GB1203998A - Apparatus for driving a pump or pumps of a machine for spinning filamentary material - Google Patents

Abstract

1,203,998. Spinning liquid supply systems. VICKERS-ZIMMER A.G. PLANUNG UND BAU VON INDUSTRIEANLAGEN. 1 Nov., 1967 [3 Nov., 1966; 27 Sept., 1967], No. 49642/67. Heading B5B. [Also in Division F2] Apparatus for driving a number of pumps of a spinning machine for spinning filamentary materials from a polymer melt or solution, comprises, as shown, a continuously variable multiplate chain main transmission disposed after the driving motor, the main transmission being followed by fine-adjustment transmissions connected directly to the pumps, each fine-adjustment transmission comprising a transmission for providing a large speed reduction and followed by at least one close-ratio change-speed transmission. The transmission shown in Figs. I and 2 is driven via a worm shaft 1 mounted in ball-bearings 3 in the top part of a transmission casing 2. A worm 4 drives a worm-wheel 5 secured by key 7 to a shaft 6, also mounted in ball-bearings 8. Access can be had to wormwheel 5 after removal of transmission casing cover 9, which comprises a viewing window 10. Gear-wheel 12 is secured by a key 11 to shaft 6 and meshes with two laterally staggered gearwheels 13. The same run on the shaft 15 mounted in ball bearings 14 and on which other gear-wheels 16 are disposed, wheel 16 driving change-wheel pairs 17, 18 and 19, 20. Only the output wheels 18, 20 are externally accessible and can be readily replaced by outward wheels having a different tooth number. Consequently, to enable minor changes to be made in the output speed of a change-speed transmission and therefore in the delivery of the associated pump, only the corresponding wheel 18 or 20 to which an output shaft 21 extending to the pump is connected is constructed for ready replacement. The method of effecting replacement is described in detail. Wheels 17 to 20 are mounted on their shafts 22, 29 by means of needle bearings 27, 28. Output wheels 18, 20 are connected to pump shafts 21 via dog clutches so devised as to compensate for minor inaccuracies in construction, e.g. in the alignment of the output wheel shafts and of the pumps, and inaccuracies due to the heating of the pump shafts 21. The mechanism for this purpose is described in detail. Wheels 18, 20 can be changed in operation, by varying the spacing between the shafts 22, 231 and 29, 29<SP>1</SP>. Shafts 29, 29<SP>1</SP> of driving wheels 17, 19 are mounted in pivoted arms 36, 37 which pivot around the shaft 15 of driving wheel 16. To facilitate pivoting the arms 36, 37 have guide members 38, 38<SP>1</SP> in which a rotatable peg or stud 39, 38<SP>1</SP> of a stationary gear-shifting shaft 40, 40<SP>1</SP> engages. Stud 39, 39<SP>1</SP> is mounted on shaft 40, 40<SP>1</SP> eccentrically, so that when shaft 40, 40<SP>1</SP> rotates the guide member 38, 38<SP>1</SP> is reciprocated in its slideway 41, 41<SP>1</SP> and the corresponding arm 36, 37 simultaneously pivots around its pivot place. Consequently, driving wheel 17, 19 is moved towards or away from associated wheel 18 or 20. In the right-hand half of Fig. 1, driving wheel 19 visible in the extreme right-hand part, is shown in its operative position in which it meshes with the wheel 20. The guide member of a slide block 38 is then at the bottom end of its slideway 41, while the centre of the stud 39 is disposed slightly below the horizontal plane passing through shaft 40. The driving wheel 17 visible in the left-hand part of the right-hand half of Figure 1 is shown in a position in which it is not in engagement with wheel 18. The slide block 38<SP>1</SP> is in its top position, while the centre of the stud 39<SP>1</SP> is disposed very closely adjacent a vertical plane passing through the centre of the shaft 40<SP>1</SP>. Pins 42 secure the shafts 29, 29<SP>1</SP> of the wheels 17, 19 to the arms 36, 37. Shaft 40 has a shift connecting member 43 and means 44 for receiving an actuating shaft 45. When in its operative position, i.e. when driving-wheel 17 or 19 is in engagement with the corresponding driven wheel 18 or 20, member 43 points downwards and abuts an adjustable abutment 46. Abutment 46, as shown, is a screw screwed into a corresponding aperture 47 in accordance with the particular wheel used, i.e., the tooth number of the wheel. In the present case, three changewheels having different tooth members provide a transmission having adequate range of adaptation, and so the embodiment shown has only three abutment places. To operate shaft 40, lever 45 is inserted in means 44, which are so constructed as also to serve as a means for locking member 43 and thus shaft 40. The locking means is described in detail. If it is required to drive just two pumps, the two gearwheels connecting the worm-wheel to the wheel driving the change-wheel pairs can be omitted and the wheel driving such pairs can be driven directly via the worm-wheel shaft. Alternatively, further pairs of change-wheels can be connected to the worm-wheel of its shaft via intermediate transmission and, e.g., six pumps disposed one beside another can be driven through just a single fine-control transmission. If required, the change-speed transmission can be a shifting transmission, as shown in Figure 4. This transmission is devised to drive just one pump. The transmission is connected via worm shaft 1<SP>1</SP> to a main drive-shaft connected to the continuously variable main transmission. Casing 2<SP>1</SP> receives the various integers of the transmission. Worm-shaft 1<SP>1</SP> has a worm 4<SP>1</SP> which meshes with the toothed rim of the worm-wheel 5<SP>1</SP>. Worm-wheel 5<SP>1</SP> is rigidly secured to the shaft 6<SP>1</SP> by means of a key 71. Shaft 6<SP>1</SP> is mounted in ball-bearings 8<SP>1</SP>. Also secured to shaft 6<SP>1</SP> by means of a key 61 is a gear-wheel 60 which is a component of three speed shifting transmissions. The same also comprising gearwheel 63 to 65 slidable on a shaft 62. Gearwheels 63 to 65 are all of the same diameter as one another but have different tooth numbers. The differences between the tooth numbers of the gear-wheels 63 to 65 can vary the speed of transmission finely enough to compensate the pump delivery. The three-speed transmission of Fig. 4 is shifted by means of a shift linkage comprising a thrust-rod 71 and, secured thereto, a fork 72 which engages round that end of the central gear-wheel 64 which is at the bottom in Fig. 4. Once the required transmission ratio has been selected by engagement of one of the wheels 63 to 65 with wheel 60, the shift linkage is locked to the casing 2<SP>1</SP> by means known. Another embodiment of a 3-speed shifting transmission is shown in Fig. 5 (not reproduced), which differs from that of Fig. 4 only in that in Fig. 5 a single sliding wheel (73) is disposed on the output shaft (62<SP>1</SP>). Three matching wheels (74) to (76) are non-movably secured to a shaft (77) by means of a key (78). Intermediate rings (79) determine the spacing between the wheels (74) to (76). To shift the transmission, gearwheel (73) is slid along the output shaft (62<SP>1</SP>). Gear-wheel (73) is connected to shaft (62<SP>1</SP>) by a sliding key (69<SP>1</SP>). The shift linkage as in Fig. 4 comprises a thrust-rod (71<SP>1</SP>) and a fork (72<SP>1</SP>) secured thereto and engaging around the bottom end of wheel (73). The transmission of Fig. 5 is driven via worm-shaft (1<SP>11</SP>), worm (4<SP>11</SP>), wormwheel (5<SP>11</SP>) and shaft (6<SP>11</SP>), the latter being mounted in ball-bearings (8<SP>11</SP>). Worm-wheel (511) is connected to shaft (6<SP>11</SP>) by an inserted key (7<SP>11</SP>). In the embodiment shown, an extra transmission stage has been interposed between the worm drive and the three-speed transmission and takes the form of a gear-wheel (12<SP>11</SP>) which an inserted key (11<SP>11</SP>) secures to the shaft (6<SP>11</SP>). Wheel (12<SP>11</SP>) meshes with gear-wheel (74) of the shifting transmission. In the present example, in which the transmission serves to drive just a single pump, the gear-wheel (74) acts merely as a reduction stage; but when it is required to drive a number of pumps simultaneously via a transmission according to the invention, the main function of the gear-wheel (74) is to distribute the line of drive to preferably two subsequent change-speed transmissions. The line of driven can then be further split in a similar way in the change-speed transmission. In Fig. 6 the line of drive is divided and the transmission is used to drive four pumps. Since both halves of the transmission are symmetrical, only one half is shown. The transmission is shown in elevation from the output side with the casing end cover removed. A worm shaft 1<SP>111</SP>, worm 4<SP>111</SP> and worm-wheel 5111 not shown, transmit the torque to a shaft 6<SP>111</SP>. The gearwheel 12<SP>111</SP>, disposed on the shaft 6<SP>111</SP> in just the same way as in Fig. 5, transmits the torque to two laterally staggered gear-wheels 13111 disposed symmetrically of the central plane of the transmission. Each gear-wheel 13<SP>111</SP> corresponds in operation to the gear-wheel 74 of the embodiment shown in Fig. 5, i.e. it forms one of the three non-sliding wheels with different tooth numbers of the three-speed transmission. The non-sliding wheels of the shifting transmission divide the line of drive further between two output shafts 62<SP>11</SP> on which displaceable single wheels 81 of the shifting transmission are disposed, being secured by sliding keys 82. Disposed below wheels 81 are thrust-rods 71<SP>11</SP> of the shift linkage, a corresponding fork 72<SP>11</SP> engaging around the bottom ends of the corresponding gear-wheels. The transmission shown in Fig. 6 is the construction requiring the lowest possible quantity of different tooth numbers to drive the specified number of pumps, only a single splitting or distributing wheel 12<SP>111</SP>, two "trio" combi