RU2251464C2 - Shaping apparatus - Google Patents

Abstract

FIELD: plastic working of metals, possibly manufacture of double-curvature articles in creep mode.

SUBSTANCE: apparatus includes shaping chamber with working organs forming single-row modules; hydraulic drives; units for providing differential degree of said drives; normalizing devices. The last include screw gages with step motors mounted in single-row modules of working organs. Communication circuits of hydraulic drive include phase mains of power hydraulic cylinders, phase mains of return hydraulic cylinders and mains for communicating four-phase systems with pressure and drainage source. Constant-pressure main lines and phase main lines are mutually communicated through hydraulic distributors and other aggregates of hydraulic systems.

EFFECT: enhanced reliability of controlling, simplified program control, enlarged assortment of shaped products.

5 cl, 19 dwg

Description

The present invention relates to the formation of gentle shells in the aircraft industry, space technology, shipbuilding, as well as in pilot production in these industries.

The molding of products from sheets and panels, which allows you to change the shape of the workpiece, without changing the device itself, but only setting the position of the forming bodies, is known and is done on pin tooling.

The molding devices, including the pin tooling, contain spaced bases connected at the periphery by walls that hold the bases from spacer forces during material deformation, and the pin tool itself, which consists of working bodies and their drives located outside the molding chamber.

Each working body consists of two deforming rods located coaxially and installed with the possibility of their movement into the molding chamber. The rods are moved by linear motors, one of which is positional, and the other differential. Positional motors are configured to define the surface shape of the material to be processed by the rods, differential motors are configured to press the workpiece with the rods to the shape specified by the positions of the opposing rods.

On equipment with constant interaction between the forming rods and the sheet material, the rods experience significant lateral forces, which lead to deviations of the ends of the rods. To reduce bending, the rods are made with large sections, and the workpiece in the clamped state under load moves when it changes from a flat to curved state, while scratching and permanent corrugations with breaks in the workpiece can occur at the touch points, or the working tool rods experience irreversible bending.

This drawback is deprived of the pin equipment contained in the shaping device according to the patent of the Russian Federation No. 2216421 B 21 D 11/20 [1].

On this equipment, the sheet material is clamped between the ends of the working body rods periodically; therefore, the deviations of the ends of the rods from the axis of the working body are controllable, insignificant, lie within the elasticity range and are a function of the clamping period τ and axial displacement Δz for the clamping period: ε = ε (τ, Δz), where ε is the deviation of the end of the rod from the axis of the working body.

All varieties of positional and differential engines considered in [1] have a movable inner part enclosed in a fixed housing. At the same time, the immobile link contains elements protruding beyond the boundaries of the fixed housing, which does not allow the forming rods to be fixed directly to the output links of the drive; the rods only rely on the links, and to ensure resistance to lateral deviations, the rod has two separate, independent of the drive, spaced bearings, relative to which it has the possibility of axial movement.

This disadvantage is deprived of the snap in the proposed molding device. The density of the working bodies is achieved by using a small section of hydraulic cylinders with a movable housing, on which the forming rod is rigidly fixed. The assembly, consisting of a movable housing and a forming rod on it, rests on the rod with a sealing assembly between the housing and the rod, and the second support is the hole for the rod to enter the molding chamber. This allows the supports of the movable part to be separated by an amount greater than the stroke of the hydraulic cylinder, and thereby reduce the deviation of the angular swing of the movable part. Acceptable deviations of the parallelism of the axes of the output links are achieved not by increased accuracy of machining the holes and parts placed in the holes, but only by spacing the supports over a sufficient distance.

In the proposed device for saving hydropower, it is proposed to use an aggregate that allows applying a pressure p ₀ lower than that acting in the power hydraulic cylinders of the working body during forming moves. This measure, with the number of working bodies of the order of a thousand or more, is justified, because from the position of the positional hydraulic motor, the displacement consists of two components: idle displacement and deformation displacement; given that the components are approximately equal, the saving of hydropower is substantial.

In the proposed device, respectively, the use of hydraulic cylinders with a movable housing, the corresponding design of a controlled travel limiter is proposed. The limiter and its drive are made coaxial to the working body, and the cross section of the power elements of the working body is less than the cross section of the drive of the limiter. This allows you to ensure high resolution of the system when specifying a pointwise skeleton of the moldable surface, but to use reliability, power elements in particular, a high density of working bodies per unit area, low cost of one-way hydraulic cylinders, both power and return hydraulic cylinders, cost-effectiveness of the device, as well as rigidity hydraulic systems under load, moderate hydraulic drive pressures, and wide controllability capabilities both in periodic modes and at constant pressures, are required and USAGE respective bases snap pin. These qualities turn out to be useless if the base flat surfaces of the bases of the pin snap are curved, much less bend under load.

Each of the bases represents a plate, flat from the side of the molding chamber, identical in plan to the plate of the opposite base. The plates are equally spaced from each other. In most known snap-ins, for technological reasons, base plates are fastened together by walls on both sides. This allows the design stiffnesses of base plates to be defined as the stiffnesses of beams.

пролетом L между стенками, удерживающими основания от распора, и параметром жесткости q₁=bh²/L³, где b - ширина плиты, h - толщина ее.Assuming that the drives of the working bodies load the plate more or less evenly, the deflection of the base is determined by the load

the span L between the walls that hold the base from the spread, and the rigidity parameter q ₁ = bh ² / L ³ , where b is the width of the plate, h is its thickness.

In some equipment, the base is made of a separate plate. The dimensions of the device are determined by the size of the forgings or rolled thick-walled sheet and the possibilities of its processing.

The demand for products whose areas exceed the dimensions of a solid base plate with a given stiffness parameter q ₁ = bh ² / L ³ force in the implementation of forming devices of this type to produce both bases and walls prefabricated [3].

It is possible to assemble the base with a large error, and then joint processing of the base assembly. But in this case, the dimensions are limited by the capabilities of the processing equipment.

The principle of processing in parts with a small error has wider possibilities, and then the parts are assembled with the necessary accuracy. An attractive embodiment of the forming device for the manufacture of large-area products is the principle of modularity, which is a special case of the principle of assembly.

In the device [1] it is proposed that the phase subgroup be made of two single-row blocks connected at the edges by screeds. Such a module allows assembly into a device of arbitrary length, however, achieving an identical arrangement of actuators, connecting modules to each other, measures to form bases with the necessary flatness are not considered in [1].

As applied to hydraulic cylinders with a movable housing and a forming rod fixed to the housing, in particular for positioning blocks, achievement of the required module stiffness is achieved due to the component h ² in the parameter q ₁ = bh ² / L ³ . During the stroke of the hydraulic cylinder l, the height of the positioning block h> 3l, because includes a rotor group, the thickness of the shelves of a multi-shelf beam, the size of the screw pair l ₁ > l and the size of the power hydraulic cylinder with a rod l ₂ > 2l.

The accuracy of setting the displacements Δz _{ij of the} forming rods by the output links of the positioning drive is unclaimed if the positioning, as well as differential drives and forming rods on them are not accurately set relative to the centers (x _ij , y _ij ) of the exit of the forming rods to the forming chamber. But even with satisfactory accuracy of the location of the centers (x _ij , y _ij ), setting the point (x _ij , y _ij , z _ij ) on the formed surface may turn out to be unsatisfactory if the axes of the output links and the rods on them have significant deviations from the geometric axes of the working bodies, and the axes of adjacent working bodies are not parallel. This entails inaccuracies ε _x , ε _y , ε _z , and instead of specifying a point (x _ij , y _ij , z _ij ), another point will actually be set (x _ij + ε _x , y _ij + ε _y , z _ij + ε _z ) .

The flatness, especially of the lower base, on which the positioning drives are located, should be quite perfect, since the side of the lower base, facing the molding chamber, is used as the zero plane when setting the movements

To achieve a technical result: the manufacture of large-area products with a high-relief relief with a wide selection of molding modes, both the modules themselves and their arrangement in the bases, and the connection of the bases with walls should have small errors, both linear and angular.

The identity of the modules in height h, in length L, as well as in the position of the drive output links and forming rods rigidly fixed to them, and small angular errors are achieved by using the frame structure as a fixed part in the form of a multiband beam, the shelves of which are stripes and the walls racks.

The material of the shelves can be a strip obtained by precision rolling directly, or the shelf can be made of a rolled sheet. The satisfactory accuracy of the shelves of rolled metal in thickness, and the accuracy of the racks in length, if they are turned, are supplemented by the principle of arranging the centers of the holes on the strip surface in the form of identical marking of the centers of the holes on all the shelves, and making holes on them while observing the perpendicularity of their axes to the flat surface shelves. These measures provide the required alignment with respect to the shelves of both movable elements and stationary.

The stability of this design is achieved by a double-row zigzag arrangement of racks relative to the shelves and the alignment of the racks on adjacent shelves. An exception is the edges of the shelves at the ends of the modules. The holes at the edges on each of the shelves are equally spaced from the ends. Structurally, the racks in the middle of the shelves and the extreme are different. Racks spaced from the ends of the shelves have a length equal to the distances between the shelves that they connect, and the coaxial racks on both sides of the shelf are fastened with pins passing through the through holes in the shelves and through holes with seats and threads in the racks. The racks at the ends of the modules are made through and hold the removable parts of the gap-free connection, with which the module is mounted on the power belt, fastening the modules to the base on one side and with the walls between the bases on the other. The size between the shelves in the area of the through posts is held by spacers.

The implementation of the bases of the modules containing single-row blocks of hydraulic cylinders and mounted on their movable bodies of the forming rods imposes certain requirements for the replacement of some modules with others, for example, during the repair or preventive replacement of connector seals and other parts. The modules are made with the possibility for each excavation and installation without disassembling the molding device.

Due to significant existing loads: bending on the bases and stretching on the walls, collapsible joints are made clearance-free in one or several directions. In the constructions of the fastening modules between the shelves, they are gapless along the z axis, and the fastening of the modules on the power belts and the fastening of the prefabricated walls between the bases are gapless in x, y, z.

The necessary accuracy in the installation of positioning modules for the formation of the base is achieved by performing power belts from a strip on which marks are located with sufficient accuracy, relative to which the fasteners of the modules are located. The installation error with respect to the mark does not accumulate, as is the case when connecting the modules, for example, with tie rods.

As module connections, self-aligning non-backlash cone-in-cone connections are used, providing high multiple installation accuracy.

Similarly, prefabricated walls between the bases are fixed on power belts. From the side of the molding chamber, the power belts are made in two rows: one row holds the removable parts of the module mounts, and the other row holds the removable parts of the prefabricated walls holding the bases.

At the same time, the rigidity of the system of working bodies and the rigidity of the bases on which the system of working bodies is located allow universal use when choosing deformation modes in the sense that both cold and heated deformation can be selected. With heated processing material, it is possible to use both faster modes of plastic deformation and slower ones in creep mode. Compared with the deformation modes on the known molding devices with constant pointwise clamping of the material, new possibilities arise associated with multiphase nature, for example, using not anticipatory deflections of the product, but anticipatory values of periodic curvature [3].

An important factor among the features of a large-area product molding device, difficult to reproduce the surface topography, and accurate reproduction is the controlled positional drive toward the differential drive, which ensures the smooth operation of the molding device even in the event of unauthorized stopping of some positional multi-position drive motors, with only a slight a decrease in the accuracy of the form in case of failure of a subset of the working bodies. It doesn’t matter if the device is used in periodic mode or in constant mode.

The listed beneficial effects that are not typical for known molding devices, and the design features of these devices that allow you to obtain these effects, not known in the used molding devices with pin snap-ins, suggest that the proposed solution does not have a prototype.

The device for forming shells with alternate contact of the working bodies and the regions of the moldable blank contains a forming chamber, working bodies, each of which is made in the form of two coaxially arranged rods, and has differential and positional hydraulic actuators located on opposite sides of the forming chamber, the working bodies are divided into phase groups and their displacement is controlled with control, and the phase groups are divided into subgroups, the positioning of one of the hydraulic drives of each rod is ensured by the presence of the differential hydraulic drive of the direct-flow regulation device, the differential hydraulic drive is made in the form of linear hydraulic motors, connected in parallel with the phase lines of the phase groups of the working bodies, each of the hydraulic motors consists of two power hydraulic cylinders with the opposite direction of the one-way strokes and a mechanical connection between their axially movable bodies, each power hydraulic cylinder contains a fixed rod and a movable housing with one sealing unit in the form of a movable radial support, while the forming rod is fixed to the housing of the power hydraulic cylinder, the fixed radial support of which is the entrance to the molding chamber; the return hydraulic cylinder is made in the form of a fixed step displacer and a movable housing consisting of two sealing units corresponding to the diameters of the step displacer, the power cylinders are connected to the phase line by means of an outlet with a shoulder located in the hollow rod and secured by a nut on the outside of the bottom, in which a hole for passing is provided the end of the branch, resting on the bottom from the inside with a shoulder, and with deforming strokes, each phase group from the side of the positional hydraulic actuators it is connected with a pressure source p ₁ , and from the side of the differential hydraulic drive, the differential motors of which make a forced return stroke, is connected with a pressure source p ₂ , while the cross-section of the rods S ₁ and S _{2 of the} corresponding power cylinders of each working body and the forces P ₁ and P ₂ satisfy the inequalities: P ₁ > P ₂ and (P ₁ -P ₂ ) <P ₂ , where P ₁ = p ₁ S ₁ , P ₂ = p ₂ S ₂ ; at idle strokes in the molding mode, the power hydraulic cylinders of the working bodies are connected with a pressure source p ₀ satisfying the inequality p ₀ << p ₂ , in the phases of rest the power hydraulic cylinders of the working bodies are connected with a drain, and their return devices, at least from the back pressure side, are communicated with a pressure source p ₀ , from the side of the form setting, each phase group of working bodies is connected with pressure sources p ₁ , p ₂ and by discharge through a constant pressure converter into a phase pulsating system containing a hydraulic distributor and at high costs and flat-valve control valves or servo control valves, valve boxes, each of which contains a sequential valve and a check valve, a group of stepper motors whose axes are connected to the axes of rotary control valves with a flat valve or with servo control valves, the latter are associated with phase highways through valve boxes that serve to fill the hydraulic drive during idling strokes from a source having lower pressure p _0, and for deforming x moves - from a source having a pressure p _1; the output of each servo action valve for high pressure p _{1 is} communicated with the inlet of the pressure sequential valve p ₀ and p ₁ , and the output of the servo action valve for low pressure p _{0 is} communicated with a check valve and through it with the main inlet of the pressure sequential valve p ₀ and p ₁ and its signal input; the output of the servo action valve along the drain and the output of the sequential pressure switch p ₀ and p _{1 are} connected to the phase line, while the outputs of the valve with a flat valve are connected with the valve at a high cost; during return strokes, the inputs of the rotary directional valves of the pressure transducer p ₀ to phase pulsating pressure are in communication with the pressure source p ₀ and out of phase outlet with outlets that are connected to the phase lines of the power cylinder return devices; from the counterpressure side, each phase group of working bodies is connected with sources of pulsating pressures p ₂ , p ₀ and a discharge at the inlets and with a constant pressure source p ₂ at the outlet through a phase pressure to pressure p ₂ converter containing valve spools with a flat spool or valve servo valves, valve boxes, each of which contains a sequential valve and a check valve, a group of stepper motors, the axes of which are connected with the axes of rotary directional control valves with a flat spool or with servo control valves, the latter are connected to the phase lines through valve boxes, which serve to fill the hydraulic drive at idle from the source with pressure p ₀ , and with deforming moves from the source with pressure p ₂ ; the output of each servo action valve for pressure p _{2 is} communicated with the inlet of the pressure sequential valve p ₀ and p ₂ , and the output of the servo action valve for pressure p _{0 is} communicated with a check valve and through it with the main valve inlet of the pressure sequential pressure p ₀ and p ₂ , it the signal input is communicated with the co-phase line from the side of the job form; the output of the servo action valve along the drain and the output of the sequential pressure switch p ₀ and p _{2 are} connected to the back pressure phase line, while the outputs of the flat spool valves are connected to the control valves at high costs, and each device for regulating the direct strokes of the power hydraulic cylinders contains screw pairs, coaxial with the power hydraulic cylinders, while each of the screws is connected to the axis of the stepper motor through the clutch of the limiting moment, each screw is located in two supports on its the ends, while the support on the side of the power hydraulic cylinder contains a radial bearing, and on the other hand, a fillet, on which there is a thrust bearing on the thread side of the screw pair, the nut of the screw pair is made with grooves on its outer surface to accommodate rods in them and is located between the rod power hydraulic cylinder and a movable stop connected by rods to the body of the hydraulic cylinder, while the screw nut of each working body in the phase of communication of the hydraulic power cylinders with a drain is shifted from the movable stop to the side th cylinder housing mounted for movement of its tasks, and in the measurement mode nut is displaced in the opposite direction in phase power cylinder communicating with the pump station. The following special cases of device execution are possible.

During hot stamping, the deforming rod and the case of the power hydraulic cylinder are fixed to each other by means of a collar on the rod and a threaded connection with a union nut on the case, with heat insulating rings located on both sides of the collar, and the ends of the rod and the cylinder body are separated by a ball or ball separator.

The device may include a constant-phase phase pressure converter from the power hydraulic cylinders with forced return, when molding is connected to the drain by two lines, one of which contains hydraulic resistance, while the line with hydraulic resistance, providing pressure p ₂ , contains a controlled valve, the outputs of which are communicated with two branches of the line, one of which is in communication with the hydraulic motor of the motor-pump group, the hydraulic resistance of which is made controlled by a given pressure s p ₂ at high flow rates, and its pump output is communicated by pressure p ₁ with a pressure source p ₁ from the side of the form setting, and the second branch contains a throttle device, the hydraulic resistance of which is controlled by the given pressure p ₂ at low flow rates.

In the device, each subgroup of working bodies can form a single-row module in the form of a frame, and consisting of two bases, each of which is made in the form of one hydraulic motor block or prefabricated, containing several blocks of the same phase fastened together, each module block contains a multiband beam, the shelves of which are fastened with racks and removable protective walls, and at its ends, on the side facing the molding chamber, are mounted clearance-free and self-governing mounts for mounting blocks in the plane of the base of the molding chamber in two directions and perpendicular to it when fixing the walls on the periphery of the forming area, on the opposite side of the ends of the block are also mounted these fasteners for attaching to the block of other blocks in two directions in a plane parallel to the base of the molding chamber, for each multi-shelf beam, from the side of the shape setting, the power hydraulic cylinders and screw pairs with their drives are installed coaxially, and the racks located between the shelves are at the top The principles of the zigzag drawn through the centers of the axes of the working bodies, the axis of symmetry of the stops and the centers of the guides for the nuts of the device for regulating the direct strokes of the power hydraulic cylinders are located in the opposite order on the said zigzag.

The screw pairs of the device for regulating the direct strokes of the power hydraulic cylinders can be installed with the possibility of moving according to the program, including the coordinates of the final and intermediate surfaces of the product, and the positions during manipulations specified by the numbers of the working bodies relative to the molding area and the marks on the axes of the working bodies relative to the workpiece plane, while the coordinates the intermediate surfaces of the product are determined by the flow rate and the frequency of the phase pressure system.

Figure 1 shows a diagram of the hydraulic communications of the power hydraulic cylinders from the side of the job form.

For each of the phase lines 1 of the power hydraulic cylinders 2, from the side of the shape setting, pressure and drain sources and the corresponding constant pressure lines 3 and 4, and drain 5 are communicated through the control valve 6 and two valves — a check valve 7 and a series valve 8 of two pressures: lower and higher. Lower pressure p ₀ and higher p ₁ come from the pumping station, providing the required pressure p ₀ and p ₁ at variable flow rates.

The sequential valve 8 according to a pressure signal from one hydraulic system (with pressure p ₀ ) to another hydraulic system (with pressure p ₁ ), as a result of which both systems communicate, is made with a control signal channel 9, which is in communication with a low pressure source p ₀ (See T.M. Bashta “Engineering Hydraulics”, a reference guide. - M.: Engineering, 1971, Sequential Valves, p. 427).

A typical design of such a valve includes a stepped plunger 10 with a shank 11, loaded from one end with a calibrated spring 12, and from the other with a signal pressure. A control valve 6 with a rotary valve and driven by a stepper motor 13, a check valve 7 and a series valve 8 of pressure p ₀ and p ₁ in the communication phase through the control valve 6 with pressure sources p ₀ and p ₁ perform the function of a single unit that controls automatically displacements of the power hydraulic cylinders from the side of the form setting in two modes: at low pressure p ₀ in idle mode and at high pressure and p ₁ in deformation mode.

In addition, a similar device, the unit is made both from the back pressure side, which is controlled through its hydraulic distributor 14 by the stepper motor 15, and through the signal pressure from the output of the sequential switching valve 8 on the shape setting side. If we take into account that stepper motors 13-15 on both sides of the phase group of working bodies work synchronously and in phase, then the whole set of electric drive on both sides and drive-controlled units connected by hydraulic signal coupling is a single aggregated system with control of the magnitude of movements of the working bodies by step according to the program and self-governing when filling power hydraulic cylinders from various pressure sources during idle and deforming movements of their stroke from valves, etc. led away by changing the pressure.

Figure 2 shows a diagram of hydraulic communications from the back pressure side.

For each of the phase lines 16 of the power hydraulic cylinders 17 from the counter-pressure side, pressure and drain sources and the corresponding constant pressure lines 18 and 19, and drain 20 are communicated through the control valve 21 and two valves — a non-return valve 22 and a series valve 23 of two pressures: lower and higher. Lower pressure p ₀ and higher p ₂ come: p ₀ - from the pumping station, p ₂ - is formed on the hydraulic resistance in the drain system.

The sequential valve 23 according to the pressure signal from one hydraulic system (phase system from the side of the form setting) to another hydraulic system (with pressure p ₂ ), as a result of which the system with pressure p ₀ and the system with pressure p ₂ communicate, is made with the channel 24 of the control signal , which is communicated with the phase line 1 from the side of the form.

Figure 3 shows a series valve.

The valve comprises a housing 25 in which a stepped plunger 10 is located, having a shank 11, two dividing fillets 26 and 27, and a neck 28 between the fillets.

The internal cavity of the housing 25 is divided by a stepped plunger 10 into five cavities. In the extreme cavities are located: on the side of the extreme separation fillet 27 - a calibrated spring 12, on the side of the shank 11 - the signal pressure cavity, adjacent to it - the cavity of the first separation fillet 26, is in communication with the atmosphere, then - the low pressure cavity p ₀ , in which neck 28, and with all possible movements of the plunger 10, the cavity by dividing fillets does not overlap, but can only communicate with the adjacent high-pressure cavity, then the high-pressure cavity, which is alternately cut off and by thallium cavity with low pressure and extreme - spring chamber 12 communicated with the atmosphere. The valve contains two inputs 29 and 30 and one output 31, as well as an input 32 for the signal pressure.

Figure 4 shows the valve.

The control valve is made on-off and contains three inputs on the body: 33, 34 and 35, and three outputs: 36, 37 and 38, as well as a drive from a stepper motor. The high and low pressure inlets and outlets with the rotary slide valve 39 are simultaneously open, with the inlet and outlet open at the drain, or simultaneously closed with the open inlet and outlet at the drain.

Figure 5 shows the combination of a two-way valve, check valve and sequential valve.

The combination allows you to sequentially use the source with a low pressure p ₀ , and then with a higher p ₁ or p ₂ , depending on where it is located, from the side of the form setting or from the back pressure side, while complying with displacement without load and with deformation movement.

On the side of the job form (see a) in figure 5) the valve 6 with a rotary valve 39 contains three input channels and three output. The input channels of the valve 6 are communicated, respectively, one 35 with a drain, the second 34 with a source of low pressure p ₀ and the third 33 with a source of higher pressure p ₁ .

The first output channel 38 is connected directly to the phase line 1. Two other output channels 37 and 36, simultaneously connected to the pressure sources p ₀ and p ₁ when the drain is closed, or simultaneously closed by the rotary slide valve 39 when the drain is open, respectively, the second 37 by low pressure p ₀ with a check valve 7 and through it with the first inlet 29 of the serial valve 8 and its channel 9 for supplying a signal pressure that controls the movements of its stepped plunger valve 10; the third output 38 of the rotary distributor 6 is in communication with the second inlet 30 of the series valve 8, through which it communicates with a pressure source p ₁ . The total output 31 of the series valve 8 is first lower pressure p ₀ and then higher p ₁ communicated with the phase line 1.

For the phase lines 16 of the power hydraulic cylinders 17 from the counter-pressure side (see c) in FIG. 5), each control valve 6 'with a rotary valve 39 also contains three input channels and three output channels. The inlet channels of the control valve 6 'are respectively communicated with one 35 with a drain, a second 34 with a low pressure source p ₀ and a third 33 with a higher pressure source p ₂ . The first output channel 38, communicated or cut off from the drain, communicates directly with the phase line 16. Two other channels 37 and 36, cutting off the pressure sources p ₀ and p ₂ when the drain is open or communicating with the valve box (in which the check valve 7 'is located and the sequential valve 8 ') when the drain is closed, the second 37 low pressure p _{0 is} connected respectively through the check valve 7', which passes fluid to the valve box with the first inlet 29 to the low pressure p ₀ sequential valve 8 ' And a second valve port 30 series connection 8 'a higher pressure p ₂ communicated with the third outlet 36 of the distributor 6' at the higher pressure p ₂ directly. The stepwise plunger spool 10 'of the sequential switching valve 8' from the back pressure side is controlled by the output pressure of the sequential switching valve of pressure 8 on the phase line 1 from the shape setting side. The output 31 of the serial valve 8 'pressure p ₀ and p ₂ communicated with the phase line 16 from the back pressure. Highways 1 and 16 of one phase group of working bodies from both the shape-setting side and the counter-pressure side are controlled by rotary switches 6 and 6 ', synchronously rotating step motors 13 and 15, configured to phase-open and close the channels 33, 34, 35 and 36, 37, 38 with flat spools 39.

Phase lines and their fluid flow control units from the side of the form setting and from the back pressure side are connected to various sources of higher pressure p ₁ and p ₂ satisfying the relations:

p ₁ > p ₂ and (p ₁ -p ₂ ) <p ₂ ,

and also differ in the control of valves 8 and 8 'of sequential switching of pressures p ₀ and p ₁ or p _2, respectively.

Figure 6 shows the positions of hydraulic units, allowing the use within the phase stroke of the pressure p ₀ and p ₁ with the movement of the power hydraulic cylinders 2 without load and during deformation.

In position I shows the position of the moving parts of the units when filling the hydraulic cylinders 2 with a liquid with a pressure p ₀ .

In position II - at the time of completion of filling.

In position III - when filling the hydraulic cylinder 2 with a liquid with a pressure p ₁ .

In position IV - the return of the plunger 10 in the valve 8 when communicating the phase line 1 with a drain.

Rotary directional control valves 6 and 6 'with flat spools 39 for alternately communicating the phase lines 1 from the side of the form setting with the sources p ₀ and p ₁ and the drain, and from the back pressure side of the lines 16 with the pressure sources p ₀ and p ₂ and the drain, can be applied only to a molding device specialized in small product sizes.

With increased molding areas and maximum strokes of the working bodies of the order of 1 m or more, the bore sections of constant pressure and phase highways significantly increase, and the moments of stepper motors become insufficient for the operation of rotary control valves.

More acceptable in this case is the scheme of control valves including a servo drive, and rotary control valves with a flat spool are single-positioned for alternately communicating outputs with a pressure source p ₀ and a drain. Alternating pressures p ₀ and discharge are signal pressures for servo-valves of large directional control valves made on-off, to drain and pressures p ₀ and p ₁ or p ₀ and p ₂ .

The alternate filling of the power hydraulic cylinders 2 and 17 from a source with a low pressure p ₀ and higher pressures p ₁ and p ₂ is supplemented by a forced tap of the power hydraulic cylinders 17 in the phases of communication with the discharge.

Note that the removal of the rods of the working bodies from the workpiece in the phases of rest allows you to get new technological capabilities that do not have a place when otherwise performing communications return hydraulic cylinders 40 from the back pressure. Firstly, the heat sink from the workpiece is significantly reduced during its formation. This is due to the fact that the rods of the working bodies after the force impact upon its termination are removed from the workpiece. Secondly, the limiting angles between the rods and the surface of the workpiece can be increased. This is due to the fact that it is difficult to bend the rods because of the short contact of the workpiece and the rod and return it to its original position by elastic forces. And thirdly, a new effect appears that consists in the fact that the workpiece can be manipulated by turning its areas to the position where the rods and the surface of the workpiece are located within the friction cone and the sliding of the rods relative to the workpiece becomes impossible, which allows deforming the workpiece in parts , get products with steeper surfaces of the largest slope. The displacement of the workpiece from its desired position during manipulation during molding is difficult due to the large number of contacting rods.

7 shows a diagram of the hydraulic communications of the return hydraulic cylinders from the back pressure side.

For phase lines 41 of return hydraulic cylinders 40, each rotary control valve 42 is made single-position. This allows you to alternately communicate with them highway 18 low pressure p ₀ and drain. The control valve 42 contains two inlets 43 and 44 and one outlet 45. One inlet 43 is connected with a drain, the second 44 with a pressure source p ₀ . The output 45 is in communication with the phase line 41 of the return cylinders 40. The control valve 42 comprises a flat rotary valve 46 and is driven by a stepper motor 47.

From the side of the job, the return cylinders 40 in most molding modes are connected with the drain, however, they can also work in phase with the hydraulic cylinders 40 from the back pressure side. In all molding modes, from the counter-pressure side, return hydraulic cylinders 40 are communicated in antiphase with respect to power hydraulic cylinders 17 with which they form functional pairs. The term “in antiphase” is understood in the sense that if the power hydraulic cylinder 17 is in communication with a drain, then at the same time the paired return hydraulic cylinder 40 is connected with a pressure source, and vice versa.

A feature of the rotary directional control valves 42 is their different opening of the passage sections in different modes. To ensure small displacements during the removal of power hydraulic cylinders 17, the costs through the phase lines 41 should be small, and when reinstalling the workpiece in a new position - large. In the latter case, the return cylinders 40 work in phase from the side of the job form and from the back pressure. Different costs are achieved by different opening of the flow sections of the control valves 42, and this in turn is achieved by turning the flat spool 46 at different angles in appropriate situations. Drive stepper motors 47 allows this.

On Fig shows a diagram of the hydraulic communications of the return cylinders from the side of the job form.

In its structure, it is identical to the scheme in Fig. 7, however, it is switched on to phase operation only in the mode of reinstalling the moldable workpiece to a new position, and in other modes, the return hydraulic cylinders are connected with a drain.

On the multi-shelf section of the base of the pin equipment between the shelves, one bordering the molding chamber and the other on which the hydraulic cylinders 2 are fixed, return cylinders 40 are used as racks.

To reduce the complexity of manufacturing and hydraulic cylinders 2, and hydraulic cylinders 40 are made one-sided.

Hydraulic motors of this type are capable of forcing the reverse stroke, therefore, for the implementation of reverse strokes equipped with return devices. As the return device of the hydraulic cylinder 2, a hydraulic cylinder 40 with a fixed step displacer and a movable housing, which is also capable of only one-way operation, is used. The function of forward and reverse strokes is carried out by using two hydraulic cylinders 2 and 40 with the opposite direction of one-way strokes. The fixed part of the return hydraulic cylinder 40 has a dual purpose and is used as a fixed element (stand) of the base. The dual use of the return device is a constructive advantage of the proposed solution.

In one embodiment of the multi-shelf base section, stepwise displacers of return hydraulic cylinders 40 are located next to the movable bodies of the power hydraulic cylinders 2.

In the proposed molding device, the projection of the working body in plan is placed within the cross section of the stepper motor 48. This is achieved by the coaxial arrangement of the regulatory device and the rest of the working body, as well as by the arrangement of the racks between the shelves at the vertices of the zigzag drawn through the centers of the axes of the working bodies. This allowed zigzag in the reverse order to place flat parts (movable stops 49) between the racks, as well as to provide access to regulatory mechanisms and other devices and parts of the working bodies.

Figure 9 shows the shelf section of the base of the pin snap. Power hydraulic cylinders 2 and return hydraulic cylinders 40 are used on the shelf, used here as racks between the shelves. On the movable bodies of the hydraulic cylinders 2, outside in the area of their seals, covering the fixed rods, shoulders 50 are made, on which stops 49 are supported, containing through holes 51, coaxial with holes 52 in the base shelf. The shelf of the base section of the pin equipment, on which the power cylinders 2 are fixed, is the thickest among the shelves of the section. The shelf is most loaded with working bodies, it contains the phase line 1 of the power hydraulic cylinders 2 and the phase lines 41 of the return hydraulic cylinders 40. The through holes 51 are used as fixed guides of the regulation device, are made combined, and their centers are symmetrical with respect to the center of the cylinder rod 2. In the holes 52 fluoroplastic tubes 53 are inserted, which are a continuation of the holes outside the shelf to have as large a base size as possible to avoid distortions and are connected x with them regulatory errors.

A feature of the regulatory device is the use of a rotary screw 54 and an immobile nut 55, which is kept from rotating together with the screw 54 by the movable guides 56, which additionally perform the power function of holding the stop 57 when it comes in contact with the nut 55 to stop the power cylinder 2, with the movable body of which it connected by link rods 56. The movable rails 56, the emphasis 49 on the housing of the hydraulic cylinder 2 and the emphasis 57 are fastened with threaded connections. The screw supports 54 are located at its ends, while one of the screw axes contains a fillet 58, on which a thrust bearing 59 is placed on the thread side, which is supported by a base that accepts tensile stresses arising when the movable stop 57, with which the nut 55 is held, is held the housing of the power hydraulic cylinder 2, communicated in this phase with the pumping station.

Figure 10 shows the details of the regulatory device. The device for setting the program for moving the nuts 55 is made in the form of a motor group consisting of stepper motors 48, the axes of which are connected to the screws 54 by the clutches of the torque limit 60. Each clutch 60 is equipped with a sensor 61 for stopping the screw 54 with the rotating motor 48. Each stepping motor 48 is equipped with a control device 62, which connects it to the power pulse generator 63, as well as to the limit torque sensor 61 and to a computer containing a program of address and control signals for switching the windings of the stepper motors 48.

11 shows a device for setting a program for moving nuts. The movement is transferred when it is repeated by the power drive to the workpiece through metal intermediate elements, loaded axially symmetrically applied loads, which cause them to stretch and compress with small deformations of the elements, while possible backlash constructive solutions are eliminated. The accuracy of the repetition by the power drives of the displacements does not significantly differ from the angles of rotation of the axes of the stepper motors 48 specified by the transducers.

In devices for hot forming, the deforming rods and bodies of the hydraulic cylinders 2 are fixed to each other through thermal insulators. The fastening comprises a collar 64 on the rod and a threaded connection with a union nut 65 on the cylinder body 2. The union nut 65 holds the collar 64 with thermally insulating rings 66 and 67 on both sides of the collar 64, and the end face of the rod and the end of the cylinder body 2 are separated by a ball 68 or ball separator in depending on load requirements. The heat transfer through the ball 68 is small due to the small area of the contacting surfaces.

On Fig shows the attachment point of the deforming rod and the housing of the power cylinder.

In hot molding, deterioration of accuracy is possible due to the different temperatures of individual rods and areas of the workpiece, but even in this case, the transferred displacements change insignificantly.

The mechanical communication of the regulatory device is a deforming rod, a mounting unit for the rod and the cylinder body 2, the cylinder body 2, the movable stop 49, the shoulder 50 on the cylinder body 2, the rod 56, the movable stop 57 and the screw section 54 between the bearing 59 and the nut 55, which holds the stop 57.

The backlash between the threads of the screw 54 and the nut 55 is eliminated by one-sided contact of the threads and during rotation of the screw 54, and when the nut 55 and the stop 57 come into contact with stopping the movement of the hydraulic cylinder housing 2. One-sided contact of the threads of the screw 54 and nut 55 is ensured by two-piece nut 55 connected by a spring 69. When mounting the nut 55 on the screw 54, the spring is wedged, and after installation, the proppants are removed. Spring 69, both parts of the nut are pulled together, and the part of the nut 55 in contact with the stop 57, touches the thread of the screw 54 on one side only in all operating modes of the screw pair.

On Fig shows a device that provides one-way touch of the threads of a screw pair in all modes of its operation. The accuracy of regulation can be affected by shock phenomena in hydraulic communications, but this factor is also eliminated by placing 2 compensators inside the cases of power hydraulic cylinders, for example, made in the form of a ring 70 made of a material whose volumetric compression module is smaller than the volumetric module of liquids used in technical hydraulics. A decrease in the rigidity of the liquid column in phase communication 1 can be achieved by a different nature by compensators, for example, springs, etc.

Of particular concern in the design of multi-shelf sections 71 is their identity. To achieve this goal, the shelves and racks are fastened to each other by a fastening unit, including a calibrated hole 72 in the rack, ending with a thread, a calibrated hole 73 in the shelf, and a threaded pin 74 containing a calibrated cylindrical part, and a thread section at one or both ends. The racks between the shelves in this case allow the execution of equal height, for example, grinding the ends of the entire package of racks, and the shelves allow equal thickness execution.

On Fig shows the fastening of the shelves of the multi-shelf section.

Here a) fastening the extreme shelves with bolts with a cylindrical calibrated part; c) fastening of shelves by racks on both sides of the shelf.

The fixing of the sections 71 to each other, as well as the fixing of the walls 75 along the periphery of the forming area, also affects the accuracy of the molding device to a lesser degree.

Two options for connecting sections and walls are possible.

One is a direct connection, the second is a connection to the frame. More developed is the connection of the sections with the frame, allowing replacement of the sections without disassembling their entirety.

On Fig shows a frame of strips and rods and the location on it of sections and walls.

The frame is made in accordance with the structure of the pin equipment and corresponds to two bases and a molding chamber between them. Outside the bases there are spaced strips 76 connected by rods 77 to each other, in a direction perpendicular to the surface of the strip 76. At the ends of the strips, rods 78 are located located in the plane of the strips.

In the area of the molding chamber, wider strips 79 are located, one edge of which is used to secure the multi-shelving sections 71, and the other to fix the walls 75.

The attachment points of the sections 71 on the strips 76 and 79 and the walls 75 on the strips 79 are made in accordance with ed. testimonial. USSR No. 1696762, class F 16 B 5/00 and contain detachable connections from covering 80 and covered by 81 sheet parts, with positioning locks 82 placed on two opposite sides of covered part 81, each of which contains a socket 83 located in adjacent edges, covering 80 and covered 81 parts.

The socket 83 is made in the form of a circular conical surface facing a large base to the outer surface of the parts 80 and 81. The geometric axis of the socket 83 is perpendicular to the plane of the sheet parts 80 and 81. The lock of the positioning lock 82 consists of a sleeve 84 and a washer 85 and a threaded connection.

The sleeve 84 has an outer conical surface mating with the surface of the socket 83. In the sleeve 84 and in the washer 85, axial holes are made for the bolt 86, which, using the nut 87, are used to position the parts 80 and 81 and fasten them by tightening the sleeve 84 and the washer 85 to stop conical surfaces of the socket 83 and the sleeve 84.

A detachable connection is shown in Fig. 16 and is made according to the method in accordance with ed. testimonial. USSR No. 1532729, class F 16 B 5/00.

With regard to the pin snap with frame construction and modular filling of the frame with multi-shelf sections 71 and removable walls 75, on strips 76 on one side thereof, and on strips 79 — protrusions 88 and depressions 89 are made on two sides, in which sheet parts 90 can be placed, fixed at the ends of the multi-shelf sections 71 and at the edges of the walls 75.

The sheet metal parts 90 protrude beyond the dimensions of the sections 71 so as to enable their installation and removal from the frame without dismantling the locks 82 in other sections.

On the edges of the protrusions 88 and parts 90, on both sides of each of the parts 90, positioning locks 82 are located.

17 shows strips 76 and 79 with parts 90 and locks 82 on both sides of each of the parts 90. Sockets 83 on the edges of the parts 88 and 90 are fixed by welding on both sides of the sheet parts and to prevent warping and other undesirable phenomena associated with welding, equipped with interchanges in the form of blind holes (drills) at the ends of the weld, made to a depth greater than the leg of the seam 1.5-2 times.

In the power relation, the bases are beams, and the partitioned walls at their ends are screeds. The efforts of the expansion of the beams by the working bodies during molding are closed on the screeds, and the beams themselves experience bending.

In the direction transverse to the surfaces of single-row modules, the power circuit is also closed and is a hollow box open at the ends, the bases of which are cylinder blocks fastened in both directions, and the walls of the molding chamber respectively.

The mechanical blocks of cylinders are fastened in both directions to two floors, and the fasteners 82 are located in two parallel spaced planes. Blocks without regulation are bonded in the same way.

The box-shaped system perceives reactions of the molded workpiece that occur in the direction transverse to the planes of the modules.

Compared with the known molding devices, the proposed device has a closed power circuit, which allows you to do without a base loaded with molding forces.

The advantages of the proposed device in comparison with the known include the possibility of forming a molding area for a given product.

The advantages of the proposed device include the dual use of hydraulic drive units: for its intended purpose and as elements of the power structure for the perception of molding loads. Blocks are used as beams, the stiffness of which is higher, the greater the height of the beam. With this in mind, the choice of the location of the power hydraulic cylinders 2 and 17 and the hydraulic return cylinders 40 is of particular importance in the specialization of the device. From the return device 40, insignificant efforts are required and the area of its working section is significantly smaller than the area of the working section of the power engine (2.17). The fixed part of the return device 40 is fixed at two extreme points and is used as a rack between the shelves of the hydraulic drive unit structure.

When the device is specialized in relatively small product sizes, the bending stiffness of the block is sufficient if the power hydraulic cylinders (2.17) and return cylinders 40 are located on the same shelf on one side of the block, i.e. next to distant geometric axes and direct contact of the moving bodies.

When specializing in devices for large areas of products and with increased loads on each of the working bodies, the coaxial arrangement of the power hydraulic cylinders (2.17) and hydraulic return cylinders 40, which in this case are connected by rods and are located on the various different shelves of the hydraulic drive unit, is preferable. This allows you to develop blocks in height and dispense with the development of their cross-sectional area, since otherwise the weight of the device and the consumption of materials for its manufacture will significantly increase.

In the proposed molding device from the side of the movable matrix, on the rods of which the surface shape of the deformable workpiece can be set, the increased pressure p ₁ enters the hydraulic system from the pressure source, the pump station. From the side of the movable punch, the rods of which counter-press on the workpiece and hold it during deformation, the increased pressure p _{2 is} obtained by the hydraulic resistance device in the drainage system, although it is also possible to use an independent source with pressure p ₂ .

The principle of the formation of back pressure p ₂ in the proposed device at different stages of deformation is different, although it boils down to the formation of constant pressure at the output of the mains from the side opposite to the shape setting corresponding to the hydraulic resistance value.

The difference in flow rates through the drain line dictates the differences in the formation of hydraulic resistance.

Among the working bodies of the order of 10 ³ and a larger line of constant pressure load motor-pumping group, which creates a back pressure p ₂ . However, the formation of backpressure in this way is achievable only at relatively high costs at the output of the phase lines of the power hydraulic cylinders from the backpressure side. When the product is kept in the relaxation mode, the displacements of the working bodies are either very small or absent, therefore, starting from a certain flow rate Q (p ₂ , t), the motor-pumping group is not able to provide the necessary hydraulic resistance (mainly due to overflows a hydraulic motor, and also due to unstable speed control at low flow rates) and the output line of constant pressure established by the control device, disconnecting the motor-pump group and comprising self-adjusting for a given pressure p ₂ etc. sselnoe device providing low flow rate Q (p _2, t) <a, where a - a certain threshold value. In addition, in series with the throttle device, a controlled valve with no overflow for shutting off the main line is located.

On Fig shows a diagram of the formation of backpressure of the motor-pumping group and the throttle device alternately in the respective modes.

The pressure line 19 p ₂ (see figure 2) contains a controlled gate valve 91 and branching into two lines 92 and 93, connected by a single-position switch 94. A controlled throttle 96 is installed on the line 93 and is connected to the drain tank. The line 94 contains a hydraulic motor 95 and a pump 96, combined by a common control to maintain pressure p ₂ in the line 93 and pressure p ₁ in the output line 98. The fluid from line 93 enters the inlet of pump 97 and from its outlet into the hydraulic system for specifying the shape. The drive control of the valve 91 and the on-off switch 94 from the computer program, and the actual drive is carried out by stepper motors. Throttle control 96 is similar. The pressure sensors 99 and 100 are equipped with transducers for moving the pressure measuring elements into electrical signals and are installed - a sensor 99 for measuring pressure p ₂ in the line 19, a sensor 100 for measuring pressure p ₁ in the line 98.

The advantage of the molding device over the known is the variety of modes of operation.

When the device is specialized in large-area products, it is preferable to work with the regulation of movements at intermediate stages by the liquid flow rate and the phase switching frequency, while the final form is regulated once by mechanical regulation devices (see Figs. 9, 10, 11, 12, 13) using stepper motors 48, prior to the start of the molding process itself, and the time for setting the displacements is not limited.

This allows you to set the final shape of the product by working off the stepper motors 48 according to a simplified scheme and use simpler controls than when setting the movements by the stepper motors 48 in alternating phases of the communication of the power motors (2.17) with a drain.

Unlike machines with constant contact of the working bodies and the workpiece and a one-time setting of the product shape by screw pairs [3], where the contact of the working bodies and the workpiece is unilateral for a long time, only from the side of the hydraulic cylinders, and the development of corrugation, and then a possible fracture of the material during an avalanche-like development the deformation process is not limited by anything, in the proposed device in the same mode, the workpiece is limited by the effects of the working bodies from its two sides.

In this mode, the amount of displacement regulating the intermediate forms of the workpiece is controlled by the flow rate Q (t) of the pumping station. The load on the working body from the side of the hydraulic cylinder 2 in communication with the pump station P ₁ = sp ₁ , after contacting it with the workpiece, is balanced by the load N + P ₂ , where P ₂ = sp ₂ is the back pressure and N is the workpiece reaction. With equal cross sections s of the drive displacers on both sides of the molding chamber, the condition of continuity of the fluid flow that flows into the working bodies and flows from them (on average) is fulfilled.

On Fig shows three areas that are affected by the i-th, j-th and k-th working bodies.

The deforming rods of the i-th organ touch the workpiece from its two sides. The deforming rod of the jth organ touches the workpiece only from the back pressure side, the second rod of the working body does not touch the surface of the workpiece.

The deforming rods of the k-th organ are in a situation where the touch is only from the side of the job form and there is no touch from the back pressure side.

The equilibrium condition of the ith region with bilateral contact

(P ₁ -P ₂ ) -N _i = 0, and, given that N _i = R _i + m _i a _i , where R _i is the deformation force of the region, m _i is the total mass of the i-th region and the moving parts i organ, and _i is the acceleration,

a _i = (P ₁ -P ₂ -R _i ) / m _i .

The accelerations a _j and a _k can be written similarly:

and _j = (P ₂ -R _j ) / m _j ,

a _k = (P ₁ -R _k ) / m _k .

The station, as well as the hydraulic resistance from the back pressure side, are configured so that at the entrance to the hydraulic system p ₁ > p ₂ , and at the output p ₁ <2p ₂ , i.e. (p ₁ -p ₂ ) <p ₂ .

These pressure ratios provide a mechanism for self-clearance of gaps, since the velocities of the regions of the ith, jth, and kth are proportional to the accelerations

V _i = t · a _i <V _j = t · a _j <V _k = t · a _k in accordance with the acting forces (P ₁ -P ₂ ), P ₂ and P ₁ , under the assumption that R _i = R _j = R _k and m _i = m _j = m _k . Here t is the time from the interval T (p ₁ ), where T (p ₀ ) + T (p ₁ ) = T ₀ is the time of the presence of pressures in the phase line.

If the case of touching the workpiece by the rods of the working body from two sides is typical for all deformation modes, the last two are rather hypothetical and illustrate the dynamic capabilities of the working bodies in these situations.

The fractional displacement is determined by the switching frequency of the phase lines and the flow rate Q (p ₁ , t).

A feature of such a molding process is the reduction in the number of moving working bodies as they are set by the end stop as a result of the exhaustion of the unformed part of the workpiece. In this case, the molding forces decrease, and for forming the remaining section, the working bodies of various phases are switched on in phase.

A molding mode is possible when the displacement values Δf _i for each inclusion of the working bodies are regulated by mechanical regulation devices. In this case, the station must maintain the flow rate Q (t) variable in automatic mode at a constant pressure p ₁ similarly to a source that absorbs the liquid flowing out of the hydraulic actuator, supporting pressure p ₂ at a variable flow rate, otherwise, if there is a lack of flow rate Q (t) movements by mechanical regulatory devices will not be repeated by the working bodies. Mixed mode of molding, when the movement specified by mechanical devices is not always repeated by the working bodies, also has its advantages, for example, if the workpiece is not calculated in advance with sufficient accuracy, or is more rigid than anticipated. In this case, the additional molding by the inclusion of working bodies in phase allows you to get the product in these conditions. With an excess of flow rate Q (t), the displacements will coincide with the given mechanical devices, but for shorter time intervals τ ^* <τ ₀ , τ ₀ is the time of connecting the phase line to the pressure source, which in this case will be greater than p ₁ , required for warping.

As for the control of mechanical regulation devices in the setting modes of all intermediate forms of the workpiece with an exact or with a mixed repetition of movements by working bodies, the stepper motors of the 48 phase group of working bodies in this mode during τ _{0 should} connect the phase group to the drain simultaneously, which in modern prior art control is feasible using multi-channel systems. The satisfactory accuracy of specifying the coordinates of the form and their force repetition by contacting only metallic or rigid elements of other materials with low coefficients of thermal expansion allows the use of working bodies for molding, including hot, and for measuring the actual shape of the workpiece by contact in heating zone.

In the program of one of the main molding modes, the intermediate and final surfaces of the workpiece are represented by marking systems relative to the plane. Marks are set along the axes of the working bodies. Each surface and each axis of the i-th working body is associated with a mark z _ik , where i is the number of the working body, k is the surface number at the k-th intermediate stage of molding. Surfaces are defined similarly to terrain on a geographical map.

Considering all previous coordinates, starting from the plane, they can be represented as the sum of increments of coordinates between each previous surface and the next

The implementation of the program is achieved by moving the nuts 55 along the screws 54 to the side of the movable stops 57 to the power cylinders 2 in the phases of communication of the working bodies with a drain, and then repeating these movements by the power cylinders 2 from the side of the form setting (see Fig. 10, 11).

такой, что Δz_ik<а. При включении i-го органа на силовое повторение заданного перемещения а деформирующий его стержень со стороны задания формы проходит некоторое фактическое перемещение

до упора в заготовку. Фактическое положение заготовки вдоль i-ой оси можно измерить отработкой гайки 55 назад, до упора ее в подвижный ограничитель 57. Пройденное гайкой 55 перемещение

назад и интересующее приращение координаты фактического положения заготовки равноMeasurement of the actual shape of the workpiece for any molding step of interest along the axis of the i-th working body is carried out by setting instead of the increment Δz _ik , which determines the surface mark at the k-th molding step, a certain mark

such that Δz _ik <a. When the i-th organ is turned on for the force repetition of a given displacement, its deforming rod from the side of the form setting undergoes some actual displacement

all the way into the workpiece. The actual position of the workpiece along the i-th axis can be measured by working off the nut 55 back, until it stops against the movable stop 57. The movement passed by the nut 55

back and the increment of interest in the coordinate of the actual position of the workpiece is equal to

где n - число шагов до остановки гайки 55 и винта 54, когда муфта предельного момента 60 отключает шаговый двигатель 48 и через ее датчик 61 в измерительную систему подается сигнал обратной связи, указывающий на окончание счета шагов φ₀, чем и фиксируется величина

The backward movement taken by nut 55 is measured by counting the steps φ ₀ and, correspondingly, by their transformed displacement h ₀ , so that

where n is the number of steps to stop the nut 55 and screw 54, when the clutch of the limiting moment 60 disconnects the stepper motor 48 and through its sensor 61 a feedback signal is fed into the measuring system, indicating the end of the step count φ ₀ , which fixes the value

до ограничения ее перемещения подвижным упором 57 в фазе сообщения i-го органа давлениями p₁ и р₀. Фактическое положение заготовки вдоль i-й оси при k-ом промежуточном этапе формованияIn other modes of molding, when Δz _{ik is} not specified by mechanical regulation, the measurement of the actual shape of the workpiece along the axis of the i-th working body is carried out, mainly at the final stages of molding, working off the nut 55 back from the final coordinate of the product z _ik by a certain amount

to limit its movement by the movable stop 57 in the phase of communication of the i-th organ with pressures p ₁ and p ₀ . The actual position of the workpiece along the i-th axis at the k-th intermediate stage of molding

As in the previous case, the end of the counting of the revolutions of the nut 55 is made according to the feedback signal when the screw pair is stopped by the increased moment at the contact of the nut 55 and the stop 57.

The interaction of the workpiece and the deforming rods in the phase mode of molding from different sides of the workpiece varies significantly not only in effort, but also in kinematics.

On the side of the job of the form, the message of the power hydraulic cylinders 2 with a drain in the corresponding phase leads to their stop, and since the neighboring power hydraulic cylinders 2 of the other phases are connected at that time with pressure sources and move towards the workpiece, and then with it, the contact is stopped groups of rods and workpieces are interrupted.

A different situation arises in this case from the backpressure side if the return cylinders, as in the case from the side of the mold setting, will also be communicated with a drain during the entire molding mode.

The movement of the areas of the deformable workpiece is carried out in the direction of the power backpressure hydraulic cylinders 17. Their forced return by the moving workpiece is carried out regardless of whether they are communicated with a pressure p ₂ or with a drain.

Communication power cylinders 17 and return cylinders 40 with a drain does not lead to rupture of contact between the rods and the workpiece, as in the case of power cylinders 2 and return cylinders 40 from the side of the form.

Such a return from the backpressure side is very desirable, since it significantly reduces heat removal from the workpiece (heat removal through the contacting rods ceases), reduces the resistance to surface movements relative to the rods, which is especially important in case of reinstallation in a new position, and, thus, reduces the required efforts to hold the workpiece in intermediate positions of reinstallation.

To open the contact between the rods and the workpiece from the back pressure side, a forced return of the power hydraulic cylinders 17, which are in the phase of their communication with the drain, is required. This can be accomplished, for example, by communicating all return hydraulic cylinders 40 of the power hydraulic cylinders 17 in various phases with a pressure source p ₀ . However, the constant communication of the return cylinders 40 with a pressure source p ₀ during the entire molding mode is not the best solution in the sense of economical use of hydraulic energy and working areas of power hydraulic cylinders 17 in the phases of their communication with the source p ₂ .

The most economical in this sense is the implementation for each phase group of power backpressure hydraulic cylinders 17 also phase communications 41 for their return hydraulic cylinders 40, which are included in antiphase with respect to the phase highways 16 of the power hydraulic cylinders 17 (see c) in FIG. 5 and FIG. .7).

In the proposed molding device, an additional low pressure source p _{0 is used} for several reasons. One of these needs is the use of low pressure p ₀ in order to save hydropower from a source p ₁ , which is used exclusively for deformation of the workpiece. All auxiliary and preparatory stages of the deforming moves themselves are carried out from the source with pressure p ₀ . On the other hand, the phased filling or emptying of the power hydraulic cylinders 2 and 17, first with a pressure of p ₀ and then with a pressure of p ₁ or p ₂ makes it easier to preserve the equipment during long-term operation.

Before touching the rods of the power hydraulic cylinders and the workpiece, both from the side of the shape setting, and from the backpressure side, and after touching, the functioning of the power hydraulic cylinders (2, 17) is significantly different. When moving the power hydraulic cylinder (2, 17) until the rod and the workpiece touch, the movement is carried out without energy consumption (or rather, overcoming the idle friction of the power hydraulic cylinder), and only after touching the workpiece and the deforming rod, or rather, after touching all moving idle rods from the job side form, it requires the expenditure of hydraulic energy to move the areas of the workpiece during its deformation.

The deformation process is impossible without creating back pressure, therefore, after touching all the idling rods from the back pressure side, the hydraulic cylinders 17, which carry out reverse strokes under load synchronously, must be connected to the hydraulic resistance that creates the back pressure p ₂ . The synchronization of hydraulic cylinders 2 and 17 both when filled with pressures p ₀ and during deformation with pressures p ₁ and p ₂ , respectively, was carried out by the synchronous operation of hydraulic units and their drives.

On the set side of the form, line 1 of the phase group of moving power hydraulic cylinders 2 is idle connected to pressure sources p ₀ and p ₁ at the outputs from the rotary valve 6, but the pressure source p _{1 is} disconnected from line 1 by a sequential valve 8. The fluid flows to the line only from the low pressure source p ₀ through the check valve 7 and the pressure sequential valve 8. The flow continues until the total volume is exhausted when the deforming rods move to touching them and the workpiece.

6 in position I shows the position of the moving parts of the units when filling the hydraulic cylinders 2 with a liquid with a pressure p ₀ . See also figure 1.

а суммарный объем V^*=L^*s.If Δf $\genfrac{}{}{0ex}{}{\text{*}}{\text{i}}$ is the stroke of the i-th power hydraulic cylinder, n is the number of hydraulic cylinders of the 2 phase group from the side of the form setting, and s is the section of the displacer, then the total stroke

and the total volume V ^* = L ^* s.

After the volume V ^{* is} filled up, the pressure p ₀ increases due to the liquid stopping and its inertia, and the sequential switching valve 8 is activated to open the channel with pressure p ₁ . With a higher pressure p _{1, the} check valve 7 closes, cutting off the source with pressure p ₀ , and the liquid with pressure p ₁ fills the power cylinders 2 of the phase group, forcing them to move after touching the rods and the workpiece until the end of the deformation phase.

6 in position II shows the position of the moving parts of the hydraulic units at the time of completion of filling with liquid with a pressure p ₀ . In particular, an increase in pressure p ₀ causes a force on the shank 11 of the plunger 10 in the direction of the calibrated spring 12 (see figure 3). The dividing fillet 27 is shifted towards the spring and allows fluid with pressure p ₁ to enter the low pressure cavity, which affects the force from the shank, and the dividing fillet 27 is shifted towards the spring 12, compressing it even more. The increased pressure closes the check valve 7, and the liquid from the source with pressure p ₁ enters the phase line 1 through the common outlet of the series valve (see position III in FIG. 6).

а суммарный объем при деформировании до окончания фазы V^**=L^** s, и суммарная энергия преодоления противодавления и деформирования E^**=V^**p₁.If Δf $\genfrac{}{}{0ex}{}{\text{**}}{\text{i}}$ is the deformation progress of the i-th phase cylinder 2 of the phase group from the side of the shape, n is the number of hydraulic cylinders of the 2 phase group from the side of the shape, and s is the section of the displacer, then the total stroke

and the total volume during deformation before the end of the phase is V ^** = L ^** s, and the total energy of overcoming backpressure and deformation is E ^** = V ^** p ₁ .

After the end of the deformation phase, the line 1 of the phase group with a hydraulic switch 6 is cut off from the pressure sources p ₀ and p ₁ and communicates with the drain.

In Fig.6, this moment is depicted in position IV. With a spring 12, the plunger 10 returns to its original position, the dividing fillet 27 closes the message of the cavities of low p ₀ and high pressure p ₁ , and the hydraulic unit is again ready to repeat the cycle in order of pressure p ₀ and p ₁ . On the counter-pressure side, the control valve 21 operates synchronously, and the same processes occur with the check valve 22, and serial valves 23, except for the presence of the control signal channel 24, which is in communication with the highway 1 on the shape setting side (see Fig. 2).

When using directional control valves including a servo drive, the same sequence of operation of hydraulic units essentially occurs in the hydraulic system, only the through sections of communications and hydraulic units increase.

The proposed molding device allows to solve differently many issues of expanding the range of products used in aviation, space technology and shipbuilding, and is the development of the device [1].

Claims (5)

1. A device for forming shells with alternate contact of the working bodies and regions of the molded workpiece, comprising a forming chamber, working bodies, each of which is made in the form of two coaxially arranged rods and having differential and positional hydraulic drives located on opposite sides of the forming chamber, the working bodies are divided into phase groups and are made with control of the magnitude of their movement, and phase groups are divided into subgroups, the positioning of one of the hydraulic drives of each rod is ensured by in the differential hydraulic drive of the direct-flow regulation device, the differential hydraulic drive is made in the form of linear hydraulic motors, connected in parallel with the phase lines of the phase groups of the working bodies, each of the hydraulic motors consists of two power hydraulic cylinders with the opposite direction of one-way strokes and a mechanical connection between their axially movable bodies, each power hydraulic cylinder contains a fixed rod and a movable housing with one sealing unit in the form of a movable radial support, at ohm, the deforming rod is mounted on the housing of the power hydraulic cylinder, the fixed radial support of which is the entrance to the molding chamber; the return hydraulic cylinder is made in the form of a fixed step displacer and a movable housing consisting of two sealing units corresponding to the diameters of the step displacer, the power cylinders are connected to the phase line by means of an outlet with a shoulder located in the hollow rod and secured by a nut on the outside of the bottom, in which a hole for passing is provided the end of the branch, resting on the bottom from the inside with a shoulder, and with deforming strokes, each phase group from the side of the positional hydraulic actuators it is connected with a pressure source p ₁ , a from the side of the differential hydraulic drive, the differential motors of which make a forced return stroke, is connected with a pressure source p ₂ , while the cross-section of the rods S ₁ and S _{2 of the} corresponding power cylinders of each working body and the forces P ₁ and P ₂ satisfy the inequalities P ₁ > P ₂ and (P ₁ -P ₂ ) <P ₂ , where P ₁ = p ₁ S ₁ , P ₂ = p ₂ S ₂ ; at idle strokes in the molding mode, the power hydraulic cylinders of the working bodies are connected with a pressure source p ₀ satisfying the inequality p ₀ << p ₂ , in the idle phases the power hydraulic cylinders of the working bodies are connected with a drain, and their return devices, at least from the back pressure side, are communicated a pressure source p ₀ from the reference phase form each group of working elements is in communication with sources of pressure p _1, p ₂ and drain through the converter constant pressure in the pulsating phase comprising gidroraspredelite and at high costs and flat-valve control valves or servo control valves, valve boxes, each of which contains a sequential valve and a check valve, a group of stepper motors whose axes are connected to the axes of rotary control valves with a flat valve or with servo control valves, the latter are associated with phase highways through valve boxes that serve to fill the hydraulic drive at idle from a source with a lower pressure p ₀ , and when deforming their moves - from a source with pressure p ₁ ; the output of each servo action valve for high pressure p _{1 is} communicated with the inlet of the pressure sequential valve p ₀ and p ₁ , and the output of the servo action valve for low pressure p _{0 is} communicated with a check valve and through it with the main inlet of the pressure sequential valve p ₀ and p ₁ and its signal input; the output of the servo action valve along the drain and the output of the sequential pressure switch p ₀ and p _{1 are} connected to the phase line, while the outputs of the valve with a flat valve are connected with the valve at a high cost; during return strokes, the inputs of the rotary control valves of the pressure transducer p ₀ to the phase pulsating pressure are in communication with the pressure source p ₀ and outflow in antiphase with the outputs that are connected to the phase lines of the power cylinder return devices; from the counterpressure side, each phase group of working bodies is connected with sources of pulsating pressures p ₂ , p ₀ and a discharge at the inlets and with a constant pressure source p ₂ at the outlet through a phase pressure to pressure p ₂ converter containing valve spools with a flat spool or valve servo valves, valve boxes, each of which contains a sequential valve and a check valve, a group of stepper motors, the axes of which are connected with the axes of rotary directional control valves with a flat spool or with servo control valves, the latter are connected to the phase lines through valve boxes, which serve to fill the hydraulic drive at idle from the source with pressure p ₀ , and with deforming moves from the source with pressure p ₂ ; the output of each servo action valve for pressure p _{2 is} communicated with the inlet of the pressure sequential valve p ₀ and p ₂ , and the output of the servo action valve for pressure p _{0 is} communicated with a check valve and through it with the main valve inlet of the pressure sequential pressure p ₀ and p ₂ , it the signal input is communicated with the co-phase line from the side of the job form; the output of the servo action valve overflow and the output of the sequential pressure switch p ₀ and p _{2 are} connected to the back pressure phase line, while the outputs of the flat-valve control valves are connected to the control valves at high costs, and each device for regulating the direct strokes of the power hydraulic cylinders contains screw pairs, coaxial with power hydraulic cylinders, with each of the screws connected to the axis of the stepper motor through a clutch of maximum torque, each screw is located in two bearings on its ends, while the support on the side of the power hydraulic cylinder contains a radial bearing, and on the other hand, a fillet on which there is a thrust bearing on the thread side of the screw pair, the screw pair nut is made with grooves on its outer surface to accommodate rods in them and is located between the rod of the power hydraulic cylinder and the movable stop connected by rods to the body of the hydraulic cylinder, while the nut of the screw pair of each working body in the phase of communication of the power hydraulic cylinders with the drain is shifted from the movable stop to the side under of a movable housing of a hydraulic cylinder installed with the possibility of setting its movement, and in the measuring mode, the nut is shifted in the opposite direction in the phase of communication of the power hydraulic cylinder with the pump station. 2. The device according to claim 1, characterized in that during hot stamping, the deforming rod and the case of the power hydraulic cylinder are fastened to each other by means of a collar on the rod and a threaded connection with a union nut on the case, with heat insulating rings located on both sides of the collar, and the ends the rod and the cylinder body are separated by a ball or ball separator. 3. The device according to claim 1, characterized in that it contains a phase pressure transducer in constant from the side of the power cylinders with forced reverse during molding, communicated with the discharge of two lines, one of which contains a hydraulic resistance, while the highway with a hydraulic resistance, providing pressure p _2, comprises a controllable valve, which outputs are communicated with the two line branches, one of which communicates with the hydraulic motor the motor-pump assembly, hydraulic resistance is formed simp trolled by a predetermined pressure p ₂ at high flow rates, and the output of the pump communicates on its pressure p ₁ to the pressure source P ₁ on the reference shape, and the second branch comprises a choke device, hydraulic resistance is formed by a controlled predetermined pressure p ₂ at low flow rates. 4. The device according to claim 1, characterized in that each subgroup of the working bodies forms a single-row module in the form of a frame and consists of two bases, each of which is made in the form of a single block of hydraulic motors or prefabricated, containing several blocks of the same phase fastened together In this case, each module unit contains a multi-shelf beam, the shelves of which are fastened by the uprights and removable protective walls, and at its ends, on the side facing the molding chamber, are mounted clearance-free and self-governing during assembly To attach the blocks in the plane of the base of the molding chamber in two directions and perpendicular to it when fixing the walls on the periphery of the forming area, on the opposite side of the ends of the block are also mentioned fasteners for connecting other blocks in two directions in the plane parallel to the base of the molding chamber, on each multi-beam beam from the side of the form setting, the power hydraulic cylinders and screw pairs with their drives are installed coaxially, and the racks located between the shelves are found are shown at the vertices of the zigzag drawn through the centers of the axes of the working bodies, the axis of symmetry of the stops and the centers of the guides for the nuts of the device for regulating the direct strokes of the power hydraulic cylinders are located in the opposite order on the said zigzag. 5. The device according to claim 1, characterized in that the screw pairs of the device for regulating the direct strokes of the power cylinders are installed with the ability to move according to the program, including the coordinates of the final and intermediate surfaces of the product, and the positions during manipulations specified by the numbers of the working bodies relative to the molding area and marks on the axes of the working bodies relative to the plane of the workpiece, while the coordinates of the intermediate surfaces of the product are determined by the flow rate and the frequency of the phase pressure system.

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