RU74765U1 - DEVICE FOR FOLDING THE FOOD PRODUCT, STAMPING MECHANISM AND DEVICE FOR MANUFACTURING SEMI-FINISHED PRODUCTS FROM THE TEST WITH THE BEGINNING (OPTIONS) - Google Patents

Abstract

1. A device for rolling out a food product containing a first pair of rollers placed on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second is formed between the working surfaces of the second pair th predetermined gap, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roll of the first pair and the working surface of the opposite to it on the same side relative to the conventional plane passing through the first and second predetermined roll gaps of the second pair, working gaps are formed , besides, with the first pressure plate connected to the housing support element facing the bearings of the end side of the rollers, through which the shafts of the first and second pairs are passed, then and as on the other end side of the rollers there is a second pressure plate connected to the housing support element, through which shafts of at least one pair are passed, wherein the housing support element is made with two housing spaced apart from each other at a predetermined distance and rigidly connected to each other plates with through holes adapted to receive bearings of bearing assemblies, characterized in that the first pressure plate is assigned from the housing plate of the housing support element facing it along

Description

FIELD OF TECHNOLOGY TO WHICH A USEFUL MODEL IS

The inventive utility models relate to the food industry. In particular, they can be used in meat processing and fish processing industries, as well as find application in the equipment of culinary and confectionery industries, catering facilities.

BACKGROUND

It is known from patent RU No. 2278518 (publ. 2006.06.27) a device for rolling out a test strip containing two endless tapes mounted with the possibility of unidirectional movement of their branches located next to the gap and passed between two rolls installed each with the possibility of contact with the reverse relative the gap surface of one of the tapes and with the location of the axis of rotation in one plane perpendicular to the direction of movement of the tapes in these branches. The device is equipped with many additional rolls installed in pairs similar to those mentioned, the rolls are stepped, with calibrating sections, the diameter of which exceeds the diameter of the main part of the roll, while on the first in the direction of movement of the specified branches of the tape paired rolls, the calibration sections are made in the middle of the rolls, and for each subsequent pair, the calibrating sections are spaced to their end edges with symmetrical relative to

the longitudinal axis of the device passing through the midpoints of the rolls and perpendicular to their rotational axes with an offset, the value of which increases along the length of the roll on each subsequent pair by an amount not exceeding the length of the calibrating section of the previous roll.

It is known from patent RU No. 2272410 (publ. 2006.03.27) high-performance device for the manufacture of semi-finished dough with filling, which contains designed to form at least two strips of shell material rolling, consisting of at least two mechanisms, including at least two rotating towards each other roller and pressure roller. The device also includes a stamping mechanism - a pair of drum cells including, mounted for rotation towards each other and a meat feeder, configured to feed the filling between the tapes and having a wedge-shaped fragment oriented with the apex toward the drums. The device comprises a dispenser, configured to portion injection of the filling through the exhaust channels of the meat feeder. The device contains a zone for forming semi-finished products, into which the belts of the material of the shell and portions of the filling are fed. This zone is located in close proximity opposite each other cells with inlets, having a given shape of the inner surfaces corresponding to the shape of the resulting semi-finished products, or including screens of the corresponding shape. The structural units of the device are made of certain shapes and sizes. The invention allows to create a device that provides the manufacture of a wide range of semi-finished products of high quality from dough with filling.

It is known from patent RU No. 2262232 (publ. 2005.10.20) a device for the manufacture of dough products with filling, which allows the product to be sealed to prevent the filling from sticking to the test casing, resulting in high quality finished products. The device comprises punching means and test tape feed units. The stamping means includes two stamping cylindrical surfaces arranged in conjunction with and with the possibility of rotation towards each other in the form of synchronously rotating stamping drums,

made with forming cells, a dispenser of portions of the filling, the output of which is made in the form of a set of channels, and the outlet openings of the channels are open in the corresponding forming cells. The outlet openings of the dispenser channels are placed along the mating line of the stamping cylindrical surfaces and within the convergence angle of the test tapes coming from the nodes of the mechanism for moving the test tapes. The channels of the outlet part of the dispenser can be equipped with oppositely located limiters, separating the space near each outlet on both sides and directing a portion of the filling to the walls of the forming cells.

The above devices are characterized by a very high productivity of the process. A common drawback inherent in all the devices for manufacturing dough products with filling disclosed above is the lack of reliability of structures due to the presence of dispensers, as well as the use of at least two mechanisms for rolling out the test strip in a single technological process.

This problem was partially solved by a device for rolling out a food product and a device for manufacturing dough products with filling, chosen as the closest analogues and disclosed in RU patent No. 50759 (publ. 2006.01.27). A device for the manufacture of dough products with filling contains stamping means made in the form of drums installed with mating and rotatable towards each other, each of which has a plurality of molding cells with a selected shape of the inlet openings, a food product rolling means configured to form two ribbon-like test strips directed to the product formation zone and the filling injection device, the output of which has at least one distribution channel fillings intended for supplying fillings between said ribbon-like strips. The drum cell is equipped with a reciprocating mounted between the provisions of the retraction back and advance forward towards the inlet of the cell ejector element, rigidly connected by means of a supporting element with a flat ellipsoid element placed inside the drum around its hub, while on an ellipsoidal

the element along the line of its small diameter has two supporting elements for two opposed ejector elements located in opposed drum cells, and a biasing element is mounted in the drum cavity so that when it interacts with the elliptical element, one of the two opposite located ejector elements for contacting the product. The food product rolling means, made in the form of a single mechanism, has four rollers rotating around its own axis, installed with a predetermined gap between each other, and mounted in the housing so that in one pair of rollers rotating towards each other, a predetermined gap between them ensures the reception of the food product into the space limited by the generators of the cylindrical surfaces of all the rollers, while in two other pairs of rollers rotating towards each other, the food product coming into the gap between them rolls and stretches with the formation of two tape-shaped strips of food product emerging from the device. The rollers are mounted on shafts located essentially parallel to each other and installed so that in the plane of the cross section of the shafts their axial lines are at the vertices of the quadrangle, while the shafts are connected by a closed kinematic chain, and any two conjugated rollers form a pair in which the rollers rotate in the opposite direction to each other.

This device is selected as the closest analogues of the claimed objects. A close analogue provides the production of semi-finished products with an attractive appearance. At the same time, however, the close analogue has some drawbacks, namely: it is difficult to configure the rolling for various shell materials, it is difficult to configure the exit from the rolling of tapes of a given thickness, it is difficult to remove excess material from the rolled material falling into the bearings on which the shafts are mounted, assembly is difficult and adjustment, the stamping mechanism (drums) wears out quickly, sanitization is difficult, in particular, disassembly of the device is difficult.

DISCLOSURE OF A USEFUL MODEL

Utility models are based on the task of eliminating the above drawbacks and creating simple and compact designs of a food product rolling device, a stamping mechanism, and a device for the manufacture of semi-finished dough products with filling, which have high operational reliability and high performance, providing products with high quality indicators, by improving the technical characteristics and optimizing the ratio of sizes and parameters.

In this aspect, the claimed utility models also make it possible to increase the compactness and transportability of equipment, increase its service life and reduce the requirements for the qualifications of staff.

Including the claimed technical result from the use of the presented utility models is to simplify the sanitization of parts and assemblies and minimize waste.

The achievement of the task contributes to the inclusion in the device for rolling the food product containing

the first pair of rollers placed on the first pair of shafts mounted to rotate in bearings of the bearing assemblies connected to the housing support element, and the second pair of rollers placed on the second pair of shafts mounted to rotate in the bearings of the bearing assemblies connected to the housing support element, with between the working surfaces of the rollers of the first pair, a first predetermined gap is formed, and between the working surfaces of the second pair a second predetermined gap is formed, the first pair of rollers being set to relative to the second pair of rollers in such a way that between the working surface of the roll of the first pair and the working surface of the opposite pair on the same side relative to the conventional plane passing through the first and second predetermined rollers of the second pair, working clearances are formed, while the first predetermined gap is adapted to receive the product blank , which is rolled into ribbon-like strips emerging from the working gaps, and its value exceeds the size of the remaining gaps, and the value of the second predetermined gap has in comparison with the size of other gaps, the smallest value, despite the fact that the working surface of each drum has a diameter set for it, and with the end face of the rollers facing the bearings

there is a first pressure plate connected to the housing support element through which the shafts of the first and second pairs are passed, while on the other end side of the rollers there is a second pressure plate connected to the housing support element through which the shafts of at least one pair are passed, the supporting element is made with two spaced apart from each other at a pre-selected distance and rigidly interconnected housing plates with through holes adapted to receive bearing bearings zlov,

The following main and particular distinguishing features.

The first pressure plate can be assigned from the body plate of the housing support element facing it along the axis of rotation of the shaft by a predetermined distance, while it is advisable to choose a predetermined distance from a range of 15-60 mm, preferably from a range of 18-30 mm.

It is desirable that the thickness of the at least one pressure plate be selected from a range of 7-20 mm, preferably 8-12 mm.

The first and second pressure plates on the supporting surfaces facing the end faces of the rollers may comprise an anti-friction coating or anti-friction linings.

The device can be equipped with an auxiliary plate located at a selected distance from the second pressure plate, while the shafts of the first and second pairs can be passed through the second pressure plate so that they extend beyond it, and their end parts are installed in bearings, the housing bearings of which are placed in the holes of the auxiliary plate.

It is advisable that the selected distance be selected from the range of 15-60 mm, preferably 18-30 mm. Preferably, the thickness of the sub-plate is selected from a range of 15-60 mm, preferably 30-36 mm.

The magnitude of the selected distance may be substantially equal to the magnitude of the predetermined distance or the magnitude of the selected distance may differ from the magnitude of the specified distance, and the dimensions of the auxiliary plate in the plane perpendicular to the axis of rotation of the shafts may differ from the dimensions of the second pressure plate.

The pre-selected distance between the housing plates can be selected from a range of 40-60 mm, preferably 42-45 mm, and the thickness of at least one housing plate can be selected from a range of 12-18 mm, preferably 14-16 mm.

In addition, the housing support element can be made in the form of a housing plate with through holes for receiving shafts, having a side facing the rollers, identified as the front side and the opposite side, identified as the back side, while the back side of the housing plate is provided with enclosing holes protruding components made in the form of tubular elements adapted to hold the bearings of the bearing assemblies. It is desirable that in this case the device was provided with at least two stiffening elements located at an angle to each other, connected with the housing support element. It is advisable that the minimum thickness of the housing plate with tubular elements be selected from a range of 12-18 mm, preferably 14-16 mm, and that the tubular elements extend beyond the surface of the back side of the housing plate to a distance selected from a range of 30-70 mm, preferably 32- 38 mm. It is desirable that the body plate with tubular elements be made in the form of a single cast or welded part, and the tubular element is made with a radial wall thickness varying along the axis of rotation of the shaft with an increase in the direction from the peripheral end to the surface of the body plate, so that its outer surface is would essentially be the surface of a truncated cone.

It is advisable that the plates were essentially parallel to each other and lay in planes essentially perpendicular to the axes of rotation of the shafts.

The connection of the bearings of the bearing units with the housing support element can be such that it is not possible to change the position of the axis of rotation of the shaft, which is achieved, for example, by installing bearings in tubular elements with a tight fit, while the axis of rotation of the support coincides with the axis of rotation of the shaft. In this case, the bearing housing is mounted motionless relative to the pressure plate.

The device may include an adjustment unit for at least one gap between the rollers, providing for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie, parallel to the transfer of the axis of rotation of the at least one shaft by its movement.

It is advisable to move the shaft by turning the support of the bearing assembly, while the support is eccentric and is provided with a through hole extending radially in relation to the axis of rotation of the shaft, adapted to receive fastening means designed to enable the support to rotate around its axis of rotation within the selected angular range when adjusting the distance and tight connection of the support with the base support element in the selected position after rotation. In this case, in embodiments of a device with a housing support element in the form of two spaced housing plates, the housing support element is provided with an arcuate bracket contacting the outer surface of the support with a through groove made in the circumferential direction of the support, and in embodiments of the device with one housing plate and tubular elements, the tubular element in which the eccentric support is located is provided with a through groove extending in the circumferential direction of the support. If the bearing assembly is eccentric in embodiments of the device with an auxiliary plate, the corresponding hole in the front plate for receiving the bearing housing of the bearing has such a configuration that allows the bearing housing, which is mated with the pressure plate, to be moved together with the shaft in the direction of movement of the shaft rotation axis, and the auxiliary plate equipped with at least one extending in the radial direction with respect to the axis of rotation of the shaft through additional holes it, adapted to receive a fastening member for fixing the bearing housing support in a selected position. Preferably, the selected angular range is approximately 90 °.

Regarding clearances between rollers.

It is advisable that the minimum value of the first predetermined gap lies approximately in the range of twice the thickness of the product-like strip bands emerging from the working gaps, while its maximum value lies approximately in the range of the quadruple thickness of the product-shaped stripes coming out of the working gaps. It is possible that the value of the first predetermined gap lies within 2-7 mm, preferably 3-5 mm, while the magnitude of the second predetermined gap lies within 0.1-1.5 mm.

It is advisable that the rollers be oriented so that their axis of rotation are generally parallel to each other.

The working surface (i.e., the outer cylindrical surface) of each roller may have a diameter set for it, selected from a range of 50-120 mm. It is advisable that the diameter of the cylindrical surfaces of the rollers was selected from the range of 65-80 - mm.

The diameters of all the rollers can be essentially the same size.

The diameters of at least two rollers may have different values from each other. It is possible that the diameters of the rollers of one pair will have a value of approximately equal to 71.6 mm, while the diameters of the rollers of the other pair will have a value of approximately equal to 71.4 mm.

It is possible that the diameters of the rollers of one pair will have a value of approximately equal to 71.8 mm, while the diameters of the rollers of the other pair will have a value of approximately equal to 71.4 mm.

It is possible that the diameters of the rollers of one pair will have a value of approximately 71.8 mm, while the diameters of the rollers of the other pair will have a value of approximately 71.6 mm.

It is advisable that the length of the rollers was selected from the range of 20-350 mm, preferably 70-250 mm

The device may further comprise at least two scraper elements adapted to prevent sticking of product-like product bands from sticking out of the working gaps, while the scraper elements are arranged to allow said strips to pass freely from the working gaps to their chosen position, while the scraper elements elements are installed so that the inverted

towards the ribbon-like strip of the product, the edge part of each scraper element lay in a plane spaced from the rotation axis of the corresponding roller by a distance which is less than the roller radius by an amount selected from the range of 2-4 mm.

It is preferable to make scraper elements from sheet stainless steel or from polymeric materials, for example, organic glass with a thickness of 1-2 mm. It is desirable to mount the scraper elements with the possibility of changing the position of their edge parts relative to the respective surfaces of the rollers.

The device may be equipped with at least one drive means providing such a synchronous rotation of all the rollers so that in each pair the rollers rotate towards each other. The drive means may include a gear motor, with the shafts having a kinematic coupling locked on the gear motor, based on a gear and / or chain gear. It is advisable to connect the gear motor to the base support element by means of a traction element made of at least two parts, one of which is made in the form of an arcuate bracket attached to the gearbox flange, and the other is made in the form of a strip radially oriented to the convex side of the bracket, one end of which is rigidly connected to the bracket, and the other is adapted for communication with the base support element., despite the fact that these parts can be made in one piece.

The achievement of the task is facilitated by the inclusion in the punching mechanism comprising a pair of including cell drums mounted rotatably towards each other, while each drum is mounted on a shaft mounted in the bearing of the bearing unit associated with the base support element; moreover, the drums have a first end surface facing the supports and a second end surface opposite to it; while between the first end surface of the drums and the base support element is placed associated with the base support element, the front plate through which the shafts are passed; despite the fact that at least part of the cells is equipped with ejection elements placed in the cells with the possibility of movement towards the inlet of the cell and

moving without going outside the cell in the opposite direction; wherein each ejection element is connected by means of a supporting element to an oval-shaped element located in the drum and surrounding the shaft, having two essentially flat surfaces, as well as an inner end face facing the shaft and an outer end face facing it; while the contour of the oval-shaped element on flat surfaces is limited by two ovals spaced a predetermined distance, the oval facing the shaft has a small diameter measured along the axis of its small axis and a large diameter measured along the axis of the major axis, while the elongated longitudinally is placed in the drum the axis of rotation of the drum, the biasing element is installed so that when it interacts with the end surface of the oval-shaped element facing the shaft, the ejecting element moves towards the input hole The cell hole within the stroke of a given value, the following main and particular distinguishing features.

The face plate of the stamping mechanism can be assigned from the base support element in the direction of the axis of rotation of the shaft at a predetermined distance.

It is advisable to select a predetermined distance from the range of 15-60 mm, preferably 18-30 mm. Preferably, the thickness of the faceplate is selected from a range of 7-20 mm, preferably 8-12 mm.

The stamping mechanism may additionally be provided with a front plate having openings spaced apart from the second end surface of the drums at a preselected distance, while the end parts of the shafts extend beyond the second end surface of the drums and are mounted in bearings whose housing supports are located in the openings of the front plate.

It is advisable to select a pre-selected distance range of 15-60 mm, preferably 18-30 mm

It is desirable that the thickness of the front plate be selected from a range of 15-60 mm, preferably 30-36 mm.

The basic support element of the stamping mechanism can be made in the form of two spaced apart from each other at a pre-selected distance and rigidly interconnected body plates with through

holes adapted to receive bearings of bearing assemblies. It is advisable to pre-selected the distance between the housing plates to choose from the range of 40-60 mm, preferably 42-45 mm

In addition, the basic support element of the stamping mechanism can be made in the form of a body plate with through holes for receiving shafts, while the plate has a side facing the front plate, identified as the front side and the opposite side, identified as the back side, despite the fact that the back side of the housing plate is equipped with protruding components enclosing the holes, made in the form of tubular elements oriented longitudinally to the shafts, adapted to hold the bearings of the bearing assemblies.

It is advisable that the tubular elements protrude beyond the surface of the body plate at a distance selected from the range of 30-70 mm, preferably 32-38 mm. It is desirable that the minimum thickness of the body plate be selected from a range of 12-18 mm, preferably 14-16 mm. It is possible to make a body plate with tubular elements in the form of a single cast or welded part. In this embodiment, the stamping mechanism of the base support element may further comprise at least two stiffeners arranged at an angle to each other and connected to the base support element.

The stamping mechanism may further comprise at least one unit for adjusting the relative position of the drums.

It is advisable that the adjustment unit provides for the possibility of adjusting the distance between the axes of rotation of the shafts in the plane in which they lie, parallel to the transfer of the axis of rotation of at least one shaft by its movement. It is preferable to move the shaft by turning the bearings of the bearing assembly. For this, the support of the bearing assembly can be made eccentric and provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to enable the support to rotate around its axis of rotation within the selected angular range at

adjusting the distance and tight connection of the support with the base support element in the selected position after rotation.

It is desirable that in the case of the base support element with two body plates, the base support element is provided with an arcuate bracket contacting the outer surface of the support, having a through groove extending in the circumferential direction of the support, and in the case of the base support element in the form of a body plate with tubular elements, so that the tubular element adapted to hold the support was made with a through groove extending in the circumferential direction of the support.

In embodiments of the stamping mechanism with bearing housings housed in the holes of the front plate in the case of an eccentric bearing assembly, it is advisable that the bearing housing mating with the front plate be made and mounted so that it can be moved together with the shaft and locked in a rigid position the connection of the eccentric support with the base support element. In this case, it is desirable that the corresponding hole of the front plate in a conditional plane perpendicular to the axis of rotation of the shaft have such a contour that would allow the bearing housing to be mated with the front plate to move in the direction of movement of the shaft, and it is desirable to provide the front plate with at least one fixing an element for fixing the bearing housing in a selected position relative to the front plate. The contour of the hole can be outlined by an oval, the major axis of which is located on a conditional line passing through the points of intersection of the axes of rotation of the shafts with said conditional plane. Preferably, the contour of the housing support in this conditional plane is outlined in a circle and the fastener is threaded and placed in an additional through hole of the front plate adapted to receive the threaded fastener, extending in the radial direction relative to the axis of rotation of the shaft along the line of the major axis of the oval.

The selected angular range can be approximately 90 °.

In addition, the adjustment unit may provide for the possibility of angular displacement of one of the drums relative to the shaft on which it is mounted.

It is advisable that the adjustment unit provides for the possibility of movement during commissioning of at least one of the drums along the axis of rotation of the shaft.

The front plate can be made with a figured cutout, providing affordable monitoring of the contact area of the outer surfaces of the drums.

It is preferred that tapered or radial thrust bearings are selected as bearings.

It is advisable that the drums with the accuracy of manufacturing errors were made identical and installed with the mating of their outer cylindrical surfaces along a line lying in the same plane with the axes of rotation of the drums.

It is desirable that the axis of rotation of the drums are essentially parallel to each other.

To ensure rotation of the drums, the stamping mechanism may include at least one drive means for synchronously rotating the drums. The drive means may include a gear motor, while the shafts will have a kinematic coupling locked on the gear motor, based on a gear and / or chain gear.

It is advisable to connect the gear motor with the base support element. It is desirable to carry out the connection by means of a traction element made of at least two parts, one of which is made in the form of an arcuate bracket fixed to the gearbox flange, and the other in the form of a strip radially oriented to the convex side of the bracket, one end of which is rigidly connected to the bracket and the other is adapted to communicate with the base support element. It is possible to complete these parts in one piece.

It is advisable to set the amount of stroke within which movement can be carried out without going beyond the cell of the ejector element towards the cell inlet (i.e., the forward direction) and

opposite direction (reverse) to choose from the range of 10-25 mm.

Preferably, the predetermined stroke value, defined as the difference between the large diameter and the small diameters of the elliptical element, is selected from a range of 12-18 mm.

It is possible that the stroke size will be approximately 15 mm, while the large diameter is approximately 81 mm, while the small diameter is approximately 66 mm.

The thickness of the oval-shaped element, determined by the distance between its flat surfaces, can be selected from the range of 1.5-2.5 mm, preferably 1.8-2.0 mm.

The predetermined distance by which the ovals are spaced can be selected from a range of 5-12 mm, preferably 7-8 mm.

The ejector element can be made in the form of a plate with a contour around the perimeter, which provides a gap between the inner side surface of the cell and the surface of the ejector element facing it, while the minimum clearance allows free movement of the ejector element.

Preferably, the supporting element is made in the form of a rod extending along the line of the minor axis of the oval-shaped element.

It is desirable that the biasing element was made in the form of a rod rigidly connected at one end to the base support element, and at the same time be mounted with the possibility of adjusting its position relative to the axis of rotation of the drum.

It is advisable that on each oval-shaped element along the line of its minor axis, two opposite supporting elements are installed for two opposed pushing elements located in opposite opposed drum cells, while the number of cells of each drum will be an even number.

The oval-shaped element and the supporting element can be made integrally in one piece.

The achievement of the task is facilitated by the inclusion in the device for the manufacture of semi-finished products from dough with filling, containing a stamping mechanism, made in the form of a pair of including cells

drums mounted on the base support element with the possibility of rotation towards each other; a device for rolling out a food product, made with the possibility of forming two ribbon-shaped test strips supplied to the product formation zone and having four rollers mounted on the housing support element with the possibility of synchronous rotation; filling supply means adapted for supplying the filling into the product forming zone between the ribbon-like strips and having a wedge-shaped fragment oriented with the apex toward the product forming zone, the following main and particular distinguishing features.

The device for rolling the food product and the stamping mechanism can be made according to any of the above described embodiments.

Housing support element can be rigidly connected with the base support element or made with it in one piece.

It is advisable that the relative orientation of the drums and the wedge-shaped fragment was such that the minimum distance between their surfaces was approximately equal to 2 mm

The zone of product formation is located in the immediate vicinity opposite each other of the cell drum of the punching mechanism, made with a given shape of the inlets.

A device for the manufacture of semi-finished products may further comprise a pump adapted for supplying the filling to the filling supplying means, it being expedient to associate it with the filling supplying means by pipelines with their number according to the number of rows of cells on the guide cylindrical surface of the drum.

The device may further comprise a conveyor kinematically connected with the stamping mechanism.

It is advisable that the means for supplying the filling was made in the form of a molded or stamped part, inside of which at least one tube made of a polymeric material is placed, along which the filling is fed into the formation zone of the products.

It is advisable that the tube is curved curved.

It is desirable that the sides of the wedge-shaped fragment facing the strip-like strips are curved curved so that the intersection lines of the surfaces of the sides with the plane perpendicular to the axes of rotation of the shaft drums are circular arcs facing the convex sides to one another, which are essentially concentric with the opposite circumferential arcs of the surface circles drums.

BRIEF DESCRIPTION OF THE DRAWINGS

Hereinafter, for the purposes of this utility model, a food rolling device is identified as rolling.

This utility model will be described in more detail using various options for its implementation with reference to the accompanying drawings, in which:

Figure 1 schematically shows a side view of the first embodiment of the possible options for the design of rolling.

Figure 2 schematically shows a rear view of the first variant of rolling, applicable to all possible options for its design.

Figure 3 schematically shows a front view of the first embodiment of the possible options for the design of the rolling, applicable to all possible options for its execution.

Figure 4 schematically shows a side view of the second variant of the possible options for the design of rolling.

Figure 5 schematically shows a side view of a third embodiment of the possible options for the design of the rolling.

Figure 6 presents one of the possible options for mounting an eccentric support, where 6a is a front view, 6b is a side view.

Figure 7 shows another possible option for mounting an eccentric support, where 7a is a front view, 7b is a side view.

Fig. 8 is a schematic front view of an auxiliary plate illustrating the relationship of the housing bearings of the rolling bearings to the auxiliary plate.

Figure 9 presents a possible embodiment of the traction element intended for mounting the motor gearbox.

Figure 10 presents a side view of a possible embodiment of a device for the manufacture of semi-finished products from dough with filling.

Figure 11 schematically shows a rear view of a possible embodiment of a device for the manufacture of semi-finished products from the dough with the filling shown in figure 10.

On Fig schematically presents a front view of a device for the manufacture of semi-finished products from dough with filling, shown in figure 10.

On Fig schematically presents a possible embodiment of the meat feeder (cut in a plane passing along the line of mating surfaces of the drums).

On Fig presents one of the drums in the plane of the cross section perpendicular to the axis of its rotation, explaining the implementation of the ejector, providing the pushing of semi-finished products from the cells.

EXAMPLE OF IMPLEMENTATION OF A USEFUL MODEL

Made in the form of a single mechanism, the rolling 1 according to the first embodiment, shown in Fig. 1, Fig. 2 and Fig. 3, comprises two upper shafts 3 and 4 mounted on a supporting housing element 2, on which two upper rollers are placed respectively 7 and 8, as well as two lower shafts 5 and 6, on which the two lower rollers 9 and 10 are placed, while in Fig. 1, from the side of the observer, the shaft 4 and the roller 8 are located behind the shaft 3 and the roller 7, respectively. Each shaft is installed in its bearing assembly 11 (for brevity, all identical whether similar bearing assemblies designated a reference numeral), and each roller is fixed against rotation on the corresponding spline shaft 12 (indicated by a single position). The axis of rotation of the spaced apart and cantilever mounted in pairs on top of each other shafts are essentially parallel to each other.

The supporting housing element 2, having the front facing the rollers and the opposite rear side thereof, is made in the form of two vertically mounted housing plates 13 (front) and 14 (rear), made with through holes for the passage of the shafts. The plates 13 and 14 spaced apart from each other at a preselected distance H are rigidly interconnected by four racks 15 located at the corners of the plates (indicated by one position and one of the upper racks is shown in the figures).

The preselected distance H by which the front plate 13 of the supporting housing element 2 located on the roll side is spaced along the axis of rotation of the shaft from the opposite rear plate 14 is selected from a range of 40-60 mm, preferably 42-45 mm.

Between the plates 13 and 14 there are placed two upper bearings 16 and 17 associated with them, as well as two lower bearings 18 and 19 for the bearing assemblies 11, respectively, of the upper shafts 3 and 4 and the lower shafts 5 and 6.

For bearing assemblies 11, tapered or radial thrust bearings with high bearing capacity can be used.

The thickness of the metal case plates 13 and 14 made of thick sheet steel is selected from the range of 12-18 mm, preferably 14-16 mm. Case plates can be made of any suitable material, including non-ferrous metal alloys, for example aluminum alloys, and their thicknesses measured along the direction of the shafts can be the same or different.

The surfaces of the plates lie in substantially parallel planes that are substantially perpendicular to the axes of rotation of the shafts.

From the end side facing the support body element 2, the rollers 7, 8, 9 and 10 are pressed against a vertically mounted first pressure plate 20 through which all shafts are passed and which is spaced from the front plate 13 (i.e., from the body support element 2) along the axis of rotation of the shaft at a predetermined distance h1 with the formation of a gap 21, and on the other end side of the roller 7, 8, 9 and 10 are pressed to the second pressure plate 22.

In all variant embodiments, the predetermined distance h _{1 is} selected from a range of 15-60 mm, preferably 18-30 mm. The thickness of the first and second pressure plates 20 and 22 is selected from the range of 7-20 mm, preferably from the range of 8-12 mm, while the height of the first pressure plate 20 may exceed the height of the second pressure plate 22.

The pressure plates 20 and 22 may be made of thick stainless steel sheet or any other suitable material approved for use in the food industry or may have a corresponding coating, and their thicknesses measured along the direction of the shafts may be the same or different.

The surfaces of the pressure plates facing the end surfaces of the rollers lie in substantially parallel planes that are perpendicular to the axes of rotation of the shafts.

The first pressure plate 20 is rigidly connected to the body plate 13 (i.e., with the support body element 2) by four racks 23, and to the second pressure plate 22 by means of the space passing in the internal volume bounded by the surfaces of all the rollers, by the rack element 24 (shown in FIG. .3), passed through the second pressure plate 22 and secured with a clamping element 25, pressing the plate 22 to the end surface of the rollers. The end parts of the upper shafts 3 and 4 located on the side of the second pressure plate 22 are placed in the openings of the second pressure plate 22 with free sliding, and the end parts of the lower shafts 5 and 6 do not protrude beyond the rollers.

The shafts 3, 4, 5 and 6 have a kinematic connection, which is closed on a power drive made in the form of a motor reducer 26. The kinematic connection is built on the basis of a gear train (Fig. 2) in the form of gears located on the rear side of the plate 14 (i.e., the back side of the base support element 2) and connected with shafts 3, 4, 5 and 6, respectively, 27, 28, 29 and 30 so that any two adjacent shafts rotate towards each other as shown by the arrows in FIG. 2. One of the shafts (in this embodiment, the shaft 3) can be leading from the motor-reducer 26. Such a rotation of the shafts can be provided by another gear, for example a chain. Gearmotor 26 may be coupled to a frequency converter (not shown).

The synchronous rotation of the rollers can be provided in another way, for example, using two motors.

As shown in figure 3, forming the first pair of rollers 7 and 8, placed on the upper pair of shafts 3 and 4, respectively, are installed with the first specified gap 31 between the working surfaces. Rollers 9 and 10 forming a second pair, located on the lower pair of shafts 5 and 6, respectively, are installed with a second predetermined gap 32 between the working surfaces of the rollers.

The first pair of rollers is mounted above the second pair of rollers in such a way that between the working surface of the roller 7 of the first pair and the working surface of the opposite pair on the same side relative to the conventional plane passing through the gaps 31 and 32 of the roller 9 of the second pair, a working gap 33 is formed, and between the working a working gap 34 is formed by the surface of the roll 8 of the first pair and the working surface of the roll 10 of the second pair, opposite the roll 8 on the same side relative to the same conditional plane. Working gaps 33 and 34 are designed to exit entoobraznyh bands sheetable product.

The size of the first gap 31, which is adapted to receive incoming from the tray 35 (figure 1) of the workpiece rolled product exceeds the size of the remaining gaps. The size of the second gap 32 has the smallest value in comparison with the size of other gaps and is selected minimally sufficient to ensure free rotation of the rollers 9 and 10.

The size of the working gaps 33 and 34 is selected based on the required thickness of the tape-like strips of the product. Depending on the type of workpiece, the minimum value of the first predetermined gap 31 may lie within the doubled thickness of the product-like product strips emerging from the working gaps 33 and 34, while its maximum value may lie within the quadruple thickness of the product strips.

For rolling, for example, dough for dumplings or dumplings, the value of the first predetermined gap 31 may lie within 2-7 mm, preferably 3-5 mm, while the value of the second predetermined gap 32 may lie within 0.1 mm - 1.5 mm, despite the fact that the size of the workers

Clearances 33 and 34 may lie in the range 0.2-0.7 mm, preferably 0.3-0.5 mm.

The surface sections of the rollers 7, 8, 9, and 10 facing each other, together with the surfaces of the pressure plates 20 and 22 located at their ends (FIG. 3), limit the pressure zone 36 for the product blank entering it.

The rack element 24 located in the increased pressure zone 36, having in this embodiment a smooth cylindrical surface, on the one hand serves to force-close the roller package from the end sides by the pressure plates 20 and 22, and on the other hand helps to move the workpiece along the axis of the rollers, i.e. . promotes mixing of the rolling mass, improving its structure and increasing uniformity. The rack element 24 may have a different shape, for example, its surface can be made in the form of a surface of a polyhedron or a cylindrical surface with grooves. The diameter of the rack element 24 may be selected from a range of 10-22 mm, preferably 14-16 mm.

The second embodiment of the rolling shown in Fig. 4 differs from the embodiment shown in Fig. 1 by another embodiment of the support housing element 2. The support housing element 2 in this embodiment is made in the form of a vertically mounted housing plate 37 having through holes for receiving shafts 3, 4, 5 and 6. The side of the plate 37 facing the rollers (the front side of the supporting housing element 2) is made with a substantially flat surface, and the opposite side (the back side of the supporting housing element 2) is provided with protruding components that enclose the openings of the housing plate 37 and are made in the form of tubular elements 38 oriented longitudinally to the axis of rotation of the shafts (for brevity, all four tubular elements are denoted by one position) adapted to hold bearings 16, 17, 18 and 19 of the bearing assemblies 11, on which shafts 3, 4, 5 and 6 are mounted, respectively. The tubular elements 38 can be made with a radial wall thickness varying along the axis of rotation of the shaft with a gradual increase in its value in the direction from The serial to the end plate 37 (i.e. to its base) so that the outer surface of the tubular is essentially the surface of a truncated cone.

Plate 37 with tubular elements 38 may be made in the form of a single cast or welded part. The plate 37 is made with its minimum thickness lying in the range of 12-18 mm, preferably 14-16 mm, and the height of the tubular elements 38 (i.e. the distance by which they extend beyond the back surface of the cabinet plate 37) may lie within 30-70 mm, preferably 32-38 mm. For the case plate 37, the same materials can be used as for the case plates 13 and 14.

In the second embodiment, an embodiment (not shown) is possible in which the pressure plate 20 can be made in the form of a raised plate, not separated from the housing element (i.e., from the plate 37) or made with it in one piece.

In the third embodiment shown in FIG. 5, the supporting housing element 2 is made in the form of one housing plate 37 with tubular elements 38 similarly to the second embodiment. The first pressure plate 20, as well as in the first and second embodiments, is assigned from the front side of the body plate 37 (i.e., from the body support element 2) to a distance h ₁ defining the gap 21. The end parts of the pressure plate 22 located on the side of the pressure plate 22 the shafts passed through it and protrude beyond the second pressure plate 22, and their peripheral sections passed through the auxiliary plate 39, placed behind the second pressure plate 22 at a selected distance h ₂ from it with the formation of a gap 40. The end parts of the shafts are supported by and bearings placed in the housing bearings 41 installed in the holes of the auxiliary plate 39.

The selected distance h ₂ may be selected from a range of 15-60 mm, preferably from a range of 18-30 mm. In various embodiments of this embodiment, a predetermined distance h ₁ and a selected distance h ₂ may have substantially the same or different values. The thickness of the subplate 39 can be selected from a range of 15-60 mm, preferably from a range of 30-36 mm. In addition, in the manufacture of an auxiliary plate, the same materials can be used as for case plates.

The overall dimensions (width and height) of the auxiliary plate 39 in the plane perpendicular to the axes of rotation of the shafts may be the same with the dimensions of the second pressure plate 22 or differ from them.

In the third embodiment, an embodiment (not shown) is possible in which the pressure plate 20 can be made in the form of a raised plate, not separated from the housing element (i.e., from the plate 37) or made integrally with it.

For the third embodiment, the rolling is also possible such an embodiment (not shown), in which the housing support element 2, in contrast to the one shown in figure 5, can be made in the form of two housing plates, similar to its execution, shown in figure 1.

The length of the rollers can be selected from a range of 20-350 mm. The preferred range for rolling dough for dumplings or dumplings is a range of 70-250 mm.

It was found that the diameter of the cylindrical surfaces of the rollers in any embodiment can be selected from the range of 50-120 mm, preferably 65-80 mm. The most optimal range for rolling dough for dumplings or dumplings is a range of 70-75 mm. The diameters of all the rollers can be essentially the same size, and the gap between any rollers can be adjustable.

The regulation of the size of the working clearances for changing the thickness of the outgoing ribbon-like strips when adjusting the rolling can be carried out by selecting at least two rollers with different diameters. So, for example, when rolling dough for dumplings to form working gaps with a value of approximately 0.5 mm, the diameters of the rollers of the upper pair can have a value of approximately 71.6 mm, while the diameters of the rollers of the lower pair can have a value of approximately 71.4 mm For the formation of working gaps with a value of approximately equal to 0.4 mm, the diameters of the rollers of the upper pair can have a value of approximately equal to 71.8 mm while the diameters of the rollers of the lower pair are approximately equal to 71.4 mm. For the formation of working gaps with a value of approximately 0.3 mm, the diameters of the rollers of the upper pair can have a value of approximately 71.8 mm, while the diameters of the rollers of the lower pair can have

approximately equal to 71.6 mm. In this case, six rollers can be included in the rolling kit. An increase in the number of interchangeable rollers increases the number of combinations of their diameters to control the size of the gaps.

The selection of combinations of rollers with different diameters allows rolling out to be more reliable and easy to use, since it eliminates the need to control the size of the gaps during operation using various blocks for adjusting the center distance between the shafts.

According to any embodiment of any embodiment, all the bearings of the bearing assemblies can be rigidly connected to the housing support element so that it is not possible to change the position of the axis of rotation of the shaft or linear movement of the axis of rotation of the shafts relative to each other. In these embodiments, in cases of rolling with the auxiliary plate, the body supports 41 can be mounted motionless relative to the auxiliary plate 39 with a tight fit in its holes.

In any embodiment, the gaps between the rollers can be made adjustable by shifting the axial lines of the corresponding pair of shafts relative to each other to diverge or approximate the selected pair of shafts to each other and thereby change the gap without changing the rollers. The adjustment can be performed by linearly moving the bearings of the respective shafts relative to each other using, for example, lever devices. The most optimal in cases of adjusting the center distance of the shafts is the use of eccentric bearings of the bearing units. In eccentric bearings, the bearing seat is made with eccentricity relative to the common center of the bearing, which allows you to change the position of the axial line of the corresponding shaft by turning the support around its axis of rotation in a predetermined angular range and fixing in the selected angular position. The support is fixed relative to the fixed housing element 2 in the selected position can be carried out in any suitable way directly or indirectly, for example, by means of a threaded connection. For this, the eccentric support can be provided with an open

from the outside of the support with a threaded hole for communication with fixing means having a mating thread.

As shown in FIG. 6, for the case of the supporting housing element 2 in the form of a housing plate 37 with tubular elements 38, an arcuate through groove is made extending in the radial direction relative to the axis of rotation of the support 19 in the tubular element 38 within the predetermined angular range (angle φ) 42, through which the fastening means 43 protruding beyond the outer surface of the tubular element 38 and having a thread allowing it to be screwed into the mating thread of the holes 44 of the support 19. By means of the fastening means 43 into in the free state of the support, it can be rotated in the desired direction within the angular range φ determined by the length of the groove 42, and then fixed in the selected angular position under the action of exerting a clamping force on the fixing means 43. The thickness of the support is selected so as to ensure reliable fixation of the support in the position selected after rotation and rigid connection with the housing support element.

It may be sufficient to limit the arcuate groove 42 of the angular range φ with a value of 90 °.

To perform (shown in Fig. 1) the support housing element 2 in the form of spaced and rigidly interconnected two housing plates, the eccentric support is also equipped, as shown in Fig. 7, with a threaded through hole 44 made in its radial direction, and limiting angular the rotation range φ of the groove 42, through which the fastening means 43 is passed, is made in an arcuate bracket 45, interconnected with a portion of the outer surface of the support and pivotally mounted on an axis 46, which is rigidly connected with the housing plates 13 and 14.

In embodiments of rolling with an eccentric support for the bearing assembly and a housing support 41 located in the front plate 39 (Fig. 5), the corresponding hole in the front plate has a configuration that allows the housing bearing mating with the pressure plate to move in the direction of movement of the shaft rotation axis while the auxiliary plate 39 is provided with at least one

a fastener designed to fix the bearing housing 41 of the bearing in a selected position relative to the axis of rotation of the shaft.

For the case of adjusting the working gaps 33 and 34, both supports 18 and 19 of the lower shafts, respectively 5 and 6, can be made eccentric. The contour of the holes 47a and 47b, the auxiliary plate 39, as well as the housing supports placed 41a and 41b, respectively, in the plane perpendicular to the axis of rotation of the shafts can be outlined in circles, while the radii of the holes 47a and 47b exceed the radii of the outer cylindrical surfaces of the housing supports 41a and 41b so that a clearance 48 is formed, which is necessary for the simultaneous movement of the body supports 41 simultaneously with the shafts 5 and 6 with the parallel transfer of the axes of rotation of the shafts. In the plate 39, additional through threaded holes are made, extending in the radial direction relative to the axis of rotation of the shaft and adapted to receive threaded fasteners 49 (respectively 49a and 49b) that are screwed when fixing the supports 41. Each of the supports 41 is fixed by two, located at right angles to each other to a friend, fasteners 49.

In embodiments of rolling with one eccentric support for adjusting one gap and changing the distance between the axes of rotation of the shafts in a conditional plane in which the axis of rotation of the shafts lie, parallel to the transfer of the axis of rotation of one shaft by moving it together with the bearing housing of the bearing, the contour of the hole 47 in the conditional plane, perpendicular to the axis of rotation of the shaft can be outlined by an oval, the major axis of which is located on a conditional line passing through the points of intersection of the axes of rotation of the shafts with the conditional plane. In this case, the fixation of the housing support 41 can be carried out by one fastening element 49, placed in an additional through threaded hole, extending in the radial direction relative to the axis of rotation of the shaft along the line of the major axis of the oval.

In any embodiment, to reduce friction between the pressure plates 20 and 22 and the end surfaces of the rollers, it is preferable to provide the supporting surfaces of the plates (i.e., sections adjacent to the end surfaces of the rollers) with an anti-friction coating or

antifriction linings. So, for example, fluoroplastic gaskets 50 can be installed (Fig. 5).

In any embodiment, to prevent sticking or twisting on the surface of the upper rollers 7 and 8 emerging from the gaps 33 and 34, respectively (Fig. 3), of ribbon-like product strips, scraper elements (one for each roll) 51 and 52, respectively, can be provided, made in the form of plates spring-loaded against the rollers 7 and 8. respectively. Scraper elements 51 and 52 can extend longitudinally to the axes of rotation of the rollers and at the same time be mounted on racks 53 and 54, respectively, located over the outgoing strip Ukta and fixed with the possibility of rotation on the second pressure plate 22.

In addition, to prevent sticking or twisting of the ribbon-like product strips on the surface of the lower rollers 9 and 10, scraper elements 55 and 56 can be provided mounted on racks located under the product strips 57 and 58, respectively.

The scraper elements are arranged so that each ribbon-like product strip can freely pass from the working gap to the selected position (for example, to the product forming zone), and the plates are installed in such a way that the edge part of the scraping plate facing the ribbon-like product strip lies in a plane spaced from the axis rotation of the drum to a distance that is less than the radius of the drum by a specially selected value. It is empirically established that it is advisable to choose this value from a range of 2-4 mm.

Scraper elements can be made of stainless steel sheet or of polymeric material, for example, organic glass 1-2 mm thick.

Additionally, the device may include a preliminary rolling unit of the product blank, configured to receive a blank of material with a thickness exceeding the gap 31, adapted for receiving it (not shown).

The device can be configured to change the ratio of linear velocities of the working surfaces of the rollers, for which

it can be equipped with a frequency converter well-known in the art (not shown).

Providing rotation of the shafts, the housing of the motor gearbox 26, for a stable fixed position can be provided with a pulling element 59, shown in Fig.9 and made in the form of a support part 60, rigidly connected with one end of the holding part 61, made in the form of a strip. The supporting part 60 is made in the form of an arcuate bracket, which comes into surface contact with a part of the end surface of the gearbox flange 62 and is fastened to it by fasteners 63. The second end of the holding part 61, oriented radially to the arc of the part 60, can be fixed on the base 64 associated with the housing by plates or can be fixed on case plates. The holding part 61 and the supporting part 60 can be made in one piece.

In any embodiment, for rolling rollers to rotate, the rolling may include other drive means providing synchronous rotation of all the rollers so that in each pair the rollers rotate towards each other.

The design of rolling allows you to use it not only for rolling dough of any consistency (dumplings, bread), but also for other suitable products, such as cottage cheese, curd mass or slightly warmed marmalade.

A device for the manufacture of semi-finished products from dough with filling, shown in figure 10 - figure 12, contains placed on the base support element 65 of the stamping mechanism 66, placed above it rolling 1, made in the form of a single mechanism for the formation of two ribbon-like strips of material shells, the means for supplying the filling 67 (hereinafter referred to as the meat feeder 67), adapted for supplying the filling into the product formation zone between the ribbon-like dough strips, as well as a pump (not shown), which provides the filling with Anna speed farshepitatel 67.

The rolling 1 can be performed in accordance with any of the above options for its execution.

In addition, in variant versions of the device, it is possible to perform rolling in the form of two mechanisms. It is possible to feed the pre-forming mechanism 66 into the forming zone

prepared ribbon-like test strips, i.e. pre-rolled, wound in the form of rolls and placed above the punching mechanism 66.

In the design of the device shown in figure 10, the rolling 1 is made according to its third embodiment.

The stamping mechanism 66 is made in the form of two drums 68 and 69 mounted on the base support element 65 with the possibility of rotation towards each other. The drums 68 and 69 are placed on the shafts 70 and 71, respectively, each of which is mounted in the bearing assemblies 11 of the bearings 72 and 73, respectively. The bearing assemblies are indicated by the same numeral 11 as the rolling bearing assemblies 1 and can be made in a similar manner.

The basic support element 65 shown in FIG. 10 is made similar to the embodiment of the housing support element 2 of the rolling 1, i.e. in the form of one body plate 65 with tubular elements adapted to hold the supports 72 and 73. The tubular elements of the plate 65 are made similarly to the tubular elements 38 of the rolling plate 37 (second embodiment) and are denoted by the same position.

From the end side facing the base support member 65, the reels 68 and 69 are pressed against a vertically mounted face plate 74 through which the shafts 70 and 71 are passed and which is spaced from the front side (i.e. facing the drums) of the base support member 65 along the axis of rotation of the shaft at a predetermined distance h ₃ with the formation of a gap 75.

The basic support element 65 of the punching mechanism 66 can be performed according to the type of execution of the housing element 2 of the rolling 1 in accordance with the first embodiment of the rolling.

The thickness of the body plates of the base support element 65 may lie within the same limits as the thickness of the body plates of the body support element 2 of the rolling 1.

In variant designs, due to technological features of the process, the supporting housing element 2 of rolling 1 and the basic supporting element 65 of the punching mechanism 66 may have the same or different design. For example, casing

rolling element 2 can be made in accordance with its execution according to the first embodiment of rolling 1, or vice versa, the basic support element 65 of the stamping mechanism 66 can be performed according to the type of housing element 2 of rolling 1 in accordance with the first embodiment of rolling.

In the embodiment shown in FIG. 10, the basic support element 65 of the stamping mechanism 66 and the support housing element 2 of the rolling 1 are integrally formed as a single part, and the predetermined distance h _{1 of the} rolling 1 is equal in magnitude to the predetermined distance h _{3 of the} stamping mechanism 66.

In embodiments, the supporting housing element 2 and the basic supporting element 65 can be made with differing from each other distance values h ₁ and h ₃ .

In embodiments, the housing support member 2 and the base support member 65 may be spaced apart from one another in the vertical or horizontal direction. Housing support element 2 and the basic support element 65 may have a different design and be rigidly interconnected. In addition, the housing support element 2 and the basic support element 65 can be fixed on different or one common basis.

The end parts of the shafts 70 and 71 extending beyond the drums 68 and 69, located on the front side of the base support member 65, are passed through a front plate 76 located at a predetermined distance h ₄ from the end surface of the drums 68 and 69 facing it to form a clearance 77 , while these end parts of the shafts 70 and 71 are based on bearings of the body bearings 78 and 79 installed in the holes of the front plate 76.

The pre-selected distance h ₄ for the gap 77 is selected from a range of 15-60 mm, preferably 18-30 mm.

The thickness of the front plate is selected from a range of 15-60 mm, preferably 30-36 mm.

In an embodiment, the stamping mechanism can be made with a basic support element in the form of a case plate with tubular

elements and not equipped with housing bearings with bearings for shafts.

Shafts 70 and 71 have a kinematic connection, which is closed on a power drive made in the form of a motor reducer 80 (Fig. 10). The kinematic connection is built on the basis of a gear train (Fig. 11) with the gears 81 and 82 located on the rear side of the base support element and connected to the shafts 70 and 71, so that the shafts rotate synchronously towards each other. One of the shafts (in this embodiment, the shaft 71) is leading from the motor-reducer 80. Such a rotation of the shafts can be provided by another transmission, for example chain. Synchronous rotation of the shafts can be provided in another way, for example, using two motors.

Under the drums on the auxiliary shafts 83 and 84 fixed to the base support element 65, installed one below each drum, brushes 85 are placed (indicated by one position). Auxiliary shafts 83 and 84 (Fig. 11) are kinematically connected by auxiliary gears 86 and 87, respectively, with gears 81 and 82 of the drums through intermediate gears 88 (indicated by one position) so that rotation from gears 81 and 82 is transmitted to the auxiliary shafts to allow rotation of the brushes 85 simultaneously with the rotation of the reels.

As shown in FIG. 11, a conveyor belt 89 is placed under the reels, one of the rollers 90 (indicated by one position) of which is connected by a chain gear 91 to one of the auxiliary shafts.

The drums with the accuracy of manufacturing errors can be identical and installed with the mating of their outer cylindrical surfaces along a line lying in the same plane with the axes of rotation of the drums. From both edges, both drums may include selections. The front plate 76 can be made with a curved neckline 92 located between the holes for the body supports (Fig. 12), which provides affordable monitoring of the contact area of the outer surfaces of the drums and the product forming zone.

Providing rotation of the shafts of the housing of the gear motor 80 for a stable fixed position can be equipped with a traction

element made similar to the traction element 59 of the rolling 1, shown in Fig.9.

In addition, the rolling 1 can be equipped with two stiffening elements 93 and 94 arranged at an angle to each other.

The stamping mechanism may be provided with at least one unit for adjusting the relative position of the drums.

The adjustment unit may provide for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which the axis of rotation of the shafts lie by parallel transfer of the axis of rotation of at least one shaft by its movement together with the housing support 78, while the corresponding hole of the front plate (similar to hole 47 the auxiliary plate of rolling 1, as shown in Fig. 8a), has an oval contour that allows moving the bearing housing 78 connected to the front plate in the direction of movement of the shaft. The housing support 78 (Fig. 12) is fixed in the selected position of the shaft by the fastening element 95 similarly to fixing the housing supports of rolling 1.

The adjustment can be performed by linearly moving the bearings of the respective shafts relative to each other using, for example, lever devices. The most optimal in cases of adjusting the interaxal distance of the shafts is the use of eccentric bearings of bearing units made similar to eccentric bearings of rolling 1, the fixing of which is provided depending on the design of the basic support element 65.

The drums can be mounted with the possibility of movement during commissioning of at least one of them along the axis of rotation of the shaft.

Particular attention is paid to the relative positioning of the drums. Preferred is their mutual arrangement in which they are in contact with their generators or between those there is a gap of the order of 0.02 mm when they are parallel. For this, an angular adjustment unit for the relative position of the drums is used, which provides for the possibility of angular displacement of one of the drums relative to the shaft on which it is mounted. For this, the hub of the gear of one of the shafts can be made with the possibility of its rotation relative to the gear.

As bearings, tapered roller or ball angular contact bearings are used.

The product formation zone is the semi-finished product molding zone, into which test strips and filling are fed - opposite molding cells 96 (Fig. 10) on drums located in close proximity opposite each other.

The inlet holes of the molding cells 96 on the cylindrical surface of the drum are distributed in rows along the guide of the cylindrical surface with a given number of rows in the direction along the generatrix of the cylindrical surface of the drum.

The shape of the inlet of the cells of the drums depending on the desired shape of the product can be oval, round, elliptical or in the form of a semicircle, or in the form of a crescent. At the same time, at least a part of such holes can be surrounded by an annular ledge — a perimeter sample, the working surface of which is designed to form the edge part of semi-finished products. The most technologically advanced is the implementation of round holes with sampling around the perimeter, having the same width around the entire perimeter. The number of cells that can simultaneously be crossed by the generatrix of the cylindrical surface of the drum can be more than 1, and the cells can be staggered on the surface of the drum. The most optimal is to perform an even number of rows on the generatrix of the cylindrical surface of the drums with an even number of cells in one row. Neighboring cells, if they are not round, can be mirrored.

The stuffer 67, placed above the stamping mechanism 66, is made with a wedge-shaped fragment oriented with its apex toward the product formation zone.

The lateral sides 97 and 98 (11) of the wedge-shaped fragment of the meat feeder 67 turned towards the cylindrical surfaces of the drums are curved curved so that the intersection lines of the surfaces of the sides with a plane perpendicular to the axis of rotation of the shaft drums are convex sides

to each other arcs of circles, essentially concentric with opposing arcs of circles of the surfaces of the drums.

The relative orientation of the drums and the meat feeder can be such that between the surface of the side of the wedge-shaped fragment and the surface of the drum facing it, a gap is provided for the strip-like strip to pass, with a minimum distance between these surfaces of approximately 2 mm.

The meat feeder 67 can be made with one input for introducing the filling into it through a pipeline from a meat pump (not shown) and one or more channels 99 for filling distribution located inside the meat feeder 67. The number of channels 99 of the distribution of the filling is determined by the number of rows of cells 96 along the generatrix of the cylindrical surface of the drum.

The most optimal in the case of several channels 99 for the distribution of the filling may be such a design of the meat feeder 67, which is shown in Fig. 13, where each channel 99 of the filling distribution is connected to the meat pump with a separate pipe 100. In this case, the meat feeder 67 can be made in the form of a cast or stamped parts in which at least one channel 99 of a polymer material tube is formed, along which the filling is fed into the product forming zone. Each tube 99 is connected to its pipe 100, located on the end side of the meat feeder 67, and bent towards the wedge-shaped fragment.

At the output of the stuffing pump or at the inlet of the stuffer 67 (in the case of the stuffing pump with one pipe), an adjustable shutter valve can be installed that can control the filling pressure in the chamber.

The stamping mechanism 66 is equipped with ejectors located in each cell 96, which can be made in various ways, for example, in the form of gravitational ejectors known from the prior art and widely used.

In the preferred embodiment shown in Fig. 14, the ejector is made in the form of several interconnected parts, one of which is the ejector element 101 is made in the form of a plate, which has

an external contour corresponding to the shape of the inlet of the cell 96 to the perimeter. The ejector element 101 is placed in the cell 96 with the possibility of free movement along the generatrix of the cylindrical surface of the cell in the forward direction, i.e. towards the inlet of the cell 96 and in the opposite direction within the stroke of a given value and without going beyond the cell 96.

The ejector element 101 is mounted on a flat elongated longitudinally guiding cylindrical surface of the cell supporting element 102 (rod), which is rigidly connected to the flat oval-shaped element 103 surrounding the shaft 70 located in the drum cavity (for example 68). The oval-shaped element 103 is made like a flat washer and has two essentially flat surfaces, as well as an inner end face facing the shaft and an outer end face opposite it. On flat surfaces, its contour is bounded by two ovals spaced a given distance, while the oval facing the shaft has a small diameter d measured along the axis of its small axis and a large diameter D measured along the axis of the major axis.

The stroke of the ejection element 101 can be defined as the difference between the large diameter D and small diameter d, and its predetermined value can be selected from the range of 10-25 mm, preferably 12-18 mm. For example, with a D value of approximately 81 mm and a d value of approximately 66 mm, the stroke will be approximately 15 mm.

The thickness of the oval-shaped element 103, determined by the distance between its flat surfaces, can be selected from a range of 1.5-2.5 mm, preferably 1.8-2.0 mm. The predetermined distance over which the ovals can be spaced is selected from a range of 5-12 mm, preferably 7-8 mm.

Elongated radially outward with respect to the oval-shaped element 103, the supporting elements 102 are fixed in pairs on opposite sides of the oval-shaped element 103 along the line of its minor axis d. In this case, the ejection elements 101 are located in opposite cells of the drum (in diameter). In this particular embodiment, the oval-shaped element 103 with two flat supporting elements 102 is made in the form of a single flat part. It is also possible their implementation in the form of separate, but rigidly interconnected parts.

To ensure the movement of the ejector element 101 during the period of its movement in the forward direction (for ejecting the finished product from the cell 96) in the lower part (i.e., under the hub of the drum) of the internal volume of each drum, a biasing element 104 is made in the form of a fixed rod, cantilever mounted on the base support element 65 and interacting with the inner end surface of the ellipse-shaped element 103. The biasing element 104 can be mounted with the possibility of adjusting its position I am relative to the axis of rotation of the drum, which is performed by known methods.

The device operates as follows.

The step of forming ribbon-like bands of the product is performed simultaneously with the step of forming products. The dough piece supplied from the rolling tray 35 to the gap 31 between the rollers 7 and 8 is drawn by them into the pressure zone 36, from which it is drawn into the gaps 33 and 34. Rolling along the line forming the cylindrical surfaces of the rollers, the dough piece leaves the gaps 33 and 34 in the form of two ribbon-like test strips. At the initial moment of operation, as well as in the case of rupture of the strips, one pair of scraper elements (51 and 52) deflects the strips down, and the other pair of opposite scraper elements 55 and 56) does not allow them to twist on the lower rollers. Tightened by drums 68 and 69, ribbon-like test strips pass into the gaps between the surfaces of the drums and the corresponding surfaces of the sides of the wedge-shaped fragment of the meat feeder 67, getting into the product formation zone, where between them through the distribution channels of the filling 99 of the meat feeder 67 by the jet (one or more depending on the number of channels ) a filling is extruded that extrudes ribbon-like strips into the forming cells 96.

During the rotation of the drums and simultaneously with the formation of the products in the forming cells, they are pressed by the cylindrical surfaces of the drums to seal the products with the closure of the filling inside the test shell. When sealing products at the time of pressing, the test shells are squeezed, the forcemeat stream is cut off and the forcemeat is squeezed out of the narrow edge part of the product partially inward

molded product, further stretching the dough, and partially in the next product.

When the drums rotate, the inner end surface of the oval-shaped element 103 runs on the biasing element 104 and the lower ejector element 101 is pushed forward to displace the formed product from the cell downward, and the rotating brushes 85 beat the products hanging on the drums to the conveyor 89.

The proposed design is characterized by high reliability, compactness, simplicity of the circuit and operation, ease of maintenance and provides high performance with high quality of the obtained products from the test shell with the filling. The device is easily retoolable for the manufacture of products of various shapes, such as dumplings, dumplings with various fillings. Compared with known devices, the design minimizes the loss of dough pieces.

Claims (187)

1. A device for rolling out a food product containing a first pair of rollers placed on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second is formed between the working surfaces of the second pair th predetermined gap, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roll of the first pair and the working surface of the opposite to it on the same side relative to the conventional plane passing through the first and second predetermined roll gaps of the second pair, working gaps are formed , besides, with the first pressure plate connected to the housing support element facing the bearings of the end side of the rollers, through which the shafts of the first and second pairs are passed, then and as on the other end side of the rollers there is a second pressure plate connected to the housing support element, through which shafts of at least one pair are passed, wherein the housing support element is made with two housing spaced apart from each other and rigidly connected to each other plates with through holes adapted to receive bearings of bearing assemblies, characterized in that the first pressure plate is assigned from the housing plate of the housing support element facing it along axis of rotation of the shaft at a given distance. 2. The device according to claim 1, characterized in that the pre-selected distance between the housing plates is selected from the range of 40-60 mm, preferably 42-45 mm 3. The device according to claim 1 or 2, characterized in that the thickness of the at least one body plate is selected from the range of 12-18 mm, preferably 14-16 mm. 4. The device according to claim 1, characterized in that the thickness of the at least one pressure plate is selected from the range of 7-20 mm, preferably 8-12 mm 5. The device according to claim 1, characterized in that the predetermined distance is selected from a range of 15-60 mm, preferably from a range of 18-30 mm. 6. The device according to claim 1, characterized in that it further comprises an adjustment unit for at least one gap between the rollers, providing for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie parallel to the transfer of the axis of rotation of at least , one shaft by moving it. 7. The device according to claim 6, characterized in that the shaft is moved by turning the bearings of the bearing assembly, the bearing being made eccentric and provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to enable the rotation of the support around its axis of rotation within the selected angular range when adjusting the distance and rigid connection of the support with the base support element in the selected position after turning company, though the housing support member is provided in contact with the outer surface of the arcuate bearing bracket with a through slot formed in the circumferential direction of the support. 8. The device according to claim 7, characterized in that the selected angular range is approximately 90 °. 9. The device according to claim 1, characterized in that the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axes of rotation of the shafts. 10. The device according to claim 1, characterized in that the rollers are oriented so that their axis of rotation are essentially parallel to each other. 11. The device according to claim 1, characterized in that for the rotation of the rollers it includes at least one drive means that provides synchronous rotation of all the rollers, despite the fact that in each pair the rollers rotate towards each other. 12. A device for rolling out a food product containing a first pair of rollers placed on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second is formed between the working surfaces of the second pair a predetermined gap, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roller of the first pair and the working surface of the opposite side of it from the same plane relative to the conditional plane passing through the first and second predetermined gaps, the rollers of the second pair are formed working gaps , moreover, with the first pressure plate connected to the housing support element facing the bearings of the end side of the rollers, through which the shafts of the first and second pairs are passed, then and as on the other end side of the rollers there is a second pressure plate through which the shafts of one pair are passed, while the housing support element is made with two housing plates spaced apart from each other in a predetermined distance and with through holes adapted to receive supports bearing assemblies, characterized in that the shafts of the second pair are passed through the second pressure plate, and all the shafts are passed through the second pressure plate so that they extend beyond it, and their end h The parts are mounted in bearings, the housing bearings of which are located in the holes of the auxiliary plate located at a selected distance from the second pressure plate. 13. The device according to p. 12, characterized in that the said selected distance is selected from the range of 15-60 mm, preferably 18-30 mm 14. The device according to item 12 or 13, characterized in that the thickness of the auxiliary plate is selected from the range of 15-60 mm, preferably 30-36 mm. 15. The device according to p. 12, characterized in that in the plane perpendicular to the axes of rotation of the shafts, the dimensions of the auxiliary plate differ from the dimensions of the second pressure plate. 16. The device according to p. 12, characterized in that it further comprises an adjustment unit for at least one gap between the rollers, providing for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie, parallel to the transfer of the axis of rotation of at least , one shaft by moving it together with the bearing housing. 17. The device according to clause 16, characterized in that the shaft is moved by turning the bearings of the bearing assembly, the bearing being made eccentric and provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to enable rotation of the support around its axis of rotation within the selected angular range when adjusting the distance and rigid connection of the support with the base support element in the selected position after orot, despite the fact that the housing support element is provided with an arcuate bracket in contact with the outer surface of the support with a through groove made in the circumferential direction of the support, while the corresponding hole in the front plate for receiving the bearing housing supports has such a configuration that allows the housing to be interfaced with the pressure plate bearing support in the direction of movement of the axis of rotation of the shaft, while the auxiliary plate is provided with at least one extending in the radial direction relative to to the axis of rotation of the shaft through hole, adapted to receive a fastener designed to fix the bearing housing in the selected position. 18. The device according to clause 16, wherein the selected angular range is approximately 90 °. 19. The device according to p. 12, characterized in that the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axes of rotation of the shafts. 20. The device according to p. 12, characterized in that the rollers are oriented so that their axis of rotation are generally parallel to each other. 21. The device according to p. 12, characterized in that for the rotation of the rollers it includes at least one drive means that provides synchronous rotation of all the rollers, despite the fact that in each pair of rollers rotate towards each other. 22. A device for rolling out a food product containing a first pair of rollers located on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second is formed between the working surfaces of the second pair a predetermined gap, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roller of the first pair and the working surface of the opposite side of it from the same plane relative to the conditional plane passing through the first and second predetermined gaps, the rollers of the second pair are formed working gaps , moreover, with the first pressure plate connected to the housing support element facing the bearings of the end side of the rollers, through which the shafts of the first and second pairs are passed, then and as on the other end side of the rollers there is a second pressure plate through which the shafts of one pair are passed, while the housing support element is made with two housing plates spaced apart from each other in a predetermined distance and with through holes adapted to receive supports bearing assemblies, characterized in that the first pressure plate is allocated from the housing plate of the support housing element facing it along the axis of rotation of the shaft by a predetermined distance, the shafts of the second ry passed through the second presser plate, wherein all the shafts are passed through a second presser plate so as to project beyond it, and their end portions mounted on bearings, bearing housing which has openings in an auxiliary plate disposed at a selected distance from the second pressing plate. 23. The device according to p. 22, characterized in that the said selected distance is selected from the range of 15-60 mm, preferably 18-30 mm 24. The device according to item 22 or item 23, wherein the thickness of the auxiliary plate is selected from the range of 15-60 mm, preferably 30-36 mm. 25. The device according to item 22, wherein said predetermined distance is selected from a range of 15-60 mm, preferably 18-30 mm 26. The device according to item 22, wherein the magnitude of said selected distance is substantially equal to the magnitude of said predetermined distance. 27. The device according to p. 22, characterized in that said selected distance is different in magnitude from said predetermined distance. 28. The device according to p. 22, characterized in that in the plane perpendicular to the axes of rotation of the shafts, the dimensions of the auxiliary plate differ from the dimensions of the second pressure plate. 29. The device according to p. 22, characterized in that it further comprises an adjustment unit for at least one gap between the rollers, providing for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie, parallel to the transfer of the axis of rotation, at least one shaft. 30. The device according to p. 22, characterized in that the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axes of rotation of the shafts. 31. The device according to item 22, wherein the rollers are oriented so that their axis of rotation are generally parallel to each other. 32. The device according to p. 22, characterized in that for the rotation of the rollers it includes at least one drive means that provides synchronous rotation of all the rollers, despite the fact that in each pair of rollers rotate towards each other. 33. A device for rolling out a food product containing a first pair of rollers located on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second is formed between the working surfaces of the second pair a predetermined gap, wherein the first pair of rollers is mounted relative to the second pair of rollers in such a way that working gaps are formed between the working surface of the roll of the first pair and the working surface of the opposite side of it on the same side relative to the conventional plane passing through the first and second predetermined roll gaps of the second pair, despite the fact that, with the end faces of the rollers facing the bearings, the first pressure plate connected to the housing support element is located, through which the shafts of the first and second pairs are passed, then and as on the other end side of the rollers there is a second pressure plate connected to the housing support element through which shafts of at least one pair are passed, characterized in that the housing support element is made in the form of a housing plate with through holes for receiving the shafts, while said plate has a side facing the rollers that is identified as the front side, and an opposite side, identified as the back side, despite the fact that the back side of the body plate is provided with enclosing openings ystupayuschimi components made in the form of tubular elements adapted to hold the poles bearing assemblies. 34. The device according to p, characterized in that the minimum thickness of said body plate is selected from the range of 12-18 mm, preferably 14-16 mm. 35. The device according to 33 or p. 34, characterized in that the tubular elements protrude beyond the surface of the back side of the housing plate at a distance selected from the range of 30-70 mm, preferably 32-38 mm. 36. The device according to p. 33, characterized in that the body plate with tubular elements is made in the form of a single cast or welded part. 37. The device according to p. 33, characterized in that the tubular element is made varying along the axis of rotation of the shaft of the radial wall thickness with an increase in the direction from the peripheral end to the surface of the housing plate, so that its outer surface is, essentially, the surface of a truncated cone . 38. The device according to p, characterized in that the thickness of the at least one pressure plate is selected from the range of 7-20 mm, preferably 8-12 mm 39. The device according to p. 33, wherein the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axes of rotation of the shafts. 40. The device according to p. 33, wherein the rollers are oriented so that their axis of rotation are generally parallel to each other. 41. The device according to p. 33, characterized in that it further comprises an adjustment unit for at least one gap between the rollers, providing for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie, parallel to the transfer of the axis of rotation, at least , one shaft by moving it. 42. The device according to paragraph 41, wherein the shaft is moved by turning the bearings of the bearing assembly, and the bearing is made eccentric and provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to enable rotation of the support around its axis of rotation within the selected angular range when adjusting the distance and rigid connection of the support with the base support element in the selected position after Orot, despite the fact that the tubular element, which houses eccentric support is provided with a through slot extending in the circumferential direction of the support. 43. The device according to § 42, wherein the selected angular range is approximately 90 °. 44. The device according to p. 33, wherein the bearings of the bearing assemblies are rigidly connected to the housing support element so that it is not possible to change the position of the axis of rotation of the shaft. 45. The device according to p. 33, characterized in that it further comprises at least two stiffening elements associated with the housing support element and located at an angle to each other. 46. The device according to p. 33, characterized in that for the rotation of the rollers it includes at least one drive means that provides synchronous rotation of all the rollers, despite the fact that in each pair of rollers rotate towards each other. 47. A device for rolling out a food product containing a first pair of rollers placed on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second second is formed between the working surfaces of the second pair a predetermined gap, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roller of the first pair and the working surface of the opposite side of it from the same plane relative to the conditional plane passing through the first and second predetermined gaps, the rollers of the second pair are formed working gaps , despite the fact that the first pressure plate connected to the housing support element is located on the end side of the rollers facing the supports, through which the shafts of the first and second pairs are passed, then yes, how is the second pressure plate located on the other end side of the rollers, through which the shafts of one pair are passed, characterized in that the housing support element is made in the form of a housing plate with through holes for receiving the shafts, said plate having a side facing the rollers, identified as the front side and the opposite side, identified as the back side, despite the fact that the back side of the body plate is provided with protruding components enclosing the holes, made in the form of a tubular x elements adapted to hold the bearings of the bearing units, despite the fact that the first pressure plate is spaced from the front side of the housing plate along the axis of rotation of the shaft by a predetermined distance. 48. The device according to 47, characterized in that the minimum thickness of said body plate is selected from the range of 12-18 mm, preferably 14-16 mm. 49. The device according to clause 47, wherein said tubular elements protrude beyond the body plate at a distance selected from the range of 30-70 mm, preferably 32-38 mm. 50. The device according to item 47, wherein the body plate with tubular elements is made in the form of a single cast or welded part. 51. The device according to clause 47, wherein the tubular element is made with a radial wall thickness varying along the axis of rotation of the shaft with an increase in the direction from the peripheral end to the surface of the housing plate, so that its outer surface is essentially the surface of a truncated cone. 52. The device according to clause 47, wherein said predetermined distance is selected from a range of 15-60 mm, preferably 18-30 mm 53. The device according to item 47, wherein the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axes of rotation of the shafts. 54. The device according to item 47, wherein the rollers are oriented so that their axis of rotation are generally parallel to each other. 55. The device according to clause 47, characterized in that it further comprises an adjustment unit for at least one gap between the rollers, providing for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie parallel to the transfer of the axis of rotation, at least , one shaft by moving it together with the bearing housing. 56. The device according to item 55, wherein the shaft is moved by turning the bearings of the bearing assembly, and the bearing is made eccentric and provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to enable rotation of the support around its axis of rotation within the selected angular range when adjusting the distance and rigid connection of the support with the base support element in the selected position after orot, despite the fact that the tubular element in which the eccentric bearing is placed is provided with a through groove extending in the circumferential direction of the bearing, while the corresponding hole in the front plate for receiving the bearing housing of the bearing has such a configuration that allows to move the bearing bearing housing mating with the pressure plate in the direction of movement of the axis of rotation of the shaft, despite the fact that the auxiliary plate is equipped with at least one extending in the radial direction with respect to the axis of rotation of the shaft An aperture adapted to receive a fastener for fixing the bearing housing in a selected position. 57. The device according to p, characterized in that the selected angular range is approximately 90 °. 58. The device according to clause 47, wherein the bearings of the bearing assemblies are rigidly connected to the housing support element so that it is not possible to change the position of the axis of rotation of the shaft. 59. The device according to clause 47, characterized in that it further comprises at least two stiffening elements associated with the housing support element and located at an angle to each other. 60. The device according to clause 47, characterized in that for the rotation of the rollers it includes at least one drive means for synchronous rotation of all the rollers, despite the fact that in each pair the rollers rotate towards each other. 61. A device for rolling out a food product containing a first pair of rollers placed on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second second is formed between the working surfaces of the second pair a predetermined gap, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roller of the first pair and the working surface of the opposite side of it from the same plane relative to the conditional plane passing through the first and second predetermined gaps, the rollers of the second pair are formed working gaps , despite the fact that the first pressure plate connected to the housing support element is located on the end side of the rollers facing the supports, through which the shafts of the first and second pairs are passed, then yes, how is the second pressure plate located on the other end side of the rollers, through which the shafts of one pair are passed, characterized in that the housing support element is made in the form of a housing plate with through holes for receiving the shafts, said plate having a side facing the rollers, identified as the front side and the opposite side, identified as the back side, despite the fact that the back side of the body plate is provided with protruding components enclosing the holes, made in the form of a tubular x elements adapted to hold the bearings of the bearing assemblies, and the shafts of the second pair are passed through the second pressure plate, and all the shafts are passed through the second pressure plate so that they extend beyond it, and their end parts are installed in bearings, the housing supports of which are located in the holes an auxiliary plate located at a selected distance from the second pressure plate. 62. The device according to p, characterized in that the said selected distance is selected from the range of 15-60 mm, preferably 18-30 mm 63. Device 61 or p. 62, characterized in that the thickness of the auxiliary plate is selected from the range of 15-60 mm, preferably 30-36 mm. 64. The device according to p, characterized in that in the plane perpendicular to the axes of rotation of the shafts, the dimensions of the auxiliary plate differ from the dimensions of the second pressure plate. 65. The device according to p. 61, characterized in that it further comprises an adjustment unit for at least one gap between the rollers, providing for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie, parallel to the transfer of the axis of rotation, at least one shaft. 66. The device according to p. 61, characterized in that the bearings of the bearing assemblies are rigidly connected to the housing support element so that it is not possible to change the position of the axis of rotation of the shaft, despite the fact that the axis of rotation of the said support coincides with the axis of rotation of the shaft, and bearing bearings mounted motionless relative to the auxiliary plate. 67. The device according to p, characterized in that the first pressure plate is made in one piece with the housing element. 68. The device according to p, characterized in that the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axes of rotation of the shafts. 69. The device according to p, characterized in that the rollers are oriented so that their axis of rotation are generally parallel to each other. 70. The device according to p, characterized in that it further comprises at least two stiffening elements associated with the housing support element and located at an angle to each other. 71. The device according to p. 61, characterized in that for the rotation of the rollers it includes at least one drive means for synchronous rotation of all the rollers, despite the fact that in each pair of rollers rotate towards each other. 72. A device for rolling out a food product containing a first pair of rollers placed on a first pair of shafts mounted for rotation in bearings of bearing assemblies connected to a housing support element, and a second pair of rollers placed on a second pair of shafts mounted for rotation in connected with a housing support element of the bearings of the bearing assemblies, while a first predetermined clearance is formed between the working surfaces of the rollers of the first pair, and a second second is formed between the working surfaces of the second pair a predetermined gap, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roller of the first pair and the working surface of the opposite side of it from the same plane relative to the conditional plane passing through the first and second predetermined clearances, the working rollers of the second pair are formed , despite the fact that the first pressure plate connected to the housing support element is located on the end side of the rollers facing the supports, through which the shafts of the first and second pairs are passed, then yes, how is the second pressure plate located on the other end side of the rollers, through which the shafts of one pair are passed, characterized in that the housing support element is made in the form of a housing plate with through holes for receiving the shafts, said plate having a side facing the rollers, identified as the front side and the opposite side, identified as the back side, despite the fact that the back side of the body plate is provided with protruding components enclosing the holes, made in the form of a tubular x elements adapted to hold the bearings of the bearing assemblies, and the shafts of the second pair are passed through the second pressure plate, and all the shafts are passed through the second pressure plate so that they extend beyond it, and their end parts are installed in bearings, the housing supports of which are located in the holes auxiliary plate located at a selected distance from the second pressure plate, despite the fact that the first pressure plate is allocated from the front side of the housing plate along the axis of rotation of the shaft at a predetermined distance. 73. The device according to claim 72, wherein said predetermined distance is selected from a range of 15-60 mm, preferably 18-30 mm. 74. The device according to claim 72 or 73, wherein said selected distance is selected from a range of 15-60 mm, preferably 18-30 mm. 75. The device according to p. 72, characterized in that the thickness of the auxiliary plate is selected from the range of 15-60 mm, preferably 30-36 mm. 76. The device according to p. 72, characterized in that in the plane perpendicular to the axes of rotation of the shafts, the dimensions of the auxiliary plate differ from the dimensions of the second pressure plate. 77. The device according to paragraph 72, wherein the magnitude of said selected distance is substantially equal to the magnitude of said predetermined distance. 78. The device according to paragraph 72, wherein said selected distance is different in magnitude from said predetermined distance. 79. The device according to item 72, wherein the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axes of rotation of the shafts. 80. The device according to p. 72, characterized in that the rollers are oriented so that their axis of rotation are generally parallel to each other. 81. The device according to p. 72, characterized in that it further comprises an adjustment unit for at least one gap between the rollers. 82. The device according to p. 72, characterized in that the bearings of the bearing assemblies are rigidly connected to the housing support element so that it is not possible to change the position of the axis of rotation of the shaft, despite the fact that the axis of rotation of the said support coincides with the axis of rotation of the shaft, and bearing bearings mounted motionless relative to the auxiliary plate. 83. The device according to p. 72, characterized in that it further comprises at least two stiffening elements associated with the housing support element and located at an angle to each other. 84. The device according to p. 72, characterized in that for the rotation of the rollers it includes at least one drive means for synchronous rotation of all the rollers, despite the fact that in each pair of rollers rotate towards each other. 85. A device for rolling out a food product containing a first pair of rollers mounted to rotate towards each other, and a second pair of rollers mounted to rotate towards each other, while a first predetermined gap is formed between the working surfaces of the rollers of the first pair, and between the workers the surfaces of the second pair formed a second predetermined gap, the first pair of rollers mounted relative to the second pair of rollers so that between the working surface of the roller of the first pair and the working the surface of the second pair of rollers opposite to it, on the same side with respect to the conditional plane passing through the first and second defined gaps, rolls of the second pair are formed, moreover, the first pressure plate is located on one end side of the rollers, while the second pressure plate is located on the other end side of the rollers a plate, despite the fact that the working surface of each drum has a diameter set for it, characterized in that the value of said specified diameter is selected from a range of 50-120 mm. 86. The device according to p, characterized in that the value of the specified diameter is selected from the range of 65-80 mm 87. The device according to p. 85 or 86, characterized in that the specified diameters of all the rollers have essentially the same value. 88. The device according to p, characterized in that the specified diameters of at least two rollers have different values from each other. 89. The device according to p, characterized in that the specified diameters of the rollers of one pair have a value approximately equal to 71.6 mm, while the specified diameters of the rollers of the other pair have a value approximately equal to 71.4 mm. 90. The device according to p, characterized in that the specified diameters of the rollers of one pair have a value approximately equal to 71.8 mm, while the specified diameters of the rollers of the other pair have a value approximately equal to 71.4 mm. 91. The device according to p, characterized in that the specified diameters of the rollers of one pair have a value of approximately equal to 71.8 mm, while the diameters of the rollers of the other pair have a value of approximately equal to 71.6 mm. 92. The device according to p, characterized in that the length of the rollers is selected from the range of 20-350 mm, preferably 70-250 mm 93. The device according to claim 85, characterized in that it further comprises at least two scraper elements adapted to prevent sticking of product-like stripes of product coming out of the working gaps, while the scraper elements are arranged to allow said passage from the working gaps to the position chosen for them, despite the fact that the scraper elements are installed in such a way that the edge part of each scraper element facing the mentioned strip lies in a plane spaced from the axis rashchenija corresponding roller by a distance which is smaller than the drum radius to a value selected from the range of 2-4 mm. 94. The device according to p. 93, characterized in that the scraper elements are made of stainless steel sheet or of a polymeric material, for example, organic glass 1-2 mm thick. 95. The device according to p. 93, characterized in that the scraper elements are mounted with the possibility of changing the position of the edge parts relative to the respective surfaces of the rollers. 96. The device p, characterized in that on the supporting surfaces facing the end faces of the rollers, the first and second pressure plates contain an antifriction coating or antifriction gaskets. 97. The device according to p, characterized in that the thickness of the at least one pressure plate is selected from the range of 7-20 mm, preferably 8-12 mm 98. The device according to p, characterized in that the plates are essentially parallel to each other and lie in planes essentially perpendicular to the axis of rotation of the rollers. 99. The device according to p, characterized in that the rollers are oriented so that their axis of rotation were located essentially parallel to each other. 100. The device according to p, characterized in that for the rotation of the rollers it includes at least one drive means that provides synchronous rotation of all the rollers. 101. A device for rolling out a food product containing a first pair of rollers mounted to rotate towards each other, and a second pair of rollers mounted to rotate towards each other, while a first predetermined gap is formed between the working surfaces of the rollers of the first pair, and between the workers a second predetermined gap is formed on the surfaces of the second pair, the first pair of rollers being installed relative to the second pair of rollers in such a way that between the working surface of the roller of the first pair and the working the surface of the second pair of rollers opposite to it, on the same side with respect to the conditional plane passing through the first and second defined gaps, rolls of the second pair are formed, moreover, the first pressure plate is located on one end side of the rollers, while the second pressure plate is located on the other end side of the rollers the plate, despite the fact that the first predetermined gap is adapted to receive the product blanks, which are rolled into strip-like strips emerging from the working gaps, and its value exceeds the size of the remaining azores, and the value of the second predetermined gap, in comparison with the size of other gaps, has the smallest value, characterized in that the minimum value of the first predetermined gap lies approximately in the range of twice the thickness of the product-like strip bands emerging from the working gaps, while its maximum value is approximately in the range of four the thickness of the product strips emerging from the working gaps. 102. The device according to p. 101, characterized in that the value of the first predetermined gap lies in the range of 2-7 mm, preferably 3-5 mm, while the magnitude of the second predetermined gap lies in the range of 0.1-1.5 mm. 103. The device according to p. 101 or 102, characterized in that the thickness of the at least one pressure plate is selected from the range of 7-20 mm, preferably 8-12 mm. 104. The device according to p. 101, characterized in that the rollers are oriented so that their axis of rotation are located essentially parallel to each other. 105. The device according to p. 101, characterized in that on the supporting surfaces facing the end faces of the rollers, the first and second pressure plates contain an antifriction coating or antifriction gaskets. 106. The device according to p. 101, characterized in that it further comprises an adjustment unit for at least one gap between the rollers. 107. The device according to p. 101, characterized in that for the rotation of the rollers it includes at least one drive means for synchronous rotation of all the rollers, despite the fact that in each pair of rollers rotate towards each other. 108. The device according to p. 107, characterized in that the drive means includes a gear motor, while the shafts have a kinematic connection that is locked on the gear motor, based on a gear and / or chain gear. 109. The device according to p. 108, characterized in that the gear motor is connected to the base support element, and the connection is via a traction element made of at least two parts, one of which is made in the form of an arcuate mounted on the gearbox flange staples, and the other is made in the form of a strip radially oriented to the convex side of the staple, one end of which is rigidly connected to the bracket, and the other is adapted for communication with the base support element. 110. The device according to p. 109, characterized in that the said parts are made in one piece. 111. A stamping mechanism comprising a pair of including cell drums mounted rotatably to meet each other, each drum mounted on a shaft mounted in the bearing of the bearing assembly associated with the base support element, the drums having a first end surface facing the bearings and an opposite a second end surface to it, moreover, between the first end surface of the drums and the base support element there is a front plate connected to the base support element, through which omitted shafts, characterized in that the face plate is spaced from the base of the support member in the direction of rotation of the shaft axis by a predetermined distance. 112. The stamping mechanism of claim 111, wherein the predetermined distance is selected from a range of 15-60 mm, preferably 18-30 mm. 113. The stamping mechanism according to p. 111 or 112, characterized in that the thickness of the front plate is selected from the range of 7-20 mm, preferably 8-12 mm. 114. The stamping mechanism according to p. 111, characterized in that the base support element is made in the form of two spaced apart from each other at a pre-selected distance and rigidly interconnected housing plates with through holes adapted to receive bearings of bearing assemblies. 115. The stamping mechanism according to p. 114, characterized in that the pre-selected distance between the housing plates is selected from the range of 40-60 mm, preferably 42-45 mm 116. The stamping mechanism according to p. 114, characterized in that at least one bearing of the bearing assembly is made eccentric and provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to enable rotation supports around its axis of rotation when adjusting the relative position of the drums and the rigid connection of the support with the base support element in the selected position after rotation, while the base support element is provided it is in contact with the outer surface of the support by an arcuate bracket having a through groove extending in the circumferential direction of the support. 117. The stamping mechanism p. 111, characterized in that the base support element is made in the form of a body plate with through holes for receiving shafts, the plate has a side facing the front plate, identified as the front side, and the opposite side, identified as the back side, despite the fact that the back side of the housing plate is provided with protruding components enclosing the holes, made in the form of tubular elements oriented longitudinally to the shafts, adapted to hold the bearings of the bearing arrangements fishing 118. The stamping mechanism according to claim 117, characterized in that at least one bearing of the bearing assembly is made eccentric and is provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to enable rotation bearings around its axis of rotation when adjusting the relative position of the drums and the rigid connection of the said bearings with the base support element in the selected position after rotation, while the tubular element, in which the eccentric support is located, is provided with a through groove extending in the circumferential direction of the support. 119. The stamping mechanism according to claim 118, wherein said tubular elements extend beyond the surface of the body plate to a distance selected from a range of 30-70 mm, preferably 32-38 mm. 120. The stamping mechanism according to claim 118, characterized in that the minimum thickness of the body plate is selected from the range of 12-18 mm, preferably 14-16 mm. 121. The stamping mechanism according to claim 118, characterized in that the housing plate with tubular elements is made in the form of a single cast or welded part. 122. The stamping mechanism according to claim 118, characterized in that it further comprises at least two stiffening elements located at an angle to each other, connected with the base support element. 123. The stamping mechanism according to p. 111, characterized in that the drums with the accuracy of manufacturing errors are identical and installed with the mating of their outer cylindrical surfaces along a line lying in the same plane with the axes of rotation of the drums. 124. The stamping mechanism according to p. 123, characterized in that the axis of rotation of the drums, essentially parallel to each other. 125. The stamping mechanism according to p. 111, characterized in that for the rotation of the drums it includes at least one drive means for synchronous rotation of the drums. 126. The stamping mechanism according to p. 125, characterized in that the drive means includes a gear motor, while the shafts have a kinematic connection that is locked on the gear motor, based on a gear and / or chain gear. 127. A stamping mechanism comprising a pair of including cell drums mounted rotatably to meet each other, each drum mounted on a shaft mounted in a bearing of a bearing assembly associated with a basic support element, the drums having a first end surface facing each other and an opposite her second end surface, despite the fact that the first end surfaces of the drums are facing the supports, characterized in that it further comprises a front plate having holes, spaced from the second end surface of the drums at a preselected distance, and the end parts of the shafts extend beyond the second end surface of the drums and are mounted in bearings, housing bearings of which are located in the holes of the front plate. 128. The stamping mechanism of claim 127, wherein said preselected distance is selected from a range of 15-60 mm, preferably 18-30 mm. 129. The stamping mechanism according to p. 127 or 128, characterized in that the thickness of the front plate is selected from the range of 15-60 mm, preferably 30-36 mm. 130. The stamping mechanism according p, characterized in that it further comprises at least one unit for adjusting the relative position of the drums. 131. The stamping mechanism according to p. 130, characterized in that the adjustment unit provides for the possibility of adjusting the distance between the axis of rotation of the shafts in the plane in which they lie, parallel to the transfer of the axis of rotation of at least one shaft by moving it together with the bearing housing, in this case, the corresponding hole of the front plate in a conventional plane perpendicular to the axis of rotation of the shaft has such a contour that allows you to move the bearing housing mating with the front plate in the direction of change shaft, and the front plate is equipped with at least one mounting element for fixing the bearing housing in a selected position relative to the front plate. 132. The stamping mechanism according to p, characterized in that the said contour is outlined by an oval, the major axis of which is located on a conditional line passing through the points of intersection of the axes of rotation of the shafts with the said conditional plane, despite the fact that the contour of the housing support in the conditional plane is outlined in a circle, and the fastener is threaded and placed in adapted for receiving the threaded fastener an additional through hole of the front plate, extending in the radial direction relative to the axis of rotation of the shaft along the line and the major axis of the oval. 133. The stamping mechanism according to p. 132, characterized in that the shaft is moved by turning the bearings of the bearing assembly, the bearing being made eccentric and provided with a through hole extending radially relative to the axis of rotation of the shaft, adapted to receive fastening means designed to provide the possibility of rotation of the support around its axis of rotation within the selected angular range when adjusting the distance and rigid connection of the support with the base support element in the selected position and after the turn. 134. The stamping mechanism according to p, characterized in that the selected angular range is approximately 90 °. 135. The stamping mechanism according to p. 130, characterized in that the adjustment unit provides for the possibility of angular displacement of one of the drums relative to the shaft on which it is mounted. 136. The stamping mechanism according to p. 130, characterized in that the adjustment unit provides for the possibility of movement when setting up at least one of the drums along the axis of rotation of the shaft. 137. The stamping mechanism according to p. 127, characterized in that the front plate is made with a figured notch, providing affordable monitoring of the contact area of the outer surfaces of the drums. 138. The stamping mechanism according to p. 127, characterized in that the bearings selected are tapered roller or radial thrust bearings. 139. The stamping mechanism according to p. 127, characterized in that for the rotation of the drums, it includes at least one drive means for synchronous rotation of the drums. 140. The stamping mechanism according to p. 139, characterized in that the drive means includes a gear motor, and the shafts have a kinematic connection that is locked on the gear motor, based on a gear and / or chain gear. 141. The stamping mechanism according to p. 140, characterized in that the gear motor is connected to the base support element, while the connection is carried out by means of a traction element made of at least two parts, one of which is made in the form of a gearbox mounted on the flange an arc-shaped bracket, and the other is made in the form of a strip radially oriented to the convex side of the bracket, one end of which is rigidly connected to the bracket, and the other is adapted to communicate with the base support element. 142. The stamping mechanism according to p. 141, characterized in that the said parts are made in one piece. 143. A stamping mechanism comprising a stamping mechanism located on a basic support element, made in the form of a pair of drum cells including, mounted for rotation towards each other, with each drum mounted on a shaft mounted in a bearing of the bearing assembly associated with the basic support element, moreover, the drums have a first end surface facing the supports and a second end surface opposite to it, while between the first end surface of the drums and the base support element m there is a front plate connected to the base support element through which shafts are passed, characterized in that it further comprises openings with a front plate spaced apart from the second end surface of the drums at a predetermined distance, and the shaft end parts protruding beyond the second end surface of the drums are installed in bearings, housing bearings which are located in the holes of the front plate, despite the fact that the front plate is assigned in the direction of the axis of rotation of the shaft from the base support element at a predetermined a predetermined distance. 144. The stamping mechanism according to p, characterized in that the said predetermined distance is selected from the range of 15-60 mm, preferably 18-30 mm 145. The stamping mechanism according to p. 144 or 144, characterized in that the said pre-selected distance is selected from the range of 15-60 mm, preferably 18-30 mm 146. The stamping mechanism according to p, characterized in that the thickness of the front plate is selected from the range of 15-60 mm, preferably 30-36 mm 147. The stamping mechanism according to p, characterized in that the thickness of the front plate is selected in the range of 7-20 mm, preferably 8-12 mm. 148. The stamping mechanism according to p, characterized in that the base support element is made in the form of two spaced apart from each other at a pre-selected distance and rigidly interconnected housing plates with through holes adapted to receive bearings of bearing assemblies. 149. The stamping mechanism according to p, characterized in that the aforementioned pre-selected distance between the housing plates is selected from the range of 40-60 mm, preferably 42-45 mm 150. The stamping mechanism according to p, characterized in that at least one bearing of the bearing assembly is made eccentric and connected with the base support element with the possibility of its rotation to move the shaft when adjusting the relative position of the drums, while the housing mating with the front plate the bearing housing support is made and mounted so that it can be moved together with the shaft and fixed in the position of the rigid connection of the eccentric support with the base support element. 151. The stamping mechanism according to p, characterized in that the base support element is made in the form of a body plate with through holes for receiving shafts, the plate has a side facing the face plate, identifiable as the front side, and the opposite side, identifiable as the back side, despite the fact that the back side of the housing plate is provided with protruding components enclosing the holes, made in the form of tubular elements oriented longitudinally to the shafts, adapted to hold the bearing supports nodes. 152. The stamping mechanism according to p. 151, characterized in that at least one bearing of the bearing assembly is made eccentric and connected to the base support element with the possibility of its rotation when adjusting the relative position of the drums, while the tubular element adapted to hold it, made with a through groove extending in the circumferential direction of the tubular element, moreover, the bearing bearing housing mating with the front plate is made and mounted so that it can be moved e with the shaft and fixation in the position of tight connection of the eccentric support with the base support element. 153. The stamping mechanism according to Claim 152, characterized in that the tubular elements protrude beyond the flat sections of the surface of the cabinet plate to a distance selected from a range of 30-70 mm, preferably 32-38 mm. 154. The stamping mechanism according to p, characterized in that the body plate with tubular elements is made in the form of a single cast or welded part. 155. The stamping mechanism according to p, characterized in that the drums with the accuracy of manufacturing errors are identical and installed with the mating of their outer cylindrical surfaces along a line lying in the same plane with the axes of rotation of the drums. 156. The stamping mechanism according to p, characterized in that the axis of rotation is essentially parallel to each other. 157. The stamping mechanism according to p, characterized in that the drums are mounted with the possibility of movement when setting up at least one of the drums along the axis of rotation of the shaft. 158. The stamping mechanism according to p, characterized in that it further comprises an angular adjustment unit for the relative position of the drums, providing for the possibility of angular displacement of one of the drums relative to the shaft on which it is mounted. 159. The device according to p, characterized in that for the rotation of the drums it includes a gear motor connected to the base support element, while the shafts have a kinematic connection locked on the gear motor, based on a gear and / or chain gear. 160. The stamping mechanism according to p. 159, characterized in that the motor gearbox is connected to the support element by means of a traction element made of two parts, one of which is made in the form of an arcuate bracket mounted on the gearbox flange, and the other is made in the form of a radially oriented to the convex side of the bracket of the strip, one end of which is rigidly connected to the bracket, and the other is adapted for communication with the housing support element. 161. The stamping mechanism according to p, characterized in that the said parts are made in one piece. 162. A stamping mechanism comprising a pair of including drum cells mounted on shafts rotatably to meet each other, at least part of the cells is equipped with ejection elements placed in the cells with the ability to move towards the cell inlet and move in the opposite direction while each ejection element is connected by means of a supporting element to an oval-shaped element located inside the drum and surrounding the shaft, having two essentially flat surfaces and the internal and opposite end surfaces facing the shaft, despite the fact that the contour of the oval-shaped element on flat surfaces is limited by two ovals spaced by a predetermined distance, while the oval facing the shaft has a small diameter measured along the axis of its small axis and measured along the lines of the major axis are a large diameter, and inside the drum there is a biasing element elongated longitudinally to the axis of rotation of the drum, installed so that when it interacts with the end surface of the shaft facing the shaft The aloe-shaped element moves the ejector element towards the cell inlet opening within the set value stroke, characterized in that the set stroke value is selected from the range of 10-25 mm. 163. The stamping mechanism according to p, characterized in that the predetermined stroke value, defined as the difference between the large diameter and small diameter, is selected from a range of 12-18 mm. 164. The stamping mechanism according to p, characterized in that the stroke is approximately 15 mm, while the large diameter is approximately 81 mm, while the small diameter is approximately 66 mm. 165. The stamping mechanism according to p, characterized in that the thickness of the oval-shaped element, determined by the distance between its flat surfaces, is selected from the range of 1.5-2.5 mm, preferably 1.8-2.0 mm 166. The stamping mechanism according to p, characterized in that said predetermined distance by which the ovals are spaced is selected from a range of 5-12 mm, preferably 7-8 mm. 167. The stamping mechanism according to p, characterized in that the ejection element is made in the form of a plate with a contour around the perimeter, which provides a gap between the inner side surface of the cell and the surface of the ejection element facing it, while the minimum clearance allows free movement of the ejection element. 168. The stamping mechanism according to p, characterized in that the supporting element is made in the form of a rod extending along the line of the minor axis of the oval-shaped element. 169. The stamping mechanism according to p, characterized in that the biasing element is made in the form of a rod rigidly connected at one end to the base support element. 170. The stamping mechanism according to p, characterized in that the biasing element is mounted with the possibility of regulating its position relative to the axis of rotation of the drum. 171. The stamping mechanism according to p, characterized in that on each oval-shaped element along the line of its minor axis there are two opposite supporting elements for two opposed pushing elements located in opposed located cells of the drum, while the number of cells of each drum is an even number . 172. The stamping mechanism according to p, characterized in that the oval-shaped element and the supporting element are made in one piece in the form of a single part. 173. The stamping mechanism according to p, characterized in that for the rotation of the drums it includes at least one drive means for synchronous rotation of the drums. 174. The stamping mechanism according to Claim 173, characterized in that the drive means includes a gear motor, and the shafts have a kinematic coupling that is locked on the gear motor and is based on a gear and / or chain gear. 175. A device for the production of semi-finished products from dough with filling, containing a stamping mechanism made in the form of a pair of including cell drums mounted on the base support element with the possibility of rotation towards each other; a device for rolling out a food product, made with the possibility of forming two ribbon-shaped test strips supplied to the product formation zone, and having four rollers mounted on the housing support element with the possibility of synchronous rotation; filling supply means adapted for supplying the filling into the product forming zone between the ribbon-like strips and having a wedge-shaped fragment oriented with the apex toward the product forming zone, characterized in that the device for rolling the food product is made according to any one of claims 1-11, or 12- 21, or 22-32, or 33-46, or 47-60, or 61-71, or 72-84, and the stamping mechanism is made according to any one of claims 85-100, or 101-110, or 111-126, or 127-142, or 143-161, or 162-174. 176. The device according to p. 175 characterized in that the housing support element is made integrally with the base support element. 177. The device according to p. 175, characterized in that the product formation zone is located in the immediate vicinity opposite each other of the drum cells of the stamping mechanism, made with a given shape of the inlets. 178. A device for the production of semi-finished dough products with filling, containing a stamping mechanism made in the form of a pair of drum cells, mounted for rotation towards each other, a food product rolling device configured to form two ribbon-like dough strips fed into the zone the formation of products, a means of supplying the filling, adapted for supplying the filling into the zone of formation of the products between the tape-shaped strips and having a wedge-shaped fragment, oriented with the apex towards the product forming zone, characterized in that the filling supply means is made in the form of a cast or stamped part, inside of which at least one tube made of polymeric material is placed, along which the filling is brought into the product forming zone. 179. The device according to p, characterized in that the said tube is curved curved. 180. The device according to p. 178 or 179, characterized in that the sides of the wedge-shaped fragment facing the strip-like strips are curved curved so that the intersection lines of the surfaces of the sides with the plane perpendicular to the axis of rotation of the shaft drums are arcs facing the convex sides to each other circles. 181. The device according to p. 180, characterized in that the arcs of circles are essentially concentric with the opposite arcs of the circles of the surfaces of the drums. 182. The device according to p, characterized in that the relative orientation of the drums and the wedge-shaped fragment is such that the minimum distance between their surfaces is approximately 2 mm. 183. The device according to p, characterized in that the product formation zone is located in the immediate vicinity opposite each other of the drum cell of the punching mechanism, made with a given shape of the inlets. 184. The device according to p, characterized in that the relative orientation of the drums and the wedge-shaped fragment is such that the minimum distance between their surfaces is approximately 2 mm. 185. The device according to p, characterized in that it further comprises a pump adapted for supplying the filling to the means for supplying the filling. 186. The device according to p. 185, characterized in that the pump is connected to the means for supplying the filling by pipelines with the number of rows of cells on the guide cylindrical surface of the drum. 187. The device according to p, characterized in that it further comprises a conveyor kinematically connected with the stamping mechanism.