CN113510520A

CN113510520A - Column workpiece loading and unloading device for horizontal machine tool

Info

Publication number: CN113510520A
Application number: CN202110805370.2A
Authority: CN
Inventors: 屈明生; 渠源; 韩绪艳; 马健; 潘品李; 董学良; 李方见
Original assignee: China Banknote Printing Technology Research Institute Co ltd; China Banknote Printing and Minting Corp
Current assignee: China Banknote Printing Technology Research Institute Co ltd; China Banknote Printing and Minting Corp
Priority date: 2021-07-16
Filing date: 2021-07-16
Publication date: 2021-10-19

Abstract

The invention discloses a cylinder workpiece loading and unloading device for a horizontal machine tool, which comprises a frame, a movable support, a mounting plate, a cylinder workpiece transfer frame and a power transmission part, wherein the frame is movably connected with the movable support; the mounting plate is arranged on the upper part of the frame; the cylinder workpiece transfer frame and the power transmission part are arranged on the mounting plate, the power transmission part is connected with the cylinder workpiece transfer frame, and the power transmission part drives the cylinder workpiece transfer frame to rotate. Compared with the prior art, the cylinder workpiece loading and unloading device for the horizontal machine tool does not need manual transportation, and mechanical loading and unloading are realized; the cylinder workpiece loading and unloading device for the horizontal machine tool is small in size and occupied space, and is suitable for production lines of various sizes.

Description

Column workpiece loading and unloading device for horizontal machine tool

Technical Field

The invention relates to a cylinder workpiece loading and unloading device for a horizontal machine tool, and belongs to the technical field of machining.

Background

When the existing horizontal machine tool is used for processing large-scale workpieces, feeding and discharging are generally carried out through a crown block, the crown block transportation belongs to hoisting operation, workpieces are suspended through steel cables, shaking can occur in the transportation and operation processes, certain danger is brought to equipment and personnel, and unmanned and intelligent operation of future engineering is not facilitated.

If the forklift is used for transportation, the problem is caused that the gravity moment of the workpiece can be balanced only when the self weight of the counter weight type forklift which can cantilever-convey hundreds of kilograms of workpieces reaches or even exceeds hundreds of kilograms, so that the operation of the counter weight type forklift in a plant is greatly limited by the volume and the weight of the counter weight type forklift; a stacker or the like having a front fork at the lower part of the front part, wherein the front fork is blocked by an equipment cover and a bracket and is difficult to extend below a machine tool, and therefore, it is difficult to convey a workpiece to a clamping position.

To sum up, if use industrial robot to transport, the problem that can arouse lies in, firstly need set up to possess a robot and be used for going up unloading on every lathe limit, secondly the heavy industrial robot that the cantilever transported hundreds of kilograms of bars is bulky, occupies great space.

Disclosure of Invention

The invention aims to provide a cylindrical workpiece loading and unloading device for a horizontal machine tool.

In order to achieve the technical purpose, the invention adopts the following technical scheme:

a device for loading and unloading a cylindrical workpiece for a horizontal machine tool comprises a frame, a movable bracket, a mounting plate, a cylindrical workpiece transfer frame and a power transmission part,

the frame is movable;

the mounting plate is arranged on the upper part of the frame;

the cylindrical workpiece transfer frame is rotatably arranged on the mounting plate and is used for supporting and transferring the cylindrical workpiece;

the power transmission part is arranged on the mounting plate and connected with the cylinder workpiece transfer frame to drive the cylinder workpiece transfer frame to rotate.

Preferably, the cylindrical workpiece transfer frame comprises a plurality of workpiece supporting seats and a plurality of rotating rings, and the plurality of workpiece supporting seats are arranged at intervals of a preset distance;

the supporting seat is provided with a rotating ring, the rotating ring rotates between a first position and a second position, and the cylinder workpiece is supported by the rotating ring in the state that the rotating ring is located at the first position; and under the state that the rotating ring is positioned at the second position, the cylinder workpiece is transferred to the horizontal machine tool.

Preferably, the rotating ring is provided with a first rotating ring and a second rotating ring with the same curvature radius, and the first rotating ring and the second rotating ring are connected through a connecting part; the first rotating ring is provided with a first transmission part, the second rotating ring is provided with a second transmission part, and the first transmission part is matched with the second transmission part to drive the rotating ring to rotate.

Preferably, the cylindrical workpiece transfer frame further comprises a first bearing beam, a second bearing beam and a connecting rod group; the two bearing beams are connected with the rotating ring through a connecting rod group.

Wherein preferably, the cylindrical workpiece transfer frame further comprises a transmission shaft,

the transmission shaft includes first gear, and the transmission shaft passes through first gear and rotatory joggle joint to the rotatory ring rotation of drive.

Wherein, the power transmission part preferably comprises a rotating frame power, a worm gear and worm speed reducer, a long gear and a sleeve gear,

the rotating frame power is connected with the worm gear speed reducer, and the rotating frame power drives the worm gear speed reducer to operate;

the worm and gear speed reducer is connected with the long gear and drives the long gear to rotate;

the long gear is connected with the sleeve gear and drives the sleeve gear to rotate;

the sleeve gear is connected with the cylinder workpiece transfer frame and drives the cylinder workpiece transfer frame to rotate.

Wherein, the sleeve gear is provided with a right inclined long hole, a left inclined long hole and a central gear,

the central gear is positioned in the middle of the sleeve gear,

the right oblique long hole is positioned on the right side of the central gear, and the left oblique long hole is positioned on the left side of the central gear.

Wherein preferably, the frame comprises a base, a column and a plurality of cantilever beams,

the base is provided with an upright post;

a plurality of cantilever arms are disposed above the columns parallel to the ground.

Preferably, the vehicle further comprises a movable bracket which is movably installed with the vehicle frame relatively.

Wherein preferably, the movable support comprises a base, a column and a support seat,

the base is provided with a plurality of stand columns, the supporting seat is arranged on the stand columns, and the supporting seat is provided with a plurality of guide grooves.

The invention has the following technical effects: compared with the prior art, the cylinder workpiece loading and unloading device for the horizontal machine tool does not need manual transportation, and mechanical loading and unloading are realized; the cylinder workpiece loading and unloading device for the horizontal machine tool is small in size and occupied space, and is suitable for production lines of various sizes.

Drawings

FIG. 1 is a perspective view of a cylindrical workpiece loading and unloading apparatus for a horizontal machine tool according to the present invention;

FIG. 2 is a schematic structural diagram of a frame and a movable support of the column workpiece loading and unloading device for the horizontal machine tool provided by the invention;

FIG. 3 is a side view of the frame of FIG. 2;

FIG. 4 is a front elevational view of the vehicle frame of FIG. 2;

FIG. 5 is a front view of the cantilever beam and support wheel unit of FIG. 2;

FIG. 6 is a side sectional view of the support wheel unit and cantilever beam of FIG. 2;

FIG. 7 is a schematic view of the movable support of FIG. 2;

FIG. 8 is a schematic view of the channel of FIG. 2;

FIG. 9 is a top view of the frame and the movable bracket;

FIG. 10 is a schematic structural view of the power unit of FIG. 2;

FIG. 11 is a schematic structural view of the frame and the movable bracket in a retracted state of the movable bracket;

FIG. 12 is a schematic view of the structure in a locked condition on the outrigger of the frame;

FIG. 13 is a schematic structural view of the unlocked position on the outrigger of the vehicle frame;

fig. 14 is a schematic structural view of a cylindrical workpiece transfer frame of the cylindrical workpiece loading and unloading device for the horizontal machine tool according to the present invention;

FIG. 15 is a schematic view of the workpiece support pedestal of FIG. 2;

FIG. 16 is a schematic view of the configuration of the workpiece support pedestal and the spin ring of FIG. 2;

FIG. 17 is a schematic view of a symmetrical configuration of a plurality of pin holes of the first transmission portion of FIG. 4;

FIG. 18 is a schematic view of a symmetrical configuration of a plurality of pin holes of the second transmission portion of FIG. 4;

FIG. 19 is a schematic structural view of the load beam and linkage of FIG. 2;

FIG. 20 is a side view of the rotating ring and load beam of the workpiece support pedestal of FIG. 2;

FIG. 21 is a schematic view of the drive shaft and the first and second teeth of the present invention in a cylindrical workpiece loader device for a horizontal machine;

FIG. 22 is a schematic structural view of a sleeve gear and a workpiece transfer rack of the column workpiece loading and unloading device for a horizontal machine tool according to the present invention;

FIG. 23 is a schematic structural view of a load beam of the present invention for a column workpiece loading and unloading apparatus of a horizontal machine tool for supporting a cylindrical workpiece;

FIG. 24 is a schematic structural view of a load beam of the present invention for a column work loader and unloader apparatus for horizontal machine tools to lift a cylindrical work;

FIG. 25 is a schematic view of the present invention showing a cylindrical workpiece loading and unloading apparatus for a horizontal machine tool supporting a cylindrical workpiece beside the horizontal machine tool;

FIG. 26 is a schematic view of the present invention showing the retraction of the movable carriage when the locking device of the column workpiece loading and unloading device for a horizontal machine tool is withdrawn;

FIG. 27 is a schematic structural view of the present invention for mounting a cylindrical workpiece on a spindle of a horizontal machine tool;

fig. 28 is a schematic structural view of the cylindrical workpiece loading and unloading device for the horizontal machine tool for completing the loading step of the cylindrical workpiece and evacuating the horizontal machine tool.

Detailed Description

The technical contents of the invention are described in detail below with reference to the accompanying drawings and specific embodiments.

As shown in fig. 1, the present invention provides a column workpiece loading and unloading device for a horizontal machine tool, which comprises a frame 1, a movable support 5, a mounting plate 12, a column workpiece transfer rack 100 and a power transmission part 200. Specifically, the frame 1 is movably connected with the movable bracket 5. The mounting plate 12 is mounted on the upper portion of the frame 1 and the movable bracket 5. The cylindrical workpiece transfer frame 100 and the power transmission part 200 are installed on the installation plate 12, and the power transmission part 200 is connected to the cylindrical workpiece transfer frame 100 and is driven by the power transmission part to rotate. The power transmission part comprises a long gear 19, a worm gear speed reducer 18 and a rotating frame power 21. The rotating frame power 21 is connected with the worm and gear speed reducer 18, the worm and gear speed reducer 18 is connected with the long gear 19, and the long gear 19 is connected with the cylindrical workpiece transfer frame. When the rotating frame power 21 drives the worm gear and worm speed reducer 18 to rotate, the cylindrical workpiece transporting frame can be driven to operate through the long gear 19.

The frame 1, the movable bracket 5, the mounting plate 12, the cylindrical workpiece transfer rack, and the power transmission section will be described in detail below.

As shown in fig. 2, the frame 1 is movably connected to the movable bracket 5, and the movable bracket 5 can move forward and backward with the frame 1 as a reference.

As shown in fig. 3 and 4, the frame 1 comprises a base 1-1, a column 1-2, a plurality of cantilever beams 1-3 and two groups of first

universal wheels

4A and 4B. A plurality of upright posts 1-2 are arranged above a base 1-1, two groups of first

universal wheels

4A and 4B are arranged below the base 1-1, the two groups of first universal wheels 4A and the first universal wheels 4B are parallel to each other, each group of first universal wheels is provided with a plurality of first universal wheels, and the plurality of first universal wheels of the first group of first universal wheels 4A are represented by 4A-1, 4A-2 and 4A-3. The plurality of cantilever beams 1-3 are arranged above the upright posts 1-2 in parallel to the ground and extend along the moving direction of the movable support 5, the plurality of cantilever beams 1-3 are also arranged in parallel, and the plurality of cantilever beams 1-3 are represented by 1-3A, 1-3B, 1-3C and 1-3D. A set of support wheel units 2, indicated 2A, 2B, 2C, is arranged on each suspension arm 1-3. The two columns 1-2A and 1-2B located at the outermost side are provided with guide means 3, respectively denoted 3A, 3B. In addition, a first hinge seat 1-4A is arranged on one side of the upright post 1-2A opposite to the guide device 3A; a first hinge block 1-4B is provided on the side of the upright 1-2B opposite to the guide 3B.

More specifically, as shown in fig. 5, the support wheel unit 2 includes an upper frame 2-1, a lower frame 2-2, support wheels 2-3, and an axle 2-4. A lower bracket 2-2 is arranged below the upper bracket 2-1, and a supporting wheel 2-3 and a wheel shaft 2-4 are arranged in the lower bracket 2-2. The upper bracket 2-1 is sleeved on the cantilever beam 1-3. As shown in FIG. 6, the upper bracket 2-1 is fixed with guide posts 2-5A, 2-5B and guide rods 2-8A, 2-8B by lower nuts 2-6A, 2-6B. The guide rods 2-8A and 2-8B fix the upper bracket 2-1 and the lower bracket 2-2 together. The cantilever beams 1-3 are provided with holes 1-3-1A, 1-3-1B, 1-3-2A and 1-3-2B which are respectively matched with the guide columns 2-5A, 2-5B and the guide rods 2-8A and 2-8B in size and number. The upper ends of the guide rods 2-8A and 2-8B are provided with upper nuts 2-7A and 2-7B. First elastic elements 2-9A and 2-9B are sleeved on the guide rods 2-8A and 2-8B between the upper support 2-1 and the cantilever beam 1-3. The first elastic elements 2-9A, 2-9B are preferably disc springs or rubber pads.

The presence of the upper carriage 2-1, the guide posts 2-5A, 2-5B and the first resilient elements 2-9A, 2-9B enables the support wheel unit 2 to move a certain distance below the cantilever beams 1-3. The position of the upper nuts 2-7A and 2-7B on the guide rods 2-8 can be adjusted to adjust the size of the elastic stroke. The specific structure of the supporting wheel unit 2 described above is one supporting wheel unit among the multiple supporting

wheel units

2A, 2B, and 2C, and the structures and principles of the other supporting wheel units 2 are the same, and are not described again.

As shown in FIG. 7, the movable support 5 comprises a base 5-2, upright posts 5-1A, 5-1B, 5-1C, a support base 5-3, guide rods 5-4A, 5-4B, a guide groove 8 and second

universal wheels

6A, 6B, 6C. A plurality of upright posts 5-1A, 5-1B and 5-1C are arranged above the base 5-2, and a plurality of second

universal wheels

6A, 6B and 6C are arranged below the base 5-2. The second universal wheels 6 are connected to the base 5-2 via elastic members 7 (not shown) for uniform loading. A supporting seat 5-3 is arranged on the plurality of upright columns 5-1A, 5-1B and 5-1C. The support base 5-3 is provided with a plurality of guide grooves 8, the plurality of guide grooves 8 are denoted by 8A, 8B, 8C, 8D, the number of the guide grooves 8 is equal to the number of the support wheel units 2, and the support wheels 2-3 of the support wheel units 2 are located on the guide grooves 8. Guide rods 5-4A and 5-4B are respectively arranged on the two outermost vertical rods 5-1A and 5-1C, and the guide rods 5-4A and 5-4B extend along the moving direction of the movable bracket 5 and are parallel to the horizontal plane. The guide rods 5-4A, 5-4B correspond to the above-mentioned

guides

3A, 3B, respectively, the guide rods 5-4A, 5-4B being insertable into holes in the

guides

3A, 3B and the guide rods 5-4A, 5-4B sliding back and forth in the holes in the

guides

3A, 3B, respectively, when the movable carriage 5 is moved back and forth. In addition, a second hinge seat 5-5A is arranged on one side of the upright rod 5-1A opposite to the guide rod 5-4A; a second hinge seat 5-5B is arranged on one side of the upright rod 5-1C opposite to the guide rod 5-4B. More specifically, as shown in fig. 8, the guide groove 8 includes an elongated wheel groove 8-1 and a catching groove 8-2. The clamping grooves 8-2 are arranged on two sides of the guide groove 8 and are positioned on two sides of the wheel groove 8-1. The width of the wheel groove 8-1 allows the support wheels 2-3 of the support wheel unit 2 to roll in the wheel groove 8-1 while restricting the drum direction of the support wheels 2-3.

The movable bracket 5 moves back and forth relative to the frame 1, and a power structure is needed for providing power. The power structure and its operation will be described in detail below.

As shown in fig. 9 and 10, the power structure includes a power member 9 and a transmission member 10. The power unit 9 is a unit capable of inputting rotational power, the transmission unit 10 is a unit converting rotational power into linear motion, and the power unit 9 and the transmission unit 10 are mounted on the vertical poles 1-2. Specifically, the power component 9 comprises a mounting plate 9-1, a power source 9-2, a speed reducer 9-3 and couplings 9-4A and 9-4B. Wherein, the power source 9-2 can be a hand wheel or a motor with a control system. The speed reducer 9-3 is a bevel gear speed reducer with output shafts on two sides.

The transmission part 10 comprises a trapezoidal screw rod 10-1, a screw rod nut 10-2, a transmission pin 10-3, a screw rod fixing seat 10-4 and a screw rod supporting seat 10-5. The screw rod fixing seat 10-4 and the screw rod supporting seat 10-5 are used for bearing a screw rod 10-1, the rotation of the screw rod 10-1 enables a screw rod nut 10-2 to move linearly along the screw rod 10-1, and a transmission pin 10-3 is arranged on the screw rod nut 10-2. The transmission member 10 has a self-locking function.

In addition, the connecting rod 11 comprises a first transmission arm 11A and a second transmission arm 11B, one end of the first transmission arm is connected with the first hinge seat 1-4A, and the other end of the first transmission arm is connected with the second hinge seat 5-5A; one end of the second transmission arm is connected with the first hinge seat 1-4B, and the other end of the second transmission arm is connected with the second hinge seat 5-5B. The first transmission arm and the second transmission arm can be bent when the movable support moves back and forth.

Specifically, the first transmission arm 11A includes a first link 11-1A and a second link 11-3A, and the first link 11-1A has a long hole 11-2A with a width corresponding to the diameter of the transmission pin 10-3A, i.e., allowing the transmission pin 10-3A to slide in the long hole 11-2A. The first connecting rod 11-1A is hinged with the first hinge seat 1-4A, and the second connecting rod 11-3A is hinged with the second hinge seat 5-5A. The second transmission arm and the first transmission arm 11A have the same structure and principle and are not described in detail.

In actual operation, the rotary power of the power source 9-2 is split by the speed reducer 9-3 and drives the screw rods 10-1A and 10-1B to rotate through the couplers 9-4A and 9-4B respectively. If the output shafts at the two sides of the speed reducer 9-3 are in a reverse rotation type, the directions of the spiral angles of the screw rods 10-1A and 10-1B are the same; if the output shafts on the two sides of the speed reducer 9-3 are in the same-direction rotating type, the directions of the spiral angles of the screw rods 10-1A and 10-1B are opposite. Therefore, the lead screw nuts 10-2A, 10-2B will move simultaneously in a direction approaching the speed reducer 9-3 or in a direction away from the speed reducer 9-3, i.e., the driving pins 10-3A, 10-3B will move simultaneously in a direction approaching the speed reducer 9-3 or simultaneously in a direction away from the speed reducer 9-3. When the transmission pins 10-3A and 10-3B move towards the direction close to the power source 9-2, the connecting rods 11-1A, 11-3A, 11-1B and 11-3B can be driven through the long holes 11-2A and 11-2B, and then the movable support 5 is driven to move backwards; when the driving pins 10-3A and 10-3B move in the direction away from the power source 9-2, the connecting rods 11-1A, 11-3A, 11-1B and 11-3B can be driven through the long holes 11-2A and 11-2B, and further the movable support 5 is driven to move forwards. Therefore, the movable bracket 5 can be moved forward and backward on the basis of the vehicle frame 1 by the power member 9, the transmission member 10, and the link 11.

Fig. 11 is a contracted state of the movable stand 5. In the figure, mounting plates 12 are provided on the frame 1 and the mobile carriage.

As shown in fig. 12, the outriggers 1-3 of the frame 1 are further provided with locking devices 22, and the first locking device 22A and the second locking device 22B are respectively provided on the outriggers 1-3A, 1-3D (not shown in fig. 1-3D, 22B). The lockout device 22 includes a sensor 22-1A and an actuator 22-2A. In the locking state, the actuator 22-2A is inserted into the slot 8-2A of the guide groove 8A, and the movable bracket 5 cannot extend and contract on the frame 1 at the moment because the guide groove 8A is positioned on the movable bracket 5 and the locking device 22 is positioned on the cantilever beam 1-3 of the frame 1. As shown in fig. 13, when the sensor 22-1A senses the obstacle 23 and the unlocking height H of the locking device 22 is satisfied, that is, the supporting wheel 2-3 of the supporting wheel unit 2 can contact the upper surface 23-1 of the obstacle 23, the sensor 22-1A drives the actuator 22-2A to disengage from the slot 8-2A and complete unlocking, and the movable support 5 can be extended and retracted on the frame 1. The sensor 22-1A may be a mechanical ramp, a roller, or a distance sensor of various principles. The actuator 22-2A may be a mechanical linkage drive plug, or an electromagnet mechanism with a control system, or the like. The sensor 22-1A and the actuator 22-2A in the embodiment are mechanical, and the sensor 22-1A and the actuator 22-2A are kept downward under the action of self gravity until being jacked up by the obstacle 23.

The cylindrical workpiece transfer rack will be described in detail below. As shown in fig. 14, the cylindrical workpiece transfer rack includes a plurality of workpiece support blocks 13A, 13B, 13C, 13D, a plurality of rotating rings 14, a first carrier beam 15A, a second carrier beam 15B, two sets of linkage groups 15-1, 15-2, 15-3, 15-4, a transmission shaft 16, and a sleeve gear 17. Specifically, the plurality of workpiece support bases 13A, 13B, 13C, and 13D are arranged at predetermined intervals. Each workpiece support block is provided with 1 rotating ring 14, which is slidably arranged along the arc-shaped edge of the workpiece support block. The plurality of rotating rings 14 are provided with a first load beam 15A and a second load beam 15B in parallel, and each load beam 15 is connected with the plurality of rotating rings 14 through a set of connecting rods.

Since the plurality of workpiece supports 13 and the plurality of rotating rings 14 have the same structure, only 1 of them and one of them will be described in detail below.

As shown in fig. 15, the workpiece support base 13 has a first arc-shaped guide groove 13-1, a second arc-shaped guide groove 13-2 (on the back of the paper surface) and a through hole 13-3 on both sides thereof with the same radius of curvature.

As shown in fig. 16, the rotary ring 14 is mounted on the work support base 13. Specifically, the rotating ring 14 has a first rotating ring 14-1 and a second rotating ring 14-2 having the same radius of curvature, and the first rotating ring 14-1 and the second rotating ring 14-2 are connected by a connecting portion 14-4. The first rotating ring 14-1 is provided with a first transmission part 14-3, and the second rotating ring 14-2 is provided with a second transmission part 14-5. The first transmission part 14-3 and the second transmission part 14-5 are used for driving the rotating ring 14 to rotate. The first transmission 14-3 and the second transmission 14-5 are preferably non-uniform gears with identical gear parameters. The first transmission part 14-3 and the second transmission part 14-5 are used for driving the rotating ring 14, so as to improve the stress of the rotating ring 14. The first rotating ring 14-1 is arranged on the first arc-shaped guide groove 13-1, and the second rotating ring 14-2 is arranged on the second arc-shaped guide groove 13-2. And the first rotating ring 14-1 can move along the first arc-shaped guide groove 13-1, and the second rotating ring 14-2 can move along the second arc-shaped guide groove 13-2. The first rotating ring 14-1, the second rotating ring 14-2 and the workpiece support base 13 may be in sliding friction or rolling friction. The material of the first rotating ring 14-1, of the second rotating ring 14-2, if sliding friction, is preferably a self-lubricating material, such as a copper alloy; in the case of rolling friction, the first rotating ring 14-1 and the second rotating ring 14-2 should be rotatable rollers.

As shown in FIG. 17, the pin holes 14-3-1, 14-3-2, 14-3-3, and 14-3-4 are provided in the first transmission part 14-3, and are bilaterally symmetrical with respect to the centers of curvature 14-6, 14-3-2, and 14-3-3 of the rotary ring 14, and 14-3-1 and 14-3-4 are bilaterally symmetrical.

As shown in FIG. 18, the second transmission part 14-5 is provided with pin holes 14-5-1, 14-5-2, 14-5-3 and 14-5-4, and the pin holes 14-3-1 and 14-5-1, 14-3-2 and 14-5-2, 14-3-3 and 14-5-3, and 14-3-4 and 14-5-4 are overlapped in the circumferential direction. And therefore are bilaterally symmetrical with respect to the centers of curvature 14-6, 14-5-2 and 14-5-3, and 14-5-1, 14-5-4 of the rotating ring 14.

As shown in FIG. 19, the load beam 15 is provided with groupings of links 15-1, 15-2, 15-3, 15-4. The connecting rod group 15-1 comprises a connecting rod 15-1-1 and a pin shaft 15-1-2; the connecting rod group 15-2 comprises a connecting rod 15-2-1 and a pin shaft 15-2-2; the connecting rod group 15-3 comprises a connecting rod 15-3-1 and a pin shaft 15-3-2; the connecting rod group 15-4 comprises a connecting rod 15-4-1 and a pin shaft 15-4-2. The load-bearing beam 15 is also fixed with ball rollers 15-8, a buffer device 15-7 is arranged between the ball rollers 15-8 and the load-bearing beam 15, and the buffer device 15-7 is preferably a disc spring or a rubber pad. The buffer 15-7 serves as a load balancing device that enables all of the ball rollers 15-8 to contact the surface of the workpiece 26 (see fig. 23). The load beam 15 includes a first load beam 15A and a second load beam 15B. A connecting rod 15-1-1A of the first bearing beam 15A is fixed on the pin hole 14-3-3A and the pin hole 14-5-3A through a pin shaft 15-1-2A; the connecting rod 15-2-1A is fixed on the pin holes 14-3-3B and 14-5-3B through a pin shaft 15-2-2A; the connecting rod 15-3-1A is fixed on the pin holes 14-3-4C and 14-5-4C through a pin shaft 15-3-2A; the connecting rod 15-4-1A is fixed on the pin holes 14-3-4D and 15-5-4D through the pin shaft 15-4-2A. A connecting rod 15-1-1B of the second bearing beam 15B is fixed on the pin hole 14-3-1A and the pin hole 14-5-1A through a pin shaft 15-1-2B; the connecting rod 15-2-1B is fixed on the pin holes 14-3-1B and 14-5-1B through a pin shaft 15-2-2B; the connecting rod 15-3-1B is fixed on the pin holes 14-3-2C and 14-5-2C through a pin shaft 15-3-2B; the connecting rod 15-4-1B is fixed on the pin holes 14-3-2D and 15-5-2D through a pin shaft 15-4-2B.

As shown in fig. 20, the load beam 15A has a plurality of link groups 15-1-1A, 15-2-1A, 15-3-1A, 15-4-1A in pairs, symmetrically distributed on both sides of the load beam 15A, and in a figure-of-eight shape, provides symmetrical support force to the load beam 15A, and securely fixes the load beam 15A to the rotary rings 14A, 14B, 14C, 14D (without being affected by a change in the movement of the center of gravity of the workpiece). Similarly, the second load beam 15B also has a pair of symmetrically arranged linkages. As shown, the groupings 15-1-1B, 15-3-1B, etc. of the second load beam 15B are splayed to secure the second load beam 15B to the rotating ring 14A. The stable triangular stress structure is formed, so that the first load-bearing beam 15A and the second load-bearing beam 15B cannot collapse due to the gravity of the cylindrical workpiece 26. With further reference to FIG. 24, the planes of symmetry of the first and second load beams 15A, 15B (the planes of the dashed arrows in the figure) intersect at the centerline 14-6 of the rotating ring 14.

The propeller shaft 16 and the socket gear 17 provide power to power the rotating ring 14A. The sleeve gear 17 is fixed in the middle of the transmission shaft 16 and meshed with the long gear 19, and in actual operation, the long gear 19 drives the sleeve gear 17, and the sleeve gear 17 is rotated to drive the transmission shaft 16 to rotate. As shown in fig. 21, the drive shaft 16 includes a first gear 16-1 and a second gear 16-2, a threaded portion 16-3, and a pin 16-4. The first gear 16-1A of the transmission shaft 16A is engaged with the first transmission part 14-3A and the second transmission part 14-5A, and the second gear 16-2A is engaged with the first transmission part 14-3B and the second transmission part 14-5B. The first gear 16-1B of the transmission shaft 16B is engaged with the first transmission part 14-3C and the second transmission part 14-5C, and the second gear 16-2B is engaged with the first transmission part 14-3D and the second transmission part 14-5D. The rotating rings 14A, 14B can be driven to rotate when the drive shaft 16A rotates, and the rotating rings 14C, 14D can be driven to rotate when the drive shaft 16B rotates. As shown in fig. 22, the sleeve gear 17 includes a right inclined long hole 17-1, a left inclined long hole 17-2, and a sun gear 17-3. The left side of the sleeve gear 17 is sleeved on the transmission shaft 16B, and the pin 16-4B slides in the left inclined long hole 17-2; the right side of the sleeve gear 17 is sleeved on the transmission shaft 16A, and the pin 16-4A slides in the right inclined long hole 17-1. The right inclined long hole 17-1 and the left inclined long hole 17-2 of the sleeve gear 17 have an opposite number of included angles relative to the axial direction thereof, and are in a splayed shape. The position of the socket gear 17 on the

drive shafts

16A, 16B is adjusted by a nut 16-5A on the threaded portion 16-3A of the drive shaft 16A and a nut 16-5B on the threaded portion 16-3B of the drive shaft 16B. When the sleeve gear 17 moves leftward in the axial direction of the

transmission shafts

16A, 16B, the right inclined long hole 17-1 forces the transmission shaft 16A to rotate downward via the pin 16-4A, and the left inclined long hole 17-2 forces the transmission shaft 16B to rotate upward via the pin 16-4B. When the sleeve gear moves rightward in the axial direction of the

transmission shafts

16A, 16B, the right inclined long hole 17-1 forces the transmission shaft 16A to rotate upward through the pin 16-4A, and the left inclined long hole 17-2 forces the transmission shaft 16B to rotate downward through the pin 16-4B. Because the right oblique long hole 17-1 and the left oblique long hole 17-2 have opposite included angles relative to the axial direction thereof, when the sleeve gear 17 moves left and right along the axial direction of the

transmission shafts

16A and 16B, the

transmission shafts

16A and 16B can be driven to rotate at the same angle and in opposite directions, and further the positions of the first carrier beam 15A and the second carrier beam 15B in the radial direction can be adjusted as shown in fig. 24. When the sleeve gear 17 rotates upwards or downwards around the axis of the sleeve gear 17, the right inclined long hole 17-1 forces the transmission shaft 16A to rotate upwards or downwards through the pin 16-4A, and the left inclined long hole 17-2 forces the transmission shaft 16B to rotate upwards or downwards through the pin 16-4B, so that the rotation of the sleeve gear 17 can drive the

transmission shafts

16A and 16B to rotate in the same direction and at the same angle, and further the angles of the first bearing beam 15A and the second bearing beam 15B in the circumferential direction are changed through the rotating rings 14A, 14B, 14C and 14D.

According to the above-described functions of the transmission shaft 16 and the socket gear 17, as shown in fig. 23, the first carrier beam 15A and the second carrier beam 15B are used to lift the cylindrical workpiece 26, and the axial center position of the cylindrical workpiece 26 coincides with the axial center 14-6 of the rotary ring 14. When the rotating directions and the rotating angles of the

transmission shafts

16A and 16B are the same, the first carrier beam 15A and the second carrier beam 15B can be driven to change the angles in the circumferential direction by rotating the rings 14A, 14B, 14C and 14D, and at the moment, the ball rollers 15-8A and 15-8B roll on the surface of the workpiece 26. As shown in fig. 24, when the

transmission shafts

16A, 16B (not shown) rotate at the same angle but in opposite directions, the first and second carrier beams 15A, 15B can be driven to extend and retract in the radial direction by the rotating rings 14A, 14B, 14C, 14D (14B, 14D are not shown), the linkage sets 15-1-1A, 15-1-2A, 15-1-3A, 15-1-4A (15-1-2A, 15-1-4A are not shown), and the linkage sets 15-1-1B, 15-1-2B, 15-1-3B, 15-1-4B (15-1-2B, 15-1-4B are not shown). The first carrier bar 15A, the second carrier bar 15B can now accommodate cylindrical workpieces 26 of different diameters. When the first load beam 15A and the second load beam 15B are retracted, the workpiece 26A with a larger diameter can be loaded; when extended, can carry a smaller diameter workpiece 26B. Since the rotation rings 14A, 14B, 14C, and 14D (14B and 14D are not shown) have the same rotation angle and opposite rotation directions, the axial center of the workpiece 26 coincides with the axial center 14-6 of the rotation ring 14, that is, the radial expansion and contraction of the first carrier beam 15A and the second carrier beam 15B does not change the height of the axial center of the workpiece 26 relative to the workpiece support base 13, regardless of the radial positions of the first carrier beam 15A and the second carrier beam 15B.

Here, as shown in fig. 24, in a state where the cylindrical workpiece 26 is placed on the cylindrical workpiece mounting and demounting device (the center line 14-6 of the rotary ring 14 overlaps with the center line of the cylindrical workpiece 26), the rotary ring 14 is located at the first position where the first load beam 15A and the second load beam 15B are symmetrical with respect to the plane on which the center line of the workpiece 26 is located. When the rotating ring 14 is located at the first position, the distance from the plane of the center line of the second load beam 15B to the plane of the center line of the movable bracket 5 is smaller than the distance from the plane of the center line of the first load beam 15A to the plane of the center line of the movable bracket 5, and preferably, the plane of the center line of the second load beam 15B is coplanar with the plane of the center line of the movable bracket 5. When the cylindrical workpiece 26 is transferred to the horizontal machine tool, the rotary ring 14 is rotated clockwise from the first position to the second position shown in fig. 23 and 27, in which the center line of the second load beam 15B is located in the plane of the center line of the cylindrical workpiece 26. It is assumed here that the second load beam 15B is closer to the cylindrical workpiece 26 than the first load beam 15A. Conversely, if the first load beam 15A is closer to the cylindrical workpiece 26 than the second load beam 15B, the center line of the first load beam 15A is located in the plane of the center line of the cylindrical workpiece 26 when the rotary ring 14 is in the second position.

In summary, when the horizontal machine tool cylinder workpiece loading and unloading device of the present invention operates, the rotating frame power 21 drives the worm gear reducer 18 to rotate, the worm gear reducer 18 drives the long gear 19 to rotate, and the long gear 19 drives the sleeve gear 17 to rotate, so as to change the angles of the first carrier beam 15A and the second carrier beam 15B in the circumferential direction. When the left and right positions of the nuts 16-5A on the transmission shaft 16A and the nuts 16-5B on the transmission shaft 16B are changed, the sleeve gear 17 cannot rotate due to the self-locking effect of the worm gear reducer 18 and can only move left and right along the axial direction of the

transmission shafts

16A and 16B, so that the positions of the first bearing beam 15A and the second bearing beam 15B on the radial direction can be adjusted by rotating the

transmission shafts

16A and 16B in the same angle and different directions to adapt to cylindrical workpieces with different diameters. Meanwhile, the tooth width of the long gear 19 is significantly larger than that of the central gear 17-3 of the socket gear 17, so that the position of the socket gear 17 in the axial direction of the

transmission shafts

16A and 16B is changed, and the meshing and transmission of the long gear 19 and the socket gear 17 are not influenced.

The following describes in detail a specific process of the present invention for feeding a cylindrical workpiece loading and unloading device for a horizontal machine tool to the horizontal machine tool on an actual production line.

As shown in fig. 25, the horizontal machine spindle 23 is fixed to the machine bed 25 via the base 24, and the height h of the axis from the machine bed 25 is equal to the height h of the workpiece 26 from the machine bed 25. The workpiece 26 is supported by the first carrier beam 15A and the second carrier beam 15B. The rotating ring 14 is now in the first position. The movable carriage 5 is in an extended state with respect to the carriage 1 and is located below the workpiece 26, and at this time, the locking device 22 is in a locked state, so that the position of the movable carriage 5 with respect to the carriage 1 is fixed, and therefore the loading and unloading device can safely advance toward the machine bed 25 without overturning. The cylinder workpiece loading and unloading device for the horizontal machine tool of the invention serves a horizontal machine tool with a definite axial height h, so that the specific dimensions of the parts such as the carrier beam 15, the rotating ring 14 and the like can be determined by the axial height h, and the workpiece 26 can be ensured to reach the position of the spindle 23 of the horizontal machine tool in the height direction.

As shown in fig. 26, when the height of the machine tool bed 25 satisfies the unlocking height H of the locking device 22, the locking device 22 is unlocked, and the movable bracket 5 can be extended and retracted on the vehicle frame 1. The invention relates to a cylindrical workpiece loading and unloading device for a horizontal machine tool, which is used for serving a horizontal machine tool with clear height H of a machine tool body 25, so that the specific sizes of components such as a frame 1, a movable support 5, a workpiece supporting seat 13 and the like can be determined by H, the locking device 22 can be unlocked when the loading and unloading device reaches the machine tool body 25, and supporting wheels 2-3 of a supporting wheel unit 2 can be in contact with the machine tool body 25.

As shown in fig. 27, the movable carriage 5 is retracted toward the carriage 1 by the power unit 9-2, thereby allowing the cantilever beam 1-3 to extend above the machine bed 25 to bring the center of gravity of the workpiece 26 into alignment with the horizontal machine spindle 23. At this time, the rotating ring 14 is located at the second position, the center line of the rotating ring 14 forms a preset included angle with the center line of the cylindrical workpiece 26, and the center line of the second load beam 15B perpendicularly intersects with the horizontal machine spindle 23. In the process, the first and second load beams 15A, 15B are rotated so that the center line of the workpiece 26 is closer to the position of the second load beam 15B in the figure (before the center line of the workpiece 26 is located on the symmetrical center line of the first and second load beams 15A, 15B) until the center line of the workpiece 26 overlaps with the center line of the second load beam 15B. The supporting wheels 2-3 of the supporting wheel unit 2 contact the machine bed 25 and provide acting force to keep the frame 1 and the movable frame 5 balanced and not to overturn, so that the loading and unloading device can not overturn due to the position change of the workpiece 26. The elastic elements 2-9 of the supporting wheel unit 2 both act as load leveling devices and enable the supporting wheels 2-3 to move a certain distance to accommodate a slight height difference between the unlocking heights H of the machine bed 25 and the locking device 22. After the workpiece 26 reaches the horizontal machine tool spindle 23, the rolling characteristic of the ball rollers 15-8 also allows the workpiece 26 to move along the axial direction, so that the workpiece can conveniently enter a clamping device (such as a chuck) of the horizontal machine tool spindle 23 and be fixed. Thus allowing circumferential rotation and axial movement of the workpiece 26 relative to the load beam 15 is the meaning and effect of using the ball rollers 15-8.

In the invention, the rotating frame power 21 is manually rotated to drive the worm gear speed reducer 18 to rotate. Since the worm gear reducer 18 is connected to the long gear 19, driving the worm gear reducer 18 to rotate causes the long gear 19 to rotate therewith. The long gear 19 is engaged with the socket gear 17, so that the long gear 19 rotates the socket gear 17; the socket gear 17 is fixed to the transmission shaft 16 so that rotating the socket gear 17 can rotate the transmission shaft 16. The first gear 16-1 of the transmission shaft 16 is meshed with the first transmission part 14-3 and the second transmission part 14-5, when the sleeve gear 17 rotates around the axis of the sleeve gear, the right inclined long hole 17-1 forces the transmission shaft 16A to rotate along with the transmission shaft through the pin 16-4A, and the left inclined long hole 17-2 forces the transmission shaft 16B to rotate along with the transmission shaft through the pin 16-4B, so that the rotation of the sleeve gear 17 can drive the

transmission shafts

16A and 16B to rotate in the same direction and at the same angle. As the

transmission shafts

16A, 16B rotate, the first gears 16-1A, 16-2A, 16-1B, 16-2B of the transmission shafts 16 also rotate in the same direction and at the same angle; the first gears 16-1A, 16-2A, 16-1B, 16-2B rotate to drive the rotating rings 14A, 14B, 14C, 14D to rotate clockwise or counterclockwise within a predetermined angle range. As described above, according to the present invention, by designing the above-described multiple gear pair structure, it is possible to transport a heavy cylindrical workpiece with a small force. According to the above-described operation principle, in fig. 27, the rotating frame 14 is rotated in the clockwise direction by the rotating frame power 21, and the first load beam 15A and the second load beam 15B are also rotated in the clockwise direction until the second load beam 15B approaches or reaches the position right below the workpiece 26. Because the workpiece 26 is supported on the load beam 15 through the ball rollers 15-8, the friction force is reduced, and the rotation of the load beam 15 can not damage the surface of the workpiece.

The horizontal machine spindle 23 is operated to receive the workpiece 26 so that the weight of the workpiece 26 is received by the horizontal machine spindle 23. As shown in fig. 28, after the workpiece 26 is fixed to the horizontal machine tool spindle 23, the second load beam 15B is already positioned below the workpiece 26, and therefore the second load beam 15B does not interfere with the leftward withdrawal of the loading and unloading apparatus. During the leftward withdrawal of the loading and unloading apparatus, the carriage 1 is moved, and the movable bracket 5 is extended below the line of symmetry of the first carrier beam 15A and the second carrier beam 15B by the power unit 9-2 (so that the gravity line of the workpiece overlaps the movable bracket 5 when the workpiece is supported by both the first carrier beam 15A and the second carrier beam 15B, preferably). When the locking device 22 is disengaged from the machine bed 25, the locking device 22 locks the mobile carriage 5 again, fixing its position with respect to the carriage 1. When the workpiece 26 is finished, it is detached from the horizontal machine spindle 23, in reverse to the procedure shown.

Compared with the prior art, the cylinder workpiece loading and unloading device for the horizontal machine tool does not need manual transportation, and mechanical loading and unloading are realized; the cylinder workpiece loading and unloading device for the horizontal machine tool is small in size and occupied space, and is suitable for production lines of various sizes.

The present invention has been described in detail. It will be apparent to those skilled in the art that any obvious modifications thereof can be made without departing from the spirit of the invention, which infringes the patent right of the invention and bears the corresponding legal responsibility.

Claims

1. A device for loading and unloading a cylindrical workpiece for a horizontal machine tool is characterized by comprising a frame, a movable bracket, a mounting plate, a cylindrical workpiece transfer frame and a power transmission part,

the frame is movable;

the mounting plate is mounted on the upper part of the frame;

the cylindrical workpiece transfer rack is rotatably mounted on the mounting plate and is used for supporting and transferring the cylindrical workpiece;

2. The cylindrical workpiece loader device for a horizontal machine tool of claim 1 wherein said cylindrical workpiece transport rack comprises a plurality of workpiece support blocks and a plurality of rotating rings,

the workpiece supporting seats are arranged at intervals of a preset distance, and 1 rotating ring is arranged on each workpiece supporting seat;

the rotating ring is arranged along the arc-shaped edge of the workpiece supporting seat in a sliding mode, the rotating ring rotates between a first position and a second position, the center line of the rotating ring is overlapped with the center line of the main workpiece in the state that the rotating ring is located at the first position, and the cylindrical workpiece is supported by the rotating ring; and when the rotating ring is positioned at the second position, the central line of the rotating ring and the central line of the main workpiece are linearly supported by a preset angle, and the cylindrical workpiece is transferred to the horizontal machine tool.

3. The cylinder work loader device for a horizontal machine tool according to claim 2, wherein said rotating ring is provided with a first rotating ring and a second rotating ring having the same radius of curvature, said first rotating ring and said second rotating ring being connected by a connecting portion; the first rotating ring is provided with a first transmission part, the second rotating ring is provided with a second transmission part, and the first transmission part is matched with the second transmission part to drive the rotating ring to rotate.

4. The cylindrical workpiece loader device for a horizontal machine tool of claim 2 wherein said cylindrical workpiece transport carriage further comprises a first load beam, a second load beam, and a linkage; the two bearing beams are connected with the rotating ring through the connecting rod group.

5. The cylindrical workpiece loader device for a horizontal machine tool of claim 2 wherein said cylindrical workpiece transport rack further comprises a drive shaft,

the transmission shaft comprises a first gear, and the transmission shaft is connected with the rotating ring through the first gear so as to drive the rotating ring to rotate.

6. The cylinder work loader device for a horizontal machine tool according to claim 1 wherein said power transmission comprises a turret power, a worm gear reducer, a long gear, a sleeve gear,

the rotating frame power is connected with the worm gear speed reducer and drives the worm gear speed reducer to operate;

the worm gear speed reducer is connected with the long gear and drives the long gear to rotate;

the sleeve gear is connected with the cylinder workpiece transfer frame, and the sleeve gear drives the cylinder workpiece transfer frame to rotate.

7. The cylinder work loader and unloader device for a horizontal machine tool according to claim 6, wherein the sleeve gear is provided with a right slanted long hole, a left slanted long hole and a center gear,

the central gear is located at the middle position of the sleeve gear,

the right oblique long hole is located on the right side of the central gear, and the left oblique long hole is located on the left side of the central gear.

8. The cylindrical workpiece loader device for a horizontal machine tool of claim 1 wherein said carriage comprises a base, a column and a plurality of outriggers,

the upright post is arranged on the base;

the plurality of cantilever arms are disposed above the column parallel to the ground.

9. The column workpiece loader device for a horizontal machine tool of claim 8 further comprising a movable carriage movably mounted relative to said carriage.

10. The cylindrical workpiece loader device for a horizontal machine tool of claim 1 wherein said movable support comprises a base, a column and a support base,

the base is provided with a plurality of upright posts, the supporting seat is arranged on the upright posts, and the supporting seat is provided with a plurality of guide grooves.