RU2199412C1 - Spring winding automatic machine, its mechanisms for cutting, forming loop, moving blanks (variants), their devices for gripping, shifting, orienting, clamping, cam devices - Google Patents

Abstract

FIELD: spring manufacture. SUBSTANCE: automatic machine is provided with mechanism for forming loop on supporting turn of spring. Said mechanism has loop forming gear wheels, device for gripping spring, device for shifting spring, device for orienting supporting turn of spring, device for clamping spring. Automatic machine also includes heat treatment apparatus, packing mechanism with packing plates, mechanism for moving spring blanks out of cutting zone to zone of forming loop and mechanism for moving blanks from loop forming zone to heat treatment zone. Each of said mechanism has gripping unit and members for their opening and closing. Mechanism for forming loop, heat treatment apparatus and mechanism for cutting are provided with their own cam devices. Cam devices of shaping and cutting mechanisms are rigidly mounted on the same working shaft joined with levers rotating motion mechanisms. Cam devices of loop forming mechanism and of heat treatment apparatus are rigidly mounted on another working shaft. Said working shafts are mounted with possibility of synchronous rotation. Cam of cutting mechanism has lifting working portion on its lateral surface. Working surface of cam of heat treatment apparatus is in the form of semicircle arc. Member for closing grip of mechanism for moving spring blank from cutting zone to loop forming zone is joined with kinematic circuit of cutting mechanism. Member for opening grip of above mentioned mechanism is joined with kinematic circuit of closing grip of mechanism for forming loop. Means for closing-opening grip of mechanism for moving spring from zone of forming loop to heat treatment zone are kinematically joined with kinematic circuit of its rocking. EFFECT: possibility for realizing the whole cycle of manufacturing process of spring. 24 cl, 25 dwg

Description

 The invention relates to the field of production of cylindrical, curly, in particular, double cone springs and can be used in the design and manufacture of spring-coiling machines that produce finished products without additional processing.

 Known machines for winding springs, which include the basic mechanisms mounted on one frame and kinematically connected to each other. So, in the invention SU 1570826, B 21 F 35/02, bull. 22, 1990 [1] the machine includes a wire feed mechanism, a spring winding mechanism, a cutting mechanism, a mechanism for processing the ends of the spring, a mechanism for removing the spring from the mandrel kinematically connected by means of a camshaft and having a common drive. In SU 1052304, B 21 F 35/02, bull. 41, 1983 [2] the machine is equipped with a manipulator for transferring the spring preform from the winding mechanism to a means for bending the ends of the spring. In SU 1726098, B 21 F 35/00, bull. 14, 1992 [3] the machine is equipped with a device for removing the finished spring. SU 1234018, B 21 F 35/00, publ. 05/30/86. [4] the machine is equipped with a device for heat treatment of a wound spring. However, these machines, including several functionally complete mechanisms, each working according to its own program, over their operation of the process of obtaining a rather complex product, such as a spring, in particular a two-cone spring, require tight synchronization of the coordinated movements of all mechanisms. Deficiencies in this part cause frequent malfunctions of the machine, thereby reducing its performance. High-performance machines require reconciliation of the beginning of one technological operation with the end of the previous one and preparation of the next operation with special accuracy, which is not provided by the indicated solutions.

 To synchronize the operation of individual nodes using various technical solutions. SU 776725, B 21 F 35/00, publ. 11/07/80. [5], SU 1268260, B 21 F 35/00, publ. 11.11.86. [6] each mechanism is powered by its own electric motor, and the program device and the program controller, which can be made in the form of a digital preset of the parameters of the winding spring or in the form of a punched tape, where the program characterizing the parameters is coordinating the work of the entire machine. Such machines are very complex, therefore, unreliable in operation, expensive and have great power consumption. Other solutions are associated with the synchronization of the mechanisms due to the kinematic connection of their working shafts with one camshaft (input) shaft. So, in SU 1657263, B 21 F 35/02, bull. 21, 1991 [7] kinematically connected by means of a camshaft a wire feed mechanism, a winding mechanism and means for bending the ends of the spring. The workpiece transfer manipulator in [2] is connected via levers to the camshaft of the machine. In SU 1194549, B 21 F 35/00, publ. 11.30.85 [8] kinematically connected by means of a drive camshaft winding mechanisms, pieces and dumping of the finished spring.

 The most developed are reliable machines, in which synchronization is carried out by coupling mechanisms with one shaft; so, for example, in SU 996011, B 21 F 35/00, publ. 02/15/83. [9], the cam of the stepping mechanism and the cutting tool are placed on one shaft mounted with the possibility of continuous rotation and kinematically connected with the shafts of the feed rollers of the wire feed mechanism.

 The kinematic connection of individual mechanisms with their working shafts is carried out by means of cams with a profiled side surface. So, in SU 1799656, B 21 F 3/00, publ. 03/07/93. [10] the spiral forming mechanism includes a profile cam and a bending disk of a spring winding mechanism configured to interact with it; in SU 506460, B 21 F 35/00, publ. 03/15/76. [11] the drive of the knife is made in the form of a cam gear mounted on its shaft, connected to the camshaft.

 Synchronizing the operation of the individual constituent mechanisms of a high-performance machine is not enough for reliable, uninterrupted operation of it as a whole. It is necessary to synchronize the operation of all the components of the machine.

The closest analogue of the proposed machine according to the ideology of constructing a kinematic scheme of the means of the same purpose, working from one electric motor, and by the availability of solutions for synchronizing the operation of the components is the invention by as 599896, M.C. ² B 21 F 35/00, published 03/30/78. , bull. 12, An automatic machine for winding springs [12], comprising a wire feed mechanism, a shaping mechanism, a chopping mechanism mounted on a bed kinematically connected to one electric motor through a drive shaft, which serves as a common drive for transmitting movement to all mechanisms of the machine. The wire feed mechanism is driven by a drive shaft, the rotation of which is fed to the pulling rollers. The shaping mechanism includes a winding mechanism and a stepping mechanism. The winding mechanism contains winding stops interacting with the supplied wire and connected with the copier, the lateral surface of which determines the shape and dimensions of the winding spring; the copier is rigidly fixed to the copier shaft. The stepping mechanism works through the cams from the cam shaft associated with the copier shaft. The cutting mechanism is kinematically connected with the winding mechanism through an additional shaft. Knives, winding stops, step stops each work from its working shaft; working shafts are synchronized through kinematic communication with a common drive shaft.

 The disadvantage of this analogue is the insufficient functionality of the machine, since it does not contain many of the mechanisms necessary for the final manufacture of the spring as a finished product, such as: a mechanism for processing the ends of the spring, a heat treatment device, a packer of finished springs, the work of which would be coordinated with the work of other composite mechanisms machine, as well as an insufficient degree of tight synchronization of the mechanisms, the complexity of the kinematic scheme of the machine, containing many workers, sync lowering and transmission shafts.

 The objective of the invention is to create a logically complete machine for winding springs, performing the entire cycle of the process from wire feed to receiving the spring as a finished product, as well as a machine with a high degree of synchronization of the work of all composite mechanisms, while simplifying its kinematic scheme, more reliable and trouble-free in operation .

This problem is solved by the design of a spring-coiling machine for the production of springs, including a wire feed mechanism, a shaping mechanism, a chopping mechanism mounted on a bed kinematically connected to an electric motor through a drive shaft, with cam means rigidly fixed to the working shafts of the machine, while the chopping mechanism is kinematically connected with the cam shaft of the forming, and the wire feeder with the drive (central) shaft, the lateral working surface of the cam of the forming is curved, the law of removing each point of which from the axis of rotation of the working shaft of the shaping mechanism corresponds to the law of changing the diameter of the spring, which is additionally equipped with a knot forming mechanism on the spring support coil with knot gears made with a spring gripping device, with a spring movement device, with a support orientation device spring coil, with spring clamping device, heat treatment device, stacking mechanism with stacking plates, as well as per the placement of the spring blanks from the cutting zone to the knot formation zone (knotting zone) and from the knotting zone to the heat treatment zone, each with a gripper and means for opening and closing them, the knot formation mechanism on the support turn, the heat treatment device and the chopping mechanism are each equipped with their own cam means, while the cam means of the shaping and cutting mechanisms are rigidly mounted on one working shaft, to which the rotation levers of the movement mechanisms are connected, the cam means of the formation mechanisms a heat treatment unit and fixedly mounted on the other working shaft which are kinematically connected also the mechanism of tying gear assembly through an intermittent rotation mechanism such as a gear sector, and the plate stacking. The working shafts are installed with synchronous rotation, for example with the same angular velocity, in one direction. The felling cam is equipped with a lifting working section of its lateral surface, the beginning of which corresponds to the beginning of the shaping of the spring, i.e. the beginning of its lifting section lies in the contact zone of the rolling roll of the shaping cam with the beginning of shaping of the shaping cam spring (to its middle line); in the case of winding biconical springs, the beginning of the lifting working section of the felling cam corresponds to the end of the transition zone of the winding spring from large diameters to small diameters of the shaping cam; the line connecting the beginning of the cutting cam working section with its axis of rotation coincides with the rotation lever of the gripping mechanism for moving the spring blank from the cutting zone to the knotting zone, i.e. the connection point of the rotation lever and the first link of the kinematic chain (for example, traction) of the workpiece movement mechanism from the cutting zone to the knotting zone lies on the line connecting the starting point of the cutting zone of the cutting cam with the axis of rotation of the shaft, on one side with the beginning of the cutting zone from their axis of rotation the shaft, the mechanism for moving the spring workpiece from the knotting zone to the heat treatment zone is configured to match its extreme lower and upper positions with the extreme lower and upper positions of the mechanism for moving the workpiece from zone p flanges to the knotting zone, respectively, namely, the positions of their grips, the working surface of the heat treatment cam is symmetrical and represents an arc of a semicircle, while the line connecting the center of its working surface with the axis of rotation, which is the axis of symmetry of the working surface of the heat treatment cam, coincides with the line connecting the beginning of the working section of the felling cam with the axis of its rotation and is located in one direction, i.e. makes an angle of 0 ^o with it, the cam of the knotting mechanism mechanism is made with a waiting area and a working zone including the contact zone of the knotting gear with the spring, while the end of the knotting gear contact zone with the cam spring of the knotting mechanism coincides with the starting point of the felling zone of the subsequent chopping cam the springs, plates of the stacking mechanism are kinematically connected with the second working shaft through the rotation lever, and their extreme position in the stacking zone (the extreme right position of the plates is shown in FIG. 1 apparently the axis) corresponds to the beginning of knotting, i.e., the beginning of contact of the knotting gear with the spring, the means for closing the gripper of the mechanism for moving the spring workpiece from the cutting zone to the knotting zone is connected with the kinematic chain of the cabin, the means for opening it is connected with the kinematic chain of closing the spring gripper in the mechanism the formation of the node, the means of closing-opening the grip of the mechanism for moving the spring from the knotting zone to the heat treatment zone are kinematically connected with its kinematic chain swing capture.

 The proposed solution allows you to create a logically complete machine for winding springs, including all the technological operations for its manufacture, not requiring the use of other devices and mechanisms outside the machine, which leads to high production capacity of the springs, their high quality, lower costs for their production, allows you to simplify the design machine and achieve a high degree of synchronization of all mechanisms of the machine, its smooth operation, also associated with high performance machine.

 The design of the machine as a whole is illustrated in figure 1. A description of the spring-coiling machine in statics and its operation are given below.

Chopping mechanism
Spring-coiling machines are known in which the wire feed is cut off for the sections of the coiled spring [9]. Such automatic machines have insufficient productivity and are quite complicated, since they assume special devices for disconnecting the wire feed. Periodically turning on / off the feed mechanism causes transient processes of acceleration and braking of the pulling rollers, shafts on which these rollers are fixed, which negatively affects the accuracy of the wire feed of the desired length for the workpiece and, as a result, leads to defective products; in addition, the acceleration / deceleration mode causes large vibrations, the noise of the machine, the wear of its parts.

 Automata are also known in which a section of a wound spring is carried out without stopping the wire feed due to the “quick cut”, for example, due to the rotation speed of the chopping cam shaft, much higher than the camshaft speed associated with the wire feed [11]. An increase in the speed of the cutting knife can be achieved by providing it with additional energy, for example, from a spring compressed just before the knife starts to move, due to the compression energy (see Cutting mechanism to the device for manufacturing springs SU 471941, M. Cl. B 21 F 35/00, published 05.30.75., Bull. 20 [13]. This design allows you to pre-compress the power spring before moving the knife to subsequently communicate its energy to the movable knife, which thereby quickly cuts the wound spring. izzhizheniya knife to the cutting area in the described structures creates a strong blow that can cause a violation of the shape of the spring and unpredictable destruction of the cutting mechanism, its individual elements and / or parts of the mating structures, which will affect the reliability of the machine and its short service life.

 To eliminate the problem of reducing the cutting speed and the related problem of reducing the working stroke of the movable knife, the location of the knife in standby mode is constantly changed in synchronization with the winding process. So, in [5], a plate with knives using a separate motor during winding of the spring can move synchronously with the winding stops, either moving away, or approaching the starting point of the wire bend.

 The closest analogue to the chopping mechanism is the cutting mechanism according to the invention of A.S. 599896, M. Cl. 2 B 21 F 35/00, published 03/30/78, bull. 12, Automatic machine for winding springs [12], which is kinematically connected with the winding mechanism through an additional shaft. The cutting mechanism contains an internal knife fixed in a movable plate, and an external knife mounted on a movable crawler. The creeper is movably mounted on one axis on the axis and the other end is on the eccentric end of the shaft mounted in the movable plate. A shaft with an eccentric is connected to a clutch, which includes a cutting mechanism at the time of the cut-off spring, and to the drive shaft. A gear rack is fixed to the plate of the inner knife, which is meshed with the gear, which is connected with the gear shaft of the winding mechanism. As a result of the kinematic connection of the winding mechanism with the knife cutting mechanism, they are in constant motion, either moving away from the spring, or approaching it; while the movement of the knives of the mechanism segments is carried out synchronously with the winding mechanism at a proportional distance and is carried out from the copy disk of the winding mechanism. This mode of operation of the cutting mechanism allows you to track the location of the winding spring, minimizing the distance of the working stroke of the cutting of knives, however, it requires complicating the kinematics of the machine, reducing the reliability of its operation, and also leads to a decrease in the working life of moving parts, more frequent changeover of the machine. In addition, the knives in [12] perform reciprocating motion along a long kinematic chain, which due to its construction is inertial, with large bending loads and backlash, large efforts of the movable knives at the time of cutting, which slow down the cutting process and can lead to desynchronization the work of the machine. Other disadvantages are the complexity of the cut mechanism, its kinematic scheme and, as a consequence, a decrease in the reliability of the machine. Another unsolved problem of the closest analogue is the withdrawal of the movable knife from the cutting area after cutting without deformation of the end of the subsequent spring.

 The objective of this invention is to increase the synchronization of the operation of the chopping mechanism with other mechanisms of the machine, simplifying the design, increasing the reliability of both the chopping mechanism and the machine as a whole while maintaining the continuity of the wire feed and the knife’s small working stroke when chopping, eliminating the deformation of the subsequent spring with the knife when it is returned to the starting position.

 The problem is solved by the design of the chopping mechanism, containing a movable knife with the possibility of interaction with another knife during chopping, with the possibility of movement during winding and chopping of the spring, associated with the cam of the cabin and kinematically connected with the cam of the slide, in which the movable knife is mounted to rotate in the plane, perpendicular to the coil of the spring at the point of cutting, the cams of the slide and the cabin are mounted rigidly and coaxially on one working shaft, the connection of the movable knife with the cam of the slide and the cam of the cabin is made one kinematic of the chain through the rolling rollers of the slide and the wheelhouse, respectively, located coaxially on one shoulder of the rocker arm of the kinematic chain, each opposite to its cam, the wheelhouse cam is provided with a lifting straight or curved working section of its side surface, the sliding cam is equipped with the first working lifting section of the side surface, straight or curved, which is located before the start of the working section of the felling cam, and the second (last) working lifting section, straight or curved, beginning which coincides with the end of the working section of the felling cam, and the second working section of the cam is made with a lifting angle (tilt) of the same sign as its first working section, and the cams of the felling mechanism are made with the possibility of their simultaneous interaction with their rolling rollers.

 The indicated design of the cutting mechanism allows to synchronize the operation of the cutting mechanism due to the relative position of both cams, to exclude constant movements of the knife and replace them with a knife movement immediately preceding the cutting process, to exclude reciprocating movements of the knife, inertial and with bending loads, to make a smooth preparatory movement the movable knife to the place of cutting by advance (before cutting) rotation of the knife relative to the axis of rotation in a plane perpendicular to the turn ruins, having previously selected all the backlashes of the kinematic chain before cutting, reducing the knife stroke by the time of cutting to a minimum, eliminating large shock loads on the spring billet and structural parts during cutting and reducing its bending forces on the spring billet; the execution of the working lateral surface of the cam of the slide with a gap makes it possible to contact the cam of the slide and chopping with its rollers at different times, i.e. the possibility of simultaneous operation of the chopping mechanism in different modes: knife movement and cutting of a spring workpiece, switching the knife at the time of cutting from the cam to the chopping cam as more massive and shockproof, without loading the cam itself, thereby ensuring the durability of the mechanism and eliminating machine malfunctions. The shape of the cam makes it possible to continue the rotary movement of the knife after cutting in the same direction as before cutting, quickly removing the knife from the cutting zone and avoiding the curvature of the end shape of the new spring being wound at this time. In this case, the efforts of the movable knife at the time of cutting will be reduced and the speed of the cutting process will be ensured. All this allows the spring to be chopped without stopping the wire feed with a simple and reliable kinematic scheme of the chopping mechanism, providing highly synchronous uninterrupted operation of the machine as a whole.

 The design of the chopping mechanism is illustrated in figures 1, 2b, 4. A description of the design and operation of the mechanism are described below.

Chopping mechanism cam
Known chopping cams designed to control the operation of the chopping mechanism in machines for winding a spring, having a profile side surface that determines the movement of the chopping knife. So, in [13], the chopping mechanism contains a movable knife with the possibility of reciprocating motion from a drive cam having a steeply falling section that determines the movement of the knife at the time of chopping. The presence of a knife stroke spring limits the possibilities of the cutting mechanism.

 [11] described cam means of the chopping mechanism, in which the drive of the movable knife of the spring-coiling machine is equipped with levers, one of which is in constant contact with the profile cam, equipped with a lifting section and rigidly mounted on a shaft kinematically connected by a reduction gear to the camshaft. The cam through the mentioned lever transmits constant oscillatory movements of the driven coupling half kinematically connected with the knife, as a result of which, on the command of the other cam, the chain of the gear electromagnetic coupling is closed through the micro switch and a quick spring cut is made. Spring cutting is performed without stopping the wire feed due to the speed of the knife at the time of cutting, much higher wire feed speeds. The reverse stroke of the knife immediately after cutting is provided by the cam 42.

 Such a device, firstly, causes large movements of the knife at the time of cutting with high speed, which causes significant shock loads on the spring, machine mechanisms and deformation of the spring during cutting, and secondly, returning the spring back immediately after cutting also leads to deformation of the next coil spring, thirdly, a device including, in addition to the kinematic chains and electric, differs in complexity and unreliability of work. The installation of cams on different shafts adversely affects the synchronization of the cutting mechanism. The described cam tool is the closest analogue of the proposed solution.

 The objectives of this invention are to reduce shock loads from the knife to the coil spring and the machine mechanisms, improve the quality of the coil springs, simplify the chopping mechanism, increase the degree of synchronization of the chopping process.

 The problems are solved by the design of the cam means of the chopping mechanism, comprising a chopping cam, a knife moving cam provided with a lifting section and adapted to interact with the kinematic chain through a contact element at its end, in which the cam means of the chopping mechanism is a double cam, consisting of rigidly connected between themselves and coaxially mounted cam slides and chopping cam, each of which is equipped with its contact element in the form of a roller, the chopping cam is equipped with a working the lifting force of its lateral surface, rectilinear or curvilinear, the size of which (the linear size of its projection onto an arc of a circle with a radius equal to the distance of its starting point of the lateral surface to the axis of rotation of the cam) is determined by the diameter of the wire used to wind the spring, and the lifting angle is determined by the cutting speed ; the working section of the felling cam may be a continuation of its lifting non-working section, as shown in figb; the beginning of the cutting cam working section in one design variant may have a value at which the distance difference from the points of the lateral cam of the sliding cam and the cutting cam lying on one axial straight line to the axis of rotation of the cams will be less than the difference of the radial dimensions (radii) of their rolling rollers; the beginning of the cutting cam working section may be an arc, the concave side of which is turned towards the rolling roller interacting with it, and whose radius is equal to the radius of this rolling roller; cams are made with the possibility of simultaneous contact of their working surfaces with their rollers; the lateral surface of the cam cam is made with four sections; the first section of the slide before cutting is located in front of the beginning of the working section of the cutting cam and represents a lifting branch, straight or curved, the linear projection size of which onto the arc of a circle with a radius equal to the distance of the starting point of this section to the axis of rotation of the cam is determined empirically depending on the distance from the place the location of the knife (its blade) in standby mode to the place of cutting, and the amount of inclination (angle of inclination) is determined by the speed that must be communicated to the knife to move it into the cutting zone to bq; this speed, in turn, depends on the start of the slide (the beginning of the first section of the shift cam) and the remoteness of the knife blade from the cutting area; the second section is made with a constant radius, and its beginning is also located to the working section of the cabin of the felling of the cabin, and the end coincides with the beginning of the cabin or with another non-end point of the section of the cabin of the cabin of the cabin; the second condition is preferable from the point of view of providing a guarantee of the start of operation of the felling cam, to ensure that the surface of the felling cam reaches the above value; the third section is lifting, the end of which coincides with the end of the cutting section of the felling cam and has a lifting value at which the difference in distance from the points of the lateral surfaces of the moving cam and the felling cam lying on one axial straight line to the axis of rotation will be greater than the difference in their radial dimensions (radii) rolling rollers; the length of this section depends on the angle of elevation; the greater the angle of inclination of this section, the shorter it is; the fourth (last) portion of the working surface of the cam of the slider is made lifting, rectilinear or curved, with an angle of elevation (tilt) of the same sign as the first working section of the cam of the slider. The values of these values are formulated for the case when the radius of the rolling cam of the wheelhouse is larger than the radius of the rolling cam of the cam and the distance from the points of the side surface of the cam to the axis of rotation of the cams is greater than the distances from the points of the side surface of the cam of the cabin to the axis of rotation of the cams. Under other (opposite) conditions, everything will be the other way around. The length of the fourth, last working section of the cam is determined by the distance from the cutting site to the final location of the knife moving when it leaves the cutting zone, and the angle of inclination of this section is determined by the required exit speed of the knife from their cutting zone. The working surfaces of the rolling rollers are located opposite the surfaces of their cams, made with a common axis of rotation and with different diameters. It is possible to ensure that the cams work at different times and with equal radii of the rollers: which side surface is farther from the axis of rotation of the cams, this or that roller will come into contact, however, in this case, failures can occur, since the end of each working section of the cams must have a sharp decline, and its beginning is a sharp rise, and inaccuracies in the manufacture of parts can affect normal operation. Therefore, the described embodiment of the cam means is preferred.

 The design of the felling cam allows a smooth preparatory movement of the movable knife to the felling site by advance (before felling) its movement to the felling site, thereby reducing the knife stroke by the time of felling to a minimum, eliminating large impact loads on the spring billet and design details during felling and reducing its bending forces on the spring billet; provides the simultaneous contact of the cams of the slide and cutting with its rollers, i.e. the simultaneous operation of the chopping mechanism in different modes: knife movements and cutting of the spring blank, switching the knife at the time of cutting from the cam to the chopping cam as more massive and shockproof, not loading the cam itself, eliminating the malfunctions of the machine and ensuring the durability of the mechanism. The shape of the cam makes it possible to continue the rotary movement of the knife after cutting in the same direction as before cutting, quickly removing the knife from the cutting zone and avoiding the curvature of the end shape of the new spring being wound at this time. In this case, the efforts of the movable knife at the time of cutting will be reduced and the speed of the cutting process will be ensured. All this allows you to chop the spring without stopping the wire feed with the simplicity and reliability of the chopping mechanism, providing highly synchronous uninterrupted operation of the machine as a whole. In addition, the design allows initial contact of the cutting cam working surface with its run-in roller not at a point, but in an arc, reducing contact stresses on this cam when it starts to contact its roller.

 On figb presents the design of the composite cam cutting.

 A description of the cam means of the chopping mechanism in statics and its operation are given below.

The device for capturing the support coil of the spring of the mechanism of formation of the node on the support coil
Known devices for orienting, fixing and clamping the spring at the time of processing of its ends, as well as gripping the ends of the spring. So, in A.S. USSR 1405938, IPC4 B 21 F 35/00, publ. 08/30/08., Bull. 24 [14] winding of the spring is carried out on a cylindrical mandrel, therefore, the orientation and fixing of the spring in the desired position is carried out by the mandrel itself, and the clamp of the last coil of the spring is carried out using a pinch roller with a cylinder. To eliminate the scroll of the spring, its first machined end interacts with the grip.

 The closest analogue to the capture device of the support coil of the spring mechanism for forming a node on the support coil is the device described in a. from. USSR 996012, M.C. 3 B 21 F 35/02, publ. 02.15.83., Bull. 6 [15], The device for the formation of the node on the supporting coil of the spring. The specified device contains a drive gear with a radial groove and a bending bar at the end of the gear, the inner surface of which is equipped with a cone located coaxially with the gear, with a groove for orienting the support coil of the spring, and a conductor with a strap for securing the support coil of the spring; on the working surface of the bending bar in the place of its conjugation with the end surface of the gear made a groove for the bent end of the spring. The axis of the cone is perpendicular to the axis of the spring. To form a node on the support coil of the spring, it is mounted on the conductor in the groove of the bar, where a part of the support coil is placed. When the conductor with the spring is pulled over the knot gear, the spring is engaged, oriented and clamped on the support coil of the spring: the spring enters the gear groove and the cone groove on the gear with the support coil; the support coil of the spring is located in the cone so that the axis of the cone is tangent to the support coil at its apex; by means of the strap and the rotation of the gear relative to the cone, the clamping and orientation of the support turn occurs; when the gear is rotated, its bending bar bends the end of the spring beyond its supporting coil, forming a knot on it.

 A disadvantage of the described device for capturing the support coil of the spring mechanism for forming a node on the support coil is that the coil of the spring is caught limited in size by the groove of the cone; the cone holds the coil only at the apex of the cone and supports it at the base of the cone, therefore, holding the coil is unreliable, and its spatial orientation and the orientation of the end of the spring are uncertain; the implementation of the conical capture in the gear housing creates the problem of the reference coil getting into the gear body when the conductor is moved onto the gear, which leads to a malfunction of the machine as a whole. In addition, the design of the gear itself and its large dimensions, determined by the dimensions of the support turn, is complicated, which leads to greater energy consumption when the large gear rotates.

 The objective of the invention is to ensure reliable capture of the spring during the mutual movement of the spring and the conical gripper, eliminating malfunctions in the operation of the machine by eliminating a miss when the spring enters the conical gripping mechanism of the node formation, simplifying the design of the gear itself and reducing its energy consumption when it is moved to the spring and knotting (knotting).

 The problem is solved in a device for capturing a spring of a mechanism for forming a node on a support coil containing a conical grip of each support coil with a cone, with the possibility of movement of the conical gripper and the spring relative to each other, in which the cone grips for two support coils are each made in the form of a pair of cones - internal and external, installed one in another coaxially and counter, i.e. the larger base of the inner cone lies in the plane of the smaller base of the outer cone, while the radius of the base of the outer cone is greater than the radius of the base of the inner cone by an amount equal to the diameter of the wire used for the spring, with the formation of a bell between the cones facing the spring, i.e. cone grips are facing each other with sockets, with the formation of an annular area between the cones at the base of the cone gripper with a seat under the spring support in the form of a gutter of square or conical section with the side of the section (height) equal to the diameter of the wire used (taking into account the technological gap), with a diameter of the platform equal to the diameter of the support coil, rigidly fixed to each other. In this case, the conical grips for the support coils are installed at an angle to each other (opening angle) or parallel, opposite each other, coaxially with the spring installed in knotting mode, at a distance not less than the axial size of the spring, with the possibility of rapprochement. When installing the grippers at an angle to each other, they are made with the possibility of rotation relative to each other to a position coaxial with the spring, when installed parallel to each other opposite each other with the possibility of reciprocating motion.

 This embodiment of the conical gripper for the spring makes it easy to catch the spring in the conical space (bell) with a wide opening towards the supporting coil of the spring when they are mutually sliding against each other, grab the spring between two conical grippers with a subsequent reduction in the distance between the grippers, holding the spring in the conical capture in the trench not at two points of the support coil, but along its entire perimeter, reliably fixing this support coil in the mechanism of formation of the node. In this case, the knot gear can be made smaller, more simple in design.

 The design of the device for capturing the spring of the mechanism of formation of the node is illustrated in figa, b, c. Description of the design and operation of the device are given below.

The device moves the spring mechanism of the formation of the node on the support coil
Known devices for the movement of the spring in the mechanism of formation of the node on the support coil. So, in A.S. USSR 1405938, IPC4 B 21 F 35/00, publ. 08/30/08., Bull. 24 [14] the movement of the spring for processing the ends of the spring is carried out by moving the cylindrical mandrel, on which the spring is wound, using a rack with gear mounted on the splines of the spindle shaft with the mandrel.

 The closest analogue of the device for moving the spring of the mechanism of formation of the node on the support coil is A. with. USSR 996012, M.cl .. 3 B 21 F 35/02, publ. 02.15.83., Bull. 6 [15]. The device comprises a drive gear with a radial groove and a bending bar at the end of the gear, the inner surface of which is provided with a cone located coaxially with the gear, with a groove for orienting the support coil of the spring, and a conductor with a strap for securing the support coil of the spring; on the working surface of the bending bar in the place of its conjugation with the end surface of the gear made a groove for the bent end of the spring. The axis of the cone is perpendicular to the axis of the spring. To form a node on the support coil of the spring, it is mounted on the conductor in the groove of the bar, where a part of the support coil is placed. When the conductor with the spring is pulled over the knot gear, the spring is engaged, oriented and clamped on the support coil of the spring: the spring enters the gear groove and the cone groove on the gear with the support coil; by means of the strap and the rotation of the gear relative to the cone, orientation and clamping of the support turn occurs; when the gear is rotated, its bending bar bends the end of the spring beyond its supporting coil, forming a knot on it.

 The disadvantage of this device is that it does not provide for the movement of the spring immediately before its clamp in order to install it in such a position that the size of the end of the spring, twisted into a knot on the support coil, is strictly defined. It is problematic to install a spring in the conductor with the free end of the support coil to form a node from it on the support coil in automatic mode. The end of the support coil of the spring for the node from the workpiece to the workpiece may have a different length, variable over a fairly wide range. As a rule, the machine for winding springs is configured for a certain number of nodes on the support turn, the number of revolutions of the knot gear, the parameters of the kinematic scheme of the knot gear depend on their number; if the length of the end of the support coil going to knot will change from spring to spring, the quality of the node will be poor. If the end length is too long, the knot end can touch adjacent spring coils, which can cause deformation of the spring itself, the end of the support coil, it can remain untwisted, impairing the quality of the spring, cling to other springs and machine parts, which can lead to a malfunction of the machine; a too short end of the spring will not be enough to wind the required number of rings in the assembly; in general, the assembly will be unreliable and of poor quality.

 The objective of the invention is to accurately determine the required length of the end of the support coil, going to the formation of the node on the support coil, in the automatic capture mode of the spring, thereby improving the quality of the springs, eliminating malfunctions of the machine as a whole.

This problem is solved by the design of the device for moving the spring of the mechanism of formation of the node on the support coil, including a conical gripper of the spring with a groove, with the means of moving the conical gripper and the spring relative to each other, in which the conical gripper for each supporting coil is made in the form of a pair of cones internal and external, installed one in the other coaxially and counter, i.e. the larger base of the inner cone is located in the plane of the smaller base of the outer cone, with radii of the bases, the difference between which is equal to the diameter of the wire used for the spring, located in the bell to the spring, with the formation of a seat between the cones in the base of the cone grip under the support coil of the spring with a diameter equal to the diameter of the support the coil, rigidly fixed to each other, the capture groove is made at the end of the support coil of the spring, necessary for knotting, at the base of the conical capture (at the base in morning cone) is oriented in a plane perpendicular to the axis of the spring installed in the knotting mode groove geometric dimensions (width and length) of the conical gripping determined from inequalities:
NπD + h <l <spring pitch,
where l is the geometrical dimensions of the groove (its width and length), equal to the required length of the end of the support coil of the spring, going to knotting;
N = an integer equal to the number of complete rings in the node; usually N = 2 or 3, but may be different;
πD is the circumference of one ring from the end of the support loop;
D is the diameter of the ring from the end of the support loop;
h is the distance between the reference and the inner loop in the area of the node,
the moving means is additionally provided with a plate rigidly fixed to the conical grip at the groove wall from the side opposite to the end point of contact of the support turn in the conical grip, the working surface of which is facing the groove,
made protruding beyond the conical grip and oriented parallel to the longitudinal axis (length) of the groove or at an acute angle to it, and the orientation of the working surface of the plate at an acute angle is more preferable. The length of the protruding portion of the plate beyond the grip is preferably greater than the radius of the support loop; the specified length may be less, but for greater reliability of the contact of the end of the spring, the first option is preferable.

 The implementation of the device of this design with the mutual movement of the spring and the grips will allow the spring at the end of its installation in the conical grippers, having bumped into the plate with its end, make an additional rotational movement (in the plane of the drawing counterclockwise), as a result of which the excess part of the end of the support coil is large, than the transverse size of the groove, it will go into a conical grip, and only a strictly fixed length will remain in the groove, determined by the dimensions of the groove according to the formula indicated above. The design of the device is illustrated in figv.

 A description of the design of the device in statics and its operation are given below.

The orientation device of the support coil of the spring mechanism for forming a node on the support coil
Known devices for orientation, fixation and clamping of the spring at the time of processing of its ends. So, in a. from. USSR 1405938, IPC4 B 21 F 35/00, publ. 08/30/08. , bull. 24 [14] winding of the spring is carried out on a cylindrical mandrel, therefore, the orientation and fixing of the spring in the desired position is carried out by the mandrel itself, and the clamp of the last coil of the spring is carried out using a pinch roller with a cylinder.

 The closest analogue of the device orientation of the support coil of the spring of the mechanism of formation of the node on the support coil is A. with. USSR 996012, M.C. 3 B 21 F 35/02, publ. 02.15.83., Bull. 6 [15]. The device comprises a drive gear with a radial groove and a bending bar at the end of the gear, the inner surface of which is provided with a cone located coaxially with the gear, with a groove for orienting the support coil of the spring, and a conductor with a strap for securing the support coil of the spring; on the working surface of the bending bar in the place of its conjugation with the end surface of the gear made a groove for the bent end of the spring. The axis of the cone is perpendicular to the axis of the spring. To form a node on the support coil of the spring, it is mounted on the conductor in the groove of the bar, where a part of the support coil is placed. When the conductor with the spring is pulled over the knot gear, the spring is engaged, oriented and clamped on the support coil of the spring: the spring enters the gear groove and the cone groove on the gear with the support coil; by means of the strap and the rotation of the gear relative to the cone, orientation and clamping of the support turn occurs; when the gear is rotated, its bending bar bends the end of the spring beyond its supporting coil, forming a knot on it.

 The disadvantage of this device is the orientation of the support coil of the spring of the formation mechanism of the node on the support coil is that the orientation of the support coil and its clamp are carried out only on a part of its length, in fact, on a short arc of the coil, determined by the width of the conductor, and two points: the contact points of the spring with the top of the cone and the base of the cone; a large (lower) part of the support coil hangs in the air, which does not provide the required reliability of orientation and clamping of the support coil; this, in turn, leads to the fact that the support coil can bend, “walking” with its free end in a large unlimited space; the diameter of the support coil from spring to spring during node formation and large acting bending loads on it varies over a fairly wide range, the support coil is deformed, which leads to non-standard final products, i.e. to deterioration of the quality of the finished springs.

 The objective of the invention is a clearer and non-disruptive orientation of the support coil of the spring when exposed to large deforming stresses during knotting and thereby ensuring the required diameter of the support coil of the spring, maintaining the shape of the support coil of the coil spring when a node is formed on the support coil at the time of knotting, thereby increasing degree of standardness of the spring and their quality.

 The problem is solved in the orientation device of the support coil of the spring of the assembly formation mechanism on the support coil, containing for each end of the spring a conical gripper with the possibility of movement of the conical gripper and the spring relative to each other, in which the conical gripper is configured to be aligned with the spring in knotting mode, conical the grip for each supporting coil is made in the form of a pair of cones - internal and external, installed one in the other coaxially and counter, i.e. the larger base of the inner cone lies in the plane of the smaller base of the outer cone, and the radius of the smaller base of the outer cone is greater than the radius of the larger base of the inner cone by the diameter of the wire used for the spring, the cones are arranged in a bell towards each other, i.e. to the spring, with the formation of a seat between the cones at the base of the grip under the support coil of the spring in the form of a square, conical cross-section with a side of the cross-section of a size equal to the diameter of the wire used (taking into account the technological gap), with a diameter of the platform (base of the gutter) equal to the diameter of the support of the coil, rigidly fixed to each other, the device is equipped with a restrictive plate with protrusions, the end pads of which (ends) are located in an arc with a radius not greater than the difference between the radius of the support coil of the spring and the diameter of the wire used for the spring and not less than half the circumference of the circle rigidly fixed to the mechanism with the possibility of moving the cone grip relative to the plate, while the outer surface of the inner cone (i.e., the surface facing inward to the inner surface of the outer cone ) and the inner surface of the outer cone are made with sampling by planes opposite the corresponding inner (end) surfaces of the protrusions of the plate with a closed grip in the mode of formation of the node (coax but with a spring set to knot mode). The plate is located at a distance from the base of the conical gripper in its closed position, equal to the diameter of the wire or slightly larger by the size of the technological gap, which can be up to 0.5 mm.

 This solution will allow for non-force "clamping", orientation of the spring support coil in the trough between the two cones of the cone grip, limiting its spatial movement along the axis of the spring to the limits of the "cone grip (trough) - plate" position, preventing the support coil from leaving this space; due to this limitation, the support coil will remain in its seat when the end of it is twisted around it, its diameter will remain unchanged, retain its shape and size, despite the large bending efforts of the support coil, which will allow the support coil of the spring to withstand its standard diameter equal to the diameter of the base capture. This will allow you to achieve a standard diameter of the support coil, equal to the diameter of the base of the cone grip.

 The design of the orientation device of the support coil of the mechanism of the formation of the node on the support coil with the formation of the diameter of the support coil is illustrated figa, b. Description of the design and operation of the device are given below.

The mechanism of formation of the node on the support coil of the spring
In many applications, coil springs must have ends that do not engage with each other and do not damage surfaces in contact with them. This is achieved by machining the ends of the spring, for example by bending, twisting, etc.

 Known technical solutions that provide for bending the ends of the coil spring (see AS USSR 1282948, IPC4 B 21 F 35/00, publ. 15.01.87., Bull. 2 [16]); in the said machine, the bending of the ends is performed using the bending mechanism, consisting of a body and a slider mounted on it. In the guides of the casing there is an unloading roller connected with the slider. Before the material is fed to the winding mandrel, its front end is bent when the slider moves in one direction, and after winding the spring, its rear end is bent by the same slider to the other side. For springs, simply bending the ends is often insufficient, for example for springs used in the furniture industry.

 The closest analogue to the mechanism of formation of the node on the support coil of the spring is A. with. USSR 996012. M.cl. 3 B 21 F 35/02, publ. 02.15.83., Bull. 6 [15], A device for forming a node on a spring support coil, comprising a drive gear with a radial groove and a bending bar at the end of the gear, the inner surface of which is provided with a cone located coaxially with the gear, with a groove for orienting the spring support coil, and a conductor with a strap for fixing the support coil of the spring; on the working surface of the bending bar in the place of its conjugation with the end surface of the gear made a groove for the bent end of the spring. The axis of the cone is perpendicular to the axis of the spring. To process the ends of the spring, it is installed on the conductor in the groove of the bar, where part of the support coil is placed. When the conductor with the spring is pulled over the knot gear, the spring is engaged, oriented and clamped on the support coil of the spring: the spring enters the gear groove and the cone groove on the gear with the support coil; by means of the strap and the rotation of the gear relative to the cone, the clamping and orientation of the support turn occurs; when the gear is rotated, its bending bar bends the end of the spring beyond its supporting coil, forming a knot on it. The knot gear contains both a groove clamp and a cone clamp on the side of the spring, inside the gear, the coil of the spring is located in the cone so that the axis of the cone is tangent to the support coil at the top of the cone, and there is a clamp and orientation of the spring; the gear with the cone combines the functions of: gripping, clamping, holding and knotting.

 Installing a spring in a conductor with a bar in the automatic mode of the machine is problematic and more consistent with its manual installation.

 The conductor with the spring on the gear wheel is driven in progress, while the conical grip is perpendicular to the axis of the spring. The capture of the support coil of the spring, its orientation and clamping are carried out only on part of its length; in fact, the spring is fixed along a short arc of the coil, determined by the width of the conductor, and two points: the contact points of the spring with the top of the cone and the base of the cone; a large (lower) part of the support coil hangs in the air, which does not provide the required reliability of either gripping, or clamping and orientation, and is a drawback of the mechanism, especially when large bending forces occur when bending the small end of the spring. Unreliable gripping and clamping of the spring lead to uncertainty in the spatial orientation of the spring, to the possibility of the spring shifting relative to the gear, to changing the geometrical dimensions of the support loop during knotting, and the malfunction of the machine as a whole.

 When the conductor with the spring hits the gear wheel, a "hard blow" occurs on the spring, additionally knocking down both its orientation and worsening its clamp. All this affects the quality of the spring. In addition, with a “hard impact” unpredictable wear of the mechanism elements takes place, which leads to a limited life of the machine for winding springs as a whole. Additionally, the large dimensions of the gear, determined by the dimensions of the support turn, lead to greater energy consumption during rotation of the knot gear.

 The objective of this invention is to ensure the operation of the mechanism, in particular, gripping and clamping, in automatic mode, increasing the reliability of gripping, holding the spring during knotting, clamping and rigid orientation relative to the nodes processing ends, which means improving the quality of the springs, reducing shock loads when gripping the spring , its initial contact with the gripper, knot gear, reducing malfunctions of the machine, increasing the life of the mechanism and the machine as a whole.

 The problem is solved in the mechanism of the formation of the node on the support coil of the spring, containing for each end of the spring knot gear with a radial groove for the support coil and a bending bar at the end of the gear with the possibility of rotational movement of the gear with the bending bar relative to the supporting coil of the spring (around the supporting coil of the spring), conical capture of the support coil with a groove, with the possibility of movement of the conical gripper and gear relative to each other and relative to the spring, in which the conical grippers are made with a conical socket towards each other (towards the spring), with a seat under the support coil at the base of the grip between the cones with a diameter equal to the diameter of the support coil, the groove of the conical grip is made at its base opposite the knot gear, the longitudinal and transverse dimensions of which are determined not less than the size of the end of the support coil the spring required for the formation of the node, the height of the knot gear with the bending bar is less than the transverse size (width) of the groove of the conical gripper, the grippers are set in the initial position by their base and at an angle to each other or parallel opposite to each other at a distance of not less than the axial size of the spring, the conical grip for each supporting coil is made to be installed coaxially with the spring, mounted on the support of the mechanism with the possibility of convergence of the conical grippers with each other with rotation in the case of the location of the grips at an angle to each other or translationally with their parallel arrangement in the initial state; the bevel grip and knot gear are each connected to the cam of the knot formation mechanism through a kinematic chain, the two end links of which are on the side of the bevel grip, the gears are interconnected with their previous link and with the bevel grip, the gear along the rotation axes parallel to each other, with the possibility setting the rotation axes in one line, i.e., with the possibility of moving the middle rotation axis to the line connecting the extreme rotation axes, one of the links of the kinematic chain of the gripping movement, the gear is equipped with a boundary reader (focus) of the movement of the middle axis of rotation. Structurally, the knot gear with a drive spline gear is installed in a knot knob attached to the plate with the possibility of movement relative to the axis of the conical gripper in its closed position, i.e., relative to the axis of the spring installed for knotting, preferably a rotary rather than translational movement, knot knob on the end face is made with a groove located opposite the groove of the conical gripper and the inner coil of the spring, the width is greater than the diameter of the spring wire by an amount that takes into account the lift m coil spring. At the same time, the connection of the knot gear with the cam of the knot formation is carried out through the mount plate of the knot knitting box. The thickness of the box should be less than the groove of the cone grip.

 The presented design of the kinematics of the mechanism using the strut system allows you to reliably grab the spring, rigidly and securely fix it around the entire perimeter of the support coil in the knotting position, from the ends of the spring, excluding shear, displacement of the spring regardless of the deforming forces applied to it, which ensures the quality of the resulting assembly springs; the brace during its "straightening" slows down the movement, which ensures the capture of the spring at low speeds of gripping the spring immediately before it comes in contact with the conical grippers and with the knot box, and also securely fasten the spring in the knot mechanism. In this case, the spring is trapped without fail in automatic mode.

 The design of the mechanism is illustrated in figures 1, 6a, b. A description of the mechanism of the formation of the node on the supporting coil of the spring in statics and its operation are given below.

 The spring clamping device of the assembly mechanism of the assembly on the support coil of the spring.

 Known device orientation, fixing the spring at the time of processing of its ends. So, in a. from. USSR 1405938, IPC 4 B 21 F 35/00, publ. 08/30/08., Bull. 24 [14] winding the spring is carried out on a cylindrical mandrel, therefore, the orientation and fixing of the spring in the right position is carried out by the mandrel itself with the clamp of the last coil of the spring using a pinch roller with a cylinder.

 The closest analogue of the device for fixing the spring mechanism for the formation of a node on the support coil is the device described in A.S. USSR 996012, M. cl. 3 B 21 F 35/02, publ. 02.15.83., Bull. 6 [15], The device for the formation of the node on the supporting coil of the spring. The specified device contains a drive gear with a radial groove and a bending bar at the end of the gear, the inner surface of which is provided with a cone located coaxially with the gear, with a groove for orienting the support coil of the spring, and a conductor with a strap for fixing (fixing) the support coil of the spring; on the working surface of the bending bar in the place of its conjugation with the end surface of the gear made a groove for the bent end of the spring. The axis of the cone is perpendicular to the axis of the spring. To form a node on the support coil of the spring, it is installed on the conductor in the groove of the strip, where it is placed and where the part of the support coil is fixed (clamped). When the conductor with the spring is pulled over the knot gear, the spring is gripped, additionally oriented and clamped on the spring support coil: the spring enters the gear groove and the cone groove on the gear with the support coil; by means of the strap and rotation of the gear relative to the cone, the orientation and clamping of the support turn occurs; when the gear is rotated, its bending bar bends the end of the spring beyond its supporting coil, forming a knot on it.

 The disadvantage of this device is that the clamp of the support loop is carried out only on part of its length; in fact, the spring is fixed along a short arc of the coil, determined by the width of the conductor, and two points: the contact points of the spring with the top of the cone and the base of the cone; the main (lower) part of the support coil hangs in the air, which does not provide the required reliability of orientation, fixation, clamping, especially when there are large bending forces that occur when the small end of the spring is bent. An unreliable spring clamp leads to a change in the geometric dimensions of the support coil during knotting and a defective assembly from the end of the spring.

 The objective of this invention is to increase the reliability of fixation, spring clamping in knotting mode.

 The problem is solved in the spring clamping device of the assembly formation mechanism on the support coil of the spring, containing for each end of the spring a conical gripper of the support coil with a groove, with the possibility of movement of the conical gripper relative to the spring, with means for fixing (securing) the spring, in which the conical gripper for supporting coils made with a seat under the support coil with an annular platform at the base with a diameter equal to the diameter of the support coil of the spring, a groove made at the end of the support coil of the spring at the base of the cone grip perpendicular to the axis of the spring installed in the knotting mode, the conical grips are installed with their bases at a distance (at an angle to each other or parallel opposite each other) not less than the axial size of the spring, with the possibility of convergence and installation of each of them coaxially with the spring, means for fixing (fixing) the spring is additionally equipped with a liner with a pin protruding above the surface of the liner, one side surface of which, facing the spring, can be made beveled at an acute angle to the axis of the springs Equal to the angle lifting coil, the insert is rigidly fixed in the conical capturing his groove liner surface facing the spring installed in the knotting mode may also be formed at an acute angle to the axis of the spring, i.e. to the axis of the conical gripper in its closed position, with platforms for part of the support and previous (inner) coil of the spring, the angle between the planes of which is equal to the angle of the coil, and a stop rigidly fixed to the base of the mechanism and located in the closed position of the conical gripper opposite the liner; its counter surface is also equipped with platforms for part of the support and internal coils parallel to the liner platforms; the emphasis is also provided with a plug with internal dimensions corresponding to the overall dimensions of the liner pin located opposite the pin in the closed position of the grippers. The gap between the opposing pads of the liner and the stop for the support coil in the closed cone grip position is determined by the diameter of the wire used for the spring. The gap between the opposing pads of the liner and the stop for the inner coil in the closed cone grip position is determined by a value slightly larger (not less) than the diameter of the wire used for the spring. This value should be small and allow some slight movement of the inner coil within 0.3 mm, determined empirically and depending on the parameters of the spring and other design features. The platform for the supporting coil of the spring on the liner can be made with approaching the side surface of the liner from the side of the groove of the conical gripper.

 This solution allows you to reliably fix and fix the support coil and fix the previous internal coil of the spring in the end machining mechanism without clamping it, eliminating the distortions of the spring with large bending forces acting on it during the formation of the nodes, to improve the quality of the spring assembly and the spring itself. The design of the proposed solution is illustrated in figa, b, c, d, e. Description of the solution in statics and its operation are given below.

Cam means of the mechanism of the formation of the node on the supporting coil of the spring
Known devices for processing spring ends, the operation of which is controlled by a cam. So, in acSU 1657263, IPC 5 B 21 F 35/02, publ. in BI 23 [17], the machine for winding springs contains a mechanism for forming ends in the form of half rings, made in the form of levers of preliminary bending pivotally mounted on the frame with rollers fixed to them and a slider connected by a rod to the camshaft cam.

 The disadvantage of this tool is its lack of functionality.

 The closest analogue selected cam tool [1] by A. with. 1570826, from which the end machining mechanism works and which is a double cam, both parts of which are fixed on one working shaft; one cam is connected to the punch and bending finger, the other interacts with a two-arm lever and two additional fingers. The shape of the first cam with a lifting section allows you to raise the punch with the bending finger for squeezing the clip and removing the end of the wire from its groove, forming the rear end of the spring without slightly bending it, then take the punch down. The second cam, through the lever interacting with it, drowns one finger, releasing the other, thereby tearing off the end of the spring from the recessed finger, and the latter bends to the required dimensions under the action of deformation and impact forces against the support and the released second finger.

 The disadvantage of the cam means is the presence of unpredictable shock deformations, the possibility of malfunctions of the machine as a result of this, the insufficient functionality of the cams, since they do not participate in the control of other nodes of the node formation mechanism on the support turn.

 The objective of the invention is to provide a cam means of the mechanism of the formation of the node on the support coil of the spring, which allows to carry out sequentially a number of actions necessary for processing the ends of the two support coils of the spring in automatic mode, as well as without impact deformation.

 The problem is solved by the design of the cam means of the mechanism, which is a composite cam mounted on the working shaft and interacting through its contact elements with actuators, in which the contact elements are made in the form of rolling rollers, for example rolling bearings, the cam is made up of three parts: the middle part, power, and two side cams: for controlling the movement of the knot knitting gear (gear) (knot gear cam) and for controlling the movement of the cone grip (cone grip cam), the side cams are each made with a side surface consisting of four zones, one of which for both cams - the waiting area - is an arc of a smaller radius, non-working, the length of which is determined by the time of waiting for the cone grip and the waiting time of the knot box ( gears), (about 1/4 of the cycle, but the calculation can be done on another part of the cycle), and its radius is determined by the layout of the elements of the end processing mechanism (their location relative to the working shaft of the gear End work) in standby mode. Opposite the arc of waiting for the cam of the knotter box (gear), there is a contact zone, which is an arc of a circle of a larger radius, the length of which is determined by the residence time of the knotter box (gear) in contact with the spring blank - the contact time of the box (knotter gear) with the spring, and its radius is determined the location of the knitting box (gear) relative to the working shaft in contact with the spring. The length of the similar arc of the contact cam of the conical grippers opposite to its waiting area is determined by the time the conical grippers stay in contact with the spring (the arc of contact of the conical grippers with the spring), and the radius is determined by the location of the conical grippers relative to the working shaft in the contact mode directly at the spring, both arcs of waiting and contact of each of the cams are located on different sides from the axis of rotation of its cam and are connected to each other by two rectilinear branches (direct and reverse) on each side, the side cams the tabs can be made symmetrical with respect to the line connecting the centers of the arcs of expectation and contact, the middle power part of the composite cam is equipped with stops located each opposite its opposite branch parallel to it at a distance equal to the diameter of the corresponding rolling roller at the end of the contact zone of its cam, and made ends with an arc facing its reverse branch, with the possibility of interaction with its obkatnoy roller, obkatnye rollers are located on their side surface opposite the side surface st of your cam on different axes of rotation. Rollers can be made with the same radii. The length of the arc of contact of the conical grippers with the spring is greater than the length of the arc of contact of the knot gears with the spring.

 Performing a cam of this design will allow the following operations to be carried out sequentially in strict sequence: first, inform the movement of the conical grippers, grab the spring from its ends by the support coils, bringing the conical grips closer to the distance equal to the axial size of the spring, and make the conical grippers contact the spring, then bring knotting gears in knotter boxes moving into motion, sliding them into the groove of the knot, making contact of the knotting gear with the spring to process the ends of the spring, twisting Nia them in a ring around the reference coil by performing these operations in automatic mode, then processing ends after the spring in the reverse order, without interruption return constituent elements of the mechanism assembly in the initial position. The ability to perform all these operations expands the functionality of the cam in automatic mode. The specified strict sequence of operations eliminates malfunctions in the operation of the mechanism of formation of the node and the machine as a whole, increases the reliability of its operation.

 The design of the cam means of the mechanism of the formation of the node on the support coil is shown in figure 1, 2B, 3.

 A description of the design in statics and the operation of the cam means are given below.

The movement mechanism (its options)
Known spring-coiling machines containing various mechanisms for moving workpieces from one workpiece processing zone to another (see, for example, RF patent 2147965, IPC 7 B 21 F 35/00, publ. 04/27/2000, bull. 12 [ 18]). The specified mechanism for moving the workpieces is made in the form of an inclined slice with a pneumatic vibrator, a conveyor and a control tray.

 The closest analogue for both versions of the mechanism for moving the spring blanks is the manipulator for transferring the spring blanks from the winding mechanism to the means for bending the ends of the spring in the Automatic machine for the manufacture of springs according to AS USSR 1052304, IPC B 21 F 35/02, publ. 11.11.83. bull. 41 [2], kinematically connected by means of a system of levers with a camshaft of the machine, comprising a lever grip consisting of two levers, one ends of which are connected to each other along the axis with the possibility of rotation around this axis of one of the levers relative to the other, with means for closing and disclosure capture. The means for opening the manipulator grip consists of a backstage mounted on the frame with cams, a pusher and pins fixed to the gripping levers, interacting with the backstop cams and the pusher.

 The specified movement mechanism has a limited scope and is not suitable for moving workpieces of sufficiently large dimensions, made of thick wire, with a large weight. The clamping device is not reliable enough, in addition, the applied displacement scheme is unacceptable for the proposed design, and it is difficult to achieve high volume inside the machine using layout solutions that allows the use of rack and pinion systems. The moment of spring clamping in a known grip is associated with shock loads on the spring, which leads to a change in its shape, and also reduces the service life of the grip parts.

 The objective of the invention is to provide a mechanism for moving large springs with large weight characteristics with a reliable grip and reduce shock loads on the gripping elements and on the spring itself at the time of gripping.

 The problem is solved by the design of the mechanism of movement of the spring workpiece, including a lever grip of two levers: movable and stationary, which are connected along the axis of rotation of the movable lever relative to the stationary in a plane perpendicular to the move of the movable lever, and are configured to contact the ends of the levers with each other with a gap equal to the diameter of the wire of the spring billet, means for moving the gripper with a system of levers of kinematic communication with the working shaft of the machine, means for closing and opening the gripper a, in which the lever grip is made with the possibility of making rocking movements between its extreme positions, the means for closing and opening the gripper contain a rod, one end fixed to the movable lever along the axis "a" parallel to the axis of rotation of the movable lever, with the possibility of rotation about this axis , the other end connected to the bracket along the middle axis of the strut "b" with the possibility of rotation about this axis parallel to the axis of rotation of the movable arm, the bracket is mounted on a fixed arm along the axis "b", with the ability to rotate around this axis parallel to the axis of rotation of the movable arm, an opening sleeve configured to impact contact with the opening lever in one extreme gripping position, a closing sleeve configured to interact in the opposite direction (as shown by the arrows in the figure), with the lever closing in the other extreme position of the capture (extreme left position), mounted on different arms of the rocker; opening-closing bushings can be combined in one part or made in the form of two parts; the sleeves made in the form of two parts can be located on different sides from the axis “b” of the connection of the rod with the bracket both horizontally and vertically; depending on the type of execution of the bushings (in the form of one part or two) and their relative position, their interaction with the opening-closing levers will have different or identical directions; so, the location of two bushings diagonally relative to the axis "b" should imply the application of the force of the opening-closing of one direction, in other cases the opposite direction; the beam is rigidly mounted on the bracket at a point located preferably in the immediate vicinity of the axis "b" of the connection of the bracket with the rod, while the rod and the bracket with their rotation axes "a", "b", "c" form a strut system, made with the possibility setting axes "a", "b", "c" in one straight line, i.e. with the possibility of moving the center axis “b” of the strut to the line “a-c” connecting the extreme axes “a”, “c”, or with the transition of this line to its opposite side (with the formation of a deflection arrow) and vice versa. The grip opening-closing means is equipped with a stroke limiter for the middle strut axis (axis “b” of the connection of the rod with the bracket) mounted on the stationary locking lever under the middle axis (line “a” - “c”) at a distance of not more than 3 mm from the middle line a -c, i.e. with the limitation of the deflection boom to 3 mm. For symmetry of the shock load, the beam can be structurally doubled, between the two planes of which the bracket is located.

 The problem is also solved by another design of the mechanism for moving the spring workpiece, including a lever grip of two levers: movable and fixed, which are connected along the axis of rotation of the movable lever relative to the fixed one, and are configured to contact the ends of the levers with each other with a gap equal to the diameter of the spring wire blanks, means for moving the gripper with a system of levers of kinematic communication with the working shaft of the machine, means for closing and opening the gripper, in which the lever gripper made with the possibility of making rocking movements between its extreme positions, the means for moving the gripper includes a swing axis of the gripper, made in the form of a torsion shaft, at one end of which a fixed gripping lever is fixed by means of a splined connection, means for closing and opening the gripper include a brace pull, one end mounted on a movable arm with the possibility of rotation around the axis "a" parallel to the axis of rotation of the movable arm relative to the stationary arm, the other end with the bracket with the ability to rotate relative to the middle axis of the strut "b" parallel to the axis of rotation of the movable arm relative to the fixed arm, the bracket is mounted on the stationary arm to rotate relative to the axis "b" parallel to the axis of rotation of the movable arm relative to the stationary arm, an open-close link on the bracket with the possibility of rotation around an axis parallel to the axis of rotation of the movable arm relative to the stationary arm, preferably located in close proximity t axis "b" of the connection of the first link with the bracket, the other end connected to one arm of the rocker arm along the axis of rotation perpendicular to the axis of rotation of the movable lever relative to the fixed, the axis of rotation of the rocker arm is fixed to the lever connected by a spline connection to the other end of the torsion shaft, the fixed plate is rigidly fixed on the machine frame, equipped with one pair of stops located on opposite sides of the second arm of the rocker arm opposite its end with the possibility of their impact interaction with the second arm of the rocker arm , and a plate with another pair of stops on its sides, while the angular distance between the stops of different pairs differs by the double twist angle of the torsion shaft, between the stops of the plate there is an open-close lever with the possibility of shock contact interaction with them, rigidly connected with the fixed locking lever mounted on a torsion shaft using a spline connection. In this case, the axes a, b, c make up the strut system with the possibility of aligning the axes in one line, i.e. with the possibility of moving the middle axis of the strut "b" to the line "a" - "c" or with the transition of this line "a" - "c", with the formation of a deflection arrow. The lever of the stops can additionally be equipped with stops, made with the possibility of their adjustment, mounted on the lever from the side of the stops with the possibility of interaction of the lever with the stops through these stops. Additionally, the fixed lever is equipped with a stroke limiter for the axis “b” of the connection of the rod with the bracket, the limiter is located under this axis at a distance from the midline of not more than 3 mm. The limiter provides an arrow of a deflection no more than 3 mm.

 The use of the strut system provides greater actuating forces and a decrease in the travel speed of the movable arm relatively stationary at the end of its movement during the closing of the gripper, thereby reducing the shock loads of the gripper on the spring and mechanism parts. The proposed solutions expand the scope of the movement mechanism, which allows you to transfer spring blanks of a sufficiently large size and heavy weight, with a reliable clamp, simple in design, to eliminate shock loads at the time of capture of the workpiece, thereby increasing the life of the mechanism and ensuring high quality undeformable during the movement springs. The design of the mechanisms is illustrated in figures 1, 5a, b, 8a, b; description of the design and operation of the movement mechanisms are given below.

Gripper mechanism for moving the spring
Known devices for capturing the spring [15], containing a gear equipped with a cone with a groove. When a spring enters the groove of the cone by turning the gear relative to the cone, the coil of the spring is clamped. When the gear is rotated relative to the cone, rotation, displacement of the spring inside the cone is also possible. Due to the location of the coil of the spring inside a large conical space, the spring is fixed in space with a sufficient degree of uncertainty.

 The closest analogue to the proposed solution is the capture of the manipulator for transferring the workpiece of the spring in the Machine for the manufacture of springs according to AS USSR 1052304, IPC B 21 F 35/02, publ. 11.11.83. bull. 41 [2], kinematically connected through a system of levers with a camshaft of an automaton containing a lever grip, consisting of two levers, one ends of which are connected to each other along the axis with the possibility of rotation around this axis of one of the levers relative to the other, which are made with the possibility of contact the ends of the levers with each other with a gap equal to the diameter of the spring wire, with means for closing and opening the grip.

 The specified capture when it is opened has a large zone of uncertainty in the position of the spring workpiece, determined from the end of the levers to the place of their connection with each other; the spring billet is grabbed by levers in its arbitrary orientation, which causes it to skew in space, as a result, the billet falls into the machining zone that is next in the technological cycle and also in any orientation, it may not be captured or retained by the grips of this zone, which will lead to rejection and malfunction the whole machine. These problems become especially relevant when it is necessary to capture and hold in an automatic mode complex shaped products, such as cylindrical, conical and other springs.

 The objective of this invention is to provide a reliable grip of the coiled spring billet with the necessary, guaranteed orientation in space, and, therefore, with respect to other subsequent mechanisms for processing the spring billet, ultimately the smooth operation of both the gripper and the machine as a whole, reducing defective products.

The problem is solved by the design of the gripping mechanism of the movement of the coiled spring workpiece, including a lever grip with the possibility of opening and closing, consisting of two levers: movable and stationary, which are made with the possibility of contact between the ends of the levers with each other with a gap equal to the diameter of the spring wire, in which the ends of the levers of the same name at the end of the grip are equipped with limiters of the spatial position of the spring at the time of its capture, mounted on a fixed arm and on a movable arm. Limiters
made with the possibility of interaction with each other with a minimum gap equal to the diameter of the wire used for the spring. The limiter of the fixed lever is a plate rigidly mounted on the fixed lever, at the end equipped with a wedge-shaped guide, and on the sides with two stops located symmetrically relative to the longitudinal axis of the plate along it, made with two beveled surfaces each. The height of the stops is determined by the distance between the movable and fixed levers in the open grip position, not less. The stops are made at the end of the plate along it, with some shift from its frontal edge, namely, near the base of the wedge-shaped guide, with the formation of a platform under the part of the coil of the spring shown in Fig. 5c by a dashed line. One beveled surface of each stop (shown in Fig. 5c with a rare hatch) is inclined toward the wedge-shaped guide and with respect to the plane of the plate; sections of these beveled surfaces located at the same height from the plate are piecewise approximated sections of arcs, upon extension of which, before connecting them to each other, a section of the arc with a radius equal to the radius of the coil of the spring is formed. Each beveled surface from another pair of beveled surfaces (shaded in FIG. 5c is shown) is located at an angle to the plane of the plate equal to 90 ^° . The specified angle is selected for reasons of greater manufacturability, but may be different, other than 90 ^o . The intersection lines of the second beveled surfaces with the plane of the plate are piecewise approximated sections of the arcs, during the extension of which, before connecting them to each other, a section of the arc with a radius equal to the radius of the coil of the spring is formed. The height of the second pair of bevels is not less than the diameter of the wire from which the spring is made. The limiter of the movable lever is also a plate with a width not greater than the distance between the stops of the first limiter, rigidly mounted on the movable lever, located parallel to the plate of the first limiter in the closed grip position. The plate of the second stopper is equipped with two stops symmetrically located relative to the longitudinal axis of the plate, located at an angle to each other at the end of the plate, equal to the angle of the wedge-shaped guide plate of the fixed lever limiter, and at a distance from each other equal to the width of the wedge-shaped guide at the place of their interaction. The stops are provided with two pairs of beveled surfaces, each of which is parallel to the corresponding beveled surface of the first stop (in Fig. 5g, the surfaces meeting the corresponding surfaces of the stops of the other plate of the fixed arm are shown by a similar shading). The distance between counter parallel bevelled surfaces with a closed grip is equal to the diameter of the wire used for the spring.

 The specified design of the grip limits the position of the spring in space, orientates it in a certain position when the grip is closed and allows for uninterrupted operation of the grip and the machine, eliminating the marriage of products and the malfunction of the machine due to the loss of the workpiece during capture and due to its incorrect orientation for the mechanisms for subsequent processing of the workpiece in the machine.

 The specified design of the capture can be used in any of the above options for the mechanism of movement of the spring blanks.

 The design of the capture itself is depicted in any of figures 5a, b, 8a, b, the design of the limiters is shown in figv, d.

 A description of the design of the capture and its operation are given below.

Description of work in statics
Figure 1 shows the kinematic diagram of the machine; on figa, b, c - the shape of the cams and their relative position, as well as the location of the rotation levers of the movement mechanisms on the working shafts of the machine; on figa, b - cam design of the mechanism of the formation of the node on the support coil in various angles; figure 4 - the mechanism of the cabin spring blanks; on figa, b - the capture device of the mechanism for moving the spring workpiece from the cutting zone to the knotting zone in the open and closed position; figure 5 c, d, d, e, g - structural elements of the limiters of the capture device individually in different angles (5c, d) and in the assembly (5e); on figa - the mechanism of the formation of the node on the support coil of two identical components for the right and left ends of the spring; in FIG. 6b is a component of this mechanism for the right end of the spring in a different perspective, in FIG. 6c shows a conical gripper design for a node formation mechanism; Fig.6g is a cross section of the conical capture in the closed position; on fig.6d, e - the design of the liner and its stop for the conical capture of the mechanism of formation of the node; Fig.6g, s - design knotter box in its various angles; 7 is an image of a spring with machined ends; in FIG. 8a, b — capture of the mechanism for moving the spring billet from the knotting zone to the heat treatment zone in the open and closed position.

 The spring-coiling machine includes a wire feed mechanism 1, a spring shaping mechanism 2, a spring blank 3 cutting mechanism, a spring blank moving mechanism 4 from the cutting zone to the knot formation zone on the support spring coil (knotting zone), the knot formation mechanism on the support coil 5, the mechanism 6 for moving the spring billet from the knotting zone to the heat treatment zone, the heat treatment device 7, the batching machine 8, located in the machine body 9 (on its bed), where the electric motor 10 is also installed, is fixed first in its lower part.

 The engine 10 is kinematically connected with a central camshaft 11, which is connected by means of gears to two working cyclic shafts - the first 12 and second 13, as well as V-belt transmission via pulleys 14, 15 of a V-belt variator - with a wire feed mechanism 1. All machine mechanisms, except the mechanism wire feed 1, receive movement and work from two working cyclic shafts 12 and 13, rotating at the same speed in one direction, and the wire feed mechanism - directly from the central camshaft 11.

 The wire feed mechanism 1 contains two pairs of clamping 16 and broaching 17 rollers; the latter through their gears 18 are connected with the shaft 19 of the lingering gearbox. The speed of rotation of the pulleys 14, 15, at least one of which consists of two disks forming a V-shaped stream, installed with the possibility of their mutual adjustment relative to each other, can be adjusted by changing the gap between these disks in order to obtain the required length of the wire stock for springs. The wire feeder is equipped with dies located after the rollers.

 The forming mechanisms 2, cutting 3, the formation of the node 5, the heat treatment device 7 are connected with their software devices made in the form of cams 20-25 with profile side surfaces through rolling rollers 26-31, made, for example, in the form of rolling bearings (see Fig. .1,2a, 2b, 2c).

 On the first working shaft 12, cams of shaping 20, slides 21, cuttings 22 are coaxially mounted with it and rigidly fixed; on the second working shaft 13, cams 23.24 of the assembly mechanism of the assembly, cam 25 of heat treatment are also aligned.

 The lateral working surface of the shaping cam 20 is made curved, the law of changing the distance of each point of which from the axis of rotation of the working shaft 12 of the shaping mechanism 2 corresponds to the law of changing the diameter of the winding spring. If it is necessary to wind a two-cone spring, the lateral working surface of the shaping cam 20 is symmetrical, with a zone of smooth removal of points lying on its surface from the center of rotation of the shaft 12, a zone of maximum removal (with a certain size of the spring, this may be not a zone, but a point), a zone smooth approach to the center of rotation of the shaft 12, and the beginning of the removal zone coincides with the end of the approximation zone, and the axis of symmetry A-A * of the forming cam 20 passes through the center of the maximum removal zone A *, the center of rotation Nia working shaft 12, a * and removal zone beginning / end of approximation the zone A (Figure 2a). The lateral surface of the cam 20 can be made of another shape for the formation of cylindrical, single cone and other springs. The forming cam 20 is connected to the run-in roller 26.

 The cam means of the chopping mechanism 3 is a double cam, consisting of a cam of the slider 21 and a cam of the chopping 22 (fig.2b). Cams are made with the possibility of simultaneous contact of their working surfaces with their rollers 27.28. This can be achieved by the design of the cams and their rollers described below.

 The working surfaces of the rolling rollers 27, 28 are located opposite the surfaces of their cams, made with a common axis of rotation and with different diameters.

 The felling cam 22 is equipped with a working section for lifting its lateral surface m * m **, rectilinear or curved, located with respect to the shaping cam 20 in a place corresponding to the beginning of the shaping of the spring, i.e. the beginning of its lifting portion lies in the contact zone of the rolling roll 26 of the shaping cam with the start zone of the shaping of the spring of the shaping cam 20 (to its middle line, the maximum removal zone for biconical springs). The most optimal location for the beginning of the cutting working zone is the beginning of shaping, in the case of double cone springs at the beginning of its removal zone AA *, corresponding to the second coil of the winding spring, with the steady-state dynamic mode of the winding process, although other options determined by the layout of the machine are not excluded. The size of the cam lifting section 22 (the linear size of its projection onto an arc of a circle with the radius of the beginning of the section centered about *) depends on the diameter of the wire used to wind the spring. The beginning of the working section of the felling cam has a value at which the difference between the distances from the points of the lateral cam of the slide and the felling cam lying on one axial straight line to the axis of rotation of the cams n ** о * and m * о * will be less than the difference of radial sizes (radii) of their rolling rollers 27, 28. This condition is true if the radius of the rolling roller 28 of the felling cam 22 is greater than the radius of the rolling roller 27 of the cam 21, and the lateral surface of the cam 21 is more distant from the axis of rotation of the cams compared to the axial distances of points b the shackle surface of the felling cam 22, as shown in FIG. In other cases, the ratio of the radial (axial) sizes of the rollers and the side surfaces of the cams will be different, opposite. The beginning of the working section of the felling cam 22 may be provided with an arc mm *, the concave side of which is facing the side of the rolling roller 28 interacting with it and whose radius is equal to the radius of this rolling roller. This allows the initial contact of the working surface of the cam of the wheelhouse 22 with its run-in roller 28 not at a point, but in an arc, reducing the contact load on the cam 22 and its wear.

 The lateral surface of the cam cam 21 has a working zone nn ****, when the movement of the working shaft is communicated to the movable knife, and the idle zone n **** n (rolling roller 27 interacts with the cam 21 without transmitting movement). The purpose of the inoperative zone is to keep the knife in its waiting area until the operating mode. The non-working zone n **** n can have an arbitrary shape with a gradual decrease in its radius from the value at n **** to its value at n.

или с другой неконечной точкой участка рубки m*m** кулачка рубки; для большей гарантии того, что в точке рубки сработает кулачок рубки и не будет сбоя работы, необходимо сохранить неизменность радиуса боковой поверхности кулачка подвижки при росте удаленности боковой поверхности кулачка рубки от центра вращения до нужного гарантированного значения, пока кулачок рубки не сработает, поэтому второй вариант предпочтительнее, но работоспособны оба варианта, и их выбор может быть определен точностью исполнения размеров кулачков. Третий участок кулачка подвижки подъемный, конец его совпадает с концом участка рубки кулачка рубки и имеет значение подъема, при котором разность расстояний от точек боковых поверхностей кулачка подвижки и кулачка рубки, лежащих на одной осевой прямой, до оси вращения n***о* и m**о* будет больше разности радиальных размеров (радиусов) их обкатных роликов. При этом должно произойти переключение ролика 28 на ролик 27. Этот участок необходим для обеспечения плавности переключения рабочей поверхности кулачка 22 на рабочую поверхность кулачка 21. Сформулированное условие должно быть соблюдено при тех же изложенных выше оговорках. Длина третьего участка зависит от угла подъема; чем больше угол наклона этого участка, тем быстрее кулачок подвижки достигнет указанного выше значения, тем он короче. Четвертый, последний участок рабочей поверхности кулачка подвижки выполнен подъемным, прямолинейным или криволинейным, с углом подъема (наклоном) того же знака, что и первый рабочий участок кулачка подвижки. Длина четвертого участка определена расстоянием от места рубки до конечного места подвижки ножа при выходе его из зоны рубки в том же направлении, а угол наклона участка определен потребной скоростью выхода ножа из зоны рубки. Как видно, взаимное расположение рабочих участков кулачков 21, 22, их конструкция (размеры, габаритные размеры) и форма этих кулачков и размеры взаимодействующих с ними обкатных роликов 27, 28 предопределяют разновременность работы этих кулачков и предполагают несколько вариантов их исполнения. На фиг.2б больший по диаметру ролик - это ролик 28 кулачка рубки 22, но может быть и другой вариант. При варианте, иллюстрируемом этой фиг.2б, при (n**o*-m*o*)<(R28-R27) контакт будет осуществлен между роликом 28 с кулачком рубки 22, при (n***о*-m**о*)>(R28-R27) будет осуществлен контакт ролика 27 с кулачком подвижки 21. Таким образом, мгновенное соотношение радиусов обкатных роликов и осевых расстояний точек рабочих боковых поверхностей кулачков подвижки и рубки определяют мгновенную рабочую точку того или другого кулачка.The lateral working surface of the cam slider is made with four sections; the first section of the slide nn * before cutting is located before the start of the working section m * m ** of the cutting cam. This advance is associated with the need to move the knife to the cutting room from the zone of its inoperative location in the cutting area. The first section nn * is a lifting branch, rectilinear or curvilinear, the linear projection size of which on an arc of a circle with the radius of the beginning of the section centered at o * is determined empirically depending on the distance from the location of the knife in standby mode to the place of cutting, and the slope (angle slope) is determined by the speed that it is necessary to inform the knife to move it into the cutting zone before cutting; this speed, in turn, depends on the start of the slide (the beginning of the first section of the shift cam) and the remoteness of the knife (its blade) from the cutting area. The second section is made with a constant radius, and its beginning n * is also located before the working section of the felling of the felling cam, and the end coincides with the beginning of the felling

or with another non-end point of the felling site m * m ** felling cam; for a greater guarantee that the felling cam will work at the felling point and there will not be a malfunction, it is necessary to maintain the radius of the lateral cam of the slide cam while increasing the distance of the lateral surface of the cam from the center of rotation to the desired guaranteed value until the felling cam is triggered, therefore the second option both options are preferable, but workable, and their choice can be determined by the accuracy of the execution of the sizes of the cams. The third section of the cam of the slide is lifting, its end coincides with the end of the section of the cabin of the cabin of the cabin and has a lifting value at which the difference in distance from the points of the lateral surfaces of the cam of the cabin and the cabin of the cabin lying on one axial line to the axis of rotation n *** о * and m ** o * will be greater than the difference in the radial dimensions (radii) of their rolling rollers. In this case, the roller 28 should switch to the roller 27. This section is necessary to ensure smooth switching of the working surface of the cam 22 to the working surface of the cam 21. The stated condition must be met with the same reservations stated above. The length of the third section depends on the angle of elevation; the greater the angle of inclination of this section, the faster the cam moves to the above value, the shorter it is. The fourth, last portion of the working surface of the cam of the slide is made lifting, rectilinear or curved, with a lifting angle (tilt) of the same sign as the first working section of the cam of the shift. The length of the fourth section is determined by the distance from the place of cutting to the final place of movement of the knife when it leaves the cutting zone in the same direction, and the angle of inclination of the section is determined by the required speed of exit of the knife from the cutting zone. As can be seen, the relative position of the working sections of the cams 21, 22, their design (dimensions, overall dimensions) and the shape of these cams and the dimensions of the rolling rollers 27, 28 interacting with them determine the timing of the operation of these cams and suggest several options for their execution. 2b, the larger roller is the roller 28 of the felling cam 22, but there may be another option. In the embodiment illustrated by this fig.2b, when (n ** o * -m * o *) <(R28-R27) contact will be made between the roller 28 with the felling cam 22, with (n *** o * -m * * o *)> (R28-R27) the roller 27 will come into contact with the cam 21. Thus, the instantaneous ratio of the radii of the running rollers and the axial distances of the points of the working side surfaces of the cam of the slide and the wheelhouse determine the instantaneous working point of one or another cam.

 The cam of the formation mechanism of the assembly 5 (Fig. 2c, 3) is rigidly fixed to the working shaft 13 and is made of three parts: the middle part, the power and side cams: 23 for controlling the movement of the knotting boxes of the assembly formation mechanism 5 and 24 for controlling the movement of the conical grips mechanism 5. These cams 23, 24 each have a side surface divided into four zones. One zone for each cam Lo1, Lo2 - the waiting arc - is a small radius arc, non-working, defining the standby mode of conical grips and knot knitting boxes; the length of the arc of waiting is determined by the waiting time of the cone grips and knot knitting boxes (approximately 1/4 of the cycle of the machine). The lengths of these arcs of different cams do not have to be equal. The radius of each arc of expectation is determined by the layout of the elements of the node of the conical grippers and knotter boxes (their location relative to the working shaft 13) in standby mode. In particular, the radius of the standby arc of knotter knots Lo1 will be determined by the location of the knotter knots in standby mode. Opposite the waiting arc of Lo1 of cam 23 is the zone Lк1 - the contact arc, which is an arc of a circle whose length is determined by the residence time of the knotter boxes in contact with the spring blank - the contact time is approximately equal to the knotting time (for reliability, slightly more than the knotting time), and in one of design options can be approximately one third of the circumference, and its radius is determined by the location of the knotting boxes relative to the shaft 13 in the knotting mode directly at the spring . The difference between the radii of the waiting arc and the contact arc is determined by the required length of movement of the knitting knots from the waiting zone to the contact zone. The length of the same contact arc Lк2 of the other cam 24 opposite the waiting zone Lo2 is determined by the residence time of the conical grippers in contact with the spring (the contact arc of the conical grippers with the spring); as can be seen from figure 3, Lk1 <Lk2. The radius Lk2 is determined by the location of the conical grips. Both arcs Lo, Lк of each of the cams are located on different sides from the axis of rotation of the cam of the shaft 13 and are connected to each other by two straight branches on each side. These branches determine the movement of knotted bolls (cam 23) and conical grips (cam 24) of the assembly forming mechanism 5 from the standby position to the contact position with the spring (straight branch) and back to its original position (reverse branch). The cams 23, 24 can be symmetrical, and the axis of symmetry of each cam passes through the centers of the waiting arcs and contact arcs. The middle power part of the composite cam is equipped with stops 32. The stops of the power part are designed to force the rolling rollers 29 and 30 to force contact with the return cam branches 23,24. The stops are each opposite their opposite branch parallel to it at a distance equal to the diameter of the corresponding rolling roller 29, 30, at the end of the contact zone of its cam, and are made at the ends with an arc facing its branch with the possibility of interaction with its rolling roller. Forced contact of the rollers 29, 30 with the reverse branches of the cams 23, 24 can be carried out by other means, in particular by springing, but this option is not reliable enough. The rollers 29, 30 are made with the same geometric dimensions, are mounted on the same arms of the twin rocker arm, have different rotation axes and are located on their side surface opposite the side surface of their cam 23 and 24, respectively. The location of the composite cam of the mechanism 5 on the axis of rotation of the shaft 13 depends on the location of the cam of the wheelhouse 22 and on the location of the rolling rollers 29, 30 with respect to the axis of rotation of the shaft 13. The moment of cabin of the spring coincides in time with the moment of knotting of the previous spring. In this case, the composite cam of the mechanism 5 is located on the axis of the working shaft 13 so that the beginning of the felling zone m * m ** of the felling cam 22 coincides with the beginning of the transition of the mechanism of formation of the node from the contact mode of the knots of knitting bollards to the standby mode, i.e. with the beginning of the removal of knotter boxes, the end of the contact arc of the knotter boxes Lк1.

The heat treatment cam 25 (FIG. 2 c) is symmetrical; the lateral surface of which is two arcs - semicircles with larger and smaller diameters with transition sections in the form of smooth steps made along the arc, and the axis of symmetry of the heat treatment cam coincides with the beginning of the cutting, namely the line connecting the midpoint of the working surface of the heat treatment cam with its axis rotation o **, makes an angle of 0 ^o with a line connecting the beginning of the working section of the felling cam with the axis of its rotation. The dimensions of the cam 25 are determined by the layout of the heat treatment elements. The cam 25 is provided with a run-in roller 31.

Shaping mechanism
The forming cam 20 is kinematically connected through an obturator roller 26, for example a rolling bearing, to the forming mechanism of the spring 2, including the forming roller 33 and the pitch stop 34; kinematic connection of the break-in roller 26 and the forming roller 33 is carried out sequentially through the beam 35, rod 36, beam 37, rod 38, lever 39.

 The chopping mechanism is generally depicted in figure 4.

 In addition to the above cams, the slides 21 and the wheelhouse 22 with their rolling rollers 27, 28, the wheelhouse mechanism includes a movable knife 40 and a fixed knife 41 rigidly fixed to the frame 9. For more precise adjustment, the knives can be made with the possibility of adjusting their position (not shown). The kinematic connection of the cam 21 through an obkatny roller (bearing) 27 with the movable knife 40 is carried out through the beam 42, the rod 43 on the axis 44 of rotation of the movable knife 40; the cutting plane (the plane of rotation of the knife blade) is perpendicular to the turn. The felling cam 22 is adapted to interact with its rolling roller 28, coaxially mounted with the roller 27 on the beam 42, and its kinematic connection with the knife is carried out in the same way as the cam cam 21 with the knife 40. This allows you to increase the degree of synchronization of the moving process knife and chopping process and simplify the kinematic scheme of the machine as a whole. The movable knife 40 is also connected to the spring return from the end point of the knife moving to its original position (not shown).

 The mechanism 4 for moving the spring billet from the cutting zone to the knotting zone includes a gripper with means for closing and opening it (FIG. 5) and means for moving the gripper (FIG. 1). Means for moving the mechanism 4 is connected to the working shaft 12 by a thrust 45 (Fig. 1, 2a), mounted on the cam of the wheelhouse 22 through an earring 46 (see Fig. 2a) forming a rotation lever; the mounting location of this earring on cam 22 is located on a line connecting the starting point of its working surface m * with the axis of rotation of the working shaft 12 with an eccentricity, the value of which is determined by the layout of the machine, and is made with the possibility of angular adjustment within small limits; the rod 45 is oriented along the specified line connecting the working surface of the cam 22 with the axis of the shaft 12 and is located on one side with the specified line from their axis of rotation. This allows you to achieve tight synchronization of the processes of cutting and moving the workpiece. Rod 45 transmits movement to the capture device through: rocker 47, rod 48, lever 49, determining the oscillating movements of the capture device 50 relative to the axis of rotation 51. The capture 50 in figure 1 is shown conditionally. The grip 50 is fixed on the axis of rotation 51 and can occupy two extreme positions: in the cutting zone of the spring billet (extreme lower position) and in the knotting zone of the ends of the spring (extreme upper position). The grip 50 has two states: open (Fig. 5a) and closed (5b), in which it holds the workpiece of a wound spring for its transfer. The grip 50 includes a movable lever 52, a stationary lever 53, which are connected along the axis of rotation of the movable lever relative to the stationary in a plane perpendicular to this axis, a rod 54, one end fixed to the movable lever 52 along the axis "a" parallel to the axis of rotation of the movable lever 52, rotatably relative to it, an arm 55 connected to the other end of the rod 54 along the b axis parallel to the axis of rotation of the movable arm 52, rotatably relative to it, and mounted on a stationary arm 53 to rotate the wok y-axis "a" parallel to the rotation axis of the movable arm 52, the closing sleeve 56, opening sleeve 57 attached to different arms of the rocker 58. The rocker 58 may structurally be formed dual between two planes which is rigidly associated therewith, bracket 55 is mounted; the junction of the bracket 55 and the rocker arm 58 is located in close proximity to the axis "b" of the connection of the bracket 55 with the rod 54, since near the axis "b" contact stresses at the junction of parts from impact will be minimal. If not guided by these considerations, the junction of the bracket 55 and the rocker arm 58 may be further from the axis "b". The axis of rotation of the bracket 55 "in" is parallel to the axis of rotation of the movable arm 52 and is mounted on the stationary lever 53. Link 54, bracket 55 with its axis of rotation "a", "b", "c" form a brace system along which the kinematics of capture; The brace provides greater actuating efforts and a reduction in the speed of travel at the end of the movement of the gripping actuator: bracket 55, rod 54, movable arm 52. Rod 54, bracket 55, rocker 58, closing sleeve 56 and opening 57 form a means for opening and closing the gripper 50. For reliable grip jamming, axis "b" should fall below line "a" - "c", forming an arrow of deflection. To reduce the deflection of the brace system to a maximum of 3 mm, the brace system on the fixed arm 53 has a limiter 59 for the axis "b" stroke of the bracket 55 under the bracket 55. If there is no limiter 59, the midpoint of the brace is further lowered below 3 mm (technological size) the movable lever 52, turning further around the axis of its connection with the stationary lever 53, can open the grip and weaken the grip of the spring.

The ends of the levers of the same name 52, 53 at the end of the gripper 50 are equipped with limiters for the position of the spring at the moment of its capture: 60 on the fixed lever 53 and 61 on the movable lever 52. These stops 60 and 61 are shown in FIG. 5c. and 5g, respectively, in different angles, as well as at the moment of their contact with each other and with the coil of the spring billet sandwiched between them (Fig. 5e). The limiters are configured to interact with each other with a minimum clearance equal to the diameter of the wire used for the spring. The limiter 60 (figv) is a plate 62, rigidly mounted on a fixed lever 53, at the end equipped with a wedge-shaped guide 63, and on the sides with two stops (actually limiters) 64, located symmetrically relative to the longitudinal axis of the plate 62 along it, made with two beveled surfaces each. The height of the stops 64 is determined by the distance (not less than) between the movable 52 and the fixed 53 levers in the position of the open gripper 50 (Fig. 5a). The stops 64 are made at the end of the plate 62, along it, with some shift from its frontal edge, namely, near the base of the wedge-shaped guide 63, with the formation of a platform for a part of the coil of the spring shown in FIG. 5c, d by a dashed line. One chamfered surface of each stop (limiter) 64 is inclined towards the wedge-shaped guide 63 (towards the grip spring) and inclined with respect to the central part of the plane of the plate 62 (shown in rare hatching in Fig. 5c); the sections of these tapered surfaces of the stops 64, located at the same height from the plate 62, are piecewise approximated sections of the arcs, upon extension of which, before connecting them to each other, a section of the arc with a radius equal to the radius of the coil of the spring is formed. Each beveled surface from another pair of beveled surfaces is located at an angle equal to 90 ^o to the plane of the plate 62 (for reasons of manufacturability) (shaded in Fig. 5c). The intersection lines of the second beveled surfaces with the plane of the plate 62 are piecewise approximated sections of arcs, upon extension of which, before connecting them to each other, a section of the arc with a radius equal to the radius of the coil of the spring is formed. The height of the second pair of bevels in size is chosen not less than the diameter of the wire from which the spring is made, for reasons of exclusion of slipping of the coil of the spring. Both stops 64 with their beveled surfaces are designed to limit the movement of the coil of the caught spring on one side (in the plane of the figure to the right). The limiter 61 (Fig. 5d) is also a plate 65 with a width not greater than the distance between the stops 64, rigidly mounted on the movable arm 52, located parallel to the plate 62 of the limiter 60 in the closed position 50. The plate 65 is provided with two symmetrically located relative to the longitudinal axis of the plate 65 stops 66 opposite the stops 64. The stops 66 are located at an angle to each other, equal to the angle of the wedge of the wedge-shaped guide 63, and at a distance from each other, equal to the width of the wedge-shaped guide 63 in the place of their interaction. The stops 66 are provided with two pairs of beveled surfaces, each of which is parallel to the corresponding counter beveled surface of the stop 64 (in FIGS. 5c, d, the counter surfaces are made with the same shading).

 The distance between counter parallel bevelled surfaces with a closed grip 50 is equal to the diameter of the wire used for the spring.

 The movement mechanism 4 is also equipped with a kinematic chain for closing the gripper 50, which is connected with the kinematic diagram of the mechanism of the cabin 3 through the beam 42, a rod 67 mounted on the shoulder of the beam 42 of the mechanism 3, the other end of which is connected to the lever 68; the gripper closing circuit also includes a lever 69 connected to the lever 68 through the torsion shaft 70, as well as with the rod 71 and the lever 72 for closing the gripper 50 with the possibility of its interaction with the closing sleeve 56 of the gripper 50 in its lowermost position. Additionally, the movement mechanism 4 is configured to interact with its opening sleeve 57 with the lever 73 of the formation mechanism of the assembly 5 (Fig. 6a).

The mechanism of the formation of the node on the supporting coil of the spring (knotting) 5 (Fig. 1, 6a) works from the second cyclic working shaft 13 through the composite cam 23, 24 and the rolling rollers 29, 30 and contains two mechanisms for processing the right one (Fig. 6b) and the left ends of the spring, made similarly. The node formation mechanism in both the right and left parts contains a pair of gripping cones - inner 74 and outer 75, installed one in the other coaxially and counterclockwise (figa, b, c), i.e. the larger base of the inner cone 74 lies in the plane of the smaller base of the outer cone 75, while the radius of the base of the outer cone is greater than the radius of the base of the inner cone by an amount equal to the diameter of the wire used for the spring (adjusted for technological clearances) located to form an annular platform 76 between them at the base of the cone grip with a seat under the support coil of the spring in the form of a trench of a square or cone section (Fig.6d) with a side size equal to the diameter of the wire used oki (taking into account the technological gap), with a diameter of the platform equal to the diameter of the support loop, rigidly fixed to each other; conical capture 74-75 is made with a groove in the base of the capture. The groove is intended for the location of the end of the support coil of the spring and is oriented perpendicular to the axis of the spring installed in the knotting mode, the geometric dimensions of the groove of the cone grip (its width and length) are determined from the inequality:
Nπ D + h <l <spring pitch,
where l is the geometrical dimensions of the groove (its width, length), equal to the length of the end of the support coil of the spring, going to knotting;
N = integer, number of complete rings in the node; usually N = 2, 3, but may be different;
πD is the circumference of one ring from the end of the support loop;
D is the diameter of the ring from the end of the support loop;
h is the distance between the reference and the inner coil in the area of the node (see Fig.7).

 The gripper 74-75 is additionally equipped with a plate 77 (Fig.6c), rigidly mounted on the conical gripper 74-75 at the extreme wall of the groove from the side opposite to the end point of contact of the support turn in the conical gripper, the working surface of which is facing the groove, protruding beyond conical capture (groove) approximately the size of the radius of the support coil for the reliability of its contact with the end of the spring with a possible change in the orientation of the spring within certain acceptable limits and is oriented parallel to the longitudinal axis of the groove or under a sharp bending to it, moreover, the orientation of the working surface of the plate at an acute angle is more preferable.

 Directly at the groove is a liner 78 rigidly fixed in the grip (Figs. 6c, 6e). The surface of the liner 78 facing the spring (indicated in FIG. 6e by shading — frequent hatching) can be made at an acute angle to the axis of the conical grips in their closed position (to the axis of the spring installed for knotting); this surface is equipped with pads for part of the supporting and previous (internal) coil of the spring (shown in Fig.6d rare hatching), the angle between the planes of which is equal to the angle of the coil. For reliable orientation of the bent end of the support turn inward to the groove, towards the center of the gripping base 74-75, when it is broken, the platform for the end of the support turn on the side surface of the insert can be made with access to the side surface of the insert 78, which is internal from the side of the groove. The insert is equipped with a pin 79, the lateral surface of which (frequent hatching) can also be made with a slope at an acute angle with respect to the axis of the spring, i.e. parallel to the plane passing tangentially through the support and internal coils of the spring.

 Opposite the insert 78 in the position of the closed conical grippers on the base (bed 9) is an emphasis 80 (Fig.6e). The lateral surface of the stop 80 is made with platforms for part of the support coil and part of the inner coil; these pads counter to the pads of insert 78 are shown in the same hatching; the stop 80 is also provided with a fork at its end, opposite the pin when the grippers are in the closed position, with internal dimensions corresponding to the dimensions of the pin 79 of the insert 78, with the possibility of the pin 79 entering the plug of the stop 80 in the closed position of the conical grips. The gap between the lateral counter surfaces of the pads of the liner 78 and the stop 80 for the support coil of the spring in the closed cone position 74-75 is determined by the diameter of the wire used for the spring. The gap between the lateral counter surfaces of the pads of the liner 78 and the stop 80 for the inner coil of the spring in the closed conical gripper position 74-75 is determined to be slightly larger than the diameter of the wire used for the spring, to prevent rigid clamping of the inner coil of the spring, leaving little freedom for its movement.

 Each part of the mechanism 5 also contains a knotter box 81 (Fig. 6g) for placement and fastening of the knotter gear 82 provided with a bending plate 83 and the spline gear 84, which are in constant mutual engagement (not shown). The transverse size of the knotting box (its thickness) is not greater than the width of the groove of the conical gripper 74-75. The knot box 81 is made with the possibility of reciprocating or pivoting movement to the spring and from the spring, i.e. relative to the axis of conical grips in their closed position (axis of the spring installed in knotting mode). The box is equipped with a groove located on the side of the groove of the conical gripper 74-75 opposite it, with an internal size equal to the diameter of the wire for the spring, taking into account the inclined position of the inner coil of the spring to the spring axis, equal to the angle of the spring (in Fig.6b knotted box 81 is shown placed in the groove of the conical grips 74-75).

Immediately near the conical gripper 74-75, a limiter plate 85 is located, the plane of which is parallel to the plane of the base of the conical gripper when it is installed in the closed position (i.e. with a spring clamped in it and set to knotting mode). The limiter is equipped with protrusions, the inner plane of its ends, forming a bounding surface for the spring support coil in the conical grip, in the form of arc sections with a radius not greater than the difference between the radius of the spring support coil and the radius of the wire used for the spring, with the possibility of limiting the course of the spring support coil in the trench with annular platform 76 of the conical gripper 74-75 in the axial direction of the spring; the protrusions of the plate 85 are located along the length of the arc is not less than half the circumference with a specified radius. The plate with protrusions is fixed on the base 86 of the mechanism 5 of the formation of the node on the supporting coil of the spring, i.e. motionless relative to the bed 9, so that when the grip is closed, the plate is located opposite its base parallel to it at a distance of the technological gap (about 0.5 mm) from the surface of the support coil located on its annular platform 76 of this base (Fig.6d). On the outer surface of the inner cone 74 and the inner surface of the outer
cones made samples for the free movement of the conical grip on the tabs of the plate 85 (pigv).

 The conical gripper 74-75 is fixed cantilever to the support 87 of the base 86. The consoles 88 with the supports 87 are rotatable around an axis perpendicular to the axis of the spring when it is located by its support coils between the cones 74, 75. The conical grips 74-75 of both parts of the mechanism 5 located in the zone of formation of the node in the initial position at an angle to each other; the maximum "opening" angle of the conical grips in the initial position determines their distance between each other not less than the axial size of the spring. Conical grips are made with the possibility of their mutual rapprochement with each other. The location of the grips at an angle to each other implies their convergence by rotation before installing them opposite each other coaxially at a distance equal to or slightly smaller than the axial size of the spring. It is also possible to install conical grips of both parts of the mechanism coaxially, opposite each other, in parallel. In this case, the rapprochement of the grips will be progressive.

 Knot knitting boxes 81 are each mounted on their plate 89 with the possibility of its rotation relative to the axis 90, parallel to the axis of the spring.

 The conical gripper 74-75 and the knotter box 81 are each connected to the composite cam of the mechanism 5 through kinematic chains of their movement to the spring and from the spring, the two end links of which both from the side of the conical gripper 74-75 and the knotter box 81 are interconnected and conical gripper 74-75, plate 89 for fixing the knotter box 81 along the rotation axes "a", "b", "c" parallel to each other, with the possibility of installing them in one line (Fig. 6b), i.e. with the possibility of displacement of the axis "b" to the line "a" - "c". The knot gear 82 is also connected by a kinematic chain with a gear sector mounted on the gear mounted on the shaft of the second working shaft 13.

 The operation of the end machining mechanism 5 is controlled by a composite cam 23-24 mounted on the shaft 13 and connected to the kinematic diagram of the mechanism 5 through the run-in rollers 29, 30. The kinematic diagram of the mechanism 5 contains a pair of conical gripper drives, knot gear box drives, knot gear drives.

 Each conical gripper drive 74-75 is powered by a cam 24 and its run-in roller 30 and includes a rocker arm 91 (located in the background behind the rocker arm 99 in FIG. 1); one shoulder of this rocker arm is connected to the lateral surface of the cam 24 through a rolling bearing 30, the second with a rod 92 and further with a three-arm lever 93 with one axis of rotation (shoulder 93a - shoulder 93b), rod 94, rocker 95 (figa, b) , traction 96, two-arm lever 97 (shoulder 97a - shoulder 97b) with a common axis of rotation of both shoulders "b"; the shoulder 97b is connected with the rod 98 along the axis of rotation "b" parallel to the axis "c", the other end of the rod 98 is connected to the console 88 of the conical gripper 74-75 along the axis "a" parallel to the axis "b". In this case, details 97b-98, namely, the axes of their rotation "a" - "b" - "c" form a system of strut cone grippers with the possibility of their alignment in one line.

 Each drive knotted boxes 81, as well as the drive of conical grippers 74-75, works from the second working shaft 13 and the composite cam, only from its other lateral part 23, according to the following scheme: cam 23, rolling roller 29, rocker 99, rod 92, three-arm lever 93 (shoulder 93a); this part of the kinematic chain coincides with the kinematic chain of conical gripper drives 74-75. Rocker arms 91 and 99 have the same design and a common axis of rotation in their middle part. In contrast to the conical grips scheme, the three-arm lever 93 uses a different shoulder 93 c. This shoulder through the rod 100 is connected with the beam 101 (Fig. 6a, b) and then through the rod 102 and the plate 89 for attaching the knotter box with the knotter box 81. In this case, the parts 101, 102, namely, the axis of rotation a-b-c, form another brace system for knotting boxes with the possibility of aligning the rotation axes "a", "b", "c" in one line (Fig. 6b).

 The movement of points “b” of both struts can be limited by the stops installed on one of the links of their kinematic chain, for example, the stops installed on the arms of the rocker arm 91, 99, opposite the shoulders with rollers 29, 30 (Fig. 1).

 The two-arm lever 97 of the left side of the assembly formation mechanism 5 is provided with an additional shoulder 97b (Fig. 6a), which together with the rod 103 and the lever 73 form means for opening the gripper 50 of the movement mechanism 4.

The knot gear 82 is powered from a second working shaft 13, on which a gear 104 is mounted with a gear sector installed therein. A gear with a gear sector is selected to transmit intermittent rotation of the knot gear during one revolution of the shaft as the most reliable system; as another intermittent rotation system, other known systems, for example, the Maltese mechanism, can be used. The gear sector occupies about 1/3 of the circumference and spatially does not always coincide with the arc of contact of the knotter boxes with the spring Lк1 of the cam 23; while the work of the gear sector in time coincides with the work of the arc of the contact cam of the knot gear, which is achieved by adjusting the angular position of the gear sector and cam of the knot formation mechanism on their working shaft 13, as well as by adjusting the shoulders of the individual links of their kinematic chain; the angular size of the gear sector is equal to the angular size of the arc of contact of the boxes 81 with the spring of the cam 23 or slightly less; so, for reliable operation of the machine without failures, the angular size of the arc Lк1 is 120 ^o , and the angular size of the gear sector is 106.6 ^o . The angular size of the gear sector is chosen smaller than the angular size of the contact arc of the knot box to ensure the latter is in contact with the spring while knot knitting gear 82 connected with the gear sector is knotted in the presence of technological errors in the execution of machine parts. With a high degree of accuracy of their manufacture, ideally, these dimensions will be equal, and the angular size of the gear sector can also be 120 ^o . The indicated dimensions are determined based on the used options of the transmission links in the kinematic scheme of the knot gears drive, the number of knot gear rotations required and can be different within certain limits. The gear sector of the gear 104 is located with the possibility of periodic engagement with the driven gear 105. The driven gear is made with parameters that allow it to crank one revolution from the gear sector. The driven gear 105 is connected to the gear 106 with a transmission coefficient equal to two, moreover, one knot gear 106 is transmitted with one direction of rotation and the other with another direction of rotation (through the gear of changing the direction of rotation 107, as shown in FIG. 1 ), since the direction of rotation of the knot gear 82 for different ends of the spring should be different. Next, the pinion gear 106 is connected with a bevel gear 108 of the cardan mechanisms 109 directly connected to the spline gear 84. The type of gears and mechanisms is determined based on the layout decisions of the machine. In order to form a knot into three rings (N = 3) with the specified gear ratios of the kinematic chain, the gear sector - knot gear needs to increase the transmission of the spline gear by 1.5 times.

 The mechanism 6 for moving the spring from the knotting zone to heat treatment includes a transport device and a gripper with means for closing and opening the gripper. The transport device is connected to the working shaft 12 through the rotation lever 110 (Fig. 1, 2a), mounted on the shaft 12, on the axis of rotation directly or with an eccentricity, the value of which, like the location of the lever relative to other cams, is determined by the layout of the machine; the attachment point of the rotation lever is adjustable with respect to the axis of rotation of the shaft 12 and is more accurately determined experimentally in the tuning process. In this case, the lower and upper positions of the gripping mechanism 6 of the spring movement from the knotting zone to heat treatment corresponds to the lower and upper positions of the gripping mechanism 4 of the spring moving from the cutting zone to the knotting zone, respectively. This is achieved by the layout of the kinematic chains, the adjustment of the shoulders of individual links of the kinematic chains and the angular adjustment of the location of the rotation levers on the working shaft.

 The rotation lever 110 of the mechanism 6 is connected to the capture device through a transport device: a rod 111, a lever 112, a torsion shaft 113, on which the capture 114 is fixed (Fig. 1 is shown conditionally, Fig. 8a, b shows its construction in the open and closed position ), determining the oscillating movements of the gripper 114, mounted on the torsion shaft 113, relative to the axis of rotation 115. The swing swing of the gripper 114 with the shaft 113 is determined by the position of the stops 116,117 (Figs. 1, 8), with which the lever 118 interacts via adjustable stops 119. The gripper 114 has two positions: open Toe (FIG. 8a) and closed (8b), holding the preform wound springs for its transfer. The grip 114 includes a movable arm 120, a fixed arm 121, a rod 122 and an arm 123.

 The movable gripping lever 120 is mounted on the stationary lever 121 on a stand along the axis with the possibility of rotation around this axis perpendicular to the plane of movement of the movable lever 120. The rod 122 is attached at one end to the movable lever 120 with the possibility of rotation around the axis "a" parallel to the axis of rotation of the movable lever 120 relative to the fixed lever 121, the other end with the bracket 123 with the possibility of rotation relative to the axis "b" parallel to the axis of rotation of the movable lever 120 relative to the fixed lever 121. Another axis of rotation of the bracket 123 "in", parallel to the axis of rotation of the movable arm 120 relative to the stationary arm 121, is mounted on the stand of the stationary arm 121. The fixed arm 121 is secured by a splined connection to the torsion shaft 113 by means of clamping plates 124.

 The grip 114 also includes means for opening and closing the grip, including a rod 125, a rocker 126, connected with a lever 127 along the pivot axis, which is rigidly fixed to the torsion shaft 113 by means of a spline connection, and also a plate 128, rigidly fixed to the machine frame 9. The plate 128 is equipped with stops 130, 131, as well as a plate 132 with stops 116, 117 on its sides (Fig. 1, 8b). The stops 130, 131 are located on opposite sides of the second arm of the rocker arm 126 opposite to it with the possibility of their impact interaction with the second arm of the rocker arm 126. The fixed arm 121 is rigidly connected to the arm 118, mounted on the torsion shaft 113 and located between the stops 116, 117 of the plate 132, using spline connection.

 Rod 122, bracket 123 with its rotary axes "a", "b", "c" form a strut system with the possibility of aligning them in one line. The capture kinematics is performed according to the principle of operation of the brace with the transition of the zero zone (with the formation of a deflection arrow) similarly to the capture of mechanism 4; the brace provides greater actuating forces and a decrease in the travel speed of the movable lever 120 relative to the stationary 121 at the end of its movement during the closing of the gripper 114. Additionally, the stationary lever 121 is equipped with a limiter 133 from the bottom of the axis “b” of the connection of the rod 122 with the bracket 123 located on the stationary lever under this axis and determining the parameters of the deflection boom. Quantitatively, the "b" axis may go lower. midline a-b-c no more than 3 mm. In the presence of a deflection boom, the grip is jammed and reliably holds the spring despite the vibration of the machine during its operation; To wedge the grip, it is necessary to apply sufficiently large shock loads to “pull it out”. With a larger deflection arrow (for this design of the lever grip, it is more than three millimeters), the movable lever 120, turning around the axis "a", will begin to open slightly, and the clamp clamp 114 will be unreliable. The ends of the levers 121, 120 of the same name at the end of the gripper 114 are equipped with stops 134,135, similar to the stops 60, 61 of the movement mechanism 4, with the possibility of interaction with a minimum gap between them equal to the diameter of the wire.

 The heat treatment device 7 contains a pair of electrical contact plates 137 located at a distance from each other equal to the axial size of the spring and connected to a current source (not shown), the required value of which and the heat treatment time are determined using engineering calculations. The current source can be a transformer, the secondary circuit of which in the form of a short-circuited coil is formed by the workpiece itself, or by a welding machine. Turning the current source on and off is carried out using the limit switch 138, interacting with the heat treatment cam 25 through the rocker arm 139, the run-in roller 31.

 The packer 8 consists of a container 140 for collecting the finished springs and a pair of actuating plates 141 located from each other at a distance approximately equal to the axial size of the spring or less for withdrawing the finished spring from the heat treatment zone to the container 140. Executive plates 141, at the ends made with curly cuts for the coil of the spring, are connected through a lever 142, a rod 143, a rotation arm 144 with a second working shaft 13. The location of the rotation arm 144 on the axis of the shaft 13 is determined by the layout of the automatic machine 8, the kinematics being made with ensuring the coincidence of the beginning of the knotting zone (the beginning of the engagement of the gear sector of the gear 104 with its driven gear 105) with the extreme position of the packer plates 143 in the packer (Fig. 1 shows the extreme right position of the packer plates conventionally about the axis).

The machine operates as follows
When you turn on the electric motor 10, the rotation of its rotor through a belt drive is transmitted to the Central camshaft 11 (figure 1). Being in meshing by means of gears with two working cyclic shafts, the first 12 and second 13, the shaft 11 drives them in rotation in one direction and at the same speed. By means of a V-belt transmission through pulleys 14, 15 of a V-belt variator, the shaft 11 drives the shaft 19 of the broaching gearbox and through it and the gears 18 the broaching rollers 17, which, when rotated, by means of two pairs of pressure rollers 16 begin to feed the wire to the forming mechanism 2.

 In this case, the first working shaft 12 begins to rotate the cams fixed on it: shaping 20 (Fig. 2a), the slider 21 (Fig. 2b) of the movable knife 40, the felling cam 22 (Fig. 2b), as well as the rod 45 of the movement mechanism 4, rigidly fixed on the cam 22, and the rotation lever 110 of the moving mechanism 6, mounted on the shaft 12. The process of moving the forming roller 33, repeating the movement of the rolling roller 26, interacting with the side surface of the cam forming 20, and the formation of the spring with turns, the diameter of which will vary zack well, to the predetermined shape of the lateral surface of the cam of forming 20. If the lateral surface of the cam 20 has three zones: the zone of removal of the points of the lateral surface of the cam 20 from the axis of rotation o * AAA * (Fig. 2a), the zone of maximum removal of A * (this may be point), the zone of approximation of the points of the lateral surface A * -A, the spring is twisted conical with supporting coils from both ends with a maximum radius with a smooth decrease to the middle of the spring, with a minimum radius in the middle of the spring and with a smooth increase in radius to the maximum its value at the other end of the reference coil spring. The movement from the cam 20 to the forming roller 33 is transmitted along the chain: rolling roller 26, rocker 35, rod 36, rocker 37, rod 38, lever 39, forming roller 33. The stepping stop 34, abutting against the newly wound turn, determines the distance between the turns springs (her step). The type of links of the kinematic chain, their number, mounting location are determined by the layout decisions of the machine. At the completion of the shaping process of the first spring, non-stop shaping (winding) of the second spring begins.

 At the beginning of the shaping of the second spring, due to the location of the working surface of the cam of the slide 21 to the zone of the minimum diameter of the spring, the process of preparing the movable knife 40 for cutting begins. This process is controlled by the cam slider 21 (Fig.2B) and occurs as follows. The cam of the slide 21, rotating together with the cam 20, on the second turn of the second winding spring begins to run into the roller 27 with its lifting section at point n. Since the difference between the distance n * and the distance from the corresponding point on the side surface of the cam 22 to the axis o *, as can be seen from Fig.2b, is greater than the difference between the radii of the rolling rollers 27, 28, the roller 28 does not touch its cam 22, and neither the roller 28 nor the cam cutting 22 in the movement of the knife 40 at this time are not involved. The cam 21, pushing the roller 27 in the direction from the axis o *, actuates the beam 42, which, turning around its axis, pushes with its other shoulder a rod 43, which rotates the knife 40 around its axis of rotation 44 towards the fixed knife 41. The beginning of the specified the process depends on the relative position of the shaping cams 20 and the slider 21, the place of their contact with their rollers relative to the axis of the shaft 12, which in turn takes into account the location of the movable knife 40 relative to the shaping zone (for the forming roller 33), the selected awn knife 40 advances, the very shape of the working surface of cam 21 advances (the angle of inclination of its working area) using engineering calculations and empirically. Having reached the place of cutting, the knife 40 stops, since the second section of the lateral surface of the cam 21 of a constant radius starts from the point n *, and the knife 40 does not move. During this time, the distance from the side surface of the cam of the deckhouse 22 to the axis of rotation o * increases to a value when the difference in axial distances of the points of the side surface of the cam 21 and cam 22 becomes less than the difference between the radii of the runner rollers 27, 28, and the roller 28 starts to touch the cam of the cabin 22 in arc mm * at the beginning of the working section of the felling cam m *. Roller 27 "freezes" in the air. The advance movement of the knife 40 is caused by the need to accelerate the process of cutting the coil spring by reducing its stroke immediately at the time of cutting. The shortness of the process of cutting itself is caused by the condition of continuous wire feed and the continuity of the process of shaping the springs, which is directly related to an increase in the productivity of the machine and an increase in the reliability of its operation. From this point m *, the movement of the rocker arm 42 begins to be determined by the cam 22. At this time, the section of the wound first spring is at the cutting site, where the last supporting coil of the first spring ends and the first supporting coil of the second spring begins. At the same time, due to the coincidence of the positions of the beginning m * of the cabin of the cabin of the cabin 22, the roller 28 and the thrust 45 of the movement mechanism 4, the gripper 50 of the movement mechanism in the open state will reach its extreme lower position by entering the wedge-shaped guide 63 of its limiter into the "body" of the spring; in this case, one of the turns of the spring will be in the space between the stops 64 and 66 (figa, c, d). The space between the stops 64, 66 is limited to move the spring; due to the height of the stop 64 to the level of the movable lever 52 of the open grip 50, the spring will occupy a position between two pairs of counter beveled surfaces of the stops 64, 66 (a rare hatching of the surfaces of Figs. 5c, d). Due to the presence of these beveled surfaces, the stops 64, 66, located parallel to the coil of the spring, further limit its spatial arrangement, eliminating its bias with respect to the grip 50. The initial moment of cutting begins with the interaction of the roller 28 with the initial section of the cabin of the cutting tree 22 (point m * Fig. .2b). From this interaction, the beam 42 again moves, transmitting the moment of movement to the lever 68 through the link 67, which through the torsion shaft 70 will transmit this movement to the other lever 69, through it to the link 71 to the lever 72. Under the action of this moment, the lever 72 will turn its shoulder, which when moving, it will hit the sleeve 56 of the closing of the gripper 50. From this impact, the rocker 58 of the gripper 50 (Fig. 5a), receiving movement, will exert pressure on the bracket 55 at the point of their connection near its axis of rotation "b" - the middle point of the strut, lowering the point " b "to the level of the zero line "AB"; the indicated motion will be smooth, since the further the point "b" falls to its zero point, the slower the increment of motion with the same effort, which characterizes the operation of the strut. Point "b" drops to the level of line "a-c", slowly lowering the movable lever 52 to the stationary lever 53; point “b” may fall slightly lower, reliably jamming the grip clamp, forming an arrow of deflection, but not more than 3 mm for this design of the lever grip, below 3 mm from the average level, the stopper 59 on the fixed arm 53 will not allow it to fall, since it may opening of the gripper due to further pivotal movement of the movable arm 52 relative to the stationary 53. A spring oriented by the beveled counter surfaces of the stops 64, 66, being between them, under the action of the beveled surfaces pushed on it (rare 5B lineart, z) parallel to one of the spring coils will lower the platform plate 62 in the wedge guide 63 (shown in phantom in Figure 5B); moving further under the same action of the chamfered surfaces of the stop 66, the spring will go into the space bounded on one side by the plate 62, on the other hand by a second pair of beveled surfaces (blackened) of the stop 66, forming sections of approximated arcs on the sides of the stop 66, on the third side by a second pair beveled surfaces (blackened) of the stop 64, forming sections of approximated arcs on the sides of the stop 64. This moment will coincide with lowering the movable lever 52 to the stationary lever 53, jamming the strut, and the wheelhouse is already clamped in cotton wool 50 springs. The roller 28 interacts with the felling cam 22, which due to the lifting of the working section of its surface, without impact (the knife 40 has already begun to contact the spring workpiece), under the influence of powerful pressure causes the knife 40 to push through the wire, cutting the spring workpiece, separating the end of the first spring workpiece the beginning of the support coil of the second spring billet. This method of cutting allows you to quickly cut the spring without impact, ensuring the cleanliness of the cut and the quality of the cut spring. The end of the cabin of the spring corresponds to the point m ** on the cam 22 (fig.2b). By this moment, cam 21, while the chopping process was ongoing, continued to rotate along with cam 22, the distance of the points on its lateral surface to the axis o * gradually increased, and to the point m ** reached its point n *** the point of contact with roller 27. At this point, the difference (n *** o * - m ** o *) became larger than the difference between the radii of the rollers 27, 28, and roller 27 came into contact with its cam, touching the surface of the cam 21 (point n *** ) From this point n *** the lifting of the last working section of the felling cam 22. begins. This working section n *** n **** can be steeper or flatter with respect to the section nn *, the speed of the knife depends on the angle of inclination of these sections 40; being also a lifting section, as well as a section nn *, n *** n **** will cause the knife to move in the same direction as before cutting; the length of this section will determine the distance that the knife 40 will move from the cutting site. The ability to leave the knife from the place of cutting in the same direction (not immediately back) removes the problem of its quick return associated with transients of changing the direction of movement, thereby not knocking the machine from the rhythm of work, maintaining the quality of the spring. It is possible to carry out the working sections of the movement of the knife nn * before cutting and n *** n **** after cutting not straightforward, but curved according to a more complex law, but in this case, it is possible to continue the movement of the knife 40 in the same direction same speed, more quickly compared to its movement to the cutting, or more slowly, i.e. the function of changing the curved side surface of the second working portion of the cam of the movement (steepness) may be the same (as the first working section) or different; In order for the knife to continue its movement in the same direction, it is necessary that the first derivative of the function of the curved surface before cutting and after cutting should have the same sign (plus or minus). After completion of the work, the return springs (not shown) will cause the rollers 27 and 28 to move to the inoperative parts of their cams.

 The use of the same kinematic scheme for closing the capture 50 as for the movement (before and after cutting) and during cutting, positive from the point of view of synchronizing the operation of the machine as a whole, simplifying its scheme, could lead to a malfunction of the machine due to the impact of large shock loads on this kinematic scheme of closing the gripper at the moment the knife exits in the same direction from the cutting area, however, the presence of a torsion shaft 70 in the chain of operation of the gripper 50 will prevent the impact of the impact on the lever 72 and through it on the rocker sleeve 58 s capture 50 with further movement of the knife after cutting; the torsion shaft 70 absorbs the impact energy, converting it into torsion energy, providing a reliable gripping clamp 50 during the exit of the knife 40 from the cutting zone without failures in the kinematic scheme.

 Thus, due to the mutual arrangement of the cams of the shaping, movement, cutting and traction 45 of the movement mechanism 4, their rolling rollers, the first spring billet will be wound to the moment of cutting the first spring billet, winding of the second spring billet, not yet separated from the first, knife 40 will come into direct contact with the last supporting coil of the first spring billet and, accordingly, with the first supporting coil of the second spring billet, the movement mechanism 4 of the spring billet will take its extreme lower position, in this case, the shock contact of the lever 72 with the sleeve 56 of the closure of the gripper 50, from which the strut system will operate, i.e. the three brace points a, b, c line up in a straight line, forming an arrow of deflection of up to 3 mm due to the stop 59, reliably jamming the gripper 50 with the spring, and the first spring billet will be cut. After chopping, the knife 40 will continue its movement in the same direction, upon reaching the end of the working area of the cam, the slide 21 will stop and, under the action of the return spring (not shown), will return to its original position without interfering with the subsequent spring winding. In this case, the movement mechanism 4 will begin to move along the swing axis 51 towards its upper position, to the zone of formation of the node on the supporting coil of the spring (knotting zone). After about 1/2 cycle after the moment of cutting (half of the rotation of the shaft 12), the movement mechanism 4 will take its upper position, delivering the workpiece to the knotting zone of the ends of the spring, and stop for a moment (instant zero position). Before reaching the grip 50 with the spring, its upper position, due to the relative position of the wheelhouse cam 22 and the composite cam 23-24 of the mechanism 5 with their rollers 28, 29, 30, due to the rotation of the shaft 13 synchronously with the shaft 12, the run-on rollers 29, 30 of the mechanism 5 will be in contact with the cam 23-24 at the end of the waiting area for bevel gears 74-75 and knotter boxes 81 with their knotter gears 82. At this time, bevel gears 74-75 are at an angle to each other equal to the maximum opening angle, in the waiting area; knotter boxes 81 are also in their waiting area with a maximum distance from the axis of the future location of the spring. Rotating synchronously with the shaft 12, the shaft 13 constantly transmits the rotation to the composite cam 23-24. Cam 24, interacting with its obkatny roller 30, runs into it with its straight branch and drives the kinematic chain: roller 30, rocker 91, rod 92, lever 93a, lever 93b rod 94 (for each grip) (figure 1); further down the chain: rocker 95 (figa, b), rod 96, lever 97a, its axis of rotation "c", lever 97b, rod 98 (for each grip) - the drives of the conical grippers 74-75 are launched, bring them together, reducing angle of their disclosure. The approach of the conical grips occurs while the movement mechanism 4 goes towards its highest position, approaching it. At the moment of arrival of the gripper 50 with the spring billet in its upper position, the conical grippers 74-75 come closer to a distance slightly larger than the length of the wound spring; the conical shape of the sockets of the grippers facing each other ensures reception of the wound spring even in this position. The support turns fall into the gap between the cones 74, 75 and, when the grips approach each other, they begin to fit into the groove along the annular platform 76 between the cones 74, 75 and partially onto the side surface of the liner 78, sliding along the inclined surface (strong shading) of the pin 79 of the liner 78 and inclined surface (strong shading) of the liner 78 itself. In this case, the ends of the support coil of the spring abut each against its plate 77, which are guides for their movement. Plates 77, located at an acute angle to the edge of the grooves of the conical grippers or moving together with the closing conical grippers 74-75, act through the ends on the spring, providing its slight rotation when it moves relative to the conical grippers around its longitudinal axis to the position where the excess length of the end of the spring, which cannot be placed in the groove of the conical grips, enters the gap of the conical grippers (the seat of the support turn), and the required length of the end is freely located in the groove of the conical gripper, limited I have a plate 77. If one end of the support turn does not reach its plate, the other end of the second support turn necessarily abuts against its plate of the second part of mechanism 5 when the spring is gripped by conical grippers; there is a turning of the spring by both plates in one direction. In this case, the spring support coil is located between the surface of the limiting plate 85 with protrusions and the base 76 of the cone gutter, since when closing the cone grips the plate 85 with its protrusions enters the spring body and limits their movement in the space of the spring support coil; samples in the body of the conical surface of the inner cone 74 will allow the protrusions of the plate to do this without touching the surface of the inner cone; this allows the support coil to maintain its spatial position between the cones in the trough, regardless of the effect of bending forces on it when the ends of the spring are twisted relative to the support coil, thereby precisely maintaining the diameter of the spring supporting coils, ensuring their quality, and further increase the reliability of holding the spring in the knot zone. In the process of installing the conical grippers 74-75 in their contact position with the spring, the rod 96 brings the brace system through the shoulder 97a of the two shoulders lever 97 to the closed position, aligning the axis of rotation "a", "b", "c" in one line, ensuring reliable retention spring billet for supporting coils. Moreover, since the movement of the strut elements — the rotation axes a, b, c — is slowed down, the conical grips 74-75 clamp the spring blank from the ends smoothly, without impacts, completing its approach to the minimum distance of the spring length. At the last moment of the movement of the conical grippers, the insert 78 with its lateral surface with pads for the spring coils is installed opposite the surface with the pads for the spring coils of the end of the stop 80, its pin 79 enters the plug of the fixed stop 80; the same parts of the support and inner coils of the spring that hit the support pads (weak shading of Fig. 6e) of the insert 78, but only on their other side, fall on the opposite side (weak shading) of the lateral surface of the stop 80 (Fig.6e). The movement of the conical grippers 74-75 is completed, the conical grippers are firmly closed by bringing them closer to a minimum equal to the axial size of the spring and fixing them in this position due to jamming of their strut elements, fixing of the support turns due to their location between the cones at their seat, restriction of their movement in the seat between the cones of the plate 85 with protrusions on the length of the arc with a size of at least a semicircle, an additional clamp of the supporting turns by the insert 78 and the counter-emphasis 80, fixing the internal turns p the rugs also with the liner 78 and the counter-emphasis 80. The rigid fixation of the inner coil of the spring is not required to provide little freedom of movement for the subsequent formation of the assembly from the end of the spring. At the moment of operation of the strut of the cone grips through the additional lever 97 in the two-arm lever 97 of one of the parts of the assembly mechanism of the assembly 5, the rod 73 is activated by the lever 73, striking the opening sleeve 57 of the gripper 50, knocking the brace a-b-in of the gripper 50 and wedging it; the spring billet, already in the conical grippers 74-75, is freed from the gripper 50 of the movement mechanism 4, which begins its downward movement in the open position (Fig. 5a), back to its lowermost position, returning for a new spring. The run-in roller 30 of the cam 24 comes into contact with its contact zone Lk2, i.e. with a zone of constant large radius (contact of grippers with a spring). The taper grips 74-75 in this mode remain stationary, clamping and holding the spring securely.

 While the rolling roller 30 is moving along the straight branch of the cam 24, the roller 29 will also interact with the straight branch of the cam 23; knotted boxes 81 will begin to move sideways to the spring axis a little later if the waiting area of the cam 23 knotted boxes is larger than the waiting area of the cam 24 of the conical grips. A delay in the start of movement of the knotter boxes with respect to the start of movement of the conical grippers is necessary for guaranteed movement of the knotter box on a fixed spring with the grippers already closed, which ensures uninterrupted operation of the machine. A more accurate implementation of the structural elements of the machine allows the waiting areas to be equal, but a more accurate execution of the mechanisms increases the cost of manufacturing the machine. Knot knitting boxes 81 are pushed onto the spring, entering their grooves into the grooves of the conical grippers 74-75, where the ends of the spring are already placed by the end of the movement of the boxes. Entering the groove of the conical gripper, the box breaks with its end against the edge of the liner 78 the end of the coil of the spring located in the groove of the conical gripper, bending it to the axis of the spring to the center of the supporting coil. The more accurate orientation of the broken end of the support coil into the groove parallel to its longitudinal axis is facilitated by the implementation of the support pad under the support coil, which extends onto the side surface of the insert 78, as shown in FIG. 6d (rare hatching). The groove of the box runs into the inner coil of the spring without deforming it. At the same time, together with the box on the spring, namely on the end of the support turn - the beginning of the internal turn - the knot gear 82 runs into its groove. The pivoting movement of the boxes to the axis of the spring (hitting the spring) is provided by a kinematic chain: cam 23, its run-in roller 29, rocker 99, rod 92, lever 93a of the three-arm lever 93, its lever 93b, rod 100, beam 101, rod 102, plate 89 (namely, the axis of the connection "a" of the rod 102 with the plate 89 of Fig.6b), knotter boxes 81. Elements 101-102, namely the axis of their rotation "a", "b", "c" form a strut system. At the inflection point of the cam 23 (transition from a straight branch to an arc of large radius Lк1), the rocker arm 101 with a thrust of 100 "compresses" the middle strut point "b" to the level of the midline without impact, clearly fixing the knotted boxes and knotted gears in the contact position with the spring.

 Thus, the movement of the knotter boxes 81 with knotter gears 82 onto the spring billet already fixed in the conical grippers ends with the end of the knotter box 81 hitting the end of the support turn of the spring billet and breaking it on the edge of the insert 78 from the groove side, as shown in FIG. 6c dotted. The inner coil of the spring enters the groove of the box, without preventing its collision into the depth of the groove of the conical gripper 74-75. In this case, the bending bar 83 of the knot gear 82 will be positioned approximately along the broken edge of the supporting spring coil at the turn, and the coil itself will be the axis of rotation of the bending bar 83.

At this time, the contact of the run-in roller 29 with the contact zone Lк1 of the cam 23 of the knotted boxes 81 with the spring begins, with which the knotting zone, which is determined by the gear sector of the gear 104 of the mechanism 5, actually coincides. The contact zone of the boxes with the spring Lk1 is an arc of a circle of constant radius of about 120 ^o ; at this time, due to the invariability of the radii of the contact zones of the cams 23,24, the above-described links of the kinematic chains of the movements of the conical grippers 74-75 and knot knitting boxes 81 will be stationary. Simultaneously with the completion of the collision of the boxes on the spring or with some delay, the knotting process begins, since the gear sector on the gear 104 engages with the driven gear 10 at the same time (or with some delay) with the roller 29 running in the contact zone of the knotter boxes 81 with the cam spring 23. Arc the gear sector of the gear 104 is, as Lk1, 120 ^o or slightly less to ensure the completion of the process of colliding boxes on the spring; its driven gear 105 makes one revolution in about one third of the rotation cycle of the shaft 13. The knotting process consists in tying two broken ends of the wound spring around its support turns by applying rotation to knot gears 82 through splined gears 84 of knotter boxes 81. It must be said, that the formation of the node on the support coil is interpreted rather conventionally, since the assembly is formed on the transition section "support coil - internal coil", which is not clearly defined, nevertheless, they are used terminology of education site on the reference coil. Kinematic chain of motion transmission to knotted gears: gear 104 with a gear sector on the shaft 13 — driven gear 105 making one revolution during the rotation of the gear sector — gear 106 (for one gear 106 an additional link 107) with a transmission coefficient equal to two, - bevel gear 108 of cardan mechanisms 109 - splined gear 84 with transmission 1: 1,5 - knot gear 82. Thus, when the shaft 13 is rotated one revolution, the knot gear receives three rotations of rotation; these three turns are made by the bending bar 83 of the knot gear 82, twisting the end of the spring blank for the support turn three times, forming three rings on the support turn or incomplete three rings (2.5) depending on the length of the end of the support turn.

After knotting, the gear sector of the gear 104 is driven with the driven gear 105, one of the links for transmitting rotation to the knot gear is braked by any known braking device, the knot gear is stopped, and the rolling roller 29 with its emphasis 32 of the power central part of the cam 23-24 is reversed a rectilinear branch of the cam 23, moving towards the arc (zone) waiting knot knitting boxes. After some time, determined by half the difference between the lengths of the arches Lk2-Lk1, another round roller 30 of the conical grips will reach the end of the contact zone Lк2 of the conical grippers with the spring (it is more than 120 ^o , as can be seen in figa, b) of the cam 24; with the help of another stop 32 opposite the lateral surface of the cam 24, this roller 30 will begin to interact with the reverse rectilinear branch of the cam 24, moving towards the waiting area of the conical grippers. In this case, partly the same kinematic chains of movements for knotting knots and cone grips (rod 92, lever 93a) will be involved. Under the action of the cam 23 and the operation of the described kinematic scheme, the boxes 81 will retreat to their original position to remove them as far as possible from the axis of the spring blank, and under the action of the cam 24 and the cone grips will increase the angle of their opening. This moment occurs at about the time of cutting with the knife 40 of the second wound spring with the location of the movement mechanism 4 in its lower position.

 After the start of the removal of knotting boxes from the spring due to the combination of the extreme lower positions of the grippers of the movement mechanisms 4 and 6, the gripper 114 of the movement mechanism 6 approaches its lower position — the knotting zone — in the open position, due to the limiter 119 of the lever 118 and the stop 117 the grip 114 is hit by its lever 118 through the corresponding limiter 119 about the stop 117, stopping, having entered the wedge-shaped guide 63 of its limiter 134 into the "body" of the spring; while one of the turns of the spring will be in the space between the stops 64 and 66, as in the movement mechanism 4 (figa). The space between the stops 64, 66 is limited to move the spring; due to the height of the stop 64 to the level of the movable lever 120 of the open grip 114, the spring will occupy a position between two pairs of counter sloping surfaces of the stops 64, 66 (a rare hatching of Figs. 5c, d). Due to the presence of these beveled surfaces, the stops 64, 66, located parallel to the coil of the spring, further limit its spatial arrangement, eliminating its bias with respect to the grip 114.

 However, the shaft 12 with the lever 110 continues to rotate and the torque starts to act on the torsion shaft 113 stopped by the limiter 119 with a stop 117. While maintaining the immobility of the plate 128 due to its rigid attachment to the frame 9, a roller mounted on the lower arm of the rocker arm 126 collides with its stop 131 and hits it (Fig. 8b). From this blow, the other arm of the same rocker arm 126 with a rod 125 fixed to it, turning around the axis of connection of this arm with the rod 125, exerts pressure on the junction of the rod 125 with the arm 123 near the middle axis "b", forcing this axis to fall down to the level the middle straight line "a" - "b" and slightly lower, with the formation of an arrow of deflection, lowering the upper lever 120 of the capture on a fixed lever 121; below this level of the axis "b" the stopper 133 on the fixed lever 121 will not allow to fall. The spring, oriented by the beveled counter surfaces of the stops 64, 66, being between them, under the action of the beveled surfaces pushed on it, parallel to one of the coil of the spring, will fall to the plate area 62 in the wedge-shaped guide 63; moving further under the same action of the chamfered surfaces of the stop 66, the spring will go into the space bounded on one side by the plate 62, on the other hand by a second pair of beveled surfaces (blackened) of the stop 66, forming sections of approximated arcs on the sides of the stop 66, on the third side by a second pair chamfered surfaces (blackened) of the stop 64, forming sections of approximated arcs on the sides of the stop 64. This moment will coincide with closing the strut (lowering the axis "b" to the line "a" - "c") and holding the grip 114 with the spring closed NII. By adjusting the position of the limiter 133, it is possible to lower the axis "b" below the midline "a" - "c", forming an arrow of deflection, securely jamming the grip 114 in the closed position, but the magnitude of the arrow of deflection should not be more than 3 mm, since from lowering the point " b "further, the movable lever 120, turning around its axis, will begin to move away from the stationary lever 121, loosening the spring clip.

 The spring is captured by the transport mechanism 6 until the conical grippers 74-75 are wedged. Since the position of the lever 110 corresponds at that moment to the contact point of the oblique roller 30 of the conical grips with the end of the contact zone of the conical grippers with the spring of the cam 24, the reverse rectilinear branch of the movement of the conical grippers of the cam 24, interacting with the oblique roller 30, will begin to breed them according to the kinematic scheme already indicated, releasing the spring for the movement mechanism 6. The conical grippers 74-75 are disengaged to the angle of their maximum opening. In the closed position of the gripper 114 with the spring with the ends tied, the movement mechanism 6, under the action of the rotation lever 110, will change the direction of movement and will go towards its upper position, to the heat treatment zone.

 When the grip 114 reaches its upper end position at the heat treatment device 7, namely, at the end spring-loaded contacts 137, due to the presence of the limiter 119 of the lever 118 and the stop 116, the grip 114 hits this stop, stopping. The moment of impact of the lever 118 about the limiter 116 (as in the lower position of the grip 114, the moment of impact of the lever 118 about the stop 117) and the stop of the grip 114 can be adjusted by the position of the limiters 119.

 However, the shaft 12 with the lever 110 continues to rotate, and on the torsion shaft 113 stopped by the stop 116, the lever 118 with the limiter 119, the torque of the other direction starts to act. While maintaining the immobility of the plate 128, a roller mounted on the lower arm of the rocker arm 126 collides with its stop 130 and hits it. From this blow, the other shoulder of the same rocker arm 126 with the rod 126 mounted on it, turning, "pulls out" the middle axis "b" up, wedging the grip by raising the movable arm 120 relative to the stationary 121. The movable arm 120 rises, releasing the spring and leaving it on contacts 137, and the transport mechanism 6, obeying the rotation of the lever 110, changing the direction of movement, returns to the knotting zone.

 At the time of installation of the spring on the spring-loaded contacts 137, the roller 31 runs through a smooth step on the working surface of the cam 25 and through the beam 139 includes a switch 138, energizing the contacts 137 of the heat treatment device 7; in this case, the spring itself is an element of an electric circuit operating in the short circuit mode. The heat treatment cycle begins after the capture of the capture 114 of the mechanism 6 for moving down and lasts approximately the time of the working shaft 13 half-turn. At this time, simple engineering calculations calculate the current strength that passes through the spring and which is sufficient to heat the spring to a certain temperature of spring release and its heat treatment.

 At the end of the heat treatment cycle of the plate 141 of the bag 8, rotating due to the kinematic link: the rotation lever 142, the rod 143, the lever 144, being in the heat treatment zone, hook the spring with their curly cuts and take it without distortions to the capacity 140 of the bag 8 to its extreme right position . Further, the entire cycle is repeated.

 Thus, the proposed design solutions regarding the machine as a whole, its mechanisms and components, covered by a single inventive concept, allow us to create a design of a machine for the production of high quality springs, operating in an automatic mode, performing the entire production cycle, from procurement to output of the final product without involvement of auxiliary, additional operations outside the machine, without involving additional equipment, high-performance, reliable, without failures and defects.

Sources of information
1. SU 1570826, B 21F 35/02, bull. 22.1990 g.

 2. SU 1052304, B 21 F 35/02, bull. 41, 1983 - a prototype of the mechanisms of movement and capture.

 3. SU 1726098, B 21 F 35/00, bull. 14.1992 g.

 4. SU 1234018, B 21 F 35/00, publ. 05/30/86.

 5. SU o 776725, B 21 F 35/00, publ. 11/07/80.

 6. SU 1268260, B 21 F 35/00, publ. 11.11.86.

 7. SU 1657263, B 21 F 35/02, bull. 21, 1991

 8. SU 1194549, B 21 F 35/00, publ. 11/30/85.

 9. SU 996011, B 21 F 35/00. publ. 02/15/83.

 10. SU 1799656, B 21 F 3/00, publ. 03/07/93.

 11. SU 506460, B 21 F 35/00, publ. 03/15/76.

 12. SU 599896, M. Cl. 2 B 21 F 35/00, published 03.30.78., Bull. 12 is a prototype for an automatic machine and its cutting mechanism.

 13. SU 471941, M.C. B 21 F 35/00, publ. 05.30.75., Bull. 20.

 14. SU 1405938, IPC4 B 21 F 35/00, publ. 08/30/08., Bull. 24.

 15. SU 996012, Mcl. 3 B 21 F 35/02, publ. 02/15/83, bull. 6 is a prototype of the node formation mechanism.

 16. SU 1282948, IPC4 B 21 F 35/00, publ. 01/15/87., Bull. 2.

 17. SU 1657263, IPC 5 B 21 F 35/02, publ. in BI 23.

 18. RU 2147965, IPC7 B 21 f 35/00, publ. 04/27/2000., Bull. 12.

Claims (24)

 1. A spring-coiling machine, including a wire feed mechanism, a shaping mechanism, a chopping mechanism mounted on a bed kinematically connected to an electric motor through a drive shaft, with cam means rigidly fixed to the working shafts of the machine, while the chopping mechanism is kinematically connected to the shaping cam shaft, and the wire feed mechanism - with a drive shaft, the lateral working surface of the forming cam is curved, the law of removing each point of which from the axis of rotation of the work its shaft of the shaping mechanism corresponds to the law of changing the diameter of the spring, characterized in that it is additionally equipped with a mechanism for forming a node on the support coil of the spring with knot gears made with a spring gripping device, with a spring movement device, with a spring support orientation device, with a spring clamp device, a heat treatment device, a stacking mechanism with stacking plates, and also mechanisms for moving the spring blanks from the cutting zone to the knot formation zone and from the formation zone of the assembly to the heat treatment zone each with a gripping device and means for opening and closing them, the assembly formation mechanism, the heat treatment device and the cutting mechanism are each equipped with their own cam means, while the cam means of the shaping and chopping mechanisms are rigidly mounted on one working shaft, with to which the rotation levers of the moving mechanisms are connected, the cam means of the knot formation and heat treatment mechanisms are rigidly mounted on another working shaft, with which it is kinematically connected There are also knotting gears of the knot formation mechanism through the intermittent rotation mechanism, and batching plates through the rotation lever, the working shafts are installed with synchronous rotation, the chopping cam is equipped with a lifting working section of its side surface, the beginning of which is located at the beginning of the shaping zone of the shaping cam spring, the gripping rotation lever the mechanism for moving the spring workpiece from the cutting zone to the site of formation of the node coincides with the line connecting the beginning of the working section of the cam of the cabin with In order to rotate it, the mechanism for moving the spring billet from the knot formation zone to the heat treatment zone is made with the possibility of coincidence of the extreme positions of its gripping with the same extreme locking positions of the workpiece moving mechanism from the cutting zone to the knot formation zone, the working surface of the heat treatment cam is an arc of a semicircle, the line connecting the center of its working surface with the axis of its rotation coincides with the line connecting the beginning of the working section of the felling cam with the axis of its rotation and oriented with it in one direction, the cam of the knotting mechanism is made with the contact zone of the knotter gear with the spring, while the end point of contact of the roller with the contact zone of the knotting gear and the cam spring of the knotting mechanism coincides with the starting point of the felling of the chopping cam, the extreme position of the stacking plates in the batching zone coincides with the beginning of the contact zone of the knotting gear with the spring, the means of closing the gripping mechanism for moving the spring workpiece from the cutting zone to the processing zone Hovhan node associated with a kinematic chain cutting mechanism, means for its opening is related to the kinematic chain of closing capture assembly of the mechanism, means of closing-opening motion capture spring mechanism of the formation zone in the heat treatment zone assembly is kinematically connected with its swing kinematic chain.  2. The chopping mechanism, comprising a movable knife with the possibility of interaction with another knife during chopping, with the possibility of movement during winding and chopping of the spring, associated with the cam of the chopping and kinematically connected with the cam of the shift, characterized in that the movable knife is mounted to rotate in the plane perpendicular to the coil of the spring at the point of cutting, the cams of the slide and the cabin are mounted rigidly and coaxially on one working shaft, the connection of the movable knife with the cam of the slide and the cam of the cabin is made along one kinematic chain through slide rollers and cuttings respectively, coaxially located on one shoulder of the kinematic chain rocker, each opposite to its cam, the chopping cam is provided with a lifting working section of its side surface, the sliding cam is equipped with a first working lifting section of the side surface, which is located in front of the beginning of the cutting cam working section, and the last working lifting section, the beginning of which coincides with the end of the working section of the felling cam, and the last working section of the shift cam is made with on a clone of the same sign as its first working section, and the cams of the cutting mechanism are made with the possibility of their simultaneous interaction with their rolling rollers.  3. Cam means of the chopping mechanism, comprising a chopping cam, a knife movement cam provided with a lifting section and configured to interact with the kinematic chain through a contact element at its end, characterized in that the cam means of the chopping mechanism is a double cam consisting of rigidly connected between each other and coaxially mounted cam shifts and chopping cam, each of which is equipped with its contact element in the form of a roller, the chopping cam is equipped with its own lifting section the lateral surface, the cams are made with the possibility of simultaneous contact of their working surfaces with their rollers, the lateral surface of the sliding cam is made with four sections, the first moving section is located in front of the beginning of the working section of the felling cam and is a lifting branch, the second section is made with a constant radius and its beginning located also to the working section of the felling of the felling cam, and the end coincides with the beginning of the felling or with another non-end point of the section of the felling of the felling cam, the third section - p demny whose end coincides with the end portion of the cam chopping chopping, the last portion of the working surface of the cam lifting motions configured with a slope of the same sign as the first operating portion of the cam motions, countertops flow forming rollers arranged opposite surfaces of their cams with a common axis of rotation.  4. The cam means of the chopping mechanism according to claim 3, characterized in that the radius of the rolling cam of the chopping cam is greater than the radius of the rolling cam of the cam, and the distance from the points of the side surface of the cam to the axis of rotation of the cams is greater than the distances from the points of the side surface of the cam of the cabin to the axis of rotation cams, the beginning of the working section of the felling cam has a value at which the difference of distances from the points of the lateral surfaces of the cam of the slide and the felling cam lying on one axial straight line to the axis of rotation of the cams will be less than earlier than the difference in the radial dimensions of their rolling rollers, the end of the third section has a lifting value at which the difference in the distances from the points of the lateral surfaces of the cam of the slide and the cutting cam lying on one axial line to the axis of rotation of the cams will be larger than the difference in the radial sizes of their rolling rollers.  5. The cam means of the chopping mechanism according to claim 3, characterized in that the beginning of the working section of the chopping cam is an arc, the concave side of which is facing the side of the rolling roller interacting with it, and the radius of which is equal to the radius of this rolling roller.  6. Cam means of the felling mechanism according to claim 3, characterized in that the cam lifting sections are made linear or curved.  7. A device for capturing a spring of a knot formation mechanism on a support coil, comprising a cone gripper for each support coil with a cone with the possibility of movement of the cone gripper and the spring relative to each other, characterized in that the cone grips each are made in the form of a pair of cones: internal and external, installed one in the other, coaxially and counterclockwise, the radius of the base of the outer cone is greater than the radius of the base of the inner cone by an amount equal to the diameter of the wire, with a bell facing the spring, with the formation of between the cones at the base of the cone grip with a seat under the spring support in the form of a gutter with a height equal to the diameter of the wire, with the diameter of the platform equal to the diameter of the support coil rigidly fixed to each other, the cone grips are installed at a distance not less than the axial size of the spring with the possibility their rapprochement. 8. A device for moving a spring of a knot forming mechanism on a support coil of a spring, comprising a conical grip of a spring with a groove with means for moving the conical grip and the spring relative to each other, characterized in that the conical grip is made in the form of a pair of cones: internal and external, installed one in another coaxially and counter, with radii of the bases, the difference between which is equal to the diameter of the wire used for the spring, with the formation of a seat between the cones in the base of the cone grip under the support coil of the springs s with a diameter equal to the diameter of the support coil, rigidly fixed to each other, located with a bell to the spring, the grip groove is made at the base of the conical grip, the geometric dimensions of the groove are determined from the inequality:
NπD + h <I <spring pitch,
where I is the geometric dimensions of the groove;
N is an integer equal to the number of complete rings in the node;
πD is the circumference of one ring from the end of the support loop;
D is the diameter of the ring from the end of the support loop;
h is the distance between the reference and the inner loop in the area of the node,
the moving means is additionally provided with a plate rigidly fixed to the conical gripper at the groove wall from the side opposite to the end point of contact of the support turn in the conical gripper, the working surface of which faces the groove, protrudes beyond the conical gripper and is oriented parallel to the groove length or at an acute angle to her.  9. A device for orienting the support coil of the spring of the assembly formation mechanism on the support coil, comprising a conical gripper with the possibility of movement of the conical gripper and the spring relative to each other, characterized in that the conical gripper is arranged to be aligned with the spring in knotting mode, the conical gripper is made in in the form of a pair of cones: inner and outer, installed one in the other coaxially and counterclockwise, the radius of the smaller base of the outer cone is greater than the radius of the larger base of the inner cone by d the diameter of the wire is located in the socket to the spring, with the formation of a seat between the cones at the base of the capture in the form of a groove with a height equal to the diameter of the wire used, with a diameter of the platform equal to the diameter of the support coil, rigidly fixed to each other, the device is equipped with a restrictive plate with protrusions, the ends of which located in an arc with a radius not greater than the difference between the radius of the support coil of the spring and the diameter of the wire, and a length of not less than half the circumference of the circle rigidly fixed to the base of the mechanism, the outer surface of the inner cone and the inner surface of the outer cone are sampled by planes opposite the corresponding inner surfaces of the protrusions of the plate with a closed grip, and the plate is located at a distance from the base of the closed conical grip, not less than the diameter of the wire.  10. The mechanism of formation of the node on the supporting coil of the spring, containing for each end of the spring knot gear with a radial groove for the supporting coil and a bending bar at the end of the gear with the possibility of rotational movement of the gear with the bending bar around the supporting coil of the spring, conical capture of the supporting coil with a groove, s the possibility of movement of the conical gripper and gear relative to each other and relative to the spring, characterized in that the conical grippers are made with a seat at the base of the gripper between the cones with a diameter rum equal to the diameter of the support coil, the groove of the cone grip is made at its base opposite the knot gear, the longitudinal and transverse dimensions of which are determined not less than the size of the end of the support coil of the spring required to form a node, the height of the knot gear with the bending bar is less than the transverse size of the groove of the cone grip, the grippers are installed at a distance from each other not less than the axial size of the spring with a conical bell to the spring with the possibility of installing conical grippers coaxially with the spring, with the possibility their proximity to each other, the bevel grip and the knot gear are each connected to the cam of the knot formation mechanism through a kinematic chain, the two end links of which are on the side of the cone grip, the gears are interconnected by their previous link and with the cone grip, the gear along the rotation axes parallel to each other, with the possibility of installing the middle axis on the connecting line of the extreme axes, while one of the links of the kinematic chain of the movement of the cone grip and knot gear equipped with a limiter of the movement of media s axis.  11. The knot formation mechanism on the spring support turn according to claim 10, characterized in that the knot gear is mounted in the knot knob mounted on the plate so that it can move relative to the axis of the closed conical gripper, the knot knob on the end face is made with a groove opposite the groove of the conical gripper and the internal coil of the spring, the width is greater than the diameter of the spring wire by the amount of lifting of the coil of the spring, while the connection of the knot gear with the cam means of the formation mechanism of the assembly NENA through the knot knitting box plate.  12. A device for clamping a spring of a knot formation mechanism on a spring support coil, comprising for each end of the spring a cone grip of the support coil with a groove with the possibility of movement of the cone grip relative to the spring with means for securing the spring, characterized in that the cone grip is made with a seat for the support coil with an annular platform at the base with a diameter equal to the diameter of the support coil of the spring, a groove is made at the end of the support coil of the spring at the base of the cone grip, the cone grips are installed in the possibility of their rapprochement and installation coaxially with the spring, the means for securing the spring is additionally equipped with a liner rigidly fixed in a conical grip at its groove, the surface of the liner facing the spring is made with platforms for part of the support and inner coil of the spring, the angle between the planes of which is equal to the angle lifting the coil, and with an emphasis rigidly fixed to the base of the mechanism and located in a closed conical gripper opposite the liner, its counter surface is also provided with platforms for part of the supporting and internal For the parallel turns of the liner, the gap between the opposing liners of the liner and the stop for the spring support in the closed cone grip position is determined by the diameter of the wire used for the spring, the gap between the opposing liners of the liner and the stop for the inner coil of the spring in the closed cone grip is not less than the diameter used for spring wire.  13. The spring clamping device of the assembly formation mechanism on the spring support coil according to claim 12, characterized in that the insert is provided with a pin protruding above the surface of the insert, the surface of the pin facing the spring is made beveled at an acute angle to the spring axis, equal to the angle of the coil , the emphasis is also provided with a plug with internal dimensions corresponding to the overall dimensions of the insert pin located opposite the pin in the closed position of the grippers.  14. The spring clamping device of the assembly formation mechanism on the spring support coil according to claim 12, characterized in that the surface of the liner facing the spring installed in the knotting mode is made at an acute angle to the spring axis.  15. The spring clamping device of the assembly formation mechanism on the support coil of the spring according to claim 12, characterized in that the pad for the support coil of the spring on the liner is made with approaching the side surface of the liner from the side of the conical grip groove.  16. Cam means of the mechanism of the formation of the node on the support coil of the spring, which is a composite cam mounted on the working shaft and connected through its contact elements with actuators, characterized in that the contact elements are made in the form of rolling rollers, the cam is made of three parts: middle part and two side cams - knot gear cam and bevel grip cam, side cams are each made with a side surface consisting of four zones, one of which is it is a waiting arc, the length of which is determined by the waiting time of the conical gripper, gear, opposite the waiting arc is a contact zone, which is an arc of a circle whose length is determined by the contact time of the gripper, the gear with the spring, both waiting arcs and contact of each of the cams are located on different the sides from the axis of rotation of the cam and are connected to each other by two rectilinear branches - direct and reverse, the middle power part of the composite cam is equipped with stops located opposite each of its return branch parallel to it at a distance equal to the diameter of the corresponding rolling roller at the end of the contact zone of its cam with the possibility of interaction with its rolling roller, and the rollers are located on their side surface opposite the side surface of their cam on different axes of rotation.  17. Cam means of the mechanism of the formation of the node on the supporting coil of the spring under item 16, characterized in that the side cams are symmetrical about the line connecting the centers of the arcs of expectation and contact.  18. Cam means of the mechanism of the formation of the node on the supporting coil of the spring according to clause 16, characterized in that the stops of the power part of the cam are made at the ends with an arc facing its reverse branch.  19. Cam means of the mechanism of the formation of the node on the supporting coil of the spring according to clause 16, wherein the length of the arc of contact of the conical grippers with the spring is greater than the contact length of the knot gears with the spring.  20. The mechanism for moving the spring workpiece, including a lever grip of two levers, movable and stationary, connected along the axis of rotation of the movable lever relative to the stationary and made with the possibility of contact of the ends of the levers with each other with a gap equal to the diameter of the wire of the spring workpiece, means for moving the gripper with a system of levers of kinematic communication with the working shaft of the machine, means for closing and opening the gripper, characterized in that the lever gripper is configured to swing movements between their extreme positions, the means for closing and opening the gripper comprise a rod, one end fixed to the movable arm along an axis parallel to the axis of rotation of the movable arm, rotatable about this axis, the other end connected to the bracket along the middle axis of the strut, rotatable relative to of this axis parallel to the axis of rotation of the movable arm, the bracket is mounted on the stationary arm along the axis with the possibility of rotation around this axis parallel to the axis of rotation of the movable arm, opening, closing can, installed with the possibility of impact contact with the opening lever in one extreme position of the gripper, with the closing lever in the other extreme position of the gripper, mounted on the arm of the rocker arm rigidly mounted on the bracket, with the possibility of moving the middle axis of the strut to the line connecting the extreme axes fastening the end of the rod on the movable lever and fixing the bracket on the fixed lever or with the transition of this line to its opposite side, and vice versa, additionally, the opening-closing means provided that the average transition limiter canting axis of said lines, mounted on a stationary arm grip under the middle axis of the strut.  21. The mechanism for moving the spring billet according to claim 20, characterized in that the beam is made double, between which there is a bracket between two planes.  22. The mechanism for moving the spring billet, including a lever grip of two levers, movable and stationary, which are connected along the axis of rotation of the movable lever relative to the stationary and are made with the possibility of contact between the ends of the levers with each other with a gap equal to the diameter of the wire of the spring billet, means for moving the gripper with a system of levers of kinematic communication with the working shaft of the machine, means for closing and opening the gripper, characterized in that the lever gripper is made with the possibility of In order to move the swinging movements between their extreme positions, the means for moving the gripper includes a torsion shaft, at the end of which a fixed gripping lever is fixed, the means for closing and opening the gripper include a brace rod, one end mounted on the movable lever with the possibility of rotation around an axis parallel to the axis of rotation of the movable the lever relative to the fixed lever, the other end with the bracket - with the possibility of rotation relative to the middle axis of the strut parallel to the axis of rotation of the moving lever includes fixed arm, the bracket is mounted on the fixed arm with the possibility of rotation relative to an axis parallel to the axis of rotation of the movable lever relative to the fixed lever, the open-close link mounted on the arm with the possibility of rotation around the axis parallel to the axis of rotation of the movable lever relative to the fixed lever, with the possibility of movement the middle axis of the strut to the line connecting the end of the strut rod mounted on the movable arm, with the bracket mounted on the fixed arm or with the course of this line, the other end connected with one arm of the rocker arm along the axis of rotation, the axis of rotation of the rocker arm is mounted on a lever connected with the other end of the torsion shaft, a plate rigidly mounted on the machine frame, equipped with a first pair of stops located on opposite sides of the second arm of the rocker arm opposite it with the possibility of their impact contact with the second arm of the beam, and the plate with the second pair of stops on its sides, while the angular distance between the stops of different pairs differs by the value of the double twist angle ion shaft between the abutments of the plate is the opening-closing lever, with the shock of contact with them, is rigidly connected to the fixed gripping arm fixed to the torsion shaft is provided with a further lever fixed stroke limiter secondary strut axis located below this axis.  23. The mechanism for moving the spring blank according to claim 22, characterized in that the opening-closing lever is additionally equipped with stops from the stops, made with the possibility of their adjustment.  24. A device for capturing a spring moving mechanism, including levers - movable and fixed, made with the possibility of contact between the ends of the levers with a gap equal to the diameter of the spring wire, characterized in that the free ends of the levers at the end of the gripper are equipped with limiters of the fixed and movable lever, limiter the fixed lever is made in the form of a plate rigidly fixed on the fixed lever, at the end provided with a wedge-shaped guide, and on the sides - with two stops arranged symmetrically along the longitudinal axis of the plate along it, with two beveled surfaces each, not less than the distance between the movable and fixed levers in the open grip position, made at the end of the plate, along it, near the base of the wedge-shaped guide, with the formation of a platform for part of the coil of the spring, one beveled the surface of each stop is inclined towards the wedge-shaped guide and to the plane of the plate, when intersecting with a plane parallel to the plane of the plate, forming arc sections with a radius equal to a radius of spring web, each chamfered surface from another pair of chamfered surfaces is located at an angle to the plane of the plate, the intersection lines of which with the plane of the plate form arc sections with a radius equal to the radius of the coil of the spring, the height of the second pair of beveled surfaces is not less than the diameter of the wire, the limiter of the movable arm is a plate width not greater than the distance between the stops of the first limiter, rigidly mounted on a movable arm, mounted with the possibility of location parallel to the plate p the first limiter in the closed position, the plate of the second limiter is equipped with two stops symmetrically located relative to the longitudinal axis of the plate, located at an angle to each other at the end of the plate, equal to the angle of the wedge-shaped guide plate of the fixed lever limiter, and at a distance from each other equal to the width of the wedge-shaped guide in the place of their interaction, the stops are made with two pairs of beveled surfaces, each of which is parallel to the corresponding beveled surface rhnosti first stop.

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