 vehicle-carrying frames, 801 vehicle-carrying frame longitudinal intervals and 802 vehicle-carrying frame transverse intervals;

a 900 cycle stereo garage longitudinal axis;

1000 linear regions, 1001 rotation regions.

Detailed Description

The following will further explain the embodiments of the present invention with reference to the drawings; see fig. 5-16.

The utility model relates to a chain plate length variable circulating stereo garage transmission system, which comprises a front group of transmission wheels 200 and a rear group of transmission wheels 200, wherein the axes of the transmission wheels are parallel to each other and drive a chain 300 to rotate;

two pairs of chains 300 which respectively rotate around the two groups of driving wheels 200 and are parallel to each other;

a plurality of link plates 400 fixed at equal intervals on the two chains 300 in corresponding positions;

a hanging beam shaft 500 of the hanging loading frame 800 is connected with the chain plate 400 through a steering device;

in the rotation area 1001, the front and rear sets of suspension beam shaft guide rails 600 are respectively arranged on the support frames 100 at the corresponding positions to support and guide the suspension beam shaft 500;

the chain plate 400 is composed of a chain plate fixing arm 401 and a chain plate movable arm 402, the chain plate fixing arm 401 of the chain plate 400 is fixed on the chain 300, and the chain plate movable arm 402 of the chain plate 400 is in telescopic connection with the chain plate fixing arm 401; in the rotation region 1001, the suspension beam shaft guide rail 600 is an n-shaped arc continuous change curve; through the connection and matching of the link plate movable arm 402 and the link plate fixed arm 401, the suspension beam shaft guide rail 600 restrains the link plate movable arm 402 of the link plate 400 to perform telescopic change in the length direction of the link plate 400 along with the position change of the suspension beam shaft guide rail 600.

As a further example, both ends of the bottom of the chain plate fixing arm 401 are respectively fixed on two adjacent link shafts 301 of the chain 300; the steering device is a bearing, and the chain plate movable arm 402 is hinged with the hanging beam shaft 500 through the bearing; the left end and the right end of the hanging beam shaft 500 are provided with hanging beam shaft rollers 501; the hoist beam axle roller 501 rolls in the hoist beam axle guide 600.

As a further embodiment, the device further comprises a chain plate deflector rod 403 and a deflector wheel disc 700, wherein the top of the chain plate fixing arm 401 is fixedly provided with the chain plate deflector rod 403 parallel to the axis of the driving wheel 200; the dial wheel disc 700 is coaxially arranged on one side of the driving wheel 200 or is concentrically fixed on the driving wheel 200, and the dial wheel disc 700 is matched with the chain plate dial 403 through a connecting device arranged on the outer edge of the dial wheel disc 700 to drive the chain plate dial 403 to rotate.

As a further example, the engaging device is a wheel tooth groove 701 on the dial wheel 700, and the dial wheel 700 is engaged with the link plate lever 403 through the wheel tooth groove 701.

As a further embodiment, within the range of the rotation angle interval (34-40) and-40-34) of the hanger beam shaft guide rail 600 in the rotation region 1001, the distance from the hanger beam shaft guide rail 600 to the axle center of the driving wheel 200 is 1.4 to 1.65 times the sum of the length 404 of the chain plate in the linear region 1000 and the radius 201 of the driving wheel; the (34-40) refers to an interval range of more than 34 degrees, less than or equal to 40 degrees, and so on.

As a further embodiment, within the range of the rotation angle interval of (28-34) and [ -34-28 ] of the hanger beam shaft guide rail 600 in the rotation region 1001, the distance from the hanger beam shaft guide rail 600 to the axle center of the driving wheel 200 is 1.2 to 1.55 times the sum of the length 404 of the chain plate in the linear region 1000 and the radius 201 of the driving wheel.

As a further embodiment, within the ranges of [ 22-28 ] and [ -28-22 ] rotation angles of the suspension beam shaft guide rail 600 of the rotation region 1001, the distance from the suspension beam shaft guide rail 600 to the axis of the driving wheel 200 is 1.15 to 1.45 times the sum of the length 404 of the chain plate in the linear region 1000 and the radius 201 of the driving wheel.

As a further embodiment, the curvature radius within the range of-30 ° of the swing angle of the suspension beam shaft guide rail 600 located in the lower swing region 1001 is greater than 2 times of the sum of the length 404 of the link plate in the linear region 1000 and the radius 201 of the transmission wheel, and the distance from the 0 ° swing angle of the suspension beam shaft guide rail 600 to the axis of the transmission wheel 200 is 1.0-1.2 times of the sum of the length 404 of the link plate in the linear region 1000 and the radius 201 of the transmission wheel.

As a further embodiment, said suspension beam shaft guide 600 is linear within the range of [ 65-90 ] and [ -90-65 ] swivel angles of the suspension beam shaft guide 600 located within the swivel region 1001 below.

The utility model discloses a circulating stereo garage transmission system with variable chain plate length, which restrains the chain plate movable arm 402 of the chain plate 400 through the hanging beam shaft guide rail 600 to change along the length direction of the chain plate 400 by extension and contraction along the hanging beam shaft guide rail 600; in the rotation area 1001, the hanging beam shaft guide rail 600 is arranged to guide the chain plate movable arm 402 to extend out, and the longitudinal distance 801 of the vehicle carrying frames is reduced under the same transverse distance 802 of the vehicle carrying frames.

When the transverse spacing 802 of the vehicle carrying frames is small, the vehicle carrying frames 800 in the revolving region 1001 of the circulating stereo garage meet adjacent vehicle carrying frames 800, and the longitudinal spacing 801 of the vehicle carrying frames is determined by the length of the chain 300 between the chain plates 400 connected with the two vehicle carrying frames 800; using the circulating stereo garage of horizontal type as an example below, the process that meets near to of carrying frame 800 and adjacent year frame 800 in the analysis gyration region 1001 explains when carrying a car frame lateral separation 802 less, the utility model discloses a variable circulating stereo garage transmission of link joint length carries the principle that a car frame longitudinal separation 801 is little than the circulating stereo garage transmission of prior art's of a car frame longitudinal separation 801 under the same year car frame lateral separation 802.

See fig. 5; in the chain plate length variable circulating stereo garage transmission system of the utility model, the longitudinal distance of the vehicle carrying frames is L1; the transverse spacing of the carriage frame is L2, and L2 is shown as a formula (3); the radius of the driving wheel 200 is r, and the axis is positioned at the point O; when the carriage frame 800 is in the linear region 1000, the length of the link plate 400 connected with the carriage frame, namely the length 404 of the link plate in the linear region 1000 is L; the suspension beam shaft guide rail 600 of the rotation region 1001 comprises two sections of curves T1C and CT2 which are connected, a T1 point and a T2 point are respectively positioned on a rotation angle pi/2 and a rotation angle-pi/2, a C point is the central point of the suspension beam shaft guide rail 600 of the rotation region 1001, and the C point is positioned on a longitudinal axis 900 of the circulating type stereo garage; the coordinates of each point on the suspension beam axle guide rail 600 are (x, y); on the curve T1C, y is a monotone non-increasing function relative to x and x is a monotone non-increasing function relative to y; on the CT2 curve, y is a monotone non-decreasing function relative to x and x is a monotone non-decreasing function relative to y; in the range of the [ 22-40 ] and the [ -40-22 ] pivot angle of the lifting beam shaft guide rail 600, the lifting beam shaft guide rail 600 is symmetrically arranged relative to the longitudinal axis 900 of the circulating type stereo garage; the distance between the suspension beam shaft guide 600 of the rotation area 1001 and the axis O of the transmission wheel 200 is L + dL; in the range of [ 22-90 ] and [ -90-22 ] pivot angle of the hanging beam shaft guide rail 600, the distance L + dL between the hanging beam shaft guide rail 600 and the axle center O of the driving wheel 200 is greater than L-0.1 star; the loading frames 800 rotate clockwise around the driving wheels 200 in sequence, the loading frame 800-1 enters the gyration region 1001 from the upper part of the linear region 1000, and the loading frame 800-2 is positioned behind the gyration region; the vehicle carrying frame 800-1 is close to meet the vehicle carrying frame 800-2 in the turning region 1001, namely the upper left corner of the vehicle carrying frame 800-1 is close to meet the lower right corner of the vehicle carrying frame 800-2 at a point P; when the load-carrying frames 800-1 and 800-2 are close to meet, the load-carrying frames 800-2 are located in a straight line region 1000, the length of the chain plate 400-2 connected with the load-carrying frames 800-2 is L, and the center 406 of the top of the chain plate 400-1 connected with the load-carrying frames 800-1 is M point; the hanging beam shaft guide rail 600 is arranged, so that the distance from the hanging beam shaft guide rail 600 at the point M to the axle center of the driving wheel 200 is greater than the sum of the length L of the chain plate of the linear region 1000 and the radius r of the driving wheel, and the point M is positioned in the range of the turning angle between minus 40 degrees and minus 22 degrees; in the rotation area 1001, the movement track 407 of the top center of the chain plate coincides with the suspension beam shaft guide rail 600, and the sum of the length of the chain plate 400-1 and the radius r of the transmission wheel is equal to the distance L + dL + r between the M point of the suspension beam shaft guide rail 600 and the axle center of the transmission wheel 200, so that the length of the chain plate 400-1 at the M point is L + dL, and dL is more than 0; dL is the protruding length of the link plate 400 with respect to the straight region 1000 of the link plate 400.

In the range of [ 22-40 ] and [ -40-22 ] pivot angles of the hanging beam shaft guide rail 600, the maximum distance from the hanging beam shaft guide rail 600 to the axle center of the driving wheel 200 is 1.45-1.65 times of the sum of the length L of the chain plates of the linear region 1000 and the radius r of the driving wheel; because L + r <0.75h, in the range of [ 22-40 ] and [ -40 ] -22 ] of the revolution angle, the horizontal distance (L + r + dL) cos (| theta |) < h < = w between the center of the top of the chain plate 400-1 connected with the load bearing frame 800-1 and the axle center of the transmission wheel 200 is calculated; therefore, when the carriage frame 800-1 and the carriage frame 800-2 are close to meet, the axis O of the driving wheel 200 is positioned above the carriage frame 800-1 and at the right side of the top center 406 of the chain plate of the carriage frame 800-2 chain plate 400, the event of the close meeting of the carriage frame 800-1 and the carriage frame 800-2 occurs in the range of (-pi/2-0) of the rotation angle theta of the chain plate 400-1 connected with the carriage frame 800-1, and the carriage frame 800-2 is always positioned in the linear region 1000 when and before the event occurs.

Referring to fig. 5, consider the motion of the carriage frame 800-1 in the turnaround area 1001; because the swing angle of the hanging beam shaft guide rail 600 is symmetrically arranged in the range of [ 22-40 ] and [ -40-22 ], a mirror symmetry point M 'of an M point relative to a longitudinal axis 900 of the circulating type stereo garage exists on the hanging beam shaft guide rail 600, and the swing angle of the M' point is in the range of [ 22-40 ]; when the top center 406 of the link plate of the load frame 800-1 moves to the point M, the horizontal distance between the load frame 800-1 and the load frame 800-2 is minimized, so that the top center 406 of the link plate of the load frame 800-2 is always on the left side of the line connecting the point M and the point M' before the minimum distance; because of the monotonicity of the beam axle guide rail 600 curves at both sides of the point C, the hanging beam axle guide rail 600 between the point M and the point M 'is positioned on the right side of the connecting line of the point M and the point M'; therefore, the link top center 406 of the load frame 800-1 is always on the suspension beam axle guide rail 600 from point M to point M 'during the movement from point M to point M' of the link top center 406 of the load frame 800-1, and the load frame 800-1 does not meet closely with the load frame 800-2.

When the top center 406 of the link plate 400-1 is located at the point T1, the horizontal distance between the load frame 800-1 and the load frame 800-2 is equal to L1; in the process that the top centers 406 of the link plates 400-1 move from the point T1 to the point M', the rotation angles θ of the top centers 406 of the link plates 400-1 are within the range of [22 ° and 90 ° of the rotation angle θ, the rotation angle of the chain 300 is pi/2- θ, the distance of the right movement of the vehicle carrying frame 800-2 is equal to the rotation length of the chain 300 and is r (pi/2- θ), and the distance between the vehicle carrying frame 800-1 and the vehicle carrying frame 800-2 in the horizontal direction is dx = L1+ (r + L + dL) cos θ -r (pi/2- θ) -6; since L1> =0, dL > = -0.1 × r, Km = L/r >0.4, dx is always greater than 0 in the range of [22 degrees, 90 degrees ] of the rotation angle θ of the center 406 of the top of the link plate 400-1, so that the carriage frame 800-1 does not meet the carriage frame 800-2; during the process of moving the top center 406 of the link plate of the load-carrying frame 800-1 from point M to point T2, the suspension beam axle guide 600 is located below point M due to the monotonicity of the suspension beam axle guide 600 at section CT2, and the load-carrying frame 800-1 does not meet the load-carrying frame 800-2 closely; therefore, in the chain plate length variable circulation type stereo garage transmission system of the present invention, the car carrying frame 800-1 located in the rotation region 1001 and the adjacent car carrying frame 800-2 located behind the same are only close to and meet at the point M.

Similarly, in the chain plate length variable circulation stereo garage transmission system of the present invention, the vehicle carrying frame 800-1 in the rotation region 1001 and the vehicle carrying frame 800 adjacent thereto and located at the lower part of the linear region 1000 are only close to meet when the center 406 of the top of the chain plate 400-1 is located at the point M'; the point M' is mirror symmetric with respect to the longitudinal axis 900 of the recycling-type stereo garage, so that the length D of the chain 300 between the chain plates 400 connected with the loading frame 800-1 and the loading frame 800-2 determines the longitudinal distance L1, L1 = D-w- (2) of the loading frame when the loading frame 800-1 and the loading frame 800-2 meet closely.

See fig. 4; in the circulating stereo garage transmission system in the prior art, the axis of the transmission wheel 200 is positioned at the point O', and the movement track 407 of the top center of the chain plate in the rotation area 1001 is semicircular; the length 404 of the chain plate and the radius 201 of the driving wheel are respectively equal to the length L of the chain plate 400-2 and the radius r of the driving wheel when the vehicle-carrying frames 800 in the transmission system of the chain plate length variable circulating stereo garage of the utility model meet closely; when the truck frame 800-1 and the truck frame 800-2 meet closely at point P, the link plate top center 406 of the link plate 400 connected to the truck frame 800-1 is also located at point M; at this time, the rotation angle of the top center 406 of the link plate 400 connected with the carriage frame 800-1 with respect to the axis O 'of the transmission wheel 200 is θ'; the longitudinal spacing of the carriage frame is L1', and L1' is shown as formula (2) '; the carriage transverse spacing is L2, and L2 is shown in formula (3).

In the utility model discloses a variable circulating stereo garage transmission system of link joint length, when link joint 400-1 moved to M point, the radius of gyration of carrying frame 800-1 equaled the sum of link joint length L + dL and drive wheel 200 radius r that are located M point position, namely r + L + dL, was greater than the radius of gyration r + L of carrying frame 800-1 in the circulating stereo garage transmission system scheme of prior art; since the carrier longitudinal spacing 801 is inversely related to the pivot radius of the carrier 800, L1< L1' with the same drive wheel radius r and the same link plate length L of the straight region 1000.

The above conclusions are quantitatively explained below by calculating the vehicle carrier longitudinal distance 801.

See fig. 5; in the chain plate length variable circulating stereo garage transmission system of the utility model, when the vehicle carrying frame 800-1 and the vehicle carrying frame 800-2 are close to meet, the horizontal distance between the center 406 of the top of the chain plate 400-2 connected with the vehicle carrying frame 800-2 and the axle center of the transmission wheel 200 is x 0; observing an OMQ of a right triangle, wherein the length of the OM is r + L + dL, the length of the OQ is h-r-L, the length of the QM, namely the distance between the M point and the axis of the driving wheel 200 along the direction of the longitudinal axis 900 of the circular stereo garage, is w-x0, and has Tan | theta | = (h-r-L)/(w-x 0) - (7), w-x0 = sqrt ((h + dL) ((2 x r +2 x L + dL-h)) - (8); the chain 300 between the link plates 400 connected to the load-carrying frames 800-1 and 800-2 comprises a section of the chain 300 in a straight area 1000 having a length of x0 and a section of the chain 300 in a turnaround area 1001 having a length of r (pi/2 + | theta |) and having a length of D; since the minimum value of D is w, there is, D = max (x0+ r (pi/2 + | θ |), w) — - (9); according to the formula (2) and the formula (9), the longitudinal spacing L1 of the carriage frame can be obtained as L1 = max (- (w-x0) + r ([ pi ]/2 + [ theta ]), 0) - (10).

See fig. 4; in the transmission system of the circulating stereo garage in the prior art, when the load-carrying frame 800-1 and the load-carrying frame 800-2 are close to meet, the horizontal distance between the top center 406 of the chain plate 400 connected with the load-carrying frame 800-2 and the axis O 'of the transmission wheel 200 along the longitudinal axis 900 of the circulating stereo garage is x 0'; the same principle as the chain plate length variable circulation type stereo garage transmission system of the utility model can obtain Tan | theta ' | = (h-r-L)/(w-x 0') - (11), w-x0' = sqrt (h _ (2 _r +2 _L-h)) - (12); the longitudinal spacing 801 of the vehicle carriers is L1' = max (- (w-x0') + r (pi/2 + | theta ' |),0) -13.

The length L + dL of the chain plate 400-1 positioned at the point M in the chain plate length-variable circulating stereo garage transmission system of the utility model is larger than the chain plate length L of the circulating stereo garage transmission system in the prior art; comparing formula (8) with formula (12), x0< x 0- > - (14), comparing formula (7) with formula (11) to obtain, | theta < | theta' | - (15); comparing the formula (10) with the formula (13) according to the formulas (14) and (15), and obtaining L1< L1'; therefore, under the circumstances of the same horizontal type circulating stereo garage drive wheel radius r and the same chain plate length L of the linear region 1000, the utility model discloses a chain plate length-variable circulating stereo garage transmission system's year car frame longitudinal separation L1 is less than prior art's horizontal type circulating stereo garage transmission system's year car frame longitudinal separation L1'.

In the chain plate length variable circulation type stereo garage transmission system of the utility model, according to the formula (7) and the formula (3), Tan | theta | = (h/2-L2/2)/(w-x 0) - (16) can be obtained; w-x0 = sqrt ((h + dL) × (L2+ dL)) - (17), as obtainable from formula (8) and formula (3); according to the formula (1) and the formula (2), r = (L2/2+ h/2)/(1+ K) - (18); according to the formula (10) and the formulas (16) to (18), the relationship curve between L1 and L2 in the chain plate length variable circulation type stereo garage transmission system of the present invention is obtained, as shown in fig. 6; fig. 6 includes three curves dL =0, 0.2h, 0.3h, and K = 0.9; when dL =0, equations (7), (8), (10) are the same as equations (11), (12), (13), respectively; therefore, the curve under the dL =0 condition also reflects the relationship between the vehicle carrier longitudinal spacing 801 and the vehicle carrier transverse spacing 802 of the circulating stereo garage in the prior art; as can be seen from fig. 6, when the vehicle frame transverse spacing 802 is smaller, the vehicle frame longitudinal spacing 801 of the circulating stereo garage and the vehicle frame transverse spacing 802 are in negative correlation.

The same principle as the circulating stereo garage transmission system in the prior art, the ratio K = L/r of the longitudinal distance 801 of the vehicle carrying frame of the circulating stereo garage transmission system with the chain plate length variable and the radius r of the transmission wheel of the chain plate length L in the linear region 1000 is negative correlation; analyzing equations (16) - (18) it can be seen that under the same L2 and dL, | θ | and w-x0 are also the same, independent of K, further analyzing equations (10) and (18) again yields that L1 is negatively correlated with K = L/r.

Under the same transverse distance L2 of the vehicle carrying frame, according to the formula (3), the sum L + r of the chain plate length of 1000 linear areas of the chain plate length variable circulating type stereo garage transmission system of the utility model and the radius 201 of the transmission wheel is the same as the sum L + r of the circulating type stereo garage transmission system of the prior art; under the same ratio K = L/r < = Km, the chain plate length variable circulating stereo garage transmission system L and r of the utility model are respectively the same as the circulating stereo garage transmission system L and r of the prior art; in the utility model discloses a variable circulating stereo garage transmission system of link joint length, in the moment that link joint 400 moves from linear region 1000 to gyration region 1001, and link joint 400 moves from gyration region 1001 to linear region 1000 in the moment, i.e. when link joint 400 moves to the T1 and the T2 position of hanging beam axle guide rail 600, because there is the impact force of circulating stereo garage's driving system through the application of drive wheel 200 to chain 300 and link axle 301, the ratio K = L/r of link joint length 404 and drive wheel radius 201 has an upper limit Km as shown in formula (1); because the distance between the suspension beam shaft guide rail 600 and the axle center of the driving wheel 200 is not more than the sum of the length L of the chain plate in the linear region 1000 and the radius r of the driving wheel at the positions of T1 and T2, the length of the chain plate 400 connected with the loading frame 800 at the positions is not more than the length L of the chain plate in the linear region 1000, and the ratio of the length 404 of the chain plate to the radius 201 of the driving wheel is less than or equal to Km, which meets the requirement of the formula (1); therefore, under the same carrier frame lateral spacing L2, for every K = L/r < = Km ratio, the utility model discloses a circulating stereo garage transmission system's of link joint length variable L1 all is less than prior art's circulating stereo garage transmission system's L1'.

Therefore, for the horizontal type circulating stereo garage, the conclusion can be drawn that under the condition of the same transverse distance 802 of the vehicle carrying frames, the longitudinal distance 801 of the vehicle carrying frames of the circulating stereo garage transmission system with the chain plates of the invention with the variable length is smaller than the longitudinal distance 801 of the vehicle carrying frames of the circulating stereo garage transmission system in the prior art; under the condition of accommodating the same number of vehicle-carrying frames 800, the circulating three-dimensional garage adopting the chain plate length-variable circulating three-dimensional garage transmission system has small volume; the conclusion that the vertical circulating stereo garage adopting the chain plate length variable circulating stereo garage transmission system is basically the same as the horizontal circulating stereo garage adopting the chain plate length variable circulating stereo garage transmission system is also established except that the working directions are different.

With w =2.4 meters, h =1.8 meters, r =0.6 meters, the adoption of L =0.5 meters the utility model discloses a circulating stereo garage parameter example of horizontal type of the variable circulating stereo garage transmission system of link joint length carries a car frame lateral separation L2=0.4 meters, in the distance of swing span axle guide 600 to drive wheel 200 axle center of gyration region 1001, with the linear region 1000 link joint length 404 with under the condition that the ratio of drive wheel radius 201 sum equals 1.3, carry car frame longitudinal separation L1 =0.

In order to obtain the smaller volume of the stereo garage, the transverse distance 802 of the vehicle carrying frames of the vertical circulating stereo garage of the chain plate length variable circulating stereo garage transmission system of the utility model is usually not more than 0.5w, correspondingly, the sum of the chain plate length 404 and the transmission wheel radius 201 is not more than 0.75w in the same way as the formula (3) of the horizontal circulating stereo garage; as another technical solution, when the sum of the chain plate length 404 and the transmission wheel radius 201 is not less than 0.75w, the vertical type circulating stereo garage adopting the chain plate length variable circulating stereo garage transmission system of the present invention includes two vehicle entrances and exits, see fig. 16; in the turning region 1001 located below, the suspension beam shaft guides 600 on the left and right sides are linear; in a turning region 1001 located below, the curvature radius of the suspension beam shaft guide rail 600 within the range of-30 ° turning angles is greater than 2 times of the sum of the length 404 of the chain plate of 1000 in the linear region and the radius 201 of the driving wheel, and the distance from the 0 ° turning angle of the suspension beam shaft guide rail 600 to the axis of the driving wheel 200 is 1.0-1.2 times of the sum of the length 404 of the chain plate in the linear region 1000 and the radius 201 of the driving wheel; the sections of the suspension beam shaft guide rails 600 are in smooth curve transition; two vehicle entrances and exits are arranged at two ends of a hanging beam shaft guide rail 600 at the bottom of a lower rotary area 1001 and at positions symmetrical to a longitudinal axis 900 of the circulating stereo garage; when the vehicle is stored and taken out, the chain 300 is rotated by the circulating stereo garage, so that two adjacent vehicle carrying frames 800 are respectively parked in the vehicle inlet and outlet.

In the vertical circulating stereo garage, when the sum of the length 404 of the chain plate and the radius 201 of the driving wheel is not less than 0.75w, two loading frames 800 can be simultaneously present in a lower turning area 1001; under the same longitudinal spacing 801 of the loading frames, the length D of the chain 300 between two adjacent loading frames 800 is the same according to the formulas (2) and (2)'; in the movement process of the two adjacent load carrying frames 800 in the rotation area 1001, the length of the chain 300 between the chain plates 400 connected with the two adjacent load carrying frames 800 is always kept as D, and the included angle phi between the top centers 406 of the chain plates 400 connected with the two load carrying frames 800 and the axis of the driving wheel 200 is phi, phi = D/r and is always kept unchanged; phi is inversely related to the drive wheel radius r.

In the vertical circulating type stereo garage in the prior art, the included angle phi is larger; if the radius r of the driving wheel is increased, the transverse distance 802 of the vehicle carrying frame is increased according to the formula (3), the volume of the stereo garage is increased, and the practical value is lost; if the transverse spacing 802 of the loading frames is kept unchanged, the radius r of the driving wheel is increased, along with the increase of the radius r of the driving wheel, according to a formula (3), L/r is reduced, two adjacent loading frames 800 are close to meet in a rotation area 1001, and the radius r = rm of the driving wheel at the moment; because the longitudinal spacing 801 of the vehicle-carrying frames is negatively related to L/r, when the radius r of the driving wheel is continuously increased and exceeds rm, the longitudinal spacing 801 of the vehicle-carrying frames is increased, D is increased, and phi is increased; therefore, under a certain vehicle carrier longitudinal spacing 801 and vehicle carrier transverse spacing 802, an upper limit rm exists on the radius r of the driving wheel, and the included angle phi between the top center 406 of the chain plate 400 connected with the two vehicle carriers 800 of the rotation area 1001 and the axle center of the driving wheel 200 is larger; when two adjacent vehicle carrying frames 800 respectively move to two sides of the lowest point of the rotation area 1001 and reach the same height, the distance between the two vehicle carrying frames 800 and the ground is large, so that vehicles cannot be accessed at the same time.

Referring to fig. 16, in the vertical type circulating stereo garage using the chain plate length variable circulating stereo garage transmission system of the present invention, under the condition that the same transmission wheel radius r, the same chain plate length L of the linear region 1000 and the same longitudinal distance 801 of the vehicle carrying frame as those of the vertical type circulating stereo garage of the prior art are adopted, the distance from the suspension beam shaft guide 600 to the axis of the transmission wheel 200 in the lower turning region 1001 is greater than r + L, and the turning radius of the vehicle carrying frame 800 is increased; therefore, when the radius r = rm of the driving wheel, the distance between two adjacent carriage frames 800 in the turning region 1001 is increased, and the approaching meeting does not occur until the radius r of the driving wheel is increased to exceed rm; therefore, adopt the utility model discloses a circulating stereo garage of perpendicular type of the changeable circulating stereo garage transmission system of link joint length, with two carry the link joint top center 406 of the link joint 400 that frame 800 links to each other and the contained angle phi in drive wheel 200 axle center than the circulating stereo car of perpendicular type of prior art the contained angle is little, when two carry frame 800 reachs the same height, two carry frame 800 and the distance on ground is little.

Adopt the utility model discloses an among the circulating stereo garage of vertical type of the variable circulating stereo garage transmission system of link joint length, the open angle that is located the gyration region 1001 bottom hanging beam axle guide rail 600 of below for the axle center of drive wheel 200 is not less than 60 degrees within ranges, the curvature radius of hanging beam axle guide rail 600 is greater than 2 times of the link joint length 404 in the linear region 1000 and the sum of drive wheel radius 201, compare with the semi-circular motion orbit of the link joint length 404 in the linear region 1000 and the sum of drive wheel radius 201 of the radius of the year frame 800 of the circulating stereo garage of vertical type of prior art, carry the motion orbit of frame 800 in gyration region 1001 bottom to be more close ground, two year frame 800 parking positions about consequently further are close to ground.

Therefore, in the vertical circulating stereo garage adopting the chain plate length variable circulating stereo garage transmission system of the utility model, when two adjacent vehicle carrying frames 800 in the lower turning region 1001 move to two sides of the longitudinal axis 900 of the circulating stereo garage and reach the same height, the distance between the two adjacent vehicle carrying frames 800 and the ground is small; by adopting the vertical circulating type stereo garage with the chain plate length variable circulating type stereo garage transmission system, the number of vehicles to be stored and taken is increased to two; when a plurality of users request to access the vehicle simultaneously, two vehicles can be accessed simultaneously through the once movement of the circulating stereo garage to the vehicle carrying frame 800, and the user waiting time is reduced.

In the turning region 1001, the toggle wheel disc 700 is engaged with the link plate toggle 403, which supports the link plate 400, and further drives the link plate movable arm 402 to push the suspension beam shaft 500 and the carriage frame 800 to move.

Example 1; as shown in fig. 7-15, the present invention relates to a chain plate length variable transmission system for a circulation type stereo garage, comprising,

front and rear two sets of driving wheels 200, the axes of which are parallel to each other, for driving the chain 300 to rotate;

a plurality of chain plates 400 are fixedly arranged on the two chains 300 at equal intervals and correspondingly;

the hanging beam shaft 500 of the hanging loading frame 800 is hinged with the chain plate 400 through a bearing;

the chain plate 400 is composed of a chain plate fixing arm 401 and a chain plate movable arm 402, the chain plate fixing arm 401 of the chain plate 400 is fixed on the chain 300, the lower part of the chain plate movable arm 402 is arranged in the chain plate fixing arm 401, and the chain plate fixing arm 401 is in sliding connection with the lower part of the chain plate movable arm 402; in the rotation region 1001, the suspension beam shaft guide rail 600 is an n-shaped arc continuous change curve; by the sliding connection and cooperation of the link plate movable arm 402 and the link plate fixed arm 401, the suspension beam shaft guide 600 constrains the link plate movable arm 402 of the link plate 400 to undergo telescopic change in the length direction of the link plate 400 as the position of the suspension beam shaft guide 600 changes.

As shown in fig. 12-14; the two ends of the bottom of the chain plate fixing arm 401 are respectively fixed on two adjacent link shafts 301 of the chain 300; two ends of the hanging beam shaft 500 are provided with hanging beam shaft rollers 501; the hoist beam axle roller 501 rolls in the hoist beam axle guide 600.

As shown in fig. 7-10; the chain plate fixing arm 401 is fixedly provided with a chain plate deflector rod 403 parallel to the axis of the driving wheel 200 at the top; the chain plate shift lever 403 is positioned on a vertical plane of the connecting line of the end points on the same side of the two link shafts 301 of the fixed chain plate 400; the poking wheel disc 700 is coaxially arranged on one side of the driving wheel 200, and the poking wheel disc 700 is meshed with the chain plate poking rod 403 through the wheel disc tooth groove 701 to drive the chain plate poking rod 403 to rotate; the number of the gear grooves 701 on the dial wheel disc 700 is equal to that of the gear grooves of the driving wheel 200; the wheel disc tooth grooves 701 are positioned on a bisector of an included angle between two adjacent tooth grooves of the driving wheel 200 and the axis of the driving wheel 200.

In the range of the rotation angle of (34-40) and [ -40-34 ] of the hanging beam shaft guide rail 600 in the rotation region 1001, the distance from the hanging beam shaft guide rail 600 to the axle center of the driving wheel 200 is 1.5 times the sum of the length 404 of the chain plate in the linear region 1000 and the radius 201 of the driving wheel.

In the rotation region 1001, within the rotation angle ranges of 70-90-and-90-70-of the hanging beam shaft guide rail 600, the hanging beam shaft guide rail 600 is linear; in the range of-20 rotation angles of the 1001 hanging beam shaft guide rail 600 in the rotation region, the hanging beam shaft guide rail 600 is linear and is vertical to a longitudinal shaft 900 of the circulating type stereo garage; the sections of the boom axle guide rails 600 in the turning area 1001 are smoothly connected with each other by the curved profile of the boom axle guide rail 600.

As shown in fig. 7-15, the embodiment of the horizontal type circulating stereo garage of the present invention is working.

In the linear region 1000, a suspension beam shaft guide 600 parallel to the chain 300 is respectively arranged on the support frame 100, the chain 300 is driven by the driving wheel 200 to drive the link plate fixing arm 401 and the link plate movable arm 402 of the link plate 400 fixed on the chain 300 to move along the horizontal direction through the link shaft 301, the link plate movable arm 402 is inserted into the link plate fixing arm 401, the suspension beam shaft 500 is connected with the link plate movable arm 402, at this time, the link plate movable arm 402 is in a contraction state, and the length of the link plate 400 is minimum.

In the rotation area 1001, the suspension beam shaft guide rails 600 are respectively arranged on two sides of the support frame 100 around the transmission wheel 200, and the suspension beam shaft guide rails 600 are positioned in a plane parallel to the track plane of the chain 300; the hanging beam shaft 500 is supported by the rolling of the hanging beam shaft roller 501 in the hanging beam shaft guide 600, and meanwhile, the link plate movable arm 402 extends and retracts along with the position of the hanging beam shaft guide 600, and at the moment, the link plate movable arm 402 is in an extending state.

The top of the chain plate fixing arm 401 is fixedly provided with a chain plate deflector rod 403 parallel to the axis of the driving wheel 200, and the chain plate deflector rod 403 is positioned on a vertical plane parallel to the connecting line of the end points at the same side of the two chain shaft 301 shafts of the fixed chain plate 400; in order to ensure the normal operation of the link plate movable arm 402 driving the hanging beam shaft 500, the driving wheel disc 700 coaxial with the driving wheel 200 is engaged with the link plate driving lever 403 through the wheel disc tooth space 701, and further drives the link plate movable arm 402 to drive the hanging beam shaft 500 and the carrier frame 800 to move.

The embodiment of the vertical circulating stereo garage is basically the same as the embodiment of the horizontal circulating stereo garage except that the working directions are different, and the principle is basically the same, so repeated description is omitted here.

Example 2; as shown in fig. 16, the present invention relates to a chain plate length variable transmission system for a circulating type stereo garage, comprising,

As shown in fig. 16, two vehicle entrances and exits are provided on the left and right sides of a revolving area 1001 in which the vertical type circulation type stereo garage is located below, which is symmetrical to a vertical axis 900 of the circulation type stereo garage.

Within the range of-35-degree rotation angle of the hanging beam shaft guide rail 600 in the rotation region 1001 located below, the hanging beam shaft guide rail 600 is linear, the linear hanging beam shaft guide rail 600 is perpendicular to the longitudinal axis 900 of the circulating type stereo garage, and the perpendicular distance from the axis of the driving wheel 200 is 1.1 times of the sum of the length 404 of the chain plate in the linear region 1000 and the radius 201 of the driving wheel.

Within the range of the turning angle between [ 55-90 ] and [ -90-55 ] of the hanging beam shaft guide rail 600 in the turning region 1001 located below, the hanging beam shaft guide rail 600 is linear.

The sections of the boom axle guide rails 600 in the lower swing area 1001 are smoothly connected by the curved profile of the boom axle guide rails 600.

The suspension beam shaft guide 600 of the upper turning area 1001 is semicircular, and the radius of the semicircular is equal to the sum of the chain plate length 404 in the straight area 1000 and the radius 201 of the transmission wheel.

As shown in fig. 16, the transmission system of the link plate length variable circulation type stereo garage of the embodiment is in operation.

In a lower turning area 1001, suspension beam shaft guide rails 600 are respectively arranged on the front side and the rear side of the support frame 100; the hanging beam shaft guide rail 600 supports the hanging beam shaft 500 by the rolling of the hanging beam shaft roller 501 in the hanging beam shaft guide rail 600, and meanwhile, the chain plate movable arm 402 extends and retracts along with the position of the hanging beam shaft guide rail 600, and at the moment, the chain plate movable arm 402 is in an extending state; in linear region 1000 and upper turnaround region 1001, link plate movable arm 402 is in a retracted state; when the circulating stereo garage receives vehicle access requests of a plurality of users, the requests of two adjacent vehicle carrying frames 800 related to the vehicle access requests of the users are selected to respond, the chain plate 400 is driven by the chain 300 to move, the two adjacent vehicle carrying frames 800 are moved to the two vehicle entrances and exits, and the users store the vehicles into the vehicle carrying frames 800 or take the vehicles from the vehicle carrying frames 800; and the circulating type stereo garage continuously responds to the vehicle access requests of the users according to the same method until all the vehicle access requests are responded.

In the above embodiments of the technical solution of the present invention, the guide rail of the carriage carrier 800 and the carriage carrier 800 holding device on the carriage carrier 800 are further provided, so that the carriage carrier 800 is always ensured to be in a horizontal state no matter where the carriage carrier 800 is located; a chain 300 guide rail is arranged beside the chain 300 in the linear area 1000, and the chain 300 moves along the chain 300 guide rail; the carriage frame 800 retaining means and chain 300 guide are prior art and will not be described again here.

The above description is only a preferred and practical embodiment of the present invention, and is not intended to limit the scope of the present invention.

Claims

1. A chain plate length variable circulating type stereo garage transmission system comprises a front group of transmission wheels and a rear group of transmission wheels, wherein the axes of the transmission wheels are parallel to each other and drive a chain to rotate;

the chain plate is characterized by comprising a chain plate fixing arm and a chain plate movable arm, wherein the chain plate fixing arm of the chain plate is fixed on a chain, and the chain plate movable arm of the chain plate is in telescopic connection with the chain plate fixing arm; the suspension beam shaft guide rail in the rotation area is an n-shaped arc continuous change curve; through the connection and matching of the chain plate movable arm and the chain plate fixed arm, the chain plate movable arm of the hanging beam shaft guide rail constraint chain plate is subjected to telescopic change in the length direction of the chain plate along with the position change of the hanging beam shaft guide rail.

2. The transmission system of the chain plate length variable circulating type stereo garage of claim 1, wherein two ends of the bottom of the chain plate fixing arm are respectively fixed on two adjacent chain link shafts of the chain; the steering device is a bearing, and the chain plate movable arm is hinged with the hanging beam shaft through the bearing; the left end and the right end of the hanging beam shaft are provided with hanging beam shaft rollers; the hanging beam shaft roller rolls in the hanging beam shaft guide rail.

3. The chain plate length variable circulating type stereo garage transmission system according to claim 1 or 2, further comprising a chain plate deflector rod and a deflector wheel disc, wherein the top of the chain plate fixing arm is fixedly provided with a chain plate deflector rod parallel to the axis of the transmission wheel; the poking wheel disc is coaxially arranged on one side of the driving wheel or is concentrically fixed on the driving wheel, and the poking wheel disc is matched with the chain plate poking rod through a catching device arranged on the outer edge of the poking wheel disc to drive the chain plate poking rod to rotate.

4. The link plate length variable circulating stereo garage transmission system of claim 3, wherein the engaging device is a wheel disc tooth groove on a driving wheel disc, and the driving wheel disc is meshed with the link plate driving lever through the wheel disc tooth groove.

5. The circulating type stereo garage transmission system with variable chain plate lengths according to claim 1 or 2 is characterized in that in the range of the rotating angle interval of the suspension beam shaft guide rail (34-40) and [ -40-34 ]), the distance from the suspension beam shaft guide rail to the axis of the transmission wheel is 1.2 to 1.65 times of the sum of the length of the chain plate in the linear region and the radius of the transmission wheel.

6. The circulating type stereo garage transmission system with variable chain plate lengths according to claim 1 or 2 is characterized in that in the range of the rotating angle interval of the suspension beam shaft guide rail (28-34) and [ -34-28 ]), the distance from the suspension beam shaft guide rail to the axis of the transmission wheel is 1.2 to 1.6 times of the sum of the length of the chain plate in the linear region and the radius of the transmission wheel.

7. The circulating type stereo garage transmission system with variable chain plate lengths according to claim 1 or 2 is characterized in that in the range of the revolving angle between [ 22-28 ] and [ -28-22 ] of the hanging beam shaft guide rail in the revolving region, the distance from the hanging beam shaft guide rail to the axis of the transmission wheel is 1.15 to 1.45 times the sum of the length of the chain plate in the linear region and the radius of the transmission wheel.

8. The circulating type stereo garage transmission system with the variable-length chain plates according to claim 1 or 2, is characterized in that the curvature radius within the range of the rotation angle between-30 degrees of the hanging beam shaft guide rail in the rotation region below is greater than 2 times of the sum of the length of the chain plates in the linear region and the radius of the transmission wheel, and the distance from the rotation angle of 0 degree of the hanging beam shaft guide rail to the axis of the transmission wheel is 1.0-1.2 times of the sum of the length of the chain plates in the linear region and the radius of the transmission wheel.

9. The link plate length-variable circulating type stereo garage transmission system according to claim 1 or 2, characterized in that the beam shaft guide is linear within the ranges of [ 65-90 ] and [ -90-65 ] pivot angles of the beam shaft guide in the pivot region located below.