JP2012515851A - Driving device for detaching roller of comber machine - Google Patents

Abstract

  The present invention is a driving device that forms an intermittent motion for the detaching rollers (A1, A2) of the combing machine, wherein the detaching rollers (A1, A2) are driving means (Z1, Z2, Z3). ) Is coupled to the drive shaft (9) of the differential gear device (1), and the frame (2) rotatably supported by the differential gear device (1) is fixed. Driven through at least one drive element (20, Z) driven at a rotational speed, the differential gear unit (1) includes a second transmission stage (G2), and the second transmission The device stage (G2) is rotatable through the shaft (33, 34, 35) in the frame (2) and the sun gear (S2) that is non-rotatably attached to the output shaft (9). Formed from the supported planetary gears (U4, U5, U6) and the first gear stage (G ), And the first gear stage (G1) includes planetary gears (U1, U2, U3), and each of the planetary gears (U1, U2, U3) has a second transmission gear. It is coaxially arranged with respect to the planetary gears (U4, U5, U6) of the device stage (G2), is non-rotatably attached to the shaft (33, 34, 35), and has another sun gear (S1). The other sun gear (S1) is non-rotatably attached to a rotatably supported drive shaft (5), and the drive shaft (5) is connected to the drive unit. (4, G3) relates to those driven by non-uniform rotational movement. In order to optimize the movement curve of the detaching roller while reducing the exerted rotational moment, the drive unit is formed from a transmission stage (G3) with non-circular gears (42, 43), The transmission stage (G3) converts the uniform rotational motion of the main drive device (HA) into a non-uniform rotational motion.

Description

  The present invention relates to a driving device for generating intermittent movement of a detaching roller of a combing machine according to the superordinate concept of claim 1.

  The detaching roller performs an intermittent motion for a detaching process and a pecing process (a process of pressing a new fleece tip on the trailing end of the combed fleece and superimposing them) on the comber machine. That is, before the subsequent detaching step, the already formed fleece is returned toward the nipper device by a predetermined amount, and a new fiber group is combined with the rear end of the fleece. Special drives are required to form intermittent movements of the detaching roller (movements that periodically move in the reverse direction while moving in the forward direction). At that time, the detaching speed of the new fiber group and the detaching speed of the detaching roller are precisely adjusted to the nipper movement and the combing cylinder movement in order to obtain the desired overlapping position or qualitatively uniform fleece. It is necessary to adapt.

  In German patent application DE 16 85 575, one configuration is described in which a differential gearing is used to create the movement. There, a frame of a differential gear device (a sun gear is rotatably supported on the frame) is driven through a uniformly driven gear, and the gear is a frame coupled to the frame. Drive-coupled to the body car. At that time, the gear is fitted on the drive shaft of the combing cylinder so as not to rotate. A plurality of planetary gears are rotatably supported in the driven frame, and the planetary gears mesh with the sun gears. Uneven motion is transmitted to the differential gear unit shaft and thus to the first sun gear coupled to the differential gear shaft via an eccentric drive coupled to the link transmission. The above described uniform drive motion is superimposed on the non-uniform motion to form the desired intermittent motion for the detaching roller. Although the structure of this transmission device has been demonstrated for many years, a complicated and sturdy structure is required to accept the high acceleration force that is generated. Further, a frictional force is formed at each joint portion in the link transmission, and it is necessary to increase the required output due to the frictional force. Since higher demands are always imposed on the number of combing operations, such a structure of the transmission will eventually reach a limit in its resistance. Furthermore, the degree of freedom in the movement curve of the detaching roller is limited by the use of a known link type transmission.

  Another proposal has already been made to realize intermittent motion using another means and a transmission unit. For example, it has been proposed to drive the detaching roller directly via one or more electric motors. Such a configuration can be seen, for example, in EP-A-374723. Furthermore, in US Pat. No. 3,604,063, a variable transmission unit is known, in which a special cam transmission unit is used to obtain the desired intermittent movement.

  U.S. Pat. No. 1,818,555 discloses a configuration in which a constant rotational motion of a drive shaft is converted into intermittent motion using a differential gear device having a non-circular gear. This intermittent movement is transmitted to the detaching roller via an output shaft coupled to the sun gear and a subsequent gear stage.

  Further, in Chinese Patent Publication No. 200710022458, an apparatus is proposed which proposes the use of a differential gear device having a transmission stage with a non-circular gear, similar to the above-mentioned US Pat. No. 1,818,855. Yes. According to the only difference from US Pat. No. 1,818,555, the frame is driven via the outer frame wheel. On the other hand, in the configuration of US Pat. No. 1,818,555, the frame is driven via a central shaft.

  In the arrangements of U.S. Pat. No. 1,818,555 and Chinese Patent Publication No. 200710022458, a corresponding intermittent movement is achieved on the basis of the transmission stage with a non-circular gear used. Such a configuration is limited in terms of transmission of high output and thus high rotational moment, since two or more planetary gears cannot be used mechanically. Furthermore, the adjustment of the drive motion of the detaching roller is limited to the arrangement in the above-mentioned US Pat. No. 1,818,555.

  The object of the present invention is to improve a known configuration, while reducing the rotational moment (output) conventionally required, and at the same time increasing the degree of freedom in the configuration of the motion curve of the detaching roller. It is providing the apparatus for driving.

  That is, an optimum movement curve of the detaching roller can be obtained while reducing the load due to the rotational moment.

  In order to solve this problem, according to the present invention, the drive unit for the sun gear of the first gear stage of the differential gear device is formed from a gear stage with a non-circular gear, The transmission stage converts the uniform rotational movement of the main drive to non-uniform rotational movement. Instead of using the known linked transmission coupled with the eccentric drive, the use of the proposed transmission with a transmission stage with a non-circular gear makes the conventional proven drive structure Can be maintained. At the same time, the proposed use of the transmission stage with non-circular gears makes it possible to realize an unknown optimization with respect to the reduction of the driving load and the adaptation of the movement curve of the detaching roller. Furthermore, the drive element for the frame is formed from a drive shaft, and a gear is non-rotatably attached to the drive shaft, and the gear is a vehicle for the frame of the frame of the differential gear device. And directly or indirectly drive coupled. The expression “indirect” includes, for example, an intermediate wheel interposed between a gear mounted on a drive shaft and a frame vehicle in order to transmit a required rotation direction to the frame.

  According to another aspect, the drive shaft comprises another drive wheel, the drive wheel is drivingly coupled with the drive element of the main drive, and the drive element simultaneously comprises a non-circular gear. Drive coupled to the transmission stage. This ensures that both drive paths are synchronized, since both drive paths are received by the same drive element of the main drive without intervening separate drive elements.

  According to yet another aspect, the drive element of the main drive device is formed from a gear rotatably supported on the machine frame, the gear being connected via another means to a central drive motor (main drive). The rotation axis of the gear is coaxially extended with respect to the input shaft of the transmission stage with a non-circular gear, and another drive wheel of the drive shaft is formed as a gear The gear is drivingly coupled with the gear of the main drive. Furthermore, a mode in which the gear of the main drive is directly attached to the input shaft of the transmission stage provided with a non-circular gear is also conceivable.

  In order to obtain adjustability, in particular to adjust the detaching point of the detaching roller with respect to the nipper movement, the input shaft of the transmission stage is non-rotatably coupled with the gear of the main drive via a detachable mounting means Has been. At this time, the attachment means includes a guide, and the guide allows adjustment of the rotation angle between the input shaft and the gear of the main drive device in a state where the attachment means is loosened. Therefore, the movement cycle of the detaching roller can be displaced with respect to the nipper movement. The nipper drive is also connected to the main drive.

  Optionally, the gear is detachably attached to the drive shaft via the attachment means, and the angular position between the drive shaft and the gear is adjustable via the means, so that the detaching roller Movement cycle displacement is obtained.

  Another aspect may optionally be used to adjust the movement cycle of the detaching roller, in which the frame wheel can be attached to and detached from the frame of the differential gear unit via means. It is attached and can be adjusted at an angular position with respect to the frame body via the adjusting means when viewed in the circumferential direction of the frame body.

  Another advantage of the present invention can be seen from the following description of the mode for carrying out the invention.

1 is a schematic cross-sectional view of a drive device formed in accordance with the present invention. It is a side view which shows the power transmission apparatus provided with the non-circular gearwheel seen in the X direction of FIG. FIG. 2 is an enlarged partial view of FIG. 1 showing one embodiment for fixing and adjusting a vehicle for a frame of a differential gear device. It is a figure which shows the drive gearwheel 18 seen in the A direction of FIG. It is a figure which shows the differential gear apparatus seen in the Y direction of FIG. It is a diagram which shows curve progress of the detaching roller motion during combing operation | movement. It is a diagram which shows the magnitude | size of the rotational moment of the drive device for detaching rollers during combing operation | movement.

  FIG. 1 shows a differential gear device 1 having a rotating frame (Steg) 2. The frame 2 is rotatably supported on the bearing 6 on one side. The bearing 6 is supported by a central shaft 5, and the shaft 5 is rotatably supported by the machine frame MS via the bearings 10 and 11 in the present embodiment. On the other side, the frame body 2 is rotatably supported by the bearing 7. The bearing 7 is supported by a hollow shaft 9, and the hollow shaft 9 is supported by the above-described shaft 5 via a bearing 8 schematically shown. Of course, many different bearing configurations are also conceivable in this regard. The rotating frame 2 includes a frame car 3, and the frame car 3 is firmly coupled to the frame. Another embodiment is shown in the enlarged view of FIG. 3, in which the car 3 for the frame is provided with a protruding basic body 12. Long vertical slits 14 are provided on both sides of a portion of the basic body 12 that protrudes from the frame vehicle, and the longitudinally extending portions of the slits 14 extend in the circumferential direction of the frame 2. One or more screws 13 protrude through the slit 14, and the screws 13 are attached to the threaded holes 15 of the frame 2. The frame wheel 3 is fixed to the frame 2 by tightening the screws 13. When the screws 13 (a plurality of screws 13 are distributed and provided along the circumference of the frame body 2) are loosened, the frame wheel 3 rotates in the circumferential direction by a predetermined value with respect to the frame body 2. This can change the angular position relative to the frame. This forms an adjustment for the attitude of the detaching position of the detaching roller relative to the nipper device (not shown). This will be described in detail later.

  A frame wheel 3 and a gear Z are engaged with each other via an intermediate wheel 37 and are coupled to each other. As schematically shown, the intermediate wheel 37 is supported by a machine frame so as to be rotatable at a bearing L via a shaft 36. The gear Z is attached to the drive shaft 20 supported by the machine frame via the support location L so as not to rotate (being non-rotatable with respect to the drive shaft 20, that is, rotating together). A further gear 16 is mounted on the drive shaft 20 at a distance from the gear Z, and the other gear 16 is drivingly coupled to the gear 18 of the main drive HA. At this time, the gear 18 supported on the machine frame at the support portion Lx via the shaft 48 is driven by the gear 19, and the gear 19 is drivingly coupled to the central transmission unit G via the shaft 38. The drive unit G is driven from the motor M via a drive coupling 40 shown schematically. Of course, such a configuration is just one of many aspects of the drive. For example, it is also conceivable to provide a belt type driving device instead of the illustrated gear pair.

  As an alternative to the adjustment shown in FIG. 3, an adjustment device as shown in FIG. 1 may be provided. In this case, the gear Z is coupled to the hollow shaft 22, and the hollow shaft 22 includes a flange 23 and extends coaxially with respect to the drive shaft 20. The flange 25 faces the flange 23, and the flange 25 similarly extends coaxially with the shaft 20, and is connected to the shaft 20 via a spring 28 (the spring 28 projects into the groove 29 of the shaft 20). Non-rotatably connected. In order to prevent the flange 25 from sliding in the axial direction, the flange is fixed by means of screws 27 shown schematically. Both flanges 23, 25 are fixed to one another via a screw connection 24 shown schematically. Therefore, the gear Z is fixed to the shaft 20 so as not to rotate. As can be seen from FIG. 5 (viewed in the Y direction in FIG. 1), a long hole 30 is provided in the vicinity of the screw coupling portion 24, and the screw coupling portion 24 is connected via the long hole 30. When loosened, the angular position between the gear Z and the shaft 20 can be changed. With such a device, the displacement of the detaching roller with respect to the position of the nipper device at the time of detaching is realized.

  The detaching rollers A1 and A2 are driven on the one hand via a gear Z that is uniformly driven, and the gear Z rotates the frame wheel 3 of the frame 2 via an intermediate wheel 37. . By this rotation, the bearing housing portions L1 to L6 coupled to the frame body 2 are also moved, and the planetary gears U1 to U6 can rotate to the bearing housing portions L1 to L6 via the shafts 33, 34, and 35. It is supported. Here, the planetary gears U1 to U3 (see FIG. 1) are drivingly coupled to the sun gear S1, and the sun gear S1 is attached to the shaft 5 so as not to rotate.

  The sun gear S2 of the second gear stage G2 of the differential gear device 1 is firmly coupled to a hollow shaft 9 that is rotatably supported, and the hollow shaft 9 is interposed via the bearing 8 as described above. The shaft 5 is rotatably supported. The sun gear S2 and the planetary gears U4 to U6 distributed along the circumference and supported by the frame body 2 are drivingly coupled. The planetary gears U4 to U6 are coupled to the planetary gears U1 to U3 via shafts 33, 34, and 35.

  A gear Z1 is fixed to the opposite end of the hollow shaft 9, and the gear Z1 is drivingly coupled to the gears Z2 and Z3. Gears Z2, Z3 are coupled to detaching rollers A1, A2 via shafts W1, W2. The detaching rollers A1, A2 or the shafts W1, W2 are supported on the machine frame MS via bearings L schematically shown.

  A sun gear S1 is attached to the shaft 5, and the shaft 5 is an output shaft of the transmission stage G3 provided with non-circular gears 42 and 43 provided at the front of the differential gear mechanism 1 at the same time, The gears 42 and 43 mesh with each other inside the housing 4. The non-circular gear 43 is non-rotatably attached to the shaft 5. The non-circular gear 42 is non-rotatably attached to the shaft 44, and a flange 50 is attached to another end of the shaft 44, and the shaft 44 uses a screw 51 via the flange 50. It is firmly connected to the gear 18 of the main drive device HA. As schematically shown, the shaft 44 is rotatably supported by the machine frame MS via a bearing 45. Of course, you may provide another support location. Furthermore, bearing points for the shaft 5 and the shaft 44 may be provided inside the housing 4, which is schematically shown in FIG.

  The screw 51 protrudes through a long hole 53 (see FIG. 4 as viewed in the direction A of FIG. 1) of the flange 50 and is accommodated in a threaded hole 55 provided in the gear 18. The gear 18 is rotatably supported on the machine frame at the bearing Lx via the shaft 48. At this time, the rotational axis of the shaft 44 and the shaft 48 extend in parallel to each other. As described above, the gear 18 is uniformly driven through the gear 19, and the gear 19 is coupled to the transmission device G through the shaft 38. The transmission device G is uniformly driven by the drive motor M. Driven at the number of revolutions.

  Instead of the adjusting device shown in FIGS. 3 and 5, an adjusting device for adjusting the motion curve of the detaching roller as shown in FIG. 4 may be provided. When the screw 51 is loosened, the flange 50 can be rotated at a predetermined rotation angle along the long hole 53, and then can be fixed again by tightening the screw 51 in a new posture. A mark (not shown) may be provided between the flange and the gear wheel 18 via which the adjustment can be defined accordingly. By such adjustment, the motion curve of the working cylinder can be displaced with respect to the motion curve of the nipper device driven by the main drive device HA as well. FIG. 6 exemplifies a motion curve of such a work roller, and the motion curve of the work roller shows a change in combing operation (tuft combing and drawing) KS. In the first range, the work roller performs a backward movement, whereby the fleece already formed is conveyed backward toward the nipper device. A reverse motion is then performed and the work roller moves forward to perform the work process. A value exceeding the zero line represents an actual fleece conveyance value.

  Such adjustment particularly changes the detaching time of the work rollers A1 and A2. The uniform rotational movement received from the gear 18 via the shaft 44 via the transmission stage G3 with non-circular gears 42, 43 is transmitted to the non-circular gear 42. This uniform rotational movement is converted into a non-uniform rotational movement in the transmission stage G3 in cooperation with the engaging non-circular gear 43, and the non-uniform rotational movement is transmitted via the shaft 5. Is transmitted to the sun gear S1. At the same time, a uniform rotational movement is transmitted from the gear 18 via the gear 16 to the shaft 20 and thus to the gear Z. The gear Z transmits a uniform rotational movement to the frame body 2 of the differential gear device 1 via the intermediate wheel 37 and the frame wheel 3 so that the planetary gears U1 to U3 are sun gears. Exercise around S1. As a result, a non-uniform rotational movement of the planetary gears U1 to U3 is formed, and this non-uniform rotational movement is caused by the planetary gears U1 to U3 and the planetary gears U4 coupled to the planetary gears U1 to U3. To U6. The planetary gears U4 to U6 transmit the uneven movement (intermittent movement) thus formed to the sun gear S2, and the sun gear S2 transmits this uneven movement to the shaft 9 and the gear Z1. Is transmitted to the gears Z2 and Z3 of the detaching roller.

  With the appropriate configuration of the non-circular gears 42, 43 of the transmission stage G3, it is possible to optimize the course of the movement curve of the detaching roller (FIG. 6), so that the load on the drive or the rotational moment exerted is: As shown in the diagram of FIG. Therein, the change in the rotational moment M (Nm) is shown for a combing operation divided into 40 indices. The curve shown by the solid line shows the course of the rotational moment that exists in the conventional drive structure. The curve indicated by the broken line shows the course of the rotational moment obtained using a drive unit with a non-circular gear according to the invention. As a result, the load due to the rotational moment can be significantly reduced on both the positive side and the negative side. As a result, the load on the driving element becomes small, and the number of combing operations can be increased without overloading the mechanical element.

  By using such a transmission stage with a non-circular gear for driving the first sun gear of the differential transmission non-uniformly, based on the free structure of this transmission stage, In order to obtain the aforementioned advantages, an optimal drive reference can be realized.

Claims (8)

A drive device that forms intermittent movements for the detaching rollers (A1, A2) of the combing machine,
The detaching rollers (A1, A2) are coupled to the drive shaft (9) of the differential gear device (1) via the drive means (Z1, Z2, Z3), and the differential gear device (1 ), Which is rotatably supported, is driven via at least one drive element (20, Z) driven at a constant rotational speed, and the differential gear device (1) The second transmission stage (G2) includes a sun gear (S2) that is non-rotatably attached to the output shaft (9), and the frame ( 2) is formed of planetary gears (U4, U5, U6) rotatably supported through shafts (33, 34, 35), and is provided with a first transmission device stage (G1). The first gear stage (G1) includes planetary gears (U1, U2, U3), and the planetary gears The cars (U1, U2, U3) are arranged coaxially with the planetary gears (U4, U5, U6) of the second transmission gear stage (G2), respectively, and are connected to the shafts (33, 34, 35). The other sun gear (S1) is non-rotatably attached and is drivingly coupled to another sun gear (S1), and the other sun gear (S1) is non-rotatable on the drive shaft (5) that is rotatably supported. Attached, and the drive shaft (5) is driven by a non-uniform rotational movement by the drive unit (4, G3).
The drive unit is formed from a transmission stage (G3) provided with non-circular gears (42, 43), and the transmission stage (G3) carries out a uniform rotational movement of the main drive unit (HA). A drive device for creating an intermittent movement for a detaching roller of a combing machine, characterized in that it converts to a non-uniform rotational movement.   A drive element for the frame (2) is formed from a drive shaft (20), and a gear (Z) is attached to the drive shaft (20) in a non-rotatable manner. ) Is drive-coupled directly or indirectly to the frame wheel (3) of the frame (2) of the differential gear device (1).   The drive shaft (20) includes another drive wheel (16), and the drive wheel (16) is drivingly coupled to the drive element (18) of the main drive unit (HA). 3. The drive device according to claim 2, wherein (18) is simultaneously drive-coupled with a transmission stage (G3) comprising non-circular gears (42, 43).   The drive element of the main drive (HA) is formed from a gear (18) that is pivotally supported on a machine frame (MS), the gear (18) comprising another means (19, 38, G, 40) is driven by a central drive motor (M), and the rotation shaft (48) of the gear (18) is provided with a non-circular gear (42, 43). ) Extends coaxially with respect to the input shaft (44), and another drive wheel of the drive shaft (20) is formed as a gear (16), which is the main drive. 4. The drive device according to claim 3, wherein the drive device is drive-coupled to the gear (18) of the (HA).   The input shaft (44) of the transmission stage (G3) with non-circular gears (42, 43) is connected to the gear (18) of the main drive device (HA) via a detachable mounting means (24). The drive device according to claim 4, wherein the drive device is non-rotatably coupled.   A guide (30) is provided in the vicinity of the mounting means (24), and the guide (30) is connected to the input shaft (44) and the main driving device (with the mounting means (24) loosened). The drive device according to claim 5, wherein adjustment of the rotation angle between the gears of HA) and the gears is allowed.   The gear (Z) is detachably attached to the drive shaft (20) via attachment means (22, 23, 24), and between the drive shaft (20) and the gear (Z). The drive device according to claim 2, wherein the angular position of the is adjustable via means (30, 24).   The vehicle (3) for the frame body is detachably attached to the frame body (2) of the differential gear device (1) via means (13). 3. The drive device according to claim 2, wherein the drive device can be adjusted at an angular position relative to the frame body (2) via the adjusting means (12, 14) when viewed in the circumferential direction.

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