Sheet metal bending press (versions)

FIELD: process engineering.

SUBSTANCE: invention relates to metal forming, particularly, to bending press. Top and bottom tables are arranged opposite each other in vertical direction. Note here that one of said tables may move relative to another one and has cutouts symmetric about central plane. Every cutout has open outer lateral side and first and second parts, second part being arranged on inner side relative to first one and jointed therewith. Note also that geometry of said part rigidity of table section between cutout and tool fastener exceeds than between second part of cutout and tool fastener. At least one element of table curvature adjustment is located in cutout first section.

EFFECT: higher quality of bending.

26 cl, 21 dwg

 

The technical field to which the invention relates.

The invention relates to a bending press with tables for controlled deformation.

The level of technology

Bending presses are machines, which themselves are well known. As shown in figa, the machine contains the lower table 12 and table top 14, is movable relative to the table 12. Often the lower table 12 is stationary, and the upper table 14 can move up to the bottom of the table under the action of the power cylinder V1and V2that affect the ends 14a and 14b of the upper table. Often the lower table 12 has a free edge 12A, provided with fastening means 16 for bending matrices 18. In the same way, the edge 14 with the top of the table 14 is equipped with fastening means 20 for bending punches 22.

Sheet metal or sheet metal F is placed on the bending matrix 18 of the lower table 12. Sheet metal F can have a variety of length L depending on the destination. Under the action of the pistons of cylinders V1and V2mounted on the upper table, the punches 22 are approaching sheet metal F laid on matrices bottom of the table. After contact of the punch with sheet metal the pressure begins to increase, and the punch zadumivaetsa in sheet metal or sheet metal F, deforming it first in the area of elastic deformation and then in the field of plastic deformation, that allows you to get a certain bending sheet metal.

Due to the fact that the force is transferred to the upper table-cylinder V1and V2that act on the ends of the table, the linear load is distributed between the two ends of the tables corresponds to the line of deformation of the top of the table in the form of a concave arc with the maximum deformation near the mid-plane of the table. This means that at the end of the bending process of the Central group of punches zadumivaetsa in sheet metal less than end groups. If bending is produced on the matrix, which when bending is perfectly straight, get a sheet metal F with a more open angle of the bend in the Central part than at the ends. Of course, such a result is unacceptable.

In practice, a matrix mounted on the lower table or, more precisely, on the free edge of the table, bending process are deformed in a concave line with a maximum in the Central part. As a result of these two strains received almost bending sheet metal is widely open angle bend in the middle part of the press and a very narrow angle of bend at the ends. In practice, the difference can reach several degrees, for example, 93° in the mid-plane of tables and 90° at the ends.

Thus obtained sheet metal has a low accuracy in relation lineanother, that gives it a form, called a "boat".

To eliminate this drawback, it was proposed various solutions to control deformation of the edges of tables with various tools with the aim of obtaining a uniform flexible along the entire length of bent sheet metal or sheet metal F.

Most often these solutions include the implementation of slits, such as slits 24 and 26, shown in figa and made in the lower table is symmetrical relative to the Central plane of the press. These slits define the Central area 28 of the lower table, in which no slits and which has a length of I0and two slots 24 and 26 in length.

In the presence of the slots 24 and 26 of classical type, that is, between leaving a significant portion 28 of length I0without slots, as shown in figv receive essentially parallel lines D1and D2deformation of the respective upper edges of the table 14 and the bottom of the table 12. When this is properly flexible. However, this result is obtained only in the case where sheet metal or sheet metal has a length essentially equal to the total length of the bottom or top of the table. In contrast, as shown in figs, in these known solutions, when the sheet metal has a length less than the length of the bottom or top of the table, both lines D'1and the d" 2strain out concave.

In the utility model Japan 2558928 in the name of AMADA CORPORATION describes a solution in which each of the two slits the bottom of the table is equipped with a movable body whose position is inside the slot can be adjusted. This movable body is in direct contact with the bottom and top edges of each slot. However, this solution allows to obtain satisfactory results only for some values of the length of sheet metal in relation to the total length of the press, and not to any length. The decision does not take into account problems related to the fact that the sheet metal can occupy a single position relative to the Central plane bending presses and yet must be provided identical flexible along the entire length of the sheet.

In the patent document EP 1112130 as solutions proposed to equip each slot in the bottom of the table body movement, connecting the upper free part of the fixed lower part of the bottom of the table to cause the approach of the upper surface of the slot to its lower surface, treating it as fixed. This allows a controlled manner to change the curvature of the line of deformation of the upper free part of the carrier matrix bottom of the table without transmitting stresses to the tables. The drawback of the solution is that is requires the installation of complex hydraulic control.

Solutions similar to the type described in patent documents JP 2001-71033, JP 2000-343125 and WO 01/43896.

Disclosure of inventions

The objective of the invention is to provide a bending press which includes correction of deformation of the edges of tables, which eliminates the aforementioned disadvantages and in particular allows to obtain essentially parallel lines of deformation of the edges of the upper and lower tables in a very wide range of lengths to be bending a metal sheet with respect to the length of the press tables as in symmetric and asymmetric position of the metal sheet relative to the Central plane of the press with the same setting of the machine; or this system allows to obtain high accuracy flexible sheets for very long lengths of materials that are considered difficult to bend.

According to the first aspect of the invention the solution of this problem is achieved in the bending press for bending sheet metal comprising upper table and the lower edge of which shall be the first bending tools, and the lower table, the upper edge of which bears the second bending tools, and two tables are movable relative to each other to transfer forces to the flexible sheet metal, while the press has a vertical middle plane, one of the tables provided throughout its thickness two slits, the location is nymi symmetrically relative to the Central plane, and each slot has a first open end facing the side edge of the table, and the closed end and the closed end define a segment table length of I0without slots.

Bending press differs in that it additionally contains an even number of (pairs of) stops, each stop is located in one of the slots at a fixed distance from the closed end stops are located symmetrically relative to the Central plane and have a predetermined coefficient of elasticity, with each focusing defines the area of the slot where it is located, the ability of the regulated between the two edges of the slot under the action of the load applied to the containing slot table. This convergence is set, at least one of the two parameters, including clearance j, originally defined this way into the slits in the absence of the applied load and the elastic deformation of this emphasis. The possibility of convergence created by the fence, closer to the closed end, less than one that creates focus, closer to the open end, if any. The possibility of convergence of the edges of the slot corresponding to the lugs and their position in the slots, is defined so that at the end of the application of force to the flexible movable table to another table through the sheet metal of the line of curvature of the edges of the tables were in existence is actually parallel to each other.

The invention is applicable for bending presses of all types, regardless of whether the movable table to the upper table or the lower table. Similarly slotted correction can be made at the top or at the bottom of the table.

However, most often moving the upper table, and the slots are cut in the lower table.

It should be understood that due to the presence of the stop or stops in each slot for metal sheets of large length (i.e. sheets, which cover not only the area of the table without slots, but also significant portions of the slots) receive essentially parallel to the deformation of the edges of the upper and lower tables. Thanks to the provided initial gap (in the absence of attached to the table load) and/or elastic deformation of the lugs attached to are provided with slots table voltage causes sequential adjustable convergence of the edges of the slot. On the one hand, by appropriate positioning of the stop or stops in each slot and, on the other hand, due to the gap created by each stop and/or ability of the fence to the elastic deformation, can be an effective way to get a parallel deformation of the edges of the upper and lower tables, even if the length is subjected to bending sheet metal is great and even if it is with a certain eccentricity from SyteLine the mid-plane R R press.

It may be provided that at least some of the stops are located in their respective slots without a significant gap in the absence of load. In this case, the deformation of the slot due solely to the ability to stop deformation. May also be provided the presence of such a gap, and in this case, the slit is deformed loosely, and then through the deformation stops.

According to the embodiment, the power supplied to the rolling table, attached to its two ends so that the two ends are provided the same travel length, and two symmetric emphasis provide the same opportunity adjustable convergence.

This embodiment is particularly suitable for cases when subject to bending of the sheet occupies a symmetrical position relative to the Central plane of the press.

According to the exemplary embodiment in accordance with the first aspect of the invention a bending press is characterized by the fact that the power supplied to the rolling table, attached to its two ends so that the two ends is provided by different travel length, and two symmetric emphasis provide the same opportunity adjustable convergence.

According to the provided invention features two symmetrical emphasis can provide opportunities ambiguity of nakiwogo adjustable convergence.

This embodiment is applicable for the case when the metal sheet has an asymmetrical position relative to the Central plane R R press. In this case, the asymmetric nature of the sheet position is compensated by the varying length of movement of the two ends of the sliding table.

In addition, preferably, the press has four stops, two stops located in each slot. Stops can define an adjustable gap j.

This location allows you to adjust the deformation of the table in two different points of the slot. Accordingly, the solution is particularly applicable to tables of considerable length, in a typical case, length 2.5 m, 3 m or more.

The initial adjustment of the position of the lugs in the slots applicable to many situations flexible. However, in some cases, it may be used to modify this adjustment, so that is interesting decision, which stops allow a simpler way to modify they identify the gap.

According to one possibility, at least one of the lugs defines a gap equal to zero. Preferably the stops determine the gap size less than 1 mm In most cases, the gap is almost less than 0.3 mm

In the preferred embodiment can be provided that the stops, which occupy a fixed p is the situation while using the press, can be adjustable in its position in the function of the particular length to be more flexible sheets. This determination of the position of focus depending on the subject to bending of the sheet can be obtained using three-dimensional mathematical models.

According to the exemplary embodiment in accordance with the first aspect of the invention, each stop includes a first wedge having a first end rigidly connected to the first edge of the slot, and a second end forming a first inclined plane relative to the direction of the slot, and a second wedge having a first end connected with the second edge of the slot, but movable relative to the edges of the slot along its direction, and the second end forming an inclined plane that is parallel to the first inclined plane and between the planes gaps exist in the absence of attached to the table load, which by moving the second wedge can adjust the gap between the two wedges when there is no load applied to the containing slot table, and therefore, between the two edges of the slot.

According to the second aspect of the invention a bending press includes upper table, equipped with a mount for the top of the instruments, and the lower table is equipped with a mount for the lower instruments, and two tables are located opposite each other in the vertical direction of one of the tables made movable relative the other in a vertical direction, one of the tables contains slots that are located symmetrically relative to the Central plane, and each slot has an open outer side end. Bending press differs in that each of the slots contains the first part of the slot and the second slot, which is located on the inner side relative to the first part of the slot and connected with the latter, the shape of these parts of the slots is such that the rigidity of the table, located between the slot and the fastening tool, more between the first part of the slot and the fastening tool, than between the second part of the slot and the fastening tool, and the first part of the slot is at least one element of the adjustment of the bending table.

As will be understood from the subsequent detailed description, these features allow to obtain high accuracy flexible as sheets of large width comparable to the length of the tables, as well as less wide sheets, providing essentially parallel to the deformation of the edges of the upper and lower tables.

Preferably, the vertical distance between the inner end of the first part of the slot with which it is connected with the second part of the slot, and fastening tools for greater vertical distance between the inner end of the second part of the slot and the fastening tool.

<> Preferably the first and second parts of the slots are tilted with respect to each other. In this case, preferably the first portion of the slot includes at least one section of the first part of the slot having a General horizontal direction, and at least the inner end of the second part of the slot opposite the first side of the slot is oriented toward the fastening tool. It is preferable that the second part of the slot were inclined to the fastening tool.

In a preferred example of execution of the second part of the slot has a curved shape, the concavity of which is directed to the fastening tool.

In a preferred example of execution of the second part of the slot has the shape of a ladder.

In a preferred example, the first part of the slot has a General horizontal direction, and the inner end of the second part of the slot is oriented essentially horizontally to the vertical middle plane of the table.

In a preferred example of execution of the second part of the slot includes at least one portion extending in a direction away from the first part of the slot.

In a preferred example, the first portion of the slot includes an outer section of the slot is made inclined in such a way that approaches the fastening tool is now relative to the inner section of the first part of the slot.

In the preferred exemplary embodiment, at least one of the parts of the slots has a vertically measured width, which varies depending on the area of this part of the slot in which the width is measured.

In the preferred exemplary embodiment the inner ends of the first parts of the slots are located so that during bending of sheet metal whose width essentially equal to the length of the top or bottom of the table, the difference in height between the peak of the convex bending up the middle of the bottom of the table and two side ends of the lower table remains within a predefined tolerance.

In the preferred exemplary embodiment the inner ends of the second parts of the slots are located so that during bending of sheet metal, is placed in the middle of the table length, i.e. sheet metal, the width of which is less than the length of the top or bottom of the table, the difference in height between the peak of the convex bending up the lower mid-table and lower part of the table in contact with the side edges of the sheet metal remains within a predefined tolerance.

In the preferred exemplary embodiment, the length of I0defined so that the area of the table between the closed ends of the slots was able to absorb a voltage essentially equal to the maximum at which the custody of, enclosed in the flexible sheet, without having to cause plastic deformation are provided with slots table. Under the "maximum voltage" is meant the maximum voltage to which the calculated bending press and which does not cause plastic deformation.

Preferably, the length between the closed ends of the slots is less than 35% of the length L of the table containing the slits. Even more preferably, this length is of the order of 20%±15%, preferably 20%±5% of the length L of the table containing the slits.

This particular length not containing slots of the table can effectively prevent the deformation between the center of the sheet and it ends when processing a shorter metal sheets with a width close to the length I0.

Preferably a bending press is characterized by the fact that the length of I0approximately 80% of the length centered on the press sheet, for which the curve deformation under the action of the sliding table is essentially insignificant.

Other features and advantages of the invention will be clear from the subsequent description.

Brief description of drawings

Next, with reference to the accompanying drawings will be described in detail embodiments of the invention that do not have restrictive. In the drawings:

figa depicts the front view a bending press of known type,

figv the submitted the deformation of the edges of tables standard bending press in the case when the sheet has a length essentially equal to the length of the tables bending press,

figs is curved deformation of the edges of tables known bending press in the case when subject to bending the sheet has a reduced length,

figure 2 depicts the front view a bending press according to the invention at rest,

figure 3 depicts the front view a bending press, representing curves deformation when subject to bending the sheet has a reduced length,

figure 4 depicts a view similar to figure 4, curves representing deformation when subject to bending sheet metal has an intermediate length,

figure 5 depicts the front view a bending press according to figure 3, curves representing deformation when subject to bending sheet metal has a length close to the length of the table,

6 depicts a portion of the lower table of the press, showing the preferred form of slots,

figa, 7B, 7C and 7D depict the curves showing the change of the distance between the edges of the slot as a function of force applied in various cases, the initial adjustment,

Fig depicts the front view of the emphasis in an embodiment,

Fig.9 depicts the front view of two of emphasis, supplied with a drive system control clearance relating to the stops,

figure 10 depicts a bending press according to the invention in an embodiment,

11 and which opens a bending press according to the invention in another embodiment according to the second aspect of the invention,

Fig-14 depict enlarged views of embodiments of slots,

Fig depicts a more classical press, compared to which was conducted comparative tests,

Fig. with 16A-16D 21-21D illustrate comparative tests.

The implementation of the invention

First, with reference to figure 2 will be described the principle of implementation of the compensation system deformation in accordance with the invention as applied to a bending press.

In figure 2 the essential elements of the bending press is shown in a state of no load on the press tables. The press includes a movable table top 30, actuated power cylinders V1and V2and a still lower table 32. This drawing does not show the holders of the instruments mounted on the free edges 30A and 32A of the upper table 30 and the bottom of the table 32. In the lower table 32 made two slits 34 and 36, each of which has an open end 36A, 34a with exit to the outside from the bottom of the table and the closed end 34b and 36b. The closed ends 34b and 36b of the slots 34, 36 define between them a Central part 38 of the table, which has no slits and forms a rigid bridge between the upper part 40 of the table above the slots 34 and 36 and the lower part 42. The distance between the closed ends 34b and 36b of the slots 34 and 36 is equal to I0.

Needless to say that edges 30A, 32A tables 30, 32 are supplied to the holders of the instruments, shown in Fig.

The slots 34 and 36 are preferably parallel to the free edge 32A. They are located symmetrically relative to the Central plane R R press, perpendicular to the length of the tables 30 and 32. Thus, the slots 34 and 36 define the top edge 34C, 36C, and the lower edge 36d, 34d slots.

According to the invention, the stops 44, 46, 48, 50 are installed in each of the slots 34 and 36 are located symmetrically relative to the Central plane R R. Thus provided a pair of stops. In the exemplary embodiment of figure 2, each slot 34, 36 are provided with two lugs, respectively, the lugs 44 and 46 to the slots 34 and the lugs 48 and 50 to the slot 36. Their distance from the ends of the bottom of the table are I1and I2. The function of the stops is the creation of the locations of the regulated rapprochement between the upper edge 34C, 36C and the bottom edge 34d, 36d of each of the slots 34, 36 under the action of a force applied to the upper table 30. These lugs 44, 46, 48 and 50 occupy a fixed position in the slots.

Hereinafter will be described a preferred example of execution of these lugs serving to identify the two initial gap, and in a broader sense to control the convergence of the two edges 34C and 34d or 36C and 36d of one slot 34 or 36. Here it should be clarified that the lugs 46 and 48, near to the closed ends of the slots 34b, 36b, determine the capacity of sblizhenie the edges 34C and 34d or 36C and 36d of one slot 34 or 36, which is less than the capacity of the approximation generated by the stops 44, 50, neighbors to the open ends 34a and 36A of the slots. Every stop 44, 46, 48, 50 are made of a suitable material and has such a horizontal section that the elastic deformation of the lock under the action of applied forces is subject subject to precise definition patterns, which at least partially corresponds to the desired to obtain correction.

In conclusion, a description of the General definition of the stabilization system of deformation of the upper and lower tables 30 and 32 should add that the length of I0zone 38 jumper between the two slots 34, 36 are greatly reduced in comparison with the length of this zone in the known devices. Area 38 jumper has a length of I0that reduced, but completely sufficient for the perception of the maximum voltage applied in the process of the flexible sheet.

Preferably the length of the I0is less than 90% of the total length of the table 30 or 32 with the slots 34, 36, and often the length of the bottom of the table 32. Of course, this length I0depends on the thickness of the table in the direction perpendicular to the plane of the drawings. Even more preferably, the length of I0is from 15 to 25% of the total length of the bottom of the table 32. It should be understood that for the presses of limited length, such as less than 2 m, the percentage will be in the upper area and range.

Further, preferably, the length of I0can be defined as follows: length of I0corresponds to at least 80% of the length of sheet metal or sheet metal bending across its length does not cause significant deformation of the free edges 30A and 32A of the upper table 30 and the bottom of the table 32, when this sheet metal or sheet metal centered relative to the Central plane R R. From a practical point of view, the width of such sheet metal or sheet metal is of the order of 80 cm, so that the length of I0is approximately 65 cm for the total length of the top of the table 30 or the bottom of the table 32, which corresponds to the standard length of a bending press with the value of 3 m

As already explained above, the function stops 44, 46, 48, 50 is to control the convergence of the edges 34C, 36C of each of the slots 34, 36 during the application of force flexible. By managing the convergence of the edges 34C and 34d or 36C and 36d of the slot 34 or 36 control the deformation of the upper edge 34C, 36C of the slot 34 or 36 and, consequently, deformation of the upper edge 32 of the lower table 32 in the presence of the slots 34, 36.

Management of convergence by using the stops 44, 46, 48, 50 or through the designated emphasis of the initial gap j, either due to elastic deformation of the support under the action of stress, or as a result of their comb the nation. Thus, using these two parameters, it is possible to achieve high accuracy in deformation of the bottom of the table for metal sheets of different length.

On figa-7D shows the curves of reduction of the distance d between the edges of the slot in the power function F for various combinations of the above parameters.

The tests show that an adequate initial gap j if there is less than 1 mm even for bending presses of great length, in a typical case, a length of 6 m To more standard presses length of the order of 3 m this gap if there is less than 0,8 mm

On figa shows a decrease in the distance d between the two edges 34C and 34d or 36C and 36d of the slot 34 or 36 (x-axis) as a function of the applied force F (y-axis) in the case when both the initial narrowing of the gap J and elastic deformation D of emphasis. On the curve point FP corresponds to the end of the flexible.

Chart on FIGU corresponds to the case when the end of the flexible FP occurs before complete closure of the gap J. Elastic deformation of the stop does not occur. This situation may occur for very short metal sheets or in the case where each slot has two or more stops, or when the zone, for which the chart on FIGU, farther away from the closed end of the slot.

<> Chart on figs corresponds to the case when the initial adjustment of the stop does not provide clearance J. Accordingly, reduction of the distance d occurs only due to elastic deformation D of emphasis.

Chart of Fig 7D corresponds to the special situation when there is no initial gap, no elastic deformation stops. This situation can only occur in the case of flexible sheet metal, located eccentrically relative to the Central plane R R.

Held on the bending press of the type described tests show that the pre-determined initial gap j, the correct length I1, I2the tappets 44, 46, 48, 50 in the slots 34, 36 and the action stops effectively achieved essentially parallel lines of deformation of the free edges 30A, 32A of the upper and lower tables 30, 32 when the length of sheet metal F and at a certain way it is centered relative to the Central plane R P machine.

As shown in figure 3, when the sheet metal has a reduced length L1two lines of deformation D2D1edges 30A, 32A of the upper table 30 and the bottom of the table 32 is essentially parallel due to the special choice of the length of I0zone 38 jumpers.

As shown in figure 4, in the case where sheet metal which has a length L 2intermediate between the total length of tables and minimum length, under the action of stress attached to the upper table 30, the deformation of the upper part 40 of the lower table 32 causes the elimination of the gap j stops 46 and 48, the nearer to the closed ends 34b and 36b of the slots 34, 36, and/or elastic deformation. However, for a given length of sheet metal lugs 44 and 50 remains certain clearance j', as shown in figure 4, there is elastic deformation. For this length of sheet metal tests show that the line of deformation of the free edges 30A, 32A of the upper table 30 and the lower table 32 essentially parallel.

Figure 5 shows the deformation of the free edges 30A, 32A of the upper table 30 and the bottom of the table 32 in the case when the length L3sheet metal sheet metal or essentially equal to the total length of the top of the table 30 or the bottom of the table 32. In this case, consistently occurs liquidation clearance j stops 46 and 48 and/or these lugs 46, 48 are deformed, and then, at the end of the effort, in turn, selects the gaps defined by the stops 44 and 50, and/or stops 44, 50 elastically deformed. Thus, as shown by the tests, the free edges 30A, 32A of the upper table 30 and the bottom of the table 32 with the deformation remain essentially parallel.

Held on the bending press about Sanogo type tests, in the case when it is necessary to conduct a more flexible product, which should be placed eccentric relative to the Central plane R R press receive mode of operation, very similar to the one described above for the centered subject to the provisions of the bending of the sheets.

On Fig shows a preferred example of execution stops. Emphasis 59 Fig formed by two wedges 60 and 62 located opposite each other. In the preferred exemplary embodiment, the upper wedge 60 includes upper end 60A, rigidly attached to the upper edge 34 of the slot 34 without movement. The other end 60b of the wedge 60 has a surface with a slight slope. The second wedge 62, which forms the stop 59 together with the first wedge 60, contains the lower end a, which is slidable on the bottom edge 34d of the slot 34. The lower wedge 62 also includes a second end 62b having a tilt relative to the edge 34d of the slot 34 and parallel to the inclined surface 60b of the upper wedge 60. Subject to the preliminary determination of the functional position of the stop 59 is fixed relative to the Central plane QQ' upper wedge 60, parallel to the Central plane R R press. Limited movement of the lower wedge 62, shown by arrows F, F', you can edit in the plane QQ' distance j between the sloping ends 60b, 62b corresponding Kline is 60, 62. As already mentioned, the possibility of movement of the lower wedge 62 in any case not possible to change the functional position of the stop 59, it allows only be adjusted with very high precision determined by the stop gap j, that is, the distance between the sloping ends 60b, 62b of the respective wedges 60, 62. In the example of execution according Fig gap can be adjusted with a precision of hundredths of a millimeter. Two forming the stop 59 of the wedge 60 and 62 made of a material which can transmit force in a few hundred thousand Newtons between the two edges 34C, 34d or 36C, 36d of the slots 34, 36 of the lower table 32, which corresponds to the power supplied power cylinders V1and V2.

Figure 9 shows an example implementation of the wedges 62 with a drive movement. Top wedges 60 stops 59 fixed relative to the upper edges 34C, 36C of the slot 34 or 36. Bottom wedges 62 stops 59 are made with the possibility of plane-parallel movement relative to the lower edge 34d, 36d of the slot 34 or 36. Drivers 70 and 72 controls movement of the movable wedges 62.

In the above-described preferred embodiments, the upper table 30 is movable, and the lower table 32 - stationary. Needless to say that in the framework of the invention may be run in reverse order, i.e. upper table can b the th fixed, and the lower movable table.

The same applies to the slots 34 and 36, are made in the lower table 32. It is obvious that the slots 34 and 36 can be performed in the upper table 30 regardless of whether it is movable or immovable, subject to the same rules the tappets 44, 46, 48, 50 or 59 and identify areas 38 jumpers, separating the closed ends 34b, 36b of the two slots 34, 36.

In the previous drawings presents the slits 34, 36, essentially parallel to the edge 32A of the lower table 32 and having an essentially constant width. However, you may be interested in another form of slots, in particular to reduce the stresses in the table with slots, preferably in the lower table 32, under the action of forces from another table 30. This option is shown on Fig.6.

This drawing shows the upper portion 40 and lower portion 42 of the lower table 32. In the drawing, the slot indicated by position 80.

In this embodiment, the slot 80 includes a first portion 82 facing the side of the table 32, the middle portion 64 and the third part 86, which ends with closed end 88 of the slot 80.

The first portion 82 of the slot 80 is made essentially rectilinear, has essentially a constant height and is held inclined at an angle α to the edge 32A of the table. This reduces the inertia of the upper end portion 40 of the lower table 32.

The intermediate portion 64 is determined is by being a condition for easier installation of the stop or stops, for example, the stops 44 and 46. She has a height greater than the height of 82.

The third part 86 includes a closed end 88 in the form of part of a circle, the radius of which is determined by the condition of reducing stress. The remaining section of the third portion 86 preferably is defined by two curved zones C1and C2that also helps to reduce stress.

Adjustment of the stops, that is, their ability to control the convergence of the edges of the slot at the expense of the initial gap and/or elastic deformation, especially suitable for cases when subject to bending of the sheet is located symmetrically relative to the Central plane of the press. In this case, the symmetric adjustment of the stops is the same way. When the sheet stack with a small deviation from the symmetric position, may be sufficient symmetric adjustment of the stops.

If the asymmetry is more significant, can be provided by differently adjusting the stops, which are located symmetrically relative to the Central plane. Another solution is that provide the same adjustment symmetric stops and provide a variety of moving the two ends of the sliding table, most often the top of the table. This result may be achieved through various management power cylinders V1and V2thus, the fact at the end of their turn receive different moving ends of the sliding table.

Of course, you may also combine different initial adjustment symmetric stops and the movements of the two ends of the sliding table.

Next will be described the solution in figure 10. In this drawing, the elements similar to elements in the previous drawings are denoted by the same items plus 100. The lower table 132 contains two slots, respectively, 134 and 136, are located symmetrically relative to the Central plane R R press.

The outer lateral ends 134a and a slots 134 and 136 are opened.

In the drawing it is seen that the adjusting elements 180 are located in the slots 134 and 136. As an example, each of the adjusting element can be formed by a wedge. As described in the previous example, run on Fig, the adjusting element can be formed, on the one hand and the top of the unit, installed at the top of the slots and adjustable in the lateral direction at the bottom of the table 132, and, on the other hand, lower block, installed in the lower part of the slots and adjustable in the lateral direction in the table. In addition, as in previous examples, the upper and lower blocks may have inclined contact surface. As mentioned, by adjusting the transverse position of contact between the inclined surfaces of the upper and lower units, it is possible to provide adjustment so that% the CoE flexible bending the top of the table 132 follows the convex curved top table 130 due to the definition of the gap between the inclined surfaces and the upper and lower blocks and/or level of compression in the vertical direction.

It should be understood that the adjusting elements 180 may have a different configuration than described. This also applies to all combinations defined by the upper and lower wedge elements.

In the drawing it is seen that each slot 134 and 136 contains the first part, respectively a and a, and the second part, respectively, 135b and 137b. In each slot, the second portion 135b and 137b is located on the inner side (the one closest to the mid-plane R R press) in relation to the first part of the slot. In each slot, the second part is connected with the first part. More precisely, each of the first portion of the slot, respectively a and a, connected to its inner end, respectively, 135 a and 137 a, with the second part of the slot, respectively 135b and 137b. As seen in the drawing, the vertical distance D1between the inner end 135 a and 137 a the first part of the slot and fastening tools 132A table 132 more vertical distances D2between it and the inner end 135'b and 137'b of the second part of the slot.

In the drawing it is seen that the first and second parts of the slots are inclined to each other.

More precisely, the first part of the slot, respectively a and a has a General horizontal direction, and the second part of the slot, respectively 135b and 137b, is oblique to the bracket 132A tools. In the example, perform the second part 135b and 137b of the PoWPA and has the shape of a straight part, passing under an angle α of about 45° to the horizontal direction of the first part of the slot. The angle α may be different within, for example, from 10° to 60°.

The above-mentioned adjusting elements 180 are located in the first part of the slot, respectively a and a.

Next will be described the solution 11. In this drawing, the elements corresponding to the elements of figure 10, are denoted by the same items plus 100. A bending press according to 11 differs from the press in figure 10 a slightly different form of the slots 234 and 236. Here the first part a and a each of the slots 234 and 236 contains a plot, respectively s and s having a common horizontal direction and connected to its inner end 235 a and 237 a with the second part of the slot, respectively, 235b and 237b. In addition to this section of the General horizontal direction of the first portion of each slot contains an outer section, respectively a and a. This outer section is tilted toward the fastening a instruments relative to the previous mentioned site, respectively s and s. In this case, the slits are made in the lower table, and the outer parts of the slots are climbing up as the distance from the second parts of the slots.

In the drawing it is seen that the elements 280 jamming are located in areas C and s the first parts of the slots having a common horizontal direction.

As seen in the drawing, measured vertically, the width E of each slot varies depending on the area of the slot in which the width is measured. In this regard, it will be described in more detail slot 234. At least one of the parts a and 235b of the slot has a width that varies depending on the area of the slot in which the width is measured. In this example, the width E of the minimum and essentially constant at the site s first part a slots having a common horizontal direction. In contrast, the width varies quite significantly as in the outer area a and second portion 235b of the slot. In this case, it is seen that the width E is uniformly increased in the outer area a as the distance outward from the plot s. In this example, perform the upper and lower edges, respectively s and 234d of the slots 234 are in the outer area a the form of angled non-parallel planar faces, radiating outward.

In the same way, the second part 235b of the slot has at least one portion extending in a direction away from the first part a slots. In the drawing it is seen that the width E is greater than on the side of the inner end of this second part 235b of the slot than at its outer end corresponding to the inner end 235 a first part a slots. In the upper edge of s and lower cu the MCA 234d slots 234 are in this second part 235b slits form of angled non-parallel planar faces, diverging in the direction towards the mid-plane R R press, until the inner end e, which has the shape of the balloon.

Needless to say that the slot 236 symmetric slits 234 relative to the Central plane R R press.

In the embodiment of Fig slot 334 may have a shape slightly different from the shape of the slot 234. In the example shown the first part a slot 334 is similar to the first part a slots 234. The second part 335b of the slot has a shape very close to the form of the second part 235b, except that in this second part 335b slotted top edge s and bottom hem 334d have a curved shape with the concavity facing the fastening tools. Thus, in General the second part 335b of the slot has a curved shape and facing concavity to the fastening tools. Width E in the slot 334 may vary as well as in the slot 334. It should be noted that the outer section a slots may be as shown in the drawing, or may be absent. In this case, the first part a slots will have a General horizontal direction, such as plot s on Fig. This means that this site continues straight outward (to the left in Fig) like the first part a in figure 10.

In the embodiment of Fig slot 434 has a slightly modified form. The first part 435a slots similar is but the first part a slots. However, it can also have a General horizontal direction, such as plot s. In contrast, the second part 435b slot has the shape of a staircase rising to the fastening tools as it approaches the inner end of e, in this case, the shape of the balloon. In forming the ladder part of the measured vertical width E between the horizontal sides forming the rungs of a ladder, can be essentially constant or slightly increase as it approaches the inner end of a.

Presented at Fig slot 534 has the following slightly modified form. In this case, the first part a slits formed one section essentially horizontal direction. However, this first part is the outer area of the slot, similar to the outer area 435d on Fig. The second part 535b slot has a widening shape (in the General shape of a truncated cone) with extension to the inner end section with a rounded end e. The shape of a truncated cone can have essentially rectilinear generatrix, as Fig or a curved generatrix. Thus, the upper edge of the second part of the slot approaches the fastening of the instruments relative to the upper edge of the first portion of the slot.

It should be understood that Fig, 13 and 14 shows only one slot, with the corresponding slots 234 in 11. It is clear that the other slot is symmetric shown relative to the Central plane R R press. Describes the shape of the cross sections are sections in the vertical plane, which remain constant in vertical planes parallel to the plane of the drawings. In these examples, elements of jamming, similar elements 280 are in the first part of the slot.

On Fig shows a more traditional bending press, which was used for comparative tests in comparison with the press on 11. On Fig used the same position as in figure 2, plus 600. In the drawing, the slots 634 and 636 bottom of the table 632 is made inclined in the direction of removal from the mounting tools as they move to the inner ends directed toward the mid-plane R R press. The angle of the slots is of the order of 15°, length And tables is the same as figure 11, and a distance between the inner ends of the slots 634 and 636 is equal to the distance between the inner ends 235 a and 237 a first parts a and a by 11.

Tests were carried out on the stainless steel sheets with thickness of 12 mm Tools bending press (matrix) were the same.

On figa-16D shows the results of comparative tests conducted on the bending press RA Fig (figa and 16B) and the bending press PI at 11 (figs and 16D). For testing we used the sheets W W what Reena L, measured horizontally in the plane of the drawings. This width L is less than the distance between the inner ends of the slots 234 and 236 press PI on 11. These sheets were subjected to bending by 90°.

In all trials, reflected on figa-16D on figa-21D, the leaves were placed symmetrically relative to the Central plane R R press. For curves on figv and 16D on the x-axis indicates the length of the top or bottom of the table in millimeters, and the grade 0 corresponds to the position of the mid-plane R R press. Y-axis presents the curve of the table, measured in millimeters. The peak of the convex curve is the highest measured value.

Curve LT shows the curve of the bottom of the table, respectively, 632 press RA (pigv) and 232 to press PI (fig.16D). Curve UT shows the curve of the top of the table, respectively, 630 to press RA and 230 to press PI. On figv and 16D curve SA shows the deviation between the curve of the upper table and lower table.

In these drawings it is seen that during bending of the sheet W, the width L is smaller than the distance between the inner ends of the slots bending press PI, there is no significant difference between the bending press RA and bending pressure PI.

Figa-17D correspond figa-16D, and flexible in this case was made for the sheet width W 2L equal to C<2L<b. Recall that b is the distance between the inner ends of the slots, press the RA. When is the alignment figv and 17D shows when the bending of the sheets so the width of the upper table has a tendency to take a concave shape, as it shows the curve UT. In contrast figv to press the RA shows that the lower table has virtually no tendency to follow this curve, as shown by the curve LT, very close to this curve figv. As a result, in this case, the bending press is represented by the curve SA divergence of the curves between the upper and lower tables is significant. In contrast to fig.17D seen that due to the specific configuration of the slots bending press PI bottom style tends better to follow the concave curve of the top of the table, as it shows the curve LT bending the bottom of the table. Thus, in this case the divergence of the curve, represented by the curve SA, is much smaller than the differences in Fig Century

Figa-18D shows the same test for the sheet width W 3L equal to 3L>B. In this case, the lower table of the press RA still not repeats concave bend the top of the table, as is shown in the curves LT bending the bottom of the table and UT bend the top of the table on figv. Accordingly, represented by the curve SA divergence of the curves are great. Opposite the lower table bending press PI better follows the curve of the top of the table, as is shown in the curves LT and UT on fig.18D. Accordingly, the divergence of the curves shown in e is th curve chart SA, very slim.

Figa-19D shows the same tests for leaf widths 4L. On FIGU shows that, starting with this width, the lower table of the press RA then be bent slightly, as shown by the curve LT. However, it is slight, and the divergence of the curves presented on FIGU curve SA, remain significant. In another case in the chart on fig.19D where you can see that the bottom-style bending press PI is much better follows the curve of the top of the table.

Fig shows the same tests for leaf widths 5L. You can see that at this time the lower table of the press RA better follows the curve of the top of the table. Curve LT on FIGU closer to the curve UT, but the curve SA shows that the divergence of the curves remains quite large. On fig.20D curves LT and UT are closer to each other, so that the curve SA, representing the divergence of the curves for the press P1 is far more gently sloping or flat.

The behavior of the two presses a few more similar when bending a sheet width 6L, as shown figa-21D.

Comparative tests allow us to understand that the characteristics of flexible sheet metal wide wide range is much smoother when running it on the bending press in accordance with the invention, in particular, in press 11. Flexible performed with higher accuracy in relation to whether the Anesti of the obtained curve. In other words, the bending angle is almost the same across the entire width of the sheet during bending press according to the invention.

In relation to bending presses on 11 it should be noted that the increase in the width of the slots in their outer parts has the consequence that the side ends of the bottom of the table deform easier. The angle of the outer parts of the slots preferably is of the order of 15°, and may be, for example, from 10° to 20° to the horizontal direction. The choice of the angle depends, in particular, the shape and/or size of tables and/or tolerances on the deformation provided with slots table and/or the desired accuracy of flexible products. In the presence of the slots of this form, the distance between the slot and fastening tools, the most great in the field essentially horizontal section of the first part of the slot. Thus, in horizontal section, the rigidity of the bottom of the table larger than its stiffness in other parts of the slot.

In a broad sense a bending press in accordance with the invention is designed so that the stiffness provided with slots table in the area of these slots corresponding to the first part of the slot (at least, in the field essentially horizontal section of the first part), than in the area that corresponds to the second part of the slot. The presence of elements 180 and 280 Zack is inania, calculated positioned in the first part of the slot, can further increase this rigidity.

It should be noted that the first part of the slots may be of a slightly inclined or undulating form. In any case, these forms are chosen such that the first part gave the corresponding field of the table greater rigidity compared to the area of the table corresponding to the second portions of the slots. The length of the second portion of the slot, measured perpendicularly to the Central plane R R press, is preferably from about one third to one half of the total length of the slot. The choice of this length depends, in particular, the shape and/or size of tables and/or tolerances on the deformation provided with slots table and/or the desired accuracy of flexible products. It is clear that by defining the shape of the slots, and their length and a suitable choice of the elements of jamming and their positions can be achieved that the difference in height between a peak of a convex curve up in the middle of the bottom of the table and bend the side ends of the bottom of the table remained within pre-defined tolerances. It's really like to be more flexible sheets of a width essentially equal to the length of the top or bottom of the table for sheets whose width is less than this length.

It should be noted that the bending prescho figure 10-14 length between the inner ends of the slots may have the same value, as the length defined in the description of figure 2.

1. A bending press for bending sheet metal comprising upper table and the lower edge of which shall be the first bending tools, and the lower table, the upper edge of which bears the second bending tools, and these two tables are movable relative to each other to transfer forces to the flexible sheet metal, while the press has a vertical middle plane, one of the tables provided throughout its thickness two slots arranged symmetrically relative to the specified mid-plane, and each slot has a first open end facing the side edge of the table, and the closed end and the closed end define a section of the table without slots having a specified length, characterized in that it additionally contains an even number of lugs, each of which is located in one of the slots at a fixed distance from the closed end, while the supports are placed symmetrically relative to the specified mid-plane and has a predetermined coefficient of elasticity, and each stop provides in the area of the slot in which it is located, the ability of the regulated between the two edges of the slot under the action of the load applied to are provided with slots table, which is set, at least one of the two parameters, vkljuchajuwih the gap, originally defined this way into the slits in the absence of the applied load and the elastic deformation of this emphasis, the possibility of convergence created by the fence, closer to the closed end, less than one that is created by any fence, closer to the open end, and the possibilities of convergence of the edges of the slot corresponding to the above stops and their position in the slots, is defined so that at the end of the application of force to the flexible movable table to another table through the sheet metal of the line of curvature of the edges of the tables were essentially parallel to each other.

2. A bending press according to claim 1, characterized in that the length of the table without slots are set so that the area of the table between the closed ends of the slots was able to absorb a voltage essentially equal to the maximum voltage applied during the flexible sheet, without having to cause plastic deformation are provided with slots table.

3. A bending press according to claim 1, characterized in that the length of the table without slots between the ends of the slits is less than 35% of the length provided with slots table.

4. A bending press according to claim 1, characterized in that the length of the table without slots equal to about 80% of the length centered on the press sheet, for which the curve deformation under the action of the sliding table is essentially nathnac is positive.

5. A bending press according to claim 1, characterized in that the length of the table without slots essentially equal to 20%±15%, preferably 20%±5% length are provided with slots table.

6. A bending press according to claim 1, characterized in that the power supplied to the rolling table, attached to its two ends so that the two ends are provided the same travel length, and two symmetric emphasis provide the same opportunity adjustable convergence.

7. A bending press according to claim 1, characterized in that the power supplied to the rolling table, attached to its two ends so that the two ends is provided by different travel length, and two symmetric emphasis provide the same opportunity adjustable convergence.

8. A bending press according to claim 1, characterized in that two symmetric emphasis provides a different opportunity adjustable convergence.

9. A bending press according to claim 1, characterized in that it contains four stops.

10. A bending press according to claim 1, characterized in that the stops define managed the gaps.

11. A bending press according to claim 10, characterized in that each stop includes a first wedge having a first end rigidly connected to the first edge of the slot, and a second end forming a first inclined plane relative to the direction of the slot, and a second wedge having a first end connected to the first with the second edge of the slot, but movable relative to the edges of the slot along its direction, and the second end forming an inclined plane that is parallel to the first inclined plane, and between these planes there is a gap in the absence of attached to the table load, which by moving the second wedge can adjust the gap between the two wedges in the absence of a load applied to are provided with slots table.

12. A bending press according to claim 1, characterized in that at least one of the lugs defines a gap equal to zero.

13. A bending press according to claim 1, characterized in that the stops determine the gap size less than 1 mm, preferably less than 0.3 mm

14. A bending press comprising upper table, equipped with a mount for the top of the instruments, and the lower table is equipped with a mount for the lower instruments, and these two tables are located opposite each other in the vertical direction, one of the tables made movable relative the other in a vertical direction, one of the tables provided with slots arranged symmetrically relative to the Central plane, each slot has an open outer end, wherein each of the slots has a first portion of the slot and the second slot, which is located on the inner side relative to the first part of the slot and connect the and with it, the shape of these parts of the slots is such that the rigidity of the table, located between the slot and the fastening tool, more between the first part of the slot and the fastening tool, than between the second part of the slot and the fastening tool, and the first part of the slot is at least one element of the adjustment of the bending table.

15. A bending press according to 14, characterized in that the vertical distance between the inner end of the first part of the slot to which it is connected with the second part of the slot, and fastening tools for greater vertical distance between the inner end of the second part of the slot and the fastening tool.

16. A bending press according to 14, characterized in that the first and second parts of the slots are tilted with respect to each other.

17. A bending press according to item 16, wherein the first portion of the slot includes at least one portion having a generally horizontal direction, and at least the inner end of the second part of the slot opposite the first side of the slot is oriented toward the fastening tool.

18. A bending press according to 17, characterized in that the second part of the slot is held inclined to the fastening tool.

19. A bending press according to 14, characterized in that the second part of the slot has kivalina the second form, the concavity of which is directed to the fastening tool.

20. A bending press according to 14, characterized in that the second part of the slot has the shape of a ladder.

21. A bending press according to 14, characterized in that the first part of the slot has a generally horizontal direction, and the inner end of the second part of the slot is oriented essentially horizontally to the vertical middle plane of the table.

22. A bending press according to 14, characterized in that the second part of the slot includes at least one portion extending in a direction away from the first part of the slot.

23. A bending press according to 14, characterized in that the first part of the slot includes an outer section of the slot is made inclined in such a way that approaches the fastening tool with respect to the inner section of the first part of the slot.

24. A bending press according to 14, characterized in that at least one of the parts of the slots has a width, measured in the vertical direction, which varies depending on the area of this part of the slot in which the width is measured.

25. A bending press according to 14, characterized in that the inner ends of the first parts of the slots are located so that during bending of sheet metal whose width essentially equal to the length of the top or bottom of the table, the difference in height between the peak of vypuklogo is bending up the middle of the bottom of the table and two side ends of the lower table remains within a predefined tolerance.

26. A bending press according to 14, characterized in that the inner ends of the second parts of the slots are located so that during bending of sheet metal, is placed in the middle of the table length, width less than the length of the top or bottom of the table, the difference in height between the peak of the convex bending up the lower mid-table and lower part of the table in contact with the side edges of the sheet metal remains within a predefined tolerance.



 

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4 dwg

FIELD: metallurgy.

SUBSTANCE: tool holder is designed for bending tool having two surfaces of fixture and receiving groove with upper rim. A clamping case with the first clamping surface is designed for interaction with one of the surfaces of the tool fixture. A clamping strap serves for pressing the tool and is installed to perform pivot turning; this strap is equipped with the second clamping surface. The strap can be in the first position corresponding to clamping of the tool, and in the second position corresponding to fixing/removal of the tool. There is also a holding element with variety of plates parallel to each other and arranged in the same plane. Each plate of the holding element has two spring deformed sections and at least one bent part. One spring deformed section is directed up and has an end designed for entry into the receiving groove of the bending tool, and it also has the part designed for interaction with a lower rim of the receiving groove at the tool turn.

EFFECT: extended technological capabilities.

10 cl, 5 dwg

FIELD: metallurgy; deformation of metals.

SUBSTANCE: tool holder contains a clamping base with the first clamping surface intended for the interaction with one of the parallel surfaces of the tool, and a clamping pad for clamping the tool, installed so that it may be rotated on a hinge and having the second clamping surface. The said pad is designed so that it may take the first position corresponding to tool clamping, in which the parallel surfaces of the tool are clamped between the first and second clamping surfaces, and the second position corresponding to the tool installation/removal, in which its clamping surface is withdrawn from the first clamping surface. The device also contains a holding element with multiple elastically deformed plates parallel to one another and installed in the same plane. Each plate has the first end rigidly connected to a crossbar, an intermediate part, which abuts the first parallel surface of the tool in the free state, and the second end having at least the first part bent at an angle towards the tool relative to the intermediate part, and the second part bent at an angle in the opposite direction so that the said parts bent at an angle may be held elastically in the receiving groove of the tool when the said plate is in the free state; in the tool installation/removal position of the said pad, the intermediate part of the plate may be elastically deformed for the installation of the said elastically deformed plate parts bent at an angle into the receiving groove and their removal from the groove.

EFFECT: increase in efficiency; simplification of design.

5 cl, 5 dwg

FIELD: plastic working of metals, namely manufacture of parts from shapes.

SUBSTANCE: method comprises steps of applying bending loads at predetermined force or camber of blank for one or several transitions along surface area of blank by means of rotation-local deforming along curvature lines by means of pressing moving roller on extensible bearing units mounted in such a way that to provide different spacing between said bearing units depending upon curvature radius of part. Shaping is realized at minimization of contact spot of upper pressing roller and blank due to lowered diameter of roller and its curvature radius in cross direction. Method is realized by means of machine tool whose upper deforming member is in the form of mounted in rod power drive of roller. Lower deforming member of machine tool is in the form of two extensible sections mounted with possibility of engaging with upper deforming roller. Machine tool is provided with manipulators for supporting worked blank.

EFFECT: modified design of machine tool, reduced power consumption.

10 cl, 4 dwg, 1 tbl, 1 ex

Sheet bending press // 2269391

FIELD: plastic working of metals, in particular, sheet bending equipment.

SUBSTANCE: press has bed, die, punch mounted on traverse for reciprocation in guides by means of two columns, drive formed as cylinder whose stem is connected with two levers, each of said levers being connected through shackle with column. Traverse rotates relative to one of columns. Other column is equipped with retainer for attachment of rotary traverse. Press is further equipped with carriage having rollers arranged in parallel with and moving relative to traverse.

EFFECT: wider operational capabilities.

2 cl, 4 dwg

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