CN218780072U - Formula of hiding car carrier based on external drive - Google Patents
Formula of hiding car carrier based on external drive Download PDFInfo
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- CN218780072U CN218780072U CN202222705968.7U CN202222705968U CN218780072U CN 218780072 U CN218780072 U CN 218780072U CN 202222705968 U CN202222705968 U CN 202222705968U CN 218780072 U CN218780072 U CN 218780072U
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Abstract
The utility model discloses a submarine automobile carrier based on external drive, belonging to the technical field of automobile carriers and comprising a support main body, wherein a support platform for supporting an automobile chassis is arranged in the middle of the support main body, linear guide rails are arranged on two sides of the support platform in parallel, two driving motors with opposite installation directions are arranged in the middle of the support platform in parallel, and the output ends of the driving motors are both connected with a first lead screw; the two clamping assemblies are respectively positioned at two ends of the bracket main body, the distance between the two clamping assemblies is adjustable, the clamping assemblies are used for clamping automobile tires, the clamping assemblies are connected with the first lead screw through nut seats, and the clamping assemblies are in rolling connection with the linear guide rail through sliding blocks; and the elastic supporting wheel assemblies are positioned on two sides of the support main body and are used for supporting when the support main body moves and the supporting height is adjustable. The utility model provides a formula of hiding car carrier based on external drive has improved vehicle handling speed, has reduced the usage space, applicable ordinary parking place, and the commonality is stronger.
Description
Technical Field
The utility model belongs to the technical field of automobile carrier, more specifically relates to a formula of hiding automobile carrier based on external drive.
Background
In people's daily life, it is difficult to park a car, and a planar parking mode is not more and more suitable for a rapidly developing society, and the occurrence of a stereo garage solves the problem in time, but the popularization of the stereo garage and the mature and perfect technology also need a development process.
The stereo garage adopts the automobile carrier to transport the automobile to embrace through the centre gripping subassembly and press from both sides the completion to lifting the vehicle to automobile tire more. The existing clamping assembly mostly adopts transmission structures such as worm and gear, gear rack, chain wheel and chain, gear transmission and the like. When the structure transmission more than adopting, the transmission part atress is very big to under the circumstances of guaranteeing equipment operating speed, the power and the volume that need the motor are great, and require very high to frame construction, need have certain intensity, thereby lead to fixture's whole volume great, need occupy great usage space. And the gear transmission and the chain wheel transmission have no structural dead points, and the mechanism is locked by the motor or the band-type brake force. If the motor is damaged or suddenly cut off the power supply and other sudden conditions occur, the clamping rod is forced to open automatically, so that the automobile is in a risk of falling. Because the wheel base of each style car is different, for the transport work of the various motorcycle types of adaptation, the centre gripping subassembly still need possess apart from the regulatory function. The automobile carrier can be divided into a hidden type and an external holding type according to the working form.
The latent carrier has more applications, and the working form is that the equipment is submerged at the bottom of an automobile, and the automobile is lifted by the clamping assembly and then carried. The existing latent carrier adopts a self-walking mode, one or more bearing wheels of equipment are driven by a motor to serve as driving wheels, and the driving force for walking of the equipment is provided by the friction force of the ground. And all the wheel trains are rigidly connected with the equipment main body. The existing latent carrier is divided into a front part and a rear part which independently move, and the front part and the rear part respectively move to different positions to adapt to the wheel base of a vehicle. The conventional concealed carrier has the following disadvantages in terms of its structure and driving method. Because the height and the size of the carrier are limited in order to submerge into the bottom of a vehicle, the diameters of the supporting wheels and the driving wheels are limited, the wheel train with the too small diameter passes through a seam and a ridge and passes through a slope extremely poorly, and the weight of the vehicle and equipment is large, the equipment shakes violently or deviates from the original form track directly due to the inertia force in the process of rapidly carrying the vehicle, and if the driving wheels meet the seam or the hollow section, the driving force is lost when the driving wheels are separated from the ground, and the equipment is stopped. The equipment operates at very low speeds without external guidance. In addition, due to the shaking and driving principle, even under the condition of external guiding, higher equipment failure rate is high due to speed increase or pit contact in the case of seam. The existing latent carriers which are put into practical use increase the equipment thickness and the diameter of supporting wheels, the thickness exceeds the ground clearance of the chassis of a conventional vehicle, and the latent carriers are matched with external guide for use. The equipment cannot be used on the flat ground of a common parking lot, and the equipment must be used on a special field which is dug to be provided with a groove and is provided with mechanical guide, has higher requirement on the flatness of the field, and does not have good universality. And high-speed operation cannot be really achieved. These also contribute to an extremely poor user experience and market acceptance.
The working mode of the outer clamp carrier is to clamp the vehicle from two sides of the vehicle. Because the device is not limited by space height, the device can adopt a large-diameter tire and a high-power motor, and the volume of the device is greatly increased. Thereby improving the running speed and stability of the equipment. But also reduces the space utilization rate and causes great scratch and rub to collide the appearance of the vehicle to the risk of damaging the vehicle. Therefore, although the speed is higher, the form is rarely practically used compared to the latent carrier.
SUMMERY OF THE UTILITY MODEL
To the defect of prior art, the utility model aims to provide a formula of hiding automobile carrier based on external drive aims at solving the whole thickness of formula of hiding automobile carrier and is thicker, crosses to sew over the bank ability poor, and the functioning speed is on the low side, the not enough problem of operating stability. The hidden type automobile carrier can rapidly, efficiently and stably carry vehicles covering most automobile models in the market in the common flat parking scene, and meanwhile, the safety of equipment in an emergency situation is improved.
In order to achieve the above object, the utility model provides a formula of hiding automobile carrier based on external drive, including:
the automobile chassis support comprises a support main body, wherein a support platform for supporting an automobile chassis is arranged in the middle of the support main body, linear guide rails are arranged on two sides of the support platform in parallel, two driving motors with opposite installation directions are arranged in the middle of the support platform in parallel, and output ends of the driving motors are connected with first lead screws;
the two clamping components are respectively positioned at two ends of the bracket main body, the distance between the two clamping components is adjustable, the two clamping components are used for clamping automobile tires, the clamping components are connected with the first lead screw through nut seats, the clamping components are connected with the linear guide rail through sliding blocks in a rolling manner, and when the driving motor works, the first lead screw drives the clamping components to move in the opposite direction or in the opposite direction;
the elastic supporting wheel assemblies are respectively positioned on two sides of the support main body and used for supporting when the support main body moves and adjusting the supporting height, and floating adjusting gaps are formed between the elastic supporting wheel assemblies and the support main body.
Furthermore, the centre gripping subassembly is including the mounting bracket, the mounting bracket bilateral symmetry is equipped with clamping bar mechanism, follow on the mounting bracket support subject length direction is fixed with drive arrangement, clamping bar mechanism including with the centre gripping drive plate that drive arrangement's output is connected, centre gripping drive plate both ends are rotated and are connected with the connecting rod, the other end of connecting rod is rotated and is connected with the clamping bar, the mounting bracket with the centre gripping drive plate all with linear guide's slider is connected, drive arrangement can drive the centre gripping drive plate moves dorsad or in opposite directions and then drives the connecting rod rotates and makes the clamping bar rotation is opened or is pressed from both sides tightly.
Furthermore, the elastic supporting wheel assembly comprises a supporting wheel frame, a supporting wheel is transversely arranged in the middle of the supporting wheel frame, first pin shafts are arranged at two ends of the supporting wheel frame and are connected with the support main body in a sliding mode through linear bearings, a spring is sleeved on each first pin shaft, the upper end of each spring is attached to the lower end face of the support main body, the lower end of each spring is attached to the end face of the supporting wheel frame, and the spring has the tendency of driving the supporting wheel frame to move downwards.
Furthermore, drive arrangement is including first motor, the output of first motor is connected with the second lead screw, the second lead screw is worn to establish on the mounting bracket and both ends with the mounting bracket passes through the bearing and rotates the connection, the axle head of second lead screw pass through the shaft coupling with first motor fixed connection, the screw thread of second lead screw is soon to following divide into levogyration and dextrorotation in the middle of the mounting bracket, the second lead screw pass through the nut seat with the centre gripping drive plate is connected, the second lead screw rotates the drive the motion of centre gripping drive plate and then drives the clamping bar is opened or is pressed from both sides tightly.
Furthermore, the clamping rod and the mounting frame are rotatably connected through a turntable bearing, a clamping rod mandrel penetrates through the turntable bearing, the bottom of the clamping rod mandrel is fixed with the mounting frame, a needle bearing is sleeved on the upper end of the clamping rod mandrel and fixed with the clamping rod, a second pin shaft is arranged on the clamping drive plate and the clamping rod, a shaft sleeve is sleeved on the second pin shaft, and the connecting rod is rotatably connected with the clamping drive plate and the clamping rod through the shaft sleeve.
Further, first lead screw with the second lead screw is followed support subject length direction parallel arrangement, first lead screw with the second lead screw distributes and sets up 1 width direction central line both sides of support subject, first lead screw is worn to establish support platform is last and both ends with support platform passes through the bearing and rotates the connection, the axle head of first lead screw pass through the shaft coupling with driving motor fixed connection, the spacing groove has been seted up at support subject both ends, first lead screw with the second lead screw all wears to be located the spacing inslot.
Furthermore, the two ends of the support wheel frame are provided with limiting faces with the same height, the middle of the support wheel frame is symmetrically provided with limiting bosses, the support main body is provided with limiting holes corresponding to the limiting bosses, and the lower end faces of the limiting faces and the support main body are provided with floating adjusting gaps.
Furthermore, still including drive mechanism includes the fixed bolster, the fixed bolster bilateral symmetry is equipped with the linear motion subassembly, the symmetry is equipped with the secondary drive spare in the middle of the fixed bolster, the equal swing joint of output of linear motion subassembly has the driving plate, the driving plate with secondary drive spare fixed connection, it is connected with driven gear to rotate on the secondary drive spare, be fixed with the driving rack along length direction on the fixed bolster, support main part below is fixed with driven rack along length direction, the driving rack with driven rack parallel arrangement and all with driven gear engagement, the linear motion subassembly during operation can drive driven gear pivoted while and edge support main part length direction reciprocating motion, and then drive support main part is along length direction reciprocating motion.
Further, be equipped with on the second grade driving medium be used for with driven gear rotates the installation department of connecting, the installation department top is followed support subject length direction is equipped with the guide part, the guide part lateral wall is equipped with first spout along the length direction symmetry, on the fixed bolster along the length direction equipartition with first spout position corresponds, the same first roller group of quantity, the second spout has been seted up in the support subject, on the guide part along the length direction equipartition have with the second roller group that the second spout corresponds.
Furthermore, the first roller group and the second roller group have the same structure, the first roller group comprises a first roller support, first rollers are uniformly distributed on the first roller support, and first guide wheels are arranged at two ends of the first roller support.
Generally, through the utility model discloses above technical scheme who conceives compares with prior art, has following beneficial effect:
1. the clamping assembly drives the clamping drive plate to do linear motion through the first motor and the second lead screw, then the linear motion of the clamping drive plate is converted into rotary motion of the clamping rod through the transmission of the connecting rod, so that the clamping rod is controlled to be opened and clamped, and the clamping assembly is matched with a rotary table bearing, a needle bearing and a linear guide rail which have extremely high load capacity and extremely low friction coefficient to respectively support and guide the motion of the clamping rod and the clamping drive plate. The transmission and guide structure reduces the load of the first motor and increases the mechanical self-locking function. And by combining the motion design, the clamping driving plate can complete the whole conversion of the rotary motion of the clamping rod by a very small linear motion stroke. Thereby realized under the condition of guaranteeing clamping assembly functioning speed and structural strength, reduced the power demand and the volume size of first motor, and then reduced the omnidirectional size of clamping assembly by a wide margin to the security of clamping assembly has been improved.
2. The size based on the clamping assembly is reduced, so that two groups of clamping assemblies used for clamping the front wheel and the rear wheel of the vehicle are arranged inside the integral support main body, and the requirement for adjusting the wheel base of most vehicle types is met. Two sets of clamping components are driven to move linearly through the driving motor and the first lead screw, and the linear guide rail with extremely strong load capacity and extremely low friction coefficient supports and guides the movement of the clamping components. The rolling friction coefficient of the linear guide rail is far lower than that of the rubber covered wheel, so that the load of the driving motor is greatly reduced. Meanwhile, the ball screw further has higher transmission precision. And further, the power requirement and the volume of the driving motor are greatly reduced, and the control precision of the wheel base adjustment is improved.
3. Because in the vehicle handling process, wheel base adjusting action and vehicle centre gripping action can not go on simultaneously, the rectilinear motion who sets up centre gripping drive plate and centre gripping subassembly provides support and direction by same group linear guide. The first lead screw and the second lead screw are arranged in parallel along the length direction of the support main body and are distributed on two sides of the central line of the support main body in the width direction. Therefore, the installation space of each main part is reduced, and the design of the structures of other parts is compactly processed, so that the size of the whole carrier in the height and width directions is reduced, the whole height of the carrier is within the height from the chassis of most vehicle types in the market to the ground, and the function of carrying the vehicle by submerging various vehicle bottoms on the flat ground of a common parking lot is realized. The universality of the carrier is greatly improved.
4. In addition, the elastic supporting wheel assemblies are arranged on the two sides of the support main body, all the elastic supporting wheel assemblies are driven wheels, only the carrier is supported, and only auxiliary support is provided at most, the supporting height can be changed, and the elastic supporting wheel assemblies are matched with springs to have a certain buffering and damping effect. Therefore, the impact influence of road conditions on the smaller polyurethane wheels is reduced to a certain degree, and the carrier is prevented from shaking violently in the vehicle carrying process, so that the carrier has certain gap-passing, sill-passing and slope-passing capacity, and the running stability of the carrier is improved.
5. In addition, the transmission mechanism of the external drive is arranged outside the carrier, and the second motor only runs in the transmission mechanism, so that the interference of external factors such as the ground and the like is avoided in the working process, and therefore the stable driving force can be provided for the carrier, and the phenomena of power loss and the like are avoided. And the transmission mechanism is fixed outside the vehicle stop position and is not limited by space, and a second motor with enough power and enough size can be selected as required, so that the running speed of the carrier is greatly improved. The transmission mechanism adopts gear rack transmission to realize speed-multiplying stroke output, drives the support main body to move, and further improves the carrying efficiency. The fixed support that drive mechanism includes still is equipped with first roller group and second grade driving medium, is equipped with the guide part on the second grade driving medium, is equipped with first spout and second roller group in the guide part. The bracket main body is also provided with a second sliding chute. The secondary transmission part is driven by the second motor to do bidirectional shuttling linear motion, and the first roller group provides support and guide for the first sliding groove. The secondary transmission part drives the carrier to do bidirectional shuttling linear motion, and the second roller group provides support and guide for the second sliding chute. The stroke of the carrier is always twice that of the secondary transmission member. The carrier is primarily supported by the first and second roller sets during operation, and the resilient support wheel assembly provides additional support and forms an internal guide mechanism within the carrier. Therefore, the carrier can stably run at a high speed under the condition of no external guide, and can be suspended to run in a certain range close to the transmission mechanism. Thus, in practical applications, the transmission mechanism can be intentionally placed slightly above the target plane to eliminate the threshold. And then the elastic supporting wheel component is matched, so that the gap-crossing, ridge-crossing and slope-crossing capacity of the concealed carrier is greatly improved, and the real rapid and stable vehicle carrying work is realized.
Drawings
Fig. 1 is a schematic structural view of an external drive-based concealed automobile carrier provided by the invention;
fig. 2 is a top view of an external drive based concealed vehicle carrier provided by the present invention;
FIG. 3 is a partial cross-sectional view of a carrier body for an externally powered concealed vehicle carrier according to the present invention;
fig. 4 is a schematic view of the clamp assembly of the external drive based concealed vehicle carrier provided by the present invention;
FIG. 5 is a schematic view of the resilient support wheel assembly of the external drive-based concealed vehicle carrier provided by the present invention;
FIG. 6 is a partial cross-sectional view of the clamp assembly of the external drive based concealed vehicle carrier provided by the present invention;
fig. 7 is a partial cross-sectional view of a clamping bar mechanism of an externally powered concealed vehicle carrier according to the present invention;
fig. 8 is an installation cross-sectional view of the clamping bar mechanism of the external drive-based concealed vehicle carrier provided by the present invention;
FIG. 9 is a cross-sectional view of the resilient support wheel assembly of the external drive based concealed vehicle carrier provided by the present invention;
FIG. 10 is a schematic assembly view of the external drive based transmission mechanism of the concealed vehicle carrier provided by the present invention;
fig. 11 is a schematic view of the internal structure of the transmission mechanism of the external drive-based concealed automobile carrier according to the present invention;
fig. 12 is a half sectional view of the transmission mechanism of the external drive based concealed vehicle carrier provided by the present invention;
FIG. 13 is an enlarged view of a portion of FIG. 12 at A;
fig. 14 is a schematic structural view of a first roller set of the external drive-based concealed vehicle carrier according to the present invention;
fig. 15 is a schematic structural view of a second roller set of the external drive-based concealed vehicle carrier according to the present invention;
fig. 16 is a schematic view of the initial state of the external drive based clamp assembly of the concealed vehicle carrier provided by the present invention;
fig. 17 is a schematic view of a second state of the external drive based clamp assembly for a latent automotive carrier according to the present invention;
fig. 18 is a third state schematic diagram of the external drive based clamp assembly of the concealed vehicle carrier according to the present invention;
fig. 19 is a schematic view of the force analysis at the instant when the gripping assembly of the external drive-based concealed vehicle carrier contacts the tire;
fig. 20 is a schematic view of the force analysis of the tire clamping process of the clamping assembly of the external drive based concealed vehicle carrier according to the present invention;
fig. 21 is a schematic view of the force analysis of the clamping assembly of the latent automobile carrier based on external driving according to the present invention;
fig. 22 is a schematic view illustrating the force analysis of the second lead screw of the latent automobile carrier based on external driving according to the present invention;
fig. 23 is a schematic view illustrating a force analysis of the first lead screw of the latent automobile carrier based on external driving according to the present invention;
fig. 24 is a schematic view of a state of the vehicle carried by the latent vehicle carrier based on external driving provided by the present invention;
fig. 25 is a schematic view of a state of the external drive based concealed automobile carrier pick-up and delivery vehicle provided by the present invention;
fig. 26 is a schematic diagram of a first stage of an external drive based latent automobile carrier delivery process provided by the present invention;
FIG. 27 is a partial cross-sectional view at B in FIG. 26;
fig. 28 is a schematic view of an intermediate stage of the external drive based latent automobile carrier delivery process provided by the present invention;
FIG. 29 is a partial cross-sectional view at C of FIG. 28;
FIG. 30 is a partial cross-sectional view taken at D of FIG. 28;
fig. 31 is a schematic diagram of the final stage of the external drive based latent automobile carrier delivery process provided by the present invention;
FIG. 32 is a partial cross-sectional view at E of FIG. 31;
fig. 33 is a partial sectional view at F in fig. 31.
The structure corresponding to each numerical mark in the drawings is as follows: 1-support body, 11-support platform, 12-linear guide, 13-drive motor, 14-first lead screw, 15-linear bearing, 16-limit groove, 17-limit hole, 18-driven rack, 19-second sliding groove, 2-clamping component, 21-mounting frame, 211-mounting frame body, 212-mounting seat, 213-nut mounting position, 22-clamping rod mechanism, 221-clamping drive plate, 222-connecting rod, 223-clamping rod, 224-turntable bearing, 225-clamping rod mandrel, 226-needle roller bearing, 227-second pin shaft, 227-shaft sleeve, 23-drive device, 231-first motor, 232-second lead screw, 3-elastic support wheel component, 31-support wheel frame, 311-limit surface, 312-limit boss, 32-support wheel, 33-first pin shaft, 34-spring, 4-transmission mechanism, 41-fixed support, 411-linear guide, 412-drive rack, 413-rack, 414-first transmission set, 41-first transmission set, 4142-first support, 4142-first roller, 4142-second roller support, 4342-second roller guide wheel, 4342-guide wheel, 4344-second roller guide wheel, 4333-second roller guide wheel, 4319-second guide wheel, 4333-second guide wheel set, 4333-guide wheel, 4319-second roller guide wheel, 4344-second roller guide wheel, 4319-guide wheel set, 4344-guide wheel, 4319-second roller guide wheel, 4344-guide wheel set, 4319-guide wheel set, and 4344-guide wheel set.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Referring to fig. 1 to 33, the utility model discloses latent formula car carrier based on external drive, including support main body 1, be equipped with the supporting platform 11 that is used for supporting vehicle chassis in the middle of support main body 1, supporting platform 11 both sides parallel are equipped with linear guide 12, linear guide divide into roll formula linear guide and slidingtype linear guide, be equipped with the roller between the slider on the roll formula linear guide and the guide rail, be rolling friction between slider and the guide rail, coefficient of friction is less, and slidingtype linear guide, be sliding friction between slider and the guide rail, coefficient of friction is great, roll formula linear guide is selected to use in this embodiment; two driving motors 13 with opposite installation directions are arranged in parallel in the middle of the supporting platform 11, and the output ends of the driving motors 13 are connected with first lead screws 14; the two clamping assemblies 2 are respectively positioned at two ends of the bracket main body 1, the distance between the two clamping assemblies 2 is adjustable, the clamping assemblies 2 are connected with the first lead screw 14 through nut seats, the clamping assemblies 2 are connected with the linear guide rail 12 through slide blocks in a rolling manner, and when the driving motor 13 works, the first lead screw 14 drives the clamping assemblies 2 to move in the opposite direction or the opposite direction, so that the two clamping assemblies 2 are suitable for the wheelbases (namely the distance between front and rear tires of an automobile) of different automobile types and clamp automobile tires; a plurality of elastic support wheel subassemblies 3 are located 1 both sides of support main part respectively for support and support height-adjustable when the support main part removes, for convenient the application in the occasion that has the slope bank, and when the local pressurized deformation takes place for the support main part, the motion can not the jamming, is equipped with the unsteady regulation clearance between elastic support wheel subassembly 3 and the support main part 1, combines specific embodiment to explain each part in detail below.
Specifically, referring to fig. 4 and 6, the clamping assembly 2 is an important component of automobile transportation, which needs to overcome the gravity of the whole automobile to complete lifting of the automobile, the clamping assembly 2 includes an installation frame 21, clamping rod mechanisms 22 are symmetrically arranged on two sides of the installation frame 21, a driving device 23 is fixed on the installation frame 21 along the length direction of the support main body 1, the clamping rod mechanism 22 includes a clamping driving plate 221 connected with the output end of the driving device 23, two ends of the clamping driving plate 221 are rotatably connected with a connecting rod 222, the other end of the connecting rod 222 is rotatably connected with a clamping rod 223, the clamping driving plate 221 is connected with the linear guide rail 12 through a sliding block in a rolling manner, the driving device 23 can drive the clamping driving plate 221 to move linearly, and further drive the clamping rod 223 through the connecting rod 222, so that the linear motion of the clamping driving plate 221 is converted into a rotary motion of the clamping rod 223, and the clamping rod 223 is opened or clamped.
In this embodiment, the driving device 23 is driven by a motor, specifically, referring to fig. 5 to 6, the driving device 23 includes a first motor 231, an output end of the first motor 231 is connected with a second lead screw 232, the second lead screw 232 is disposed on the mounting frame 21 in a penetrating manner, and both ends of the second lead screw 232 are rotatably connected with the mounting frame 21 through a bearing, a shaft end of the second lead screw 232 is fixedly connected with the first motor 231 through a coupling, in order to realize synchronous control of rotation of the clamping rod 223, a thread direction of the second lead screw 232 is divided into a left rotation and a right rotation from the middle of the mounting frame 21, the second lead screw 232 is connected with the clamping driving plate 221 through a nut seat, the second lead screw 232 rotates to drive the clamping driving plate 221 to move linearly, and further drive the clamping rod 223 through a connecting rod 222, so as to convert the linear motion of the clamping driving plate 221 into a rotational motion of the clamping rod 223, so as to open or clamp the clamping rod 223; the clamping driving plate 221 converts the pushing force into the rotating force of the clamping rod 223 through the connecting rod 222, so that a lever mechanism is formed, and the clamping driving plate 221 can enable the clamping rod 223 to carry out clamping action through a small stroke.
Specifically, referring to fig. 7 to 8, since the clamping assembly 2 needs to overcome the gravity of the whole vehicle to complete the lifting of the vehicle, the clamping bar 223 always bears a great vertical downward pressure during the whole process from the time when the clamping bar 223 contacts the vehicle tire to the time when the vehicle is transported and the vehicle is put down, and the pressure generates a great overturning moment on the rotating shaft of the clamping bar 223. In order to bear and balance the overturning moment and make the opening or clamping process of the clamping rod 223 smoother, the clamping rod 223 is rotatably connected with the mounting frame 21 through a turntable bearing 224, a clamping rod mandrel 225 penetrates through the turntable bearing 224, the bottom of the clamping rod mandrel 225 is fixed with the mounting frame 21, and a needle bearing 226 is sleeved on the upper end of the clamping rod mandrel 225 and fixed with the clamping rod 223. Meanwhile, during the vehicle clamping action, the clamping rod 223 will bear the pressure along the length direction of the bracket main body 1, and the pressure is balanced by the way that the clamping driving plate 221 converts the thrust into the rotating force of the clamping rod 223 through the connecting rod 222. In order to maintain the stability of structural strength and the smoothness of component operation in the process of converting the thrust into the rotational force, the clamping driving plate 221 and the clamping rod 223 are both provided with a second pin shaft 227, the second pin shaft 227 is sleeved with a shaft sleeve 228, and the end parts of the connecting rods 222 are both sleeved on the shaft sleeve 228.
Specifically, fig. 16 to 21 and fig. 7 show views of each state and stress conditions in each state during the operation of the clamping assembly 2. Now, the width direction of the stent body 1 is defined as X direction, the length direction of the stent body 1 is defined as Y direction, and the thickness direction of the stent body 1 is defined as Z direction. The clamping bar 223 is initially in the home position, parallel to the second lead screw 232, as shown in fig. 16. When a clamping action is required, the first motor 231 drives the second lead screw 232 to rotate, so that the clamping driving plate 221 moves back to back, and then drives the two-side connecting rods 222 to rotate, and further drives the two-side clamping rods 223 to rotate. The process mechanism moves in an unloaded state before the clamping bar 223 contacts the vehicle tire, as shown in fig. 17-18. The first motor 231 need provide little torque output during this process.
Further, the clamping bar 223 comes into contact with the tire rear mechanism to start bearing load, as shown in fig. 19 to 20 and fig. 7. As can be seen from the force analysis diagram of each component on the figure, the clamping rod 223 is subjected to the automobile tire pressure F223 in the YZ plane, and further F223 can be divided into a component F223Z along the Z direction and a component F223Y along the Y direction, and assuming that the gravity borne by one automobile tire is G, as can be seen from the force balance, F223Z = G/2, and f223y = (G/2) tan α. Wherein, F223z is carried by the rigidity of the clamping rod 223 itself, and generates a great overturning moment on the rotation axis O in the XZ plane, as shown in fig. 7. The event the utility model discloses choose for use simultaneously to possess the revolving stage bearing 224 of very big axial and radial bearing capacity as rotatory main tributary support element to the antidumping ability of supplementary promotion axle center O department of cooperation clamping bar dabber 225 and bearing 226, and then guarantee that the produced overturning moment of F223z is whole balanced by axle center department connecting piece. Still further, F223y also generates a rotational moment M223y in the XY plane with respect to the rotational axis O, as shown in fig. 19 to 20. F223y can be divided into a centripetal (centrifugal) force directed toward the axis 0, F223yn and a tangential force F223yt perpendicular to the F223yn, the moment arm of F223yt to the axis O is L, and F223yn = (G/2) tan α · sin β, and F223yt = (G/2) tan α · cos β are substituted. Where F223yn is balanced by the radial load capacity of turntable bearing 224 and needle bearing 226. The moment generated by the F223yt to the shaft center O is borne by the lower transmission structure. The lower transmission structure of the present invention is a connecting rod 222. In the process, the stress on the connecting rod 222 is shown in fig. 19 to fig. 20, the resultant force is F222 along the connecting line of the two stress points of the connecting rod, and F222 can be divided into a centripetal force F222n pointing to the axis O and a tangential force F222t perpendicular to the centripetal force F222n, the moment arm of F222t to the axis O is R, and the moment balance indicates: f223yt · L = F222t · R, further, F222t = (G/2) tan α · cos β · L/R, and still further, F222= (G/2) tan α · cos β · L/R/cos γ. Still further, F222 may be divided into components F222X and F222Y along the X direction and the Y direction, where F222X = (G/2) tan α · cos β · L/R/cos γ · cos θ, and F222Y = (G/2) tan α · cos β · L/R/cos γ · sin θ. Still further, F222x is balanced by linear guide 12's side direction load capacity, so the utility model discloses choose for use to possess load such as four directions and the extremely strong roller linear guide 12 of load capacity to provide support and direction to the linear motion of clamping drive plate 221, F222y then is balanced by second lead screw 232's thrust. Thus, the thrust F232' ≧ F222y = (G/2) tan α · cos β · L/R/cos γ · sin θ of the second lead screw 232 is sufficient.
Specifically, as shown in fig. 19 to 20 and the derivation above. In the present invention, the thrust F232' required by the second lead screw 232 changes with the load G of the vehicle tire, the arms of force L, R, and the angles α, β, γ, and θ. Wherein G is 1/4 of the weight of the automobile, L is the distance between two front wheels or two rear wheels of the automobile, and is an external condition. R is the design size is quantitative. Further, as can be seen from fig. 19 to 20, as the tire clamping process proceeds, α, β, γ, and θ all gradually decrease, tan α and sin θ decrease, and cos β and cos γ increase. Further, as shown in fig. 19 to 20, it can be seen that the change amounts of the β angle and the cos β value are extremely small and negligible, and as shown by F232'≧ F222y = (G/2) tan α · cos β · L/R/cos γ · sin θ and the diagram, the thrust F232' required by the second lead screw 232 decreases geometrically as the tire clamping process proceeds, and the maximum thrust required is only at the moment when the clamping bar just contacts the tire. Due to the fact that the whole tire clamping process is designed to be 2-3 seconds, the load operation time is only 1.25 seconds in total, and therefore the instant high thrust F232' can be bridged by the instant strong overload torque of the servo motor. And contrast the utility model discloses other common schemes except that, like gear drive, rack and pinion transmission, worm gear transmission etc. because there is not middle level driving medium connecting rod 222 in the structure, same external condition and design size are the same, under the same condition of G, L, R promptly, for maintaining system balance, from pressing from both sides the child and ending, the required thrust that provides of gear, rack or worm equals all the time the utility model discloses well connecting rod 222 is to tangential force F222t that axle center O provided. Comparing F222t = (G/2) tan α · cos β · L/R and F222y = (G/2) tan α · cos β · L/R/cos γ · sin θ, and the instant state where the clamping bar 223 contacts the tire shown in fig. 19, it can be seen that F222y is slightly smaller than F222t at that instant, and during the subsequent operation, as shown in fig. 20, F222y gradually decreases to be much smaller than F222t as γ and θ decrease. Further, the present invention can select a smaller motor 231 with smaller power and smaller volume and a smaller and lighter support structure. Thereby significantly reducing the overall size of the clamping assembly 2.
Still further, when the clamping bar 223 rotates 90 ° to reach the maximum stroke, the clamping motion is completed, as shown in fig. 21. In conjunction with the above discussion, when the angle θ is 0 °, F222= F222x, the force direction of the link 222 is perpendicular to the Y direction, i.e., the downward load force of the vehicle cannot act on the linear motion direction of the clamping driving plate 221 along the Y direction, i.e., the dead point of motion is reached. Meanwhile, the angle γ is a reverse angle, that is, under the condition that there is an error in the actual machining geometry and the actual position of the connecting rod 222 is not completely perpendicular to the Y direction, the vehicle load force gives a backward thrust to the clamping driving plate 221, so that the clamping driving plate 221 contacts with the mounting frame 21 and is mechanically locked. Further, through the double insurance, even if the motor fails or has power failure suddenly and other accidents happen, the clamping rod 223 still locks, the vehicle cannot fall off, and the safety of the equipment is greatly improved.
So far, it has been shown and described that the clamping assembly 2 of the present invention, which is smaller and safer in size, is required to further reduce the overall equipment size of the control carrier in order to ensure that the carrier can submerge into the bottom of various vehicles on the flat ground of a common parking lot. Specifically, the mounting frame 21 includes a mounting frame main body 211, one end of the mounting frame main body 211 is provided with a mounting seat 212 for fixing the first motor 231, a nut mounting position 213 is arranged in the middle of the mounting frame main body 211, and a nut seat for connecting the clamping assembly 2 and the first lead screw 14 is fixedly arranged inside the nut mounting position 213 in a penetrating manner. Further, first lead screw 14 and second lead screw 232 follow 1 length direction parallel arrangement of support subject, first lead screw 14 distributes with second lead screw 232 and sets up in 1 width direction central line both sides of support subject, first lead screw 14 wears to establish on supporting platform 11 and both ends and supporting platform 11 pass through the bearing and rotate and be connected, shaft coupling and driving motor 13 fixed connection are passed through to first lead screw 14's axle head, spacing groove 16 has been seted up at 1 both ends of support subject, first lead screw 14 and second lead screw 232 all are located spacing groove 16.
Specifically, fig. 22 shows the stress state of each component when the clamping assembly 2 is in a load operation during the clamping action. Assuming that the mass of the clamping assembly 2 is m and the rolling friction coefficient of the linear guide 12 is μ, it can be seen from the above that, under the load of the car tire, the thrust force of the single link 222 acting on the clamping driving plate 221 is F222, the component force of the F222 in the X direction is F222X, and the component force of the F222 in the Y direction is F222Y. Further, in the X direction, the positive pressure applied to the single linear guide rail is 2 · F222X, in the Z direction, the positive pressure applied to the single linear guide rail is the automobile tire load G plus half mg/2 of the self weight of the clamping assembly 2, further, in the clamping process, the frictional resistance generated on the single guide rail is μ (2 · F222X + G + mg/2), further, the total frictional resistance F221=2 · μ (2 · F222X + G + mg/2) = μ [4 · (G/2 tan α cos β) · L/R/cos γ · cos θ +2g mg ] applied to the clamping drive plate 221, and further, in the Y direction, the resultant force applied to the clamping drive plate 221 may be equivalent to F221, F221=4 · F222Y + F, and the resultant force of the equivalent F is located on the X-direction geometric centerline of the clamping drive plate 221, i.e., on the centerline of the width direction of the stent body 1. The clamping drive plate is further subjected to a thrust force F232 of the second lead screw 232, in order to maintain the balance of the clamping drive plate 221 in the Y direction, F232= F221=4 · (G/2 tan α cos β) · L/R/cos γ · sin θ + μ [4 · (G/2 tan α cos β) · L/R/cos γ · cos θ +2G + mg ]. Still further, can calculate out F232's numerical value under various load condition and each motion state according to above formula, second lead screw 232's load numerical value promptly, further again according to "mechanical design manual" and relevant calculation lectotype standard of firm product manual can select to satisfy the utility model discloses the demand just can ensure the utility model discloses the minimum model of specification size of operation safety and stability, and then confirmed second lead screw 232's lectotype and furthest's the overall dimension who has compressed second lead screw 232.
Further, as shown in fig. 23, after the clamping action is completed, the two groups of clamping assemblies 2 move synchronously to adjust the stress state of each component in the process of vehicle position adjustment. As described above, after the tire clamping operation is completed, the automobile tire load only has a force F222 in a direction perpendicular to the Y direction on the link 222. Further, in this state, the positive pressure applied to the single linear guide rail in the X direction is 2 · F222, the positive pressure applied to the single linear guide rail in the Z direction is the automobile tire load G plus half mg/2 of the self weight of the clamping assembly 2, further, the frictional resistance generated on the single linear guide rail is μ (2 · F222+ G + mg/2), further, the resultant frictional resistance force applied to the clamping assembly 2 in the moving process with load is F2, F2=2 · μ (2 · F222+ G + mg/2), and F2 is located on the X-direction geometric centerline of the clamping assembly 2, that is, the width-direction centerline of the stent body 1. Still further, the clamping component 2 is further subjected to a thrust F14 of the first lead screw 14, and F14= F2, so as to maintain the clamping component 2 balanced in the Y direction, F14= F2= μ [4 · (G/2 tan α cos β) · L/R/cos γ +2g + mg ].
Still further, can calculate out F14's numerical value under various load condition and each motion state according to above formula, the load numerical value of first lead screw 14 promptly, further again according to "mechanical design manual" and relevant calculation lectotype standard of choosing of firm product manual can select to satisfy the utility model discloses demand load just can ensure the utility model discloses the minimum model of specification size of operation safety and stability. More special, because linear guide 12's the numerical value of rolling friction coefficient mu is minimum, is no longer than 0.005, consequently, first lead screw 14's load demand F14 numerical value is minimum, and is further, only consider under the condition of load demand, select minimum diameter's roller lead screw and can satisfy the utility model discloses a demand, nevertheless two fixed end spans of first lead screw 14 are big on the left and right sides, and the critical rotational speed nc of roller lead screw of undersize diameter will be difficult to satisfy the utility model discloses demand to speed. As can be seen from the critical rotation speed calculation formula "nc =10^7 · f · d2/lc2 ≧ nmax", the larger "d2" is, the smaller "lc" is, the larger "nc" is, in the formula, "d2" is the base diameter of the first lead screw 14, "lc" clamping component 2 moves to the limit position, the distance from the nut seat to the far fixed end of the first lead screw 14, and "nmax" is the highest rotation speed of the first lead screw 14 during the use of the present invention. Further, in order to obtain a larger "nmax" and a smaller "d2" according to the present invention, a smaller "lc" is provided in the geometric design of the structure, as shown in fig. 23. Specifically, a nut mounting position 213 is arranged in the middle of the mounting frame main body 211, and a nut seat connecting the clamping assembly 2 and the first lead screw 14 is fixedly arranged in the nut mounting position 213 in a penetrating manner, so that the movement of the clamping assembly 2 at two ends is limited to a smaller size of lc, and further, the selection of the first lead screw 14 meeting the load requirement F14 and the maximum rotation speed requirement of nmax is determined, and the overall dimension of the first lead screw 14 is compressed to the maximum extent. Still further, since the F14 value is extremely small, the power requirement on the driving motor 13 is greatly reduced, and the volume of the driving motor 13 and the requirement on the corresponding installation space are further greatly reduced.
Further, for a more compact spatial layout, the first lead screw 14 and the second lead screw 232 are disposed parallel to the length direction of the stent body 1 and distributed on two sides of the geometric centerline in the X direction, i.e. two sides of the centerline in the width direction of the stent body 1. Further, as shown in fig. 22 and 23, since the centerline of the first lead screw 14 and the centerline of the second lead screw 232 are not collinear with the geometric centerline of the X direction, although the F221 and the F232 have the same size and are opposite in direction and balanced in the Y direction, the two forces will form a set of couples to the clamping driving plate 221, the couple arm length of the couple is the distance a between the centerline of the second lead screw 232 and the geometric centerline of the X direction, further, the couple moment generated by the pair of clamping driving plates 221 is M232, M232= F232 · a, further, the F14 and the F2 also form a set of couples, the couple arm length is the distance b between the centerline of the first lead screw 14 and the geometric centerline of the X direction, and the couple moment generated by the pair of clamping assembly 2 is M14, M14= F14 · b. Both M232 and M14 are balanced by the torque resistance of linear guide 12. Still further, since the wheel base adjusting action and the vehicle clamping action are not performed simultaneously during the vehicle transportation process, the linear motion of the clamping drive plate 221 and the clamping assembly 2 is supported and guided by the same set of linear guide rails 12 for more compact spatial layout.
With the above description and derivation, the X-direction pressure applied to the linear guide rail 12 during the clamping operation is 2 · F222X =2 · (G/2) tan α · cos β · L/R/cos γ · cos θ, and the applied torque M232= F232 · a = {4 · (G/2 tan α cos β) · L/R/cos γ · sin θ + μ [4 · (G/2 tan α cos β) · L/R/cos γ · cos θ +2g + mg ] } · a; in the process of synchronously moving and adjusting the position of the vehicle by two groups of clamping assemblies 2, the X-direction pressure is 2 · F222=2 · (G/2 tan α cos β) · L/R/cos γ, and the torque M14= F14 · b = μ [4 · (G/2 tan α cos β) · L/R/cos γ +2G + ] ·; the Z-direction positive pressure applied in the whole process of carrying the automobile is G + mg/2. Further, load demand and the moment of torsion demand of linear guide 12 under various load condition and each motion state can be calculated according to above-mentioned formula, and further again, according to firm product manual, can confirm satisfying the utility model discloses what the demand just can ensure the utility model discloses the model that the specification and dimension of operation safety and stability's linear guide 12 is minimum, and then confirmed linear guide 12's lectotype.
Still further, through the aforesaid design and arrangement, the carrier is including the littleer and safer centre gripping subassembly 2 of volume size, the littleer and safe first motor 231 of volume size, the littleer and safe second lead screw 232 of volume size, the littleer and safe driving motor 13 of volume size, the littleer and safe first lead screw 14 of volume size, the littleer and safe linear guide 12 of volume size, and more compact structural design and overall arrangement, and then compressed supporting platform 1's overall dimension, thereby compressed the whole size at height and width direction of carrier, make carrier overall height within the height of most motorcycle type chassis in the market to ground, and then realized that the carrier can sneak into the function that various vehicle bottoms carried to the vehicle in the parking area on ordinary level ground. The universality of the carrier is greatly improved.
The elastic supporting wheel assembly 3 is used as a walking support when the support platform 1 moves linearly. The size of the resilient support wheel assembly 3 and the support wheels 32 included therein is also greatly limited due to the overall height dimension of the carrier, and the support wheels 32 are typically made of a polyurethane material. In order to eliminate negative effects such as power loss and equipment severe shaking caused by external factors such as the ground and the like on the undersize roller, all the elastic supporting wheel assemblies are driven wheels, only the carrier is supported, and the supporting height can be adjusted in a floating manner. Specifically, the elastic supporting wheel assembly 3 includes a supporting wheel frame 31, a supporting wheel 32 is transversely disposed in the middle of the supporting wheel frame 31, first pin shafts 33 are disposed at two ends of the supporting wheel frame 31, the first pin shafts 33 are slidably connected with the support main body 1 through linear bearings 15, springs 34 are sleeved on the first pin shafts 33, upper ends of the springs 34 are attached to the lower end face of the support main body 1, lower ends of the springs 34 are attached to the end face of the supporting wheel frame 31, the springs 34 have a tendency of driving the supporting wheel frame 31 to move downward, when a slope or a gap is encountered, or the supporting platform 1 deforms under pressure, the supporting height can change, and the springs 34 have a certain buffering and damping effect to avoid clamping stagnation. Further, the impact influence of road surface condition to less polyurethane wheel has been reduced to a certain extent, thereby makes the carrier has possessed certain seam and has crossed bank and cross the slope ability to the stability of carrier operation has been improved.
Because the elastic support wheel subassembly 3 is from the driving wheel, the utility model discloses still be provided with drive mechanism 4 in the carrier outside, for the transport efficiency and the functioning speed that improve automobile carrier, the utility model discloses a drive mechanism 4 that has doubly fast journey structure is as drive element.
Further, because the whole height of carrier is limited, the floating adjustment clearance of elastic support wheel subassembly 3 also receives the restriction thereupon, and it is limited to the improvement of carrier seam crossing bank and climbing ability, in order to further promote carrier seam crossing bank and climbing ability and operating stability by a wide margin, specifically, be equipped with on second grade driving medium 43 and be used for with driven gear 47 rotation connection's installation department 431, the installation department 431 top is equipped with guide part 432, the guide part 432 upper end is seted up and is used for driven rack 18 to remove spacing guide way 4321.
Further, in order to guide and limit the movement of the guide part 432, first sliding grooves 4322 are respectively formed on two sides of the guide part 432, first roller groups 414 are uniformly distributed on the fixed bracket 41 along the length direction of the first sliding grooves 4322, and further, each first roller group 414 comprises a first roller support 4141, first rollers 4142 are uniformly distributed on the first roller support 4141, the first rollers 4142 are located in the first sliding grooves 4322 and are arranged parallel to the side wall of the first sliding groove 4322, first guide wheels 4143 are respectively arranged at two ends of the first roller support 4141, and the first guide wheels 4143 are located in the first sliding grooves 4322 and are arranged perpendicular to the side wall of the first sliding groove 4322.
Still further, in order to perform limiting and guiding on the movement of the bracket main body 1, a second roller group 433 is further fixed at the upper end of the guide part 432, the second roller group 433 has the same structure as the first roller group 414, second sliding grooves 19 corresponding to the second roller group 433 are symmetrically arranged below the bracket main body 1 along the width direction of the bracket main body 1, further, the second roller group 433 includes a second roller support 4331, second rollers 4332 are uniformly distributed on the second roller support 4331, the second rollers 4332 are located in the second sliding grooves 19 and are arranged in parallel with the side walls of the second sliding grooves 19, second guide wheels 4333 are respectively arranged at two ends of the second roller support 4331, and the second guide wheels 4333 are located in the second sliding grooves 19 and are arranged in perpendicular to the side walls of the second sliding grooves 19.
Specifically, the secondary transmission member 43 is driven by the second motor 42 to move in a two-way reciprocating linear manner, and the first sliding slot 4322 is supported and guided by the first roller group 414. The secondary transmission member 43 drives the stent main body 1 to perform a bidirectional shuttling linear motion, the second roller group 433 supports and guides the second sliding slot 19, and the stroke of the stent main body 1 is always 2 times that of the secondary transmission member 43. Further, the primary support is provided by the first roller set 414 and the second roller set 433 through the first roller 4142 and the second roller 4332 during the operation of the carrier, the auxiliary support is provided by the resilient support wheel assembly 3, and further, the first roller set 414 and the second roller set 433 also provide guidance for the operation of the carrier through the first guide wheel 4143 and the second guide wheel 4333. Further, because the stroke of support main part 1 is 2 times the stroke of secondary drive spare 43 forever, secondary drive spare 43 forms an interior guiding mechanism in support main part 1 is inside to guaranteed that the carrier can high-speed steady operation under the condition of no outside direction, more made the carrier can unsettled operation near drive mechanism 4 within a certain limit. Thus, in practical applications, the transmission mechanism 4 can be intentionally placed slightly above the target plane to eliminate the steep bank. And then the elastic supporting wheel component is matched, so that the gap-crossing, ridge-crossing and slope-crossing capacity of the concealed carrier is greatly improved, and the real rapid and stable vehicle carrying work is realized.
Specifically, figure 24 shows to be the utility model discloses the transport vehicle in-process carries car state schematic diagram, and figure 25 shows to be the utility model discloses the transport vehicle in-process connects the car and send the car state schematic diagram. Further, fig. 26 to 33 show the car feeding process and the states in the respective processes according to the present invention. Specifically, as shown in fig. 26, the transmission mechanism 4 is disposed at a position slightly higher than the target plane, so as to eliminate a steep sill between the device and the target ground or the rack, further, as shown in fig. 27, which is a partial cross-sectional view of a position B in fig. 26, as can be seen from the figure, in this state, the elastic support wheel assembly 3 disposed in the region of the position B leaves a slight gap with the ground, and is in a suspended state, the support wheel frame 31 moves downward to the maximum floating adjustment gap under the action of the spring 34, the first pin 33 contacts with the bracket main body 1, the spring 34 reaches the maximum deformation length, and the elastic support wheel assembly suspends and does not provide a supporting force for the bracket main body 1. Therefore, when the support body 1 is located in the area close to the transmission mechanism 4, the support body 1 is completely supported and guided by the secondary transmission piece 43, the support body 1 runs in a suspended state on the ground, and then crosses a gap between the fixed support 41 and the ground, so that the road condition and the gap in the area do not affect the running of equipment.
Further, the supporting body 1 continues to move forward to about a half of the total stroke, as shown in fig. 28, since the region of the C-position is gradually far away from the fixing bracket 41 and the stroke of the secondary transmission member 43 is only a half of the stroke of the supporting body 1, the supporting effect of the secondary transmission member 43 on the supporting body 1 of the region of the C-position is weakened. Further, fig. 29 is a partial sectional view at C in fig. 28, and as can be seen from fig. 29, in this state, due to the deformation of the bracket main body 1 caused by a load stress or due to a change in road conditions, the elastic support wheel assembly 3 arranged in the region of the C portion contacts with the ground, the spring 34 is compressed by a force, the first pin 33 and the support wheel frame 31 move upward, the floating adjustment gap is reduced, the elastic support wheel assembly 3 arranged in the region of the C portion provides an auxiliary support force to the bracket main body 1 in the region, and the support force is a spring force generated by the deformation of the spring 34. Further, fig. 30 is a partial cross-sectional view at D in fig. 28, and it can be seen from fig. 30 that in this state, the region of D just passes through the gap between the fixed bracket 41 and the ground, the bracket body 1 in this region is still supported and guided by the secondary transmission member 43, the elastic support wheel assembly 3 just passing through the gap between the fixed bracket 41 and the ground is suspended, and the floating adjustment gap is maximized under the action of the spring 34 but still has a gap with the ground.
Further, the holder body 1 is moved to the target position, i.e., the required maximum stroke, as shown in fig. 31, and in this state, the secondary transmission member 43 almost loses the supporting function to the holder body 1 in the region of the E portion in the drawing, and the supporting function to the holder body 1 in the region of the F portion in the drawing is weakened. Specifically, fig. 32 is a partial cross-sectional view of fig. 31, and as can be seen from fig. 32, in this state, due to the deformation of the bracket body 1 caused by load stress or due to a change in road conditions, the spring 34 is stressed and increased and continues to be compressed, the first pin shaft 33 and the support wheel carrier 31 continue to move upward, the limit boss 312 is in contact with the bracket body 1, the floating adjustment gap is reduced to 0, and the elastic support wheel assembly 3 arranged in the region where the E position is located provides all support force for the bracket body 1 in the region. Further, fig. 33 is a partial sectional view of fig. 31, and it can be seen from fig. 33 that the elastic supporting wheel assembly 3 arranged in the region of the F part contacts with the ground to provide an auxiliary supporting force to the support main body 1 in the region, and the supporting force is the spring force generated by the deformation of the spring 34. Still further, fig. 33 clearly shows the state of self-adaptive adjustment of the elastic supporting wheel assemblies 3 on uneven road, so that the impact influence of road conditions on smaller polyurethane wheels is reduced to a certain extent, and the elastic supporting wheel assemblies 3 can provide auxiliary support for the support main body 1 within a certain range, thereby improving the stability of the operation of the carrier. Still further, after the vehicle has been brought to the target location and the clamping bar 223 is opened, the apparatus is reversed and returned to the home position.
Use the utility model provides a latent formula car carrier based on external drive, and when adopting drive mechanism 4 to drive, two driving motor 13 drive first lead screw 14 respectively and rotate, adjust the car wheel base of the interval of 1 both ends clamping component 2 of support main part and required transport and keep unanimous, drive mechanism 4 and driving motor 13 simultaneous working, it carries out linear motion to the bottom of the car to drive support main part 1, and is further, clamping component 2 begins to embrace the clamp tire and lifts the whole vehicle, and is further, drive mechanism 4 and driving motor 13 simultaneous working, transport the vehicle to drive mechanism 4 top and adjust the vehicle to position placed in the middle through support main part 1, and is further, go up and down and sideslip drive mechanism aligns with appointed parking stall to the target floor through other equipment, and is further, drive mechanism 4 and driving motor 13 simultaneous working, transport the vehicle to the assigned position of perhaps heteropleural through support main part 1, further, clamping component 2 loosens and embraces the clamp, accomplish the transport of vehicle, and is further, drive mechanism 4 and driving motor 13 simultaneous working, move support main part 1 and clamping component 2 to the assigned position of initial side, and carry out the operation of waiting for next round operation and accomplish an instruction.
It will be understood by those skilled in the art that the foregoing is merely exemplary of the present invention, and is not intended to limit the invention to the particular forms disclosed, and all changes, equivalents and modifications that fall within the spirit and scope of the invention are intended to be embraced thereby.
Claims (10)
1. An external drive-based concealed vehicle carrier comprising:
the automobile chassis supporting device comprises a support main body (1), wherein a supporting platform (11) used for supporting an automobile chassis is arranged in the middle of the support main body (1), linear guide rails (12) are arranged on two sides of the supporting platform (11) in parallel, two driving motors (13) with opposite installation directions are arranged in the middle of the supporting platform (11) in parallel, and output ends of the driving motors (13) are connected with first lead screws (14);
the two clamping assemblies (2) are respectively positioned at two ends of the bracket main body (1), the distance between the two clamping assemblies is adjustable, the two clamping assemblies are used for clamping automobile tires, the clamping assemblies (2) are connected with the first lead screw (14) through nut seats, the clamping assemblies (2) are connected with the slide blocks of the linear guide rails (12), and when the driving motor (13) works, the first lead screw (14) drives the clamping assemblies (2) to move in the opposite direction or the opposite direction;
the elastic supporting wheel assemblies (3) are respectively positioned on two sides of the support main body (1) and used for supporting when the support main body (1) moves and adjusting the supporting height, and floating adjusting gaps are formed between the elastic supporting wheel assemblies (3) and the support main body (1).
2. An external drive based concealed vehicle carrier as claimed in claim 1 wherein: centre gripping subassembly (2) is including mounting bracket (21), mounting bracket (21) bilateral symmetry is equipped with clamping bar mechanism (22), follow on mounting bracket (21) support subject (1) length direction is fixed with drive arrangement (23), clamping bar mechanism (22) including with centre gripping drive plate (221) that the output of drive arrangement (23) is connected, centre gripping drive plate (221) both ends are rotated and are connected with connecting rod (222), the other end of connecting rod (222) is rotated and is connected with clamping bar (223), mounting bracket (21) with centre gripping drive plate (221) all with the slider of linear guide (12) is connected, drive arrangement (23) can drive centre gripping drive plate (221) dorsad or motion in opposite directions, and then drive connecting rod (222) rotate and make clamping bar (223) rotation is opened or are pressed from both sides tightly.
3. An external drive based concealed vehicle carrier as claimed in claim 1 wherein: elastic support wheel subassembly (3) is including supporting wheel carrier (31), violently be equipped with supporting wheel (32) in the middle of supporting wheel carrier (31), supporting wheel carrier (31) both ends are equipped with first round pin axle (33), first round pin axle (33) through linear bearing (15) with support main part (1) sliding connection, the cover is equipped with spring (34) on first round pin axle (33), spring (34) upper end with terminal surface laminating under support main part (1), spring (34) lower extreme with the terminal surface laminating of supporting wheel carrier (31), spring (34) have the drive support wheel carrier (31) downward movement's trend.
4. An external drive based concealed vehicle carrier as claimed in claim 2 wherein: drive arrangement (23) is including first motor (231), the output of first motor (231) is connected with second lead screw (232), second lead screw (232) wear to establish on mounting bracket (21) and both ends with mounting bracket (21) are passed through the bearing and are rotated the connection, the axle head of second lead screw (232) pass through the shaft coupling with first motor (231) fixed connection, the screw thread of second lead screw (232) is to following be divided into levogyration and dextrorotation in the middle of mounting bracket (21), second lead screw (232) through the nut seat with centre gripping drive plate (221) are connected, second lead screw (232) rotate the drive centre gripping drive plate (221) move and then drive clamping bar (223) are opened or are pressed from both sides tightly.
5. An external drive based concealed vehicle carrier as claimed in claim 4 wherein: the clamping rod (223) is rotatably connected with the mounting frame (21) through a turntable bearing (224), a clamping rod mandrel (225) penetrates through the turntable bearing (224), the bottom of the clamping rod mandrel (225) is fixed with the mounting frame (21), a needle bearing (226) is sleeved on the upper end of the clamping rod mandrel (225), the needle bearing (226) is fixed with the clamping rod (223), a second pin shaft (227) is arranged on the clamping drive plate (221) and the clamping rod (223), a shaft sleeve (228) is sleeved on the second pin shaft (227), and the connecting rod (222) is rotatably connected with the clamping drive plate (221) and the clamping rod (223) through the shaft sleeve (228).
6. An external drive based concealed vehicle carrier as claimed in claim 4 wherein: first lead screw (14) with second lead screw (232) are followed support subject (1) length direction parallel arrangement, first lead screw (14) with second lead screw (232) distribute to be set up support subject (1) width direction central line both sides, first lead screw (14) are worn to establish supporting platform (11) go up and both ends with supporting platform (11) rotate through the bearing and connect, the axle head of first lead screw (14) pass through the shaft coupling with driving motor (13) fixed connection, spacing groove (16) have been seted up at support subject (1) both ends, first lead screw (14) with second lead screw (232) all are located in spacing groove (16).
7. An external drive based latent vehicle carrier as defined in claim 3 wherein: the support wheel carrier (31) both ends are equipped with highly the same spacing face (311), the symmetry is equipped with spacing boss (312) in the middle of support wheel carrier (31), be equipped with on support main part (1) with spacing hole (17) that spacing boss (312) correspond, spacing face (311) with the lower terminal surface of support main part (1) is equipped with the regulation clearance that floats.
8. An external drive based concealed vehicle carrier as claimed in claim 1 wherein: still including drive mechanism (4), drive mechanism (4) include fixed bolster (41), fixed bolster (41) bilateral symmetry is equipped with the linear motion subassembly, the symmetry is equipped with secondary drive spare (43) in the middle of fixed bolster (41), the equal swing joint of output of linear motion subassembly has driving plate (46), driving plate (46) with secondary drive spare (43) fixed connection, it is connected with driven gear (47) to rotate on secondary drive spare (43), be fixed with drive rack (413) along length direction on fixed bolster (41), support main part (1) below is fixed with driven rack (18) along length direction, drive rack (413) with driven rack (18) parallel arrangement and all with driven gear (47) meshing, the linear motion subassembly during operation can drive driven gear (47) pivoted while and follow support main part (1) length direction reciprocating motion, and then drive support main part (1) is along length direction reciprocating motion.
9. An external drive based latent vehicle carrier as defined in claim 8 wherein: be equipped with on second grade driving medium (43) be used for with driven gear (47) rotate installation department (431) of connecting, installation department (431) top is followed support main part (1) length direction is equipped with guide part (432), guide part (432) lateral wall is equipped with first spout (4322) along the length direction symmetry, fixed bolster (41) go up along the length direction equipartition with first spout (4322) position corresponds, the same first roller group (414) of quantity, second spout (19) have been seted up on support main part (1), on guide part (432) along the length direction equipartition have with second roller group (433) that second spout (19) correspond.
10. An externally powered latent vehicle carrier as set forth in claim 9 wherein: the first roller set (414) and the second roller set (433) are identical in structure, the first roller set (414) comprises a first roller support (4141), first rollers (4142) are uniformly distributed on the first roller support (4141), and first guide wheels (4143) are arranged at two ends of the first roller support.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222705968.7U CN218780072U (en) | 2022-10-12 | 2022-10-12 | Formula of hiding car carrier based on external drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222705968.7U CN218780072U (en) | 2022-10-12 | 2022-10-12 | Formula of hiding car carrier based on external drive |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN218780072U true CN218780072U (en) | 2023-03-31 |
Family
ID=85712995
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202222705968.7U Active CN218780072U (en) | 2022-10-12 | 2022-10-12 | Formula of hiding car carrier based on external drive |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN218780072U (en) |
-
2022
- 2022-10-12 CN CN202222705968.7U patent/CN218780072U/en active Active
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