Crowd-forming machine and crowd-forming assembly comprising a group of such machines

Abstract

Crowd-forming machine and crowd-forming assembly comprising a group of such machines. The machine (9) includes a rotary electric motor, a crank, a drive lever, and a drive rod. The motor stator (23) includes winding laminations (33) extending radially between an external stator diameter (D23e) and an internal stator diameter (D23i), and electrical windings (39). The motor rotor (29) includes a rotor shaft (51) centered on a main axis (A1), surrounded by a cylindrical portion (53) of the rotor and integral with the cylindrical portion and the crank, and permanent magnets (57). The ratio of the stator's external diameter (D23e) to a length (L53) of the cylindrical portion (53), measured parallel to the main axis without exceeding the permanent magnets, is between 2.0 and 4.0, preferably between 2.5 and 3.5, and even more preferably between 2.8 and 3.2. (See Figure 3 for abbreviations.)

Description

Title of the invention: Crowd-forming machine and crowd-forming assembly comprising a group of such machines

[0001] The present invention relates to a crowd training machine and a crowd training assembly comprising a group of such machines.

[0002] The invention relates to the technical field of crowd forming machines of the connecting rod actuator type to the frame, for a loom with heddle frames.

[0003] It is known to employ a plurality of electric actuators on the frame to drive beam frames into vertical oscillations. Depending on the technology employed, the electric actuators produce either oscillating or continuous rotation. In particular, EP4144903A1 and EP4219813A1 describe crowd-forming machines in which each electric actuator drives the corresponding beam frame via a drive mechanism, comprising a crankpin, connecting rods, and levers, which transforms the rotation produced by the actuator into a reciprocating translation of the beam frame.

[0004] During operation, the motor must stop and restart frequently, depending on the desired position of the heddle frame with each stroke of the loom. Therefore, it is desirable that the rotational inertia of the motor rotor be minimal to avoid excessive vibration and significant energy consumption during these accelerations. Furthermore, the space available for arranging the motors is relatively small. Consequently, the actuators used in such heddle-forming machines have relatively low torque due to constraints on inertia and size. However, it is desirable that the torque developed by the actuators be sufficiently high to drive the heddle frames, which can be relatively heavy and on which the tensioned warp threads exert forces tending to oppose their movement.Furthermore, the speed required to drive the frames is generally lower than the nominal speed of the motors, so the motors operate with relatively low efficiency.

[0005] It is also known from FR3004468A3 to add a gearbox to the output of the rotor of a crowd-forming machine motor. In practice, this makes it possible to obtain a higher torque at the gearbox output and therefore to adopt an operating mode in which the motor efficiency is higher. However, adding a gearbox is expensive, poses space constraints, and is not optimal in terms of efficiency due to losses related to the gearbox. Furthermore, the inertia of the entire geared motor assembly is significantly increased because of the rotating parts of the gearbox, whose rotational inertia is added to that of the rotor.

[0006] The aim of the invention is therefore to propose a crowd formation machine whose moment of inertia is reduced, without causing an excessive increase in size and cost and without lowering the efficiency and nominal torque.

[0007] To this end, the invention relates to a heddle-forming machine for actuating a heddle frame of a loom in an alternating translational stroke along a frame axis, the heddle-forming machine comprising: • a rotary electric motor, comprising: • a frame, centered on a main axis of the rotary electric motor and configured to be fixed to a machine frame of the loom, • a stator, integral with the frame, • a rotor, arranged in the stator and comprising a cylindrical part, centered on the main axis and comprising an external peripheral wall, • a first bearing, arranged in a first plane, perpendicular to the main axis, on one front side of the rotary electric motor, and • a second bearing, arranged in a second plane, perpendicular to the main axis, on a rear side of the rotary electric motor, the first bearing and the second bearing guiding a rotation of the rotor relative to the stator around the main axis; • a crank, fixed to the rotor and comprising a crank defining an eccentric axis, parallel to the main axis and distant from the main axis by a distance of eccentric center distance; • a drive lever, which is configured to pivot about a first lever axis relative to the machine frame, to actuate the beam frame, the first lever axis being fixed relative to, and parallel to, the main axis; and • a connecting rod, which includes: • a first end, attached to the crankpin and pivoting around the eccentric axis relative to the crankpin, and • a second end, attached to the attack lever by pivoting around a second lever axis relative to the attack lever, the second lever axis being parallel to the first lever axis;

[0008] characterized in that: • The stator includes: • winding laminations, surrounding the main axis and extending radially between an external stator diameter and an internal stator diameter centered on the main axis, the winding laminations forming winding teeth distributed around the main axis, directed towards the main axis and defining stator slots between them, which extend parallel to the main axis, and • electrical windings, each electrical winding being wound around several of the winding teeth as they are received in the stator slots; and • The rotor includes: • a rotor shaft, centered on the main axis, surrounded by the cylindrical part of the rotor and being integral with the cylindrical part of the rotor and the crank, and • permanent magnets, arranged on the outer peripheral wall of the cylindrical part and distributed around the main axis, each permanent magnet comprising a respective external surface, the external surfaces being opposite the winding teeth and inscribed on a rotor circle, centered on the main axis and defining a rotor diameter; and • a ratio of the external diameter of the stator to a length of the cylindrical part, measured parallel to the main axis without exceeding the permanent magnets, is between 2.0 and 4.0, preferably between 2.5 and 3.5, preferably still between 2.8 and 3.2.

[0009] A key idea of ​​the invention is that the rotor comprises, in addition to the cylindrical portion, a rotor shaft. This reduces the rotor's moment of inertia compared to the prior art, since a larger proportion of the rotor's mass is brought closer to the main axis by being concentrated in the rotor shaft rather than in the cylindrical portion. Retaining the cylindrical portion nevertheless allows for a significant lever arm, ensuring that the electromagnetic field imparted by the stator to the rotor's permanent magnets, which are mounted on the cylindrical portion, allows for a relatively high rated torque. Furthermore, retaining the cylindrical portion allows the rotary electric motor to be designed with a relatively large external stator diameter, in particular larger than the length of the cylindrical portion, without an excessive increase in the moment of inertia.The ratio between the stator's external diameter and the length of the cylindrical section gives the rotary electric motor a higher rated torque and a lower rated rotational speed than in the prior art. During operation, the motor can therefore be used at a speed closer to its rated speed, ensuring maximum efficiency. Since the crank is directly attached to the rotor shaft, meaning no mechanical reduction gear is required between the rotor and the crank, the overall size, rotational inertia, and cost are not excessive.

[0010] According to other advantageous aspects of the invention, the invention includes one or several of the following characteristics, taken individually or in all technically possible combinations: • The rotor comprises a first set of permanent magnets, comprising 12 to 40 permanent magnets, preferably 30 to 35 permanent magnets, preferably 30 permanent magnets, distributed equally around the main axis, and the stator comprises 24 to 48 slots, preferably 32 to 40 slots, preferably 36 slots, distributed equally around the main axis. • The rotor includes a second set of permanent magnets, offset from the first set of permanent magnets along the main axis, each permanent magnet of the second set of permanent magnets being adjacent to one of the permanent magnets of the first set of permanent magnets, along the main axis, and each permanent magnet of the first set of permanent magnets is angularly offset, around the main axis, from the permanent magnet of the second set of permanent magnets which is adjacent to it, by an angle of 0.5 to 5 degrees, preferably 1 to 2 degrees, preferably another 1 degree. • The external diameter of the stator measures between 160 and 200 mm, preferably between 170 and 190 mm, and even more preferably between 175 and 185 mm. • The rotor is designed so that a moment of inertia of the rotor is less than 100 kg.cm2, preferably less than 90 kg.cm2, preferably less than 80 kg.cm2. • The crowd forming machine includes an electrical cabinet, comprising an electrical power circuit configured to electrically supply the rotary electric motor and in that the rotary electric motor develops a nominal torque of between 30 and 100 Nm, preferably between 50 and 70 Nm, preferably between 60 and 70 Nm. • The electrical power circuit delivers a supply current of intensity I to the rotary electric motor which develops a torque reported per unit current I of between 6.5 and 8 Nm / A, preferably between 7 and 7.5 Nm / A, when the rotational speed of the rotor is maintained at 750 revolutions per minute. • It is expected that (i) each winding tooth will include: • a tooth head, delimited by the internal diameter of the stator, • a tooth root, delimited by the external diameter of the stator, and • a tooth body, which extends perpendicularly to the main axis, which connects the tooth head to the tooth shank and which has a generally rectangular shape when projected into the foreground, each tooth body having a length, measured radially with respect to the main axis, of between 19 and 25 mm, preferably between 20 and 23 mm, preferably between 21 and 23 mm; and that

[0011] (ii) each electrical winding forms three layers of wire around the winding tooth around which said electrical winding is wound. • The rotor shaft comprises a single piece which extends to connect the first plane and the second plane. • The rotor includes a disc, extending perpendicularly to the main axis, comprising recesses distributed around the main axis and a central bore, through which the disc is fitted onto the rotor shaft, and the cylindrical part is integral with the rotor shaft and the disc and surrounds the disc. • The rotor shaft includes a centering wall, cooperating with the central bore to center the disc on the rotor shaft, and a collar, extending radially to the main axis and being arranged between the first plane and the second plane, the disc being fixed to the collar by means of at least one screw parallel to the main axis. • It is planned that (i) the crank includes: • a base, fixed to the rotor shaft, and • a connecting piece, integral with the crankpin and mounted on the base; and that

[0012] (ii) The crowd-forming machine includes an adjustment system, which includes locking means, configured to: • allow adjustment of the eccentric center distance, by a relative displacement between the base and the connecting piece, in an adjustment system configuration, and • Secure the base with the connecting piece, in a locked configuration of the adjustment system. • The base includes a cam groove, defining a spiral around the main axis, and the linkage piece includes a follower finger circulating along the cam groove to guide the linkage piece relative to the base when the adjustment system is in adjustment configuration and thus vary the eccentric center distance. • The connecting piece and the base pivot relative to each other around a crank axis parallel to the main axis, when the adjustment system is in adjustment configuration. • It is expected that (i) a rotational stroke without a change of direction of the rotor around the main axis corresponds to an oscillation stroke of the lever attack around the first lever axis, the oscillation stroke including a high frame orientation, a crossover orientation and a low frame orientation of the attack lever, the crossover orientation being median between the high frame orientation and the low frame orientation; and that

[0013] (ii) The rotary electric motor includes locking means, which allow: • a locking configuration, in which the locking means immobilize the rotor relative to the stator around the main axis, selectively according to several predetermined reference orientations, including: • a crowd amplitude adjustment orientation, in which the attack lever is in the high frame orientation or in the low frame orientation, and • a crowd height adjustment orientation, at 90 degrees to the crowd amplitude adjustment orientation and in which the attack lever is in the crossing orientation; and • a release configuration, in which the locking means permit rotation of the rotor about the main axis relative to the stator. • The locking means include a locking pin, movable relative to the stator in a direction parallel to the main axis, a first notch, belonging to the rotor and cooperating with the locking pin in the locking configuration, to immobilize the rotor in the crowd amplitude adjustment orientation, and a second notch, belonging to the rotor and cooperating with the locking pin in the locking configuration, to immobilize the rotor in the crowd height adjustment orientation. • The crowd forming machine is arranged so that, when the rotary electric motor is in a locked configuration with the rotor in the crowd amplitude adjustment orientation, then the main axis, the eccentric axis and the second lever axis are substantially coplanar. • The crowd-forming machine includes: • a front flange, integral with the frame and including a circular flange, configured to cooperate with the machine frame, so that the frame can be positioned on the machine frame; • means for fixing the rotary electric motor to the machine frame, for fixing the rotary electric motor to the machine frame when the circular flange cooperates with the machine frame; and • an indexing means, which is separate from the fastening means and which requires that, when the circular flange cooperates with the machine frame, the frame be positioned so that: • the attack lever either in the high frame orientation or in the low frame orientation when the rotor is in the crowd amplitude adjustment orientation in lock configuration, and • the attack lever is in the crossing orientation when the rotor is in the crowd height adjustment orientation in the locking configuration. • The first lever axis and the second lever axis are connected by a lever arm line perpendicular to the second lever axis; the eccentric axis and the second lever axis are connected by a connecting rod line perpendicular to the second lever axis and defining a connecting rod-lever angle with the lever arm line; and the connecting rod-lever angle is 97 degrees, plus or minus 2 degrees, when the attack lever is in the crossing orientation.

[0014] The invention also relates to a crowd formation system, comprising a group of crowd formation machines as defined above and in which: • each group crowd formation machine defines a lever arm distance, measured between the first lever axis and the second lever axis; • The lever arm distance of each crowd-forming machine in the group is equal to the lever arm distance of each other crowd-forming machine in the group; and • When the group's crowd-forming machines are in a locked configuration with the rotor in one of the reference orientations, then the respective main axes, eccentric axes, and second lever axes of the group's crowd-forming machines are coplanar.

[0015] The invention will become clearer upon reading the following description, given solely by way of non-limiting example and with reference to the accompanying drawings in which:

[0016] [Fig-1] [Fig.1] is a side view of a crowd formation set comprising several groups of crowd forming machines mounted on a machine frame, according to a first embodiment of the invention, an attack lever and an attack rod belonging to one of the crowd forming machines and driving a frame of rails being shown, the attack lever being of a first type.

[0017] [Fig.2] [Fig.2] is a view from an opposite side of the crowd formation assembly of [Fig.1], an attack lever and an attack rod belonging to another of the crowd-forming machines and driving another rail frame being shown, the attack lever being of a second type.

[0018] [Fig.3] [Fig.3] is a longitudinal cross-sectional view of one of the machines of crowd formation of figures 1 and 2, centered on a main axis belonging to the rotary electric motor of this crowd formation machine.

[0019] [Fig.4] [Fig.4] is a partial front view of the crowd-forming machine of [Fig.3], where the driving rod is omitted.

[0020] [Fig.5] [Fig.5] is a view similar to that of [Fig.3], where the rotary electric motor is in a blocking configuration and receives a setting tool.

[0021] [Fig.6] [Fig.6] is a perspective view of a rear side of the crowd forming machine of Figures 3 to 5, with the setting tool of [Fig.5], the crowd forming machine being in the locked configuration and being mounted on the machine frame.

[0022] [Fig.7] [Fig.7] is a cross-sectional view of a stator of the rotary electric motor of the preceding figures.

[0023] [Fig.8] [Fig.8] shows a detail B of [Fig.7].

[0024] [Fig.9] [Fig.9] is an exploded perspective view of part of the electric motor rotating and part of a crank belonging to the crowd-forming machine of the preceding figures.

[0025] [Fig.10] [Fig.10] is a view similar to that of [Fig.1], in which part of the crowd-forming assembly is omitted and in which an attack lever and an attack rod belonging to another of the crowd-forming machines and driving another rail frame are shown, the attack lever being of a third type.

[0026] [Fig. 11] [Fig. 11] is a view similar to that of [Fig. 1], in which part of the crowd-forming assembly is omitted and in which an attack lever and an attack rod belonging to another of the crowd-forming machines and driving another rail frame are shown, the attack lever being of a fourth type.

[0027] [Fig.12] [Fig.12] is a view similar to that of [Fig.1], in which part of the crowd-forming assembly is omitted and in which an attack lever and an attack rod belonging to another of the crowd-forming machines and driving another rail frame are shown, the attack lever being of a fifth type.

[0028] [Fig. 13] [Fig. 13] is a view similar to that of [Fig. 1], in which part of the crowd-forming assembly is omitted and in which an attack lever and an attack rod belonging to another of the crowd-forming machines and driving another rail frame are shown, the attack lever being of a sixth type.

[0029] [Fig.14] [Fig.14] is a view similar to that of [Fig.1], in which part of the crowd formation assembly is omitted and in which an attack lever and an attack rod belonging to another of the crowd-forming machines and driving another frame of smooths are shown, the attack lever being of a seventh type.

[0030] [Fig. 15] [Fig. 15] is a view similar to that of Figures 10 to 14, of an assembly crowd formation comprising groups of crowd formation machines, according to a second embodiment of the invention.

[0031] [Fig. 16] [Fig. 16] is a cross-sectional view similar to that of [Fig. 3] of a crowd training machines according to a third embodiment of the invention.

[0032] [Fig. 17] [Fig. 17] is a front view similar to that of [Fig. 4] of the machine crowd formation of the [Fig. 16].

[0033] [Fig. 18] [Fig. 18] is an exploded perspective view of the forming machine the crowd in figures 16 and 17.

[0034] [Fig. 19] [Fig. 19] is a cross-sectional view similar to that of [Fig. 3] of a machine crowd formation according to a fourth embodiment of the invention.

[0035] [Fig.20] [Fig.20] is a front view similar to that of [Fig.4] of the machine crowd formation of the [Fig. 19].

[0036] [Fig.21] [Fig.21] is a perspective view of a crank belonging to a crowd training machine according to a fifth embodiment of the invention.

[0037] Consider a loom 1, partially shown in Figures 1 and 2, according to a first embodiment of the invention. The loom 1 comprises heddle frames 3 and a sheaf-forming assembly 5 for operating the heddle frames 3.

[0038] The crowd formation assembly 5 comprises a frame 7, fixed in the Earth's frame of reference, and crowd formation machines 9. In each of Figures 1 and 2, only one frame 3 is shown. The crowd formation machines 9 are partially shown, except for the one actuating this frame 3, which is shown in full.

[0039] Here, sixteen crowd forming machines 9 and sixteen rail frames 3 are provided, each crowd forming machine 9 respectively operating one of the frames 3. Alternatively, it may be provided that the same crowd forming machine 9 operates several rail frames 3. The rail frames 3 are superimposed in a direction perpendicular to the rail frames 3 and offset from each other by a distance of approximately 12mm in this direction, for example.

[0040] Each frame 3 advantageously comprises an upper cross member 42A, a lower cross member 42B parallel to the cross member 42A, and two uprights 33A and 33B parallel to each other and connecting the cross members 42A and 42B. Preferably, the cross members 42A Heddle beams 3 and 42B are horizontal, while uprights 33A and 33B are vertical. Crossbeams 42A and 42B are approximately 2 meters long. Each heddle frame 3 is equipped with a row of heddles, not shown, connecting crossbeams 42A and 42B and arranged between uprights 33A and 33B, distributed along crossbeams 42A and 42B. Each heddle has an eyelet through which a warp thread passes, the warp threads forming a web of warp threads. For example, each heddle frame 3 has a mass of approximately 7 kg and is subjected to tension forces from the warp threads adding an equivalent load of approximately 50%. The loom 1 advantageously includes other components, such as a beater, means for inserting a weft thread, and a weft feeder, which are not shown.

[0041] For the purpose of weaving, each sheaf-forming machine 9 is designed to actuate the corresponding heddle frame 3 along a reciprocating translational stroke C3, relative to the frame 7, along a frame axis Z3 specific to that frame 3. The term "stroke" refers to the path traveled by the frame 3 during its movement. Being moved by the machine 9 along the stroke C3, the frame 3 is moved parallel to the axis Z3, in a rectilinear motion, moving back and forth between an extreme upper position H3, corresponding to an upper limit of the stroke C3, and an extreme lower position B3, corresponding to a lower limit of the stroke C3. For example, the stroke C3 has a reference amplitude of approximately 100 mm, this amplitude being advantageously adjustable, as explained below.The Z3 axis, and therefore the displacement of frame 3, is preferably vertical, or at least parallel to the heddles of the frame 3 under consideration. The reference position P3 is defined as a central position, which can correspond to the crossing position of the loom 1 for all the warp thread sheets whose travels are centered with respect to a central plane comprising the heddle eyelets of the frames in position P3.

[0042] During weaving, for the insertion of each weft thread, the position of the frames 3 along their respective path C3 is determined by the action of the machines 9, independently for each frame 3, to define the sheave of the loom 1 receiving the inserted weft thread. The loom 1 then produces a fabric of warp and weft threads with a desired weave.

[0043] The frame 7 is preferably an assembly of welded or otherwise joined parts, fixed to the ground and positioned at one end of the beam frames 3. The frame 7 comprises two parts 7A and 7B, part 7A being more clearly visible in [Fig. 1] and part 7B being more clearly visible in [Fig. 2]. Parts 7A and 7B are arranged parallel to each other and to the beam frames 3 and face each other. Each part 7A or 7B comprises slots 11, each slot 11 receiving one of the crowd-forming machines 9, which is thus fixed to the frame 7. Here, each subset 7A or 7B comprises eight locations 11, receiving respectively eight of the machines 9.

[0044] Each crowd forming machine 9 comprises a rotary electric motor 13 and a crank 15, visible in more detail in Figures 3 and 4, as well as a connecting rod 17 and a drive lever 19, visible in Figures 1 and 2, through which the motor 13 actuates the frame 3. The rotary electric motors 13 and the cranks 15 of the sixteen crowd forming machines 9 are advantageously identical to each other, or essentially similar to each other.

[0045] Each crowd formation machine 9 preferably includes an adjustment system allowing adjustment of the crowd height, i.e. the reference position P3 relative to the ground, and on the other hand the crowd amplitude, i.e. the stroke amplitude C3, i.e. the distance between the extreme high position H3 and the extreme low position B3 taken by the frame 3 when it is driven under the action of the rotary electric motor 13.

[0046] Each rotary electric motor 13 is preferably controlled by a microcontroller housed in a control cabinet, not shown. The control cabinet includes, for example, a central processing unit, itself comprising a master controller, which exchanges data with each microcontroller of each sheaf-forming machine 9. The loom 1 advantageously includes a terminal allowing a weaver to apply different settings to the loom 1, depending on the desired woven articles. In practice, the weaver selects a weaving program for an article via the terminal, with a predetermined weave, speed, and profile. This instruction is transmitted to the central processing unit, which converts it into position commands for the rotary electric motors 13 of each sheaf-forming machine 9.The position commands are transmitted to the associated microcontroller and then to the rotary electric motor 13 via a power electrical circuit.

[0047] As can be clearly seen in Figures 3 and 4, the rotary electric motor 13 comprises a frame 21, a stator 23, a rotor 29, a first bearing 31A and a second bearing 31B. A first plane PI is defined in which the first bearing 31A extends and a second plane P2 in which the second bearing 31B extends.

[0048] The rotary electric motor 13 is a permanent magnet synchronous motor whose structure is detailed below. The choice of this motor technology offers several advantages for the application, including precise speed and torque control providing fine control of the frame 3, simplified construction and maintenance thanks to the fact that the rotor 29 is winding-free, and the ability to maintain high torque even at low speeds, thus eliminating the need for a gearbox between the rotor 29 and the crank 15.

[0049] The casing 21 constitutes the interface of the rotary electric motor 13 with respect to the frame 7 by being fixed on one of the locations 11. The carcass 21 is centered on a main axis Al of the motor 13, which is perpendicular and fixed with respect to the frame axis Z3.

[0050] Advantageously, the frame 21 includes an inner peripheral part 22, an outer peripheral part 24, a front flange 25 and a rear flange 27. The inner peripheral part 22 surrounds the main axis Al and is fixed to the front flange 25 and the rear flange 27. The flanges 25 and 27 are perpendicular to the main axis Al, and close the axial ends of the inner peripheral part 22. The outer peripheral part 24 encloses the inner peripheral part 22.

[0051] Parts 22 and 24 advantageously define between themselves a helical channel 28, centered on the axis A1, constituting a cooling circuit, intended to guide the circulation of a heat transfer fluid within the thickness of the casing 21, to cool the engine 13. The outer peripheral portion 24 comprises two radial channels 30 fluidically connected to respective ends of the helical channel 28, respectively to supply the helical channel 28 with heat transfer fluid and to drain the heat transfer fluid from said helical channel. The casing 21 preferably includes two seals 32, interposed radially between the inner peripheral portion 22 and the outer peripheral portion 24, being arranged axially on either side of the channels 28 and 30, in order to contain the heat transfer fluid inside the casing 21.The radial channels 30 are connected to a cooling circuit, preferably common to all machines 9, which includes tubes, a pump for circulating the heat transfer fluid in the cooling circuit, a heat dissipation device and a tank.

[0052] Advantageously, the front flange 25 is fixed by screws to the inner peripheral part 25. The front flange 25 includes a circular flange 26, cooperating with the frame 7, allowing the carcass 21 to be positioned on the frame 7. In particular, at location 11, the frame 7 forms a circular opening 34 complementary to the circular flange 26, and which coaxially receives the circular flange 26, without constraining the orientation of the circular flange 26, and therefore of the carcass 21, around the axis Al, relative to the frame 7. The carcass 21 also bears forward along the axis Al against the frame 7, by bringing a bearing face 36 of the front flange 25 into contact with a corresponding face 38 of the frame 7, surrounding the circular opening 34, at location 11.The machine 9 further includes an indexing means, allowing the orientation of the frame 21 to be imposed relative to the frame 7 around the axis AL. For example, the indexing means includes an indexing pin 89, which is received both in an orifice formed in the front flange 25, parallel and at a distance from the axis Al, and in a corresponding orifice formed at the location 11 of the frame 7, formed at the periphery of the circular opening 34. The indexing means can be considered as . a rotating keying device, imposing a single orientation of the carcass 21 relative to the frame 7 around the axis Al. This allows the motor 9 to be positioned in a particular position in which the mechanical efficiency of the transmission formed by the crank 15, the connecting rod 17 and the lever 19 is optimal, and in which these elements take a particular position facilitating the adjustment of crowd height or crowd amplitude, as explained later.

[0053] In addition to the aforementioned indexing means, the machine 9 includes fastening means, also clearly visible in [Fig.6], for fixing the motor 13 to the frame 7. For example, the fastening means consist of screws 84, which pass through a screw flange 86 belonging to the frame 21 and are screwed into the frame 7 to fix the motor 13 to the frame 7.

[0054] The stator 23, visible in [Fig.3] and shown individually in Figures 7 and 8, is fixedly attached to the frame 21, being enclosed inside the frame 21. Together with the frame 21, the stator 23 represents the fixed part of the rotary electric motor 13. The function of the stator 23 is to generate a magnetic field when the rotary electric motor 13 is supplied by the aforementioned power circuit from the control cabinet.

[0055] For this purpose, the stator 23 includes winding laminations 33, winding teeth 35 and electrical windings 39, as well as, preferably, two plastic end caps 40.

[0056] The winding laminations 33, visible in Figures 3 and 7, each have a ring shape surrounding the main axis AL. Each winding lamination 33 is flat, perpendicular to the main axis AL. The winding laminations 33 are stacked along the main axis AL to form a ferromagnetic core of the motor 13, tubular in shape around the main axis AL. The stator 23 is fixed to the inner part 24 of the frame 21 by means of the laminations 33. Each winding lamination 33 extends radially between an external stator diameter D23e and an internal stator diameter D23i, centered on the main axis AL.

[0057] The two plastic tips 40 are positioned respectively at each axial end of the winding core formed by the winding sheets 33.

[0058] Advantageously, and as shown in [Fig. 8], each winding lamination 33 is made up of several contiguous toothed laminations 47, radially oriented and evenly distributed around the main axis AL. Each toothed lamination 47 has a relief 49 cooperating with a complementary relief on the adjacent toothed lamination 47 belonging to the same lamination 33, said reliefs positioning the adjacent toothed laminations 47 relative to each other. Thus, the manufacture of the stator 23 is simplified and is optimal in terms of the amount of material used, particularly compared to block machining which would require more manufacturing time and result in material losses due to the removal of a central portion.

[0059] The winding teeth 35, one of which is shown in more detail in [Fig.8], are formed by the winding laminations 33. Each winding tooth 35 is formed by the stacking of several tooth laminations 47 aligned along the main axis Al. Each tooth lamination 47 belongs to a single winding tooth 35. The tooth laminations are advantageously made of steel.

[0060] The winding teeth 35 are directed towards the main axis AL. The teeth 35 delimit the stator slots 37, which extend parallel to the main axis Al and are open in the direction of the main axis AL. Each slot 37 is delimited between two successive teeth 35 by these two teeth 35. Advantageously, each winding tooth 35 comprises a tooth head 41, delimited by the internal diameter of the stator D23i, a tooth root 43, delimited by the external diameter of the stator D23e, and a tooth body 45, which extends perpendicularly to the main axis Al, which connects the tooth head 41 to the tooth root 43. The stator slot 37 is formed between the two adjacent tooth heads 41. As clearly visible in [Fig.8], the tooth body 45 has a general rectangular shape when projected into a transverse plane of the stator 23.The tooth body 45 also has a length L45, measured radially with respect to the main axis Al, of between 19 and 25 mm, preferably between 20 and 23 mm, preferably between 21 and 23 mm.

[0061] Advantageously, the external diameter of the stator D23e measures between 160 and 200 mm, preferably between 170 and 190 mm, and even more preferably between 165 and 185 mm. Advantageously, the use of a motor with a large external diameter of the stator D23e allows for the creation of an electromagnetic circuit that exploits the distance to the main axis Al of the motor 13, and promotes the application of a lever arm of the drive forces of the rotor 51 by the stator 37 over a long distance. In other words, the external diameter of the stator D23e provides a significant nominal torque to the motor 13 of the crowd-forming machine. Advantageously, the stator slots 37 are 24 to 48 in number, preferably 32 to 40, preferably 36, and are distributed equitably around the main axis AL. Advantageously, the stator slots 37 have a width of 5.5 mm, measured orthoradially, and a height of 22.1 mm, measured radially.These dimensions allow for an optimal compromise between the torque of the rotary electric motor 13 and its size.

[0062] Each electrical winding 39 is wound around the winding teeth 35 after being received in the stator slots 37. Advantageously, there are three electrical windings 39, each wound around ten winding teeth 35 distributed equally around the main axis AL. The plastic end caps 40 mechanically protect the electrical windings 39 in their winding, so that they are not cut by the laminations 33 at the axial ends of the core. Each electrical winding 39 forms three layers. Of these three layers, the first The first layer advantageously has 17 turns of conductive wire around the winding tooth 35 around which the electrical winding 39 is wound. The second layer preferably has 15 turns of wire. The third layer preferably has 8 turns of conductive wire. In this way, the wire length used is optimized to obtain a magnetic field, and therefore an electromagnetic torque, sufficient for the application, while limiting heat dissipation along the wire, in order to improve the efficiency of the rotary electric motor 13. The wire diameters are preferably chosen to be on the order of 1.12 mm, which is also compatible with the expected performance while minimizing heating of the stator 29 thanks to sufficient heat dissipation in the stator slots 37.

[0063] The motor 13 advantageously comprises a terminal block, not shown, integral with the frame 21, to which the windings 39 are electrically connected. The terminal block allows the motor 13 to be electrically connected to the aforementioned power circuit from the control cabinet. When the motor 13 is energized, an electric current flowing through the windings 39 generates the magnetic field.

[0064] As shown in Figures 3 and 9, the bearings 31A and 31B are coaxial with the axis Al and are mounted in the stator 23. In particular, the bearing 31A is mounted on the front flange 25 and the bearing 31B is mounted on the rear flange 27. The first bearing 31A, located on the front side where the motor 13 is loaded, is about twice as large as the second bearing 31B, in order to support greater dynamic forces on the front side of the motor 13. Preferably, the first plane PI and the second plane P2 are less than 120mm apart.

[0065] The rotor 29 is disposed in the stator 23 and is pivotally mounted relative to the stator 23 about the main axis Al via bearings 31A and 31B. The rotor 29, visible in particular in Figures 3 and 9, is disposed in the stator 23 and comprises a rotor shaft 51, a cylindrical portion 53, and permanent magnets 57. The rotor shaft 51 is centered on the main axis Al and is received in bearings 31A and 31B, at the ends of the rotor shaft 51. In particular, the rotor shaft 51 passes through each of the two bearings 31A and 31B. The rotor 29 is thus guided in rotation by bearings 31A and 31B via the rotor shaft 51. Advantageously, the rotor shaft 51 comprises a single piece, which extends to connect the first plane PI and the second plane P2. This single piece is received in each of the bearings 31A and 31B. In the present example, the rotor shaft 51 consists of this single single piece.This optimizes the coaxiality of the rotor 29 and the stator 23, unlike a multi-piece rotor, which could cause misalignments between the pieces. Using a single-piece component also simplifies the assembly of the motor 13 and improves the guidance accuracy of the rotor 51 relative to the stator 23, particularly to ensure a position. precise operation of the magnets relative to the stator.

[0066] The rotor shaft 51 is generally tubular in shape. Advantageously, more precisely, the rotor shaft 51 comprises three hollow cylindrical housings 52A, 52B, and 52C arranged successively along the axis Al, giving the shaft 51 its tubular shape. The rotor shaft 51 thus forms an internal conduit 83, coaxial with the axis Al, extending from one end of the shaft 51 to the other. The internal conduit 83 is formed here by the successive cylindrical housings 52A, 52B, and 52C. The overall shell of the rotor shaft 51 preferentially extends inside a virtual cone, centered on the axis Al and whose apex is directed towards the rear of the motor 13, the cone passing successively through the balls of bearing 31A and bearing 31B. Since shaft 51 is tubular and hollow, its inertia is minimized due to an overall envelope that is close to the AL axis.

[0067] The cylindrical part 53 surrounds the rotor shaft 51, being coaxial with the latter and with the main axis AL. The cylindrical part 53 and the rotor shaft 51 are fixedly joined to each other, so that the rotor shaft 51 can be driven in rotation around the axis Al relative to the stator 23, by rotating the rotor 29 via the cylindrical part 53.

[0068] As clearly visible in [Fig.9], the rotor 29 preferably includes a disc 61, through which the cylindrical part 53 is integral with the main shaft AL. The disc 61 is disposed between the planes PI and P2.

[0069] Preferably, the disc 61 is integral with the cylindrical part 53, forming a single piece with the cylindrical part 53. Alternatively, the disc 61 can be a piece assembled with the cylindrical part 53. Preferably, the disc is arranged between the axial ends of the cylindrical part 53, so that the cylindrical part 53 and the disc have a longitudinal cross-section in the shape of a "T".

[0070] Preferably, the disc 61 is integral with the rotor shaft 51 by being fitted onto the rotor shaft and fixed for rotation around the rotor shaft 51. For this purpose, the disc 61 is advantageously fitted onto the rotor shaft 51 between planes PI and P2, so that the rotor shaft 51 passes through it via a central bore 63 in the disc 61. The rotor shaft 51 includes a centering wall 67, which is here an external radial wall, cooperating with the bore 63 in a cylinder-to-cylinder connection. Advantageously, the rotor shaft 51 includes a collar 69, which extends radially to the main axis A1 and is arranged between the first plane PI and the second plane P2. The disc 61 is fixed to the collar 69, for example by means of several assembly screws 70, for example ten assembly screws 70, parallel to the main axis Al and distributed around this axis, and several elastic pins 72, for example three.The attachment of the disc 61 to the collar 69 fixes the disc 61 in rotation around the rotor shaft 51.

[0071] Preferably, the disk 61 includes recesses 65, for example ten recesses, distributed around the main axis Al. Radially, the recesses 65 are arranged between the cylindrical part 53 and the rotor shaft 51, in particular between the cylindrical part 53 and the collar 69. Each recess 65 is an opening passing through the disk 61 through and through parallel to the axis Al.

[0072] Using a disc 61 to secure the cylindrical part 53 minimizes the inertia of the rotor 29, particularly if the disc 61 is equidistant, or nearly equidistant, from planes PI and P2. Preferably, to minimize rotational inertia, a single disc 61 is used to connect the cylindrical part 53 to the shaft 51, with the cylindrical part 53 and the shaft 51 being connected only by this single disc 61. Alternatively, several discs 61 can be used to connect the cylindrical part 53 to the rotor shaft 51.

[0073] The permanent magnets 57 are arranged on an external peripheral wall 55 of the cylindrical part 53. The external peripheral wall 55 is advantageously an external radial surface, centered on the axis Al, which extends preferably from one axial end to the other of the cylindrical part 53, opposite the winding laminations 33, over the entire length of the winding teeth 33.

[0074] Each permanent magnet 57 comprises a respective external surface S57, the external surfaces S57 being opposite the winding teeth 35 and inscribed on a rotor circle 60, centered on the main axis Al, perpendicular to the axis Al, and defining a rotor diameter D29. Advantageously, the magnets 57 have a length, measured parallel to the main axis Al, of 30 mm, a width, measured orthoradially, of 10.5 mm, and a thickness, measured radially, of 3.5 mm.

[0075] A length L53 of the cylindrical part 53 is defined, which is measured parallel to the main axis AL. The length L53 is measured without exceeding the permanent magnets 57 in the direction of the axis Al, that is to say, in the present example, from a front end of one of the permanent magnets 57 of the assembly arranged at the front of the rotor 29, to the rear end of one of the permanent magnets 57 of the assembly arranged at the rear of the rotor 29.

[0076] The rotor 29 is dimensioned such that the ratio of the external diameter of the stator D23e to the length L53 of the cylindrical part 53 is between 2.0 and 4.0, preferably between 2.5 and 3.5, and even more preferably between 2.8 and 3.2. This dimensioning is optimal for obtaining high torque while minimizing inertia. In other words, this dimensioning is optimal for ensuring a high energy density of the motor 13. The motor torque constant Kt is defined as the torque value obtained per unit current I delivered by the power circuit. The torque constant Kt is calculated here at a motor speed of 750 revolutions per minute, which corresponds to a working speed of 1500 strokes per minute. Advantageously, the motor 13 develops a torque constant Kt of between 6.5 and 8 Nm / A. preferably between 7 and 7.5 Nm / A.. Achieving such a value of motor torque constant Kt corresponds to the use of a motor with good efficiency.

[0077] Preferably, the external diameter of the stator D23e is equal to 180 mm and the length L53 is equal to 60 mm. Alternatively, the length L53 is less than 60 mm, and the external diameter of the stator D29e is adjusted to still obtain the above ratio.

[0078] Advantageously, the rotor 29 comprises a first set 59A of permanent magnets 57, comprising twelve to forty permanent magnets 57, preferably thirty to thirty-five permanent magnets 57, preferably thirty permanent magnets 57, distributed equally around the main axis Al. The permanent magnets 57 of this first set 59A are arranged one after the other around the main axis AL. Preferably, the permanent magnets 57 of this first set 59A are arranged in the same plane perpendicular to the axis AL. Coupled with the dimensions of the stator 23 mentioned above, these dimensions are optimal for maximizing torque while minimizing size.

[0079] Advantageously, the rotor 29 comprises a second set 59B of permanent magnets 57, offset from the first set 59A along the main axis AL. As with the first set 59A, the magnets 57 of this second set 59B are arranged one after the other around the main axis AL. Preferably, the permanent magnets 57 of this second set 59B are arranged along the same plane perpendicular to the axis Al, axially offset from the plane of the first set 59A. As can be seen in [Fig.9], each permanent magnet 57 of the second set 59B is adjacent to one of the permanent magnets 57 of the first set 59A, along the main axis AL. In addition, each permanent magnet 57 of the first set 59A is angularly offset, around the main axis Al, relative to the permanent magnet 57 of the second set 59B which is adjacent to it, for example by an angle of 0.5 to 5 degrees, preferably 1 to 2 degrees, preferably still 1 degree.Thus, for a given position of the rotor 29 around the axis Al, two permanent magnets 57 belonging to two different assemblies 59A and 59B, adjacent to each other, are not aligned with the same portion of the stator 23. This angular offset aims to reduce the occurrence of intermittent, jerky movements of the rotor 29, particularly during the starting of the motor 13, a phenomenon sometimes called cogging torque, detent torque, or "cogging" torque, which applies to motors with permanent magnet rotors. In other words, this angular offset aims to smooth the operation of the motor 13 by reducing torque oscillations. This design is particularly advantageous, since the present application requires relatively low-speed operation and repeated starts.

[0080] Advantageously, the rotor 29 is further dimensioned so that a moment rotor inertia 29 is less than 100 kg.cm2, preferably less than 90 kg.cm2, preferably less than 80 kg.cm2. This dimensioning helps to guarantee a high torque without excessively increasing the diameter of the rotor, whose inertia is usually detrimental, when too high, to the dynamic operation of the kinematic chain.

[0081] During weaving, the rotor 29 rotates at a speed of approximately 750 revolutions.min-1 relative to the stator.

[0082] Preferably, the rotary electric motor 13 has a rated torque between 30 and 100 Nm, preferably between 50 and 70 Nm, and preferably between 60 and 70 Nm. The motor 13, dimensioned as described above, has a torque of 65 Nm, up to 93 Nm at peak acceleration, an inertia of 78 kg.cm², and a rated power of 5.2 kW. The formula for rated power is the torque multiplied by the continuous and uniform angular velocity of the motor: P = Cco, co = 2pin / 60, with the motor's rotational speed n expressed in rpm.

[0083] The motor 13 advantageously includes a position sensor 91, for example of the resolver type, a measurement of which reflects the orientation of the rotor 29 around the axis Al, relative to the stator 23. Preferably, the position sensor 91 is located at a rear end of the shaft 51. The sensor 91 includes, for example, a fixed part attached to the stator 23 via the flange 27, and a movable part attached to the rear end of the shaft 51. For example, the sensor 91 allows the measurement of 4096 distinct discrete positions of the rotor 29 around the axis Al relative to the stator 23. The microcontroller associated with the rotary electric motor 13 determines and supplies the current to the various windings of the stator 23 as a function of the position of the rotor 29, based on the signals from the sensor 91 and the position commands.

[0084] Advantageously, the rotary electric motor 13 further comprises locking means, namely a locking pin 79 and at least two notches 81 and 82, enabling a locking configuration in which the rotor 29 is immobilized relative to the stator 23 around the main axis AL. The locking configuration is shown in [Fig. 5]. The locking pin 79 is movable relative to the stator 23 in a direction parallel to the main axis AL. The first notch 81, belonging to the rotor 29, cooperates with the locking pin 79 so as to immobilize the rotor 29 in a crowd amplitude adjustment orientation. The second notch 82, belonging to the rotor 29, cooperates with the locking pin 79 so as to immobilize the rotor 29 in a crowd height adjustment orientation. These specific orientations come into play when adjusting crowd height and crowd amplitude, which will be detailed later in the description.The release configuration is the configuration in which the locking means allow the rotor 29 to rotate around the stator 23. The release configuration is shown in [Fig. 3]. This is the . configuration which is used during weaving. Preferably, the notches 81 and 82 are formed at a rear axial end of the cylindrical part 53. Preferably, the locking pin 79 is mounted through the rear flange 27, so that it can be operated from outside the motor 13, at the rear of the motor 13, in particular manually.

[0085] When the locking pin 79 cooperates with the notch 81 in the locked position, the rotor 29 is immobilized in a first orientation relative to the stator 23, referred to as the "crowd amplitude adjustment orientation." When the locking pin 79 cooperates with the notch 82 in the locked position, the rotor 29 is immobilized in a second orientation relative to the stator 23, referred to as the "crowd height adjustment orientation." Preferably, the notch 82 is positioned at 90 degrees relative to the notch 81 about the axis AL. The crowd height adjustment orientation is therefore at an angle of 90° to the crowd amplitude adjustment orientation. In practice, four notches are advantageously provided, including two diametrically opposed notches 81 and two diametrically opposed notches 82, the notches 81 and 82 being spaced 90 degrees apart.

[0086] The rotational movement of the rotor 29 thus produced by the rotary electric motor 13 is then converted into the translational movement of the frame 3 by means of a connecting rod-crank-lever system, including the crank 15, the drive rod 17 and the drive lever 19.

[0087] As clearly shown in [Fig. 4], the crank 15 is directly attached to the rotor shaft 51, without any intermediate transmission or reduction gear. The crank 15 is located at the front of the motor 3. Plane PI separates the crank 15 from the cylindrical portion 53.

[0088] The crank 15 comprises a base 73, a connecting piece 75, and a crankpin 71.

[0089] The base 73 is fixed to the rotor shaft 51, so as to be driven in rotation by the rotor 29 about the axis Al relative to the stator 23. The base 73 is, for example, fixed to the rotor shaft 51 by means of three spring pins 85 and three assembly screws 74, parallel to the main axis Al and evenly distributed around this axis AL. A different number of pins 85 and screws 74 can be chosen. In the present example, the base 73 forms a radial plate and two rails, forming a sliding guide for the connecting piece 75.

[0090] The connecting piece 75 is mounted on the base 73. In this embodiment, the connecting piece 75 is a through axial sliding flange which is able to slide relative to the base 73, in a radial direction relative to the axis AL. The connecting piece 75 is received between the rails and is supported against the base plate 73 to be guided in sliding by the base 73.

[0091] The crank pin 71 defines an eccentric axis A2, parallel to the main axis Al and distant from the main axis Al by an eccentric center distance RL. The crank pin 71 and the connecting piece 75 are fixedly joined to each other.

[0092] The sliding of the connecting piece 75 and the crankpin 71 relative to the base 73 allows the center distance of the eccentric RI to be changed.

[0093] The connecting piece 75 belongs to an adjustment system for the crowd forming machine 3, allowing the center-to-center distance of the eccentric RL to be modified. Indeed, due to the structure of the crowd forming machine 9, the crowd amplitude is directly related to the center-to-center distance of the eccentric RL. In this case, the greater the distance RI, the greater the stroke amplitude C3, i.e., the greater the distance between positions B3 and H3. Modifying the center-to-center distance of the eccentric RI therefore allows the amplitude of the crowd opening controlled by the frame 3 to be modified.For example, it is expected that the distance RI can be varied from a minimum value of 20 mm to a maximum value of 60 mm, to vary the amplitude of the stroke C3 from a minimum value of 50 mm to a maximum value of 160 mm, when the height of the stroke C3 is centered on the reference position P3, i.e. with positions B3 and H3 equidistant from position P3.

[0094] The adjustment system also includes an adjusting screw 77, visible in [Fig. 3], which selectively allows the connecting piece 75 to slide relative to the base 73 and to lock the base 73 to the connecting piece 75. When the adjustment system is in an adjustment configuration, the screw 77 is loosened and sliding is permitted. Conversely, when the adjustment system is in a locking configuration, the adjusting screw 77 is tightened and sliding is impossible. Thus, the center distance of the eccentric RI can be adjusted if and only if the adjustment system is in the adjustment configuration, and is fixed if the adjustment system is in the locking configuration. During weaving, the adjustment system is in the locking configuration.

[0095] As shown in Figures 3 and 4, the adjusting screw 77 is advantageously provided to be coaxial with the axis AL. The adjusting screw 77 has a body that passes through an oblong opening 76, belonging to the connecting piece 75. A clamping nut 78 is provided in the oblong opening 76, into which the screw 77 is screwed. The screw 77 further has a head 80, by means of which the screw 77 can be rotated. The base 73 and the connecting piece 75 are axially interposed between the nut 78 and the head 80, so that tightening the screw 77 in the nut 78 clamps the connecting piece 75 against the base 73 to prevent sliding. The head 80 is preferentially arranged inside the internal conduit 83 of the rotor shaft 51. As shown in the [Fig.5], the head 80 is thus accessible from the rear of the motor 3, to be operated using an adjustment tool 88, for example a screwdriver, inserted up to the head 80 from the rear of the motor 3 via the internal conduit 83. The screw 77 is chosen to be short, so as to be more resistant to forces. torsion applied by the setting tool 88, as well as to minimize the inertia of the rotor 29, especially compared to a screw whose body would extend over the entire length of the rotor shaft 51. The sleeve of the shaft 51 is brought as close as possible to the axis Al, while leaving a central passage just sufficient to introduce the setting tool 88.

[0096] The connecting rod 17 is, at one end, attached to the crankpin 71 and pivots about the eccentric axis A2 relative to the crankpin 71, and therefore relative to the crank 15. At a second end, the connecting rod 17 is attached to the drive lever 19, pivoting about a lever axis A4 relative to the drive lever 19. The lever axis A4 is parallel to the main axis AL

[0097] Let R2 be a connecting rod center distance, defined as the distance between the lever axis A4 and the eccentric axis A2. Advantageously, the connecting rod 17 comprises two parts, telescopic relative to each other, so as to allow the connecting rod center distance R2 to be varied. The aforementioned adjustment system includes a means for adjusting the distance R2, allowing a connecting rod center distance adjustment configuration R2 and a connecting rod center distance locking configuration R2. In the crowd height adjustment configuration, sliding between the two parts of the connecting rod 17 is possible to vary the connecting rod center distance R2. This has the effect of offsetting the stroke C3 along the axis Z3 relative to the ground, i.e., adjusting the height of positions H3, B3, and P3 along the axis Z3.In locked configuration, the sliding between the two parts is locked, so that the two parts are fixed together and the center distance of connecting rod R2 is fixed, thus fixing the height of the stroke C3 relative to the ground along the axis Z3.

[0098] The drive lever 19, visible in figures 1 and 2, pivots about a lever axis A3 relative to the frame 7. The first lever axis A3 is fixed relative to, and parallel to, the main axis AL. Thus, the pivoting of the drive lever 19 about the axis A3 is constrained by the connecting rod 17 to the rotational movement of the crank 15, and therefore to the rotation of the rotor 29. At its end not attached to the drive rod 17, the drive lever 19 is attached to a lower end of the upright 33A of the frame of runners 3 which it actuates, preferably via a connecting rod.

[0099] By default, the locking system of the rotary electric motor 13 is in the release position and the adjustment system is in the locked position. During weaving, the microcontroller controls the power-up of the rotary electric motor 13, whose rotor shaft 51 then describes a rotational stroke around the main axis AL. Via the connecting rod-crank system described above, the movement is transmitted to the drive lever 19, which then describes an oscillating stroke around the first lever axis A3, driving the heddle frame 3 along the stroke C3. The stroke The oscillation of the leading lever 19 includes a high frame orientation, in which the frame 3 is in its high position H3, a crossover orientation, in which the frame 3 is in its reference position P3, and a low frame orientation, in which the frame 3 is in its low position B3. The leading lever in its high frame orientation 19' and the leading lever in its low frame orientation 19” are shown in Figures 10 to 14. The desired movement for the rail frame is thus obtained from the rotary electric motor 13, which is optimized for the application in terms of torque and size.

[0100] The aforementioned indexing means, i.e. the indexing pin 89, requires that the frame 21 and the locking system be oriented around the axis Al relative to the frame 7, so that the drive lever 19 is in the high frame orientation or in the low frame orientation when the rotor 29 is in the crowd amplitude adjustment orientation in the locking configuration, and that the drive lever 19 is in the crossing orientation when the rotor 29 is in the crowd height adjustment orientation in the locking configuration.

[0101] Advantageously, the crowd-forming machine 3 is arranged so that, when the motor 13 is in a locked configuration with the rotor 29 in the crowd amplitude adjustment orientation, then the main shaft A1, the eccentric shaft A2, and the second lever shaft A4 are substantially coplanar. This arrangement is also achieved by means of the aforementioned indexing mechanism. In other words, the connecting rod 17 is substantially positioned along the extension of a sliding direction of the connecting piece 75 relative to the base 73. This particular arrangement allows the eccentric center distance R1 to be adjusted by driving the connecting rod 17.

[0102] By "substantially coplanar" it is permissible that the axes Al, A2 and A4 are not perfectly coplanar. With respect to a perfectly coplanar orientation between a first plane defined by the axes Al and A2 and a second plane defined by the axes A2 and A4, a tolerance of a few degrees is permitted for an angle that the first plane would form with respect to the second plane.

[0103] The first lever axis A3 and the second lever axis A4 are connected by a lever arm line D34 perpendicular to the second lever axis A4. The eccentric axis A2 and the second lever axis A4 are connected by a connecting rod line D24 perpendicular to the second lever axis A4. The connecting rod-lever angle BL is the angle between the lever arm line D34 and the connecting rod line D24. Advantageously, the connecting rod-lever angle α is 97 degrees, plus or minus 2 degrees, when the leading lever 19 is in the crossover orientation. Thus, the asymmetry of the stroke is minimized, and the forces in the connecting rod are optimized.

[0104] The aforementioned crowd formation set 5 comprises one to sixteen groups of crowd training machines 9, each group consisting of several crowd training machines 9, preferably from two to sixteen crowd training machines 9.

[0105] In the present example, the frame 7 is provided with a group G1 of four crowd forming machines 9 belonging to part 7A and one crowd forming machine 9 belonging to part 7B, a group G2 of three crowd forming machines 9 belonging to part 7A and one crowd forming machine 9 belonging to part 7B, a group G3 of two crowd forming machines 9 belonging to part 7B, and five crowd forming machines 9 which do not belong to any group.

[0106] The attack lever 19 can be of several types. Advantageously, crowd-forming machines 9 of the same group have the same type of attack lever 19. Attack levers 19 of the same type are preferably identical levers 19, or at least have similar dimensions. By way of example, Figures 1 and 12 show the lever 19 of the crowd-forming machines 9 of group G1, Figures 2 and 10 show the lever 19 of the crowd-forming machines 9 of group G3, [Fig. 13] shows the lever 19 of a crowd-forming machine 9 of group G2, and [Fig. 14] shows the attack lever 19 of a crowd-forming machine not belonging to any group. The lever arm distance d34 of a crowd forming machine 9 is defined as the distance between the first lever axis A3 and the second lever axis A4 of said crowd forming machine 9, measured along the lever arm line D34.For each group, the lever arm distance d34 of each machine 9 in the group is equal to the lever arm distance d34 of each other machine 9 in said group, such that these levers are of the same type. Within a given group, when the machines 9 in the group are in a locked configuration with the rotor 29 in one of the reference orientations, then the principal axes A1, the eccentric axes A2, and the respective second lever axes A4 of the crowd-forming machines 9 in said group are advantageously coplanar. Thus, for a given type of drive lever 19, the rotors 29 of each of the machines 9 in the same group are in the same angular position when the rotary electric motors 13 are in a locked configuration.

[0107] Providing the indexing means, namely the indexing pin 89, makes it easy to install the motor 13 on the frame 7, ensuring that the axes A1, A2, and A4 are coplanar. Indeed, the indexing means 89 ensures that the orientation of the frame 21, and therefore of the stator 23, is correct, given that the locking system is partially mounted on the stator 23, namely the locking pin 79. With the stator 23 and the locking system correctly oriented by the indexing means, the rotor 29 is itself correctly oriented when the machine 3 is in the configuration of The indexing means ensures the aforementioned coplanarity. It also ensures that the rotor 29 and stator 23 are optimally positioned for the development of the motor 13's power during weaving, considering that the accelerations and decelerations of the motor 13 occur at known angles that are always the same and correspond, for example, to the extreme positions B3 and H3 of the actuated frame 3. The indexing means also ensures that the position sensor 91 is correctly positioned to maximize detection accuracy at these specific angles.

[0108] Thanks to these arrangements, the motor is able to stop very precisely at these particular positions, to accelerate efficiently from these particular positions, and the detection that these particular positions have been reached is very precise. Advantageously, the permanent magnets 57 and the winding teeth 33 are indexed with respect to these particular positions, in order to provide maximum efficiency.

[0109] During crowd height adjustment, the adjustment system is put into the adjustment configuration by inserting the locking pin 79 into the second notch 82. This immobilizes the rotor 29 in its crowd height adjustment orientation. Thanks to the indexing by the indexing pin 89, this orientation of the rotor 29 corresponds to the crossing position of the drive lever 19, and therefore to the reference position P3 of the beam frame 3. Then, the drive rod 17 is put into the configuration for adjusting the center distance of the drive rod R2. By manually moving the beam frame, the length of the drive rod 17 is then changed, which is equivalent to changing the crowd height. Once the adjustment is made, the drive rod 17 is again put into the locking configuration for the center distance of the drive rod R2.Finally, the locking system is returned to the release configuration by removing the locking pin 79 from the second notch 82, so that the rotary electric motor 13 can rotate again.

[0110] When adjusting the crowd amplitude, the adjustment system is put into the adjustment configuration by inserting the locking pin 79 into the first notch 81. Thus, the rotor 29 is immobilized in its crowd amplitude adjustment orientation. Thanks to the indexing by the indexing pin 89, this orientation of the rotor 29, located at 90 degrees with respect to the crowd height adjustment orientation, corresponds to the high frame position or the low frame position of the attack lever 19, therefore to the high position H3 or the low position B3 of the rail frame 3. Then, the adjustment system is put into the adjustment position by unscrewing the adjustment screw 77 with the help of the adjustment tool 88. By manually moving the rail frame 3 or with the help of a dedicated actuator, not shown, the connecting piece 75 is then slid relative to the base 73, which amounts to changing the eccentric distance RI, and therefore the crowd amplitude.Once the adjustment has been made, the adjustment system is reset. locked position by screwing the adjusting screw 77 using the adjusting tool 88. Finally, the locking system is returned to the release configuration by removing the locking pin 79 from the first notch 81, so that the rotary electric motor 13 can rotate again.

[0111] Figure 15 relates to a loom 101 according to a second embodiment of the invention. This loom 101 is identical to the loom 1 of Figures 1 to 14 except for the differences mentioned below. The features of the loom 101 that are identical or that function in the same way as those of the loom 1 bear the same reference numeral. The modified features bear a reference numeral augmented by 100. The loom 101 differs from the loom 1 in that it has only four sheaf-forming machines 9 instead of sixteen. The loom 101 includes a frame 107, which replaces the frame 7, comprising only four slots 11, each receiving one of the four machines 9.

[0112] A group G101 of two crowd-forming machines 9 and two other crowd-forming machines 9 that do not belong to any group are envisaged here.

[0113] Alternatively, the loom is provided to include from two to thirty swarm-forming machines.

[0114] Figures 16 to 18 relate to a loom 201 according to a third embodiment of the invention. This loom 201 is identical to the loom 1 of Figures 1 to 14 except for the differences mentioned below. The features of the loom 201 that are identical or that function in the same way as those of the loom 1 bear the same reference numeral. The modified features bear a reference numeral augmented by 200. The loom 201 differs from the loom 1 of the first embodiment in that the connecting piece 275 no longer slides relative to the base 273, but these two pieces pivot relative to each other about a crank axis A5, parallel to the main axis AL

[0115] As clearly seen in [Fig. 18], the connecting piece 275 includes a through hole defining a first internal circular surface S273, centered on the crank axis A5, complementary to the base 273, and a second internal surface S278, centered on the crank axis A5 and complementary to the clamping nut 278. The first internal surface S273 and the second internal surface S278 form a pivot joint between, on the one hand, the connecting piece 275, and on the other hand, the base 273 and the clamping nut 278 which are fixed relative to each other around the axis A5.

[0116] The crankpin 271, being fixed on the connecting piece 275 and being eccentric with respect to the axis Al, defines a center distance of eccentric RI which varies according to the angular position of the connecting piece 275 with respect to the base 273.

[0117] Rotation of the connecting piece 275 relative to the base 273 is permitted when the The adjustment system is in the adjustment configuration, meaning that nut 278 is loosened by loosening screw 77, so that the center distance of the eccentric RI can be changed. The rotation of the connecting piece 273 relative to the base 275 is blocked when the adjustment system is in the locked configuration by tightening nut 278 with screw 77, thus fixing the center distance of the eccentric RI.

[0118] Figures 19 and 20 relate to a loom 301 according to a fourth embodiment of the invention. This loom 301 is identical to the loom 201 of Figures 16 to 18 except for the differences mentioned below. The features of the loom 301 that are identical or that function in the same way as those of the loom 201 bear the same reference numeral. The modified features bear a reference numeral increased by 100. The loom 309 differs from the loom 209 of the third embodiment in that the clamping screw 377 is eccentric with respect to the axis A1, being centered on the axis A5. The machine 209 also differs from the machine 309 in the shape of the clamping nut 378, which has a circular cross-section and is centered on the axis A5. As a result, the clamping screw 377 is coaxial with the second internal surface S278.

[0119] Figure [Fig. 21] relates to a loom 401 according to a fifth embodiment of the invention. This loom 401 is identical to loom 1 of Figures 1 to 14 except for the differences mentioned below. The features of loom 401 that are identical or that function in the same way as those of loom 1 bear the same reference numeral. Modified features bear a reference numeral augmented by 400.

[0120] In place of the crank 15, the loom 401 includes a crank 415, which performs the same function. The crank 415 includes a base 473, a connecting piece 475, and a crankpin 471.

[0121] The base 473 is fixed to the rotor shaft 51, to be driven in rotation by the rotor 29 around the axis Al relative to the stator 23. In the present example, the base 473 forms a radial plate, without the rails provided for the base 73.

[0122] The connecting piece 475 is mounted on the base 473. In this embodiment, the connecting piece 475 is a through axial sliding flange that is able to slide relative to the base 473, radially relative to the axis AL. The connecting piece 475 is in sliding support against the plate of the base 473. Unlike the connecting piece 75, the connecting piece 475 can pivot around the axis Al relative to the base 475, since the connecting piece 475 is not constrained by rails as is the connecting piece 75.

[0123] The crankpin 471 and the connecting piece 475 are fixedly joined to each other. Like the crankpin 71, the crankpin 471 defines the eccentric axis A2, parallel to the axis main Al and distant from the main axis Al by the eccentric center distance RI. As for the crankpin 71, the axis Al of the crankpin 471 is fixed relative to the connecting part 471.

[0124] The crank 415 is configured so that the pivoting of the connecting piece 475 about the axis Al relative to the base 473 is constrained by the radial sliding of the connecting piece 475 relative to the base 473. To achieve this, unlike the base 73, the base 473 advantageously includes a cam groove 492, and the connecting piece 475 advantageously includes a follower finger 493, which cooperates with the cam groove 492 by moving along the cam groove 492, thus constraining the radial translation of the connecting piece 475 to be accompanied by a rotation of the connecting piece. For this purpose, the cam groove 492 follows a spiral path around the main axis Al.

[0125] In practice, the cam groove 492 is preferably formed by a spiral groove, hollowed out on the surface of the base 473. The follower finger 493 is, for its part, preferably centered on the eccentric axis A2.

[0126] The movement of the follower finger 493 in the cam groove 492 guides the connecting piece 475 through a displacement relative to the base 473, which notably includes a radial translation relative to the base 473, allowing the center distance of the eccentric RL to be modified.

[0127] The connecting piece 475 therefore belongs to an adjustment system allowing the center distance of the eccentric RI to be modified, and, consequently, the amplitude of the swarm, in a manner similar to that described above for the loom 1.

[0128] The adjustment system of the loom 401 includes, as in the loom 1, an adjusting screw 477, visible in [Fig. 21], suitable for selectively allowing movement of the connecting piece 475 relative to the base 473 and for locking the base 473 to the connecting piece 475. When the adjustment system is in an adjustment configuration, the screw 477 is loosened and movement is permitted. Conversely, when the adjustment system is in a locking configuration, the adjusting screw 477 is tightened and movement is impossible. Thus, the center distance of the eccentric RI can be adjusted if and only if the adjustment system is in the adjustment configuration, and is fixed if the adjustment system is in the locking configuration. During weaving, the adjustment system is in the locking configuration.

[0129] As shown in Figure 21, the adjusting screw 477 is advantageously provided to be coaxial with the axis Al and to have a body that passes through an oblong opening 476 which passes through the connecting piece 475. In the oblong opening 476, a clamping nut 478 is provided, into which the screw 477 is screwed. The screw 477 further has a head 480, through which the screw 477 can be rotated. The base 473 and the connecting piece 475 are axially interposed between the nut 478 and the head 480, so that tightening the screw 477 in the nut 478 clamps the connecting piece 475 against the base 473 to prevent the connecting piece 475 from moving. The head 480 is preferably accessible from the rear of the motor 3 so that it can be operated.

[0130] For this embodiment, the nut 478 guides the pivoting of the connecting piece 475 around the axis Al. The connecting piece 475 is therefore guided in its movement both by the nut, around the axis Al fixed relative to the base 473, and by the follower finger 493, around the axis A2 fixed relative to the connecting piece 475.

[0131] In what follows, the invention is explained with reference to an experimental example, which is in no way limiting.

[0132] The experiment consists of evaluating examples of rotary electric motors according to the invention, namely motors B and C, against a comparative electric motor A.

[0133] The comparative motor A is a commercially available motor, the structure of which is described in EP1953276A1 and which has the characteristics shown in Table 1 below. The characteristics of motor A were either observed directly on motor A (diameters and lengths were measured) or provided by the manufacturer (rated torque). The moment of inertia was estimated by numerical modeling of the rotor using computer-aided design software.

[0134] The motor B according to the invention is an experimental motor that has not been manufactured, but only modeled numerically. The motor B has a structure conforming to that of the motor 9 of the first embodiment of Figures 1 to 15 described above. The motor B has the characteristics indicated in Table 1 below. The characteristics were all obtained by numerical modeling (dimensions, moment of inertia) or estimated by calculation (nominal torque).

[0135] The motor C according to the invention is an experimental motor that has been tested on a test bench. The motor C has a structure conforming to that of the motor 9 of the first embodiment of Figures 1 to 15 described above. The motor C has the characteristics indicated in Table 1 below.

[0136] In the table below, the ratio R corresponds to the ratio between the external diameter of the stator and the length of the cylindrical part of the rotor. The ratio Kt corresponds to the motor torque constant, expressed as a torque value obtained per unit current I delivered by the power circuit. The torque constant is calculated at a comparable motor speed for the different motors tested, here at 750 revolutions per minute, which corresponds to a working speed of 1500 strokes per minute.

[0137] [Tables 1] Motor A Motor B Motor C Crank drive With gearbox Without gearbox Without gearbox Presence of a rotor shaft surrounded by a cylindrical rotor section carrying the permanent magnets NO YES YES Rotor moment of inertia without crank and, if a gearbox is present, without gearbox (kg.cm2) 45 95 78 Stator external diameter 128 200 180 Length of cylindrical section 165 50 60 Ratio R 0.8 4 3 Rotor diameter 80 156 117 Rated torque, at the rotor (Nm) 60 65 65 Ratio Kt (Nm / A) at 750 rpm 3 6 7 Number of magnet sets 2 2 2 Number of permanent magnets per set 12 40 30 Number of slots 15 48 36

[0138] Motor C develops a torque constant Kt = C / 1 = 65 Nm / 9.2 A = 7 Nm / A, whereas motors A and B develop known torque constants Kt of 3 Nm / A and 6 Nm / A respectively at a speed of 750 rpm. Achieving such a high torque constant corresponds to the use of a high-efficiency motor.

[0139] Motor A has axially elongated proportions, with a small stator outer diameter and a particularly long cylindrical section. Motor A is therefore particularly bulky lengthwise. Motor A exhibits a particularly low moment of inertia. However, the rated rotor torque is low for the application, necessitating the use of a gearbox. The small diameter limits the motor's ability to deliver high torque at low current. The gearbox significantly increases the moment of inertia of motor A and reduces its efficiency. mechanical and increases the overall length, already large due to the engine itself.

[0140] Motor B is relatively short and radially larger, with a large stator outer diameter and a relatively short cylindrical section. Motor B's radial bulk imposes constraints on the design of the crowd-forming assembly, requiring the arrangement of several motors side-by-side. The large stator and rotor outer diameters allow for a high number of permanent magnets around the cylindrical section and a high number of stator slots, resulting in a high number of windings. Motor B thus provides sufficient rated torque for the application, eliminating the need for a gearbox. Thanks to the rotor shaft being enclosed within the cylindrical section, motor B exhibits a moderately high moment of inertia, despite its large rotor diameter.The moment of inertia of motor B is suitable for the application, especially since it is not necessary to provide a gearbox.

[0141] The motor C has balanced proportions, which facilitates the design of the crowd-forming assembly, which is not too bulky and allows for easy placement of several motors side-by-side. The relatively large external diameter of the stator and rotor allows for a relatively high number of permanent magnets around the cylindrical section and a relatively high number of slots in the stator, with a relatively high number of windings. The motor B thus provides sufficient rated torque for the application, eliminating the need for a gearbox. Surprisingly, the moment of inertia is particularly low, which is highly advantageous for the application, especially since no gearbox is required.

Claims

Demands

1. Crowd-forming machine (9), for actuating a heddle frame (3) of a loom (1; 101; 201; 301; 401) along a stroke (C3) in alternating translation about a frame axis, the crowd-forming machine (9) comprising: • a rotary electric motor (13), comprising: • a frame (21), centered on a main axis (Al) of the rotary electric motor and configured to be integral with a machine frame (7) of the loom (1; 101; 201; 301; 401), • a stator (23), integral with the frame (21), • a rotor (29), disposed in the stator (23) and comprising a cylindrical part (53), centered on the main axis (Al) and comprising an external peripheral wall (55), • a first bearing (31 A), arranged in a first plane (PI), perpendicular to the main axis (Al), on a front side of the rotary electric motor (13), and • a second bearing (31B), arranged in a second plane (P2), perpendicular to the main axis (Al), on a rear side of the rotary electric motor (13), the first bearing (31 A) and the second bearing (31B) guiding a rotation of the rotor (29) relative to the stator (23) around the main axis (Al); • a crank (15; 415), fixed to the rotor (29) and comprising a crankpin (71; 271; 371; 471) defining an eccentric axis (A2), parallel to the main axis (Al) and distant from the main axis (Al) by an eccentric center distance (RD; • a drive lever (19), which is configured to pivot about a first lever axis (A3) relative to the machine frame (7), to actuate the rail frame (3), the first lever axis (A3) being fixed relative to, and parallel to, the main axis (Al); and • a connecting rod (17), which includes: • a first end, attached to the crankpin (71; 271; 371; 471) by pivoting around the eccentric axis (A2) relative to the crankpin (71; 271; 371; 471), and • a second end, attached to the attack lever (19) by pivoting around a second lever axis (A4) relative to the attack lever (19), the second lever axis (A4) being parallel to the first lever axis (A3); characterized in that: • the stator (23) comprises: • winding laminations (33), surrounding the main axis (Al) and extending radially between an external stator diameter (D23e) and an internal stator diameter (D23i) centered on the main axis (Al), the winding laminations (33) forming winding teeth (35) distributed around the main axis (Al), directed towards the main axis (Al) and defining between them stator slots (37), which extend parallel to the main axis (Al), and • electrical windings (39), each electrical winding (39) being wound around several of the winding teeth (35) as received in the stator slots (37); and • the rotor (29) comprises: • a rotor shaft (51), centered on the main axis (Al), surrounded by the cylindrical part (53) of the rotor (29) and being integral with the cylindrical part (53) of the rotor (29) and the crank (15; 415), and • permanent magnets (57), arranged on the outer peripheral wall (55) of the cylindrical part (53) and distributed around the main axis (Al), each permanent magnet (57) comprising a respective external surface (S57), the external surfaces (S57) being opposite the winding teeth (35) and inscribed on a rotor circle (60), centered on the main axis (Al) and defining a diameter of rotor (D29); and • a ratio of the external diameter of stator (D23e) to a length (L53) of the cylindrical part (53), measured parallel to the main axis (Al) without exceeding the permanent magnets (57), is between 2.0 and 4.0, preferably between 2.5 and 3.5, preferably still between 2.8 and 3.

2.

2. Crowd forming machine (9) according to claim 1, wherein: • the rotor (29) comprises a first set of permanent magnets (59A), comprising 12 to 40 permanent magnets (57), preferably 30 to 35 permanent magnets (57), preferably 30 permanent magnets (57), distributed equally around the main axis (Al); and • the stator (23) comprises 24 to 48 slots (37), preferably 32 to 40 slots (37), preferably a further 36 slots (37), distributed equally around the main axis (Al).

3. Crowd forming machine (1) according to claim 2, wherein: • the rotor (29) comprises a second set of permanent magnets (59B), offset from the first set of permanent magnets (59A) along the main axis (Al), each permanent magnet (57) of the second set of permanent magnets (59B) being adjacent to one of the permanent magnets (57) of the first set of permanent magnets (59A), along the main axis (Al); and • each permanent magnet (57) of the first set of permanent magnets (59A) is angularly offset, around the main axis (Al), from the adjacent permanent magnet (57) of the second set of permanent magnets (59B), by an angle of 0.5 to 5 degrees, preferably 1 to 2 degrees, preferably a further 1 degree.

4. Crowd-forming machine (9) according to any one of the claims previous indications, in which the external diameter of stator (D23e) measures between 160 and 200 mm, preferably between 170 and 190 mm, preferably again between 175 and 185 mm.

5. Crowd forming machine (9) according to any one of the preceding claims, wherein the rotor (29) is designed so that a moment of inertia of the rotor (29) is less than 100 kg.cm2, preferably less than 90 kg.cm2, preferably less than 80 kg.cm2.

6. Crowd forming machine (9) according to any one of the preceding claims, wherein the crowd forming machine (9) comprises an electrical cabinet, including an electrical power circuit configured to electrically supply the rotary electric motor (13) and wherein the rotary electric motor (13) develops a rated torque of between 30 and 100 Nm, preferably between 50 and 70 Nm, preferably between 60 and 70 Nm.

7. Crowd forming machine (9) according to claim 6, wherein the electrical power circuit delivers a supply current of intensity I to the rotary electric motor (13) which develops a torque per unit current I of between 6.5 and 8 Nm / A, preferably between 7 and 7.5 Nm / A, when the rotational speed of the rotor (29) is maintained at 750 revolutions per minute.

8. A crowd-forming machine (9) according to any one of the preceding claims, wherein: • each winding tooth (35) comprises: • a tooth head (41), delimited by the internal stator diameter (D23i), • a tooth root (43), delimited by the external stator diameter (D23e), and • a tooth body (45), which extends perpendicularly to the main axis (Al), which connects the tooth head (41) to the tooth root (43) and which has a generally rectangular shape in projection in the first plane (PI), each tooth body (45) having a length (L45), measured radially with respect to the main axis (Al), of between 19 and 25 mm, preferably between 20 and 23 mm, preferably between 21 and 23 mm; and • each electrical winding (39) forms three layers of wire around the winding tooth (35) around which said electrical winding (39) is wound.

9. Crowd forming machine (9) according to any one of the preceding claims, wherein the rotor shaft (51) comprises a single piece which extends so as to connect the first plane (PI) and the second plane (P2).

10. Crowd forming machine (9), according to any one of the preceding claims, in which: • the rotor (29) comprises a disc (61), extending perpendicularly to the main axis (Al), comprising recesses (65) distributed around the main axis (Al) and a central bore (63), through which the disc (61) is fitted onto the rotor shaft (51), • the cylindrical part (53) is integral with the rotor shaft (51) and the disc (61) and surrounds the disc (61).

11. Crowd forming machine (9) according to claim 10, wherein the rotor shaft (51) comprises: • a centering wall (67), cooperating with the central bore (63) to center the disc (61) on the rotor shaft (51); and • a collar (69), extending radially to the main axis (Al) and being arranged between the first plane (PI) and the second plane (P2), the disc (61) being fixed to the collar (69) by means of at least one screw parallel to the main axis (Al).

12. A crowd-forming machine (9) according to any one of the preceding claims, wherein: • the crank (15; 415) comprises: • a base (73; 273; 373; 473), integral with the rotor shaft (51), and • a connecting piece (75; 275; 375; 475), integral with the crankpin (71; 271; 371; 471) and mounted on the base (73; 273; 373; 473); and • the crowd-forming machine (9) comprises a system adjustment, which includes locking means, configured for: • allow adjustment of the eccentric center distance (RI), by a relative displacement between the base (73; 273; 373; 473) and the connecting piece (75; 275; 375; 475), in an adjustment system configuration, and • secure the base (73; 273; 373; 473) with the connecting piece (75; 275; 375; 475), in a locked configuration of the adjustment system.

13.

14.

15. Crowd-forming machine (9), according to claim 12, wherein: the base (473) includes a cam groove (492), defining a spiral around the main axis (Al); and the connecting piece (475) includes a follower finger (493) running along the cam groove (492) to guide the connecting piece (475) relative to the base (473) when the adjustment system is in adjustment configuration and thus vary the eccentric center distance (RI). Crowd forming machine (9), according to claim 12, wherein the connecting piece (275; 375) and the base (273; 373) are pivotable relative to each other about a crank axis (A5) parallel to the main axis (Al), when the adjustment system is in adjustment configuration. Crowd-forming machine (9), according to any one of the preceding claims, wherein: A rotational stroke without a change of direction of the rotor (29) around the main axis (Al) corresponds to an oscillation stroke of the drive lever (19) around the first lever axis (A3), the oscillation stroke including a high frame orientation, a crossover orientation and a low frame orientation of the drive lever, the crossover orientation being median between the high frame orientation and the low frame orientation; and • The rotary electric motor (13) includes locking means, which allow: • a locking configuration, in which the locking means immobilize the rotor (29) relative to the stator (23) around the main axis (Al), selectively according to several predetermined reference orientations, including: • a crowd amplitude adjustment orientation, in which the attack lever (19) is in the high frame orientation or in the low frame orientation, and • a crowd height adjustment orientation, at 90 degrees to the crowd amplitude adjustment orientation, and in which the attack lever (19) is in the crossover orientation; and • a release configuration, in which the locking means permit the rotation of the rotor (29) around the main axis (Al) relative to the stator (23).

16. Crowd-forming machine (9), according to claim 15, wherein the blocking means comprise: • a locking pin (79), movable relative to the stator (23) in a direction parallel to the main axis (Al); • a first notch (81), belonging to the rotor (29) and cooperating with the locking pin (79) in the locking configuration, to immobilize the rotor (29) in the crowd amplitude adjustment orientation; and • a second notch (82), belonging to the rotor (29) and cooperating with the locking pin (79) in the locking configuration, to immobilize the rotor (29) in the crowd height adjustment orientation.

17. Crowd-forming machine (9) according to any one of claims 15 or 16, wherein the crowd-forming machine (9) is arranged so that, when the rotary electric motor (13) is in lock configuration with the rotor (29) in the crowd amplitude adjustment orientation, then the main axis (A1), the eccentric axis (A2) and the second lever axis (A4) are substantially coplanar.

18. Crowd forming machine (9) according to any one of claims 15 to 17, wherein the crowd forming machine (9) comprises: • a front flange (25), integral with the frame (21) and comprising a circular flange (26), configured to cooperate with the machine frame (7), so that the frame (21) can be positioned on the machine frame (7); • means for fixing the rotary electric motor (13) to the machine frame (7), for fixing the rotary electric motor (13) to the machine frame (7) when the circular flange (26) cooperates with the machine frame (7);and • an indexing means, which is separate from the fastening means and which requires that, when the circular flange (26) cooperates with the machine frame, the frame (21) is positioned so that: • the drive lever (19) is in the high frame orientation or in the low frame orientation when the rotor (29) is in the crowd amplitude adjustment orientation in the locking configuration, and • the drive lever (19) is in the crossing orientation when the rotor (29) is in the crowd height adjustment orientation in the locking configuration.;

19. A crowd-forming machine (9) according to any one of claims 15 to 18, wherein: • the first lever axis (A3) and the second lever axis (A4) are connected by a lever arm line (D34) perpendicular to the second lever axis (A4); • the eccentric axis (A2) and the second lever axis (A4) are connected by a connecting rod line (D24) perpendicular to the second lever axis (A4) and defining a connecting rod-lever angle (BL) with the lever arm line (D34); and • the connecting rod-lever angle (BL) is 97 degrees, plus or minus 2 degrees, when the attack lever (19) is in the crossing orientation.

20. Crowd-forming assembly (5), comprising a group (G1; G2; G3; G4) of crowd-forming machines (9) according to any one of the preceding claims and wherein: • each crowd-forming machine (9) in the group (G1; G2; G3; G4) defines a lever arm distance (d34), measured between the first lever axis (A3) and the second lever axis (A4); • the lever arm distance (d34) of each crowd-forming machine (9) in group (G1; G2; G3; G4) is equal to the lever arm distance (d34) of each other crowd-forming machine (9) in group (G1; G2; G3; G4); and • when the crowd forming machines of group (9) are in a locked configuration with the rotor (29) in one of the reference orientations, then the principal axes (Al), the eccentric axes (A2) and the respective second lever axes (A4) of the crowd forming machines (9) of group (G1; G2; G3; G4) are coplanar.

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