CS217778B1 - Gearbox, especially for multi-spindle lathes of one type series - Google Patents

Abstract

Gearbox, especially for multi-spindle lathes of one type series, the part for driving the work spindles and the part for driving the feeds and rapid feeds are equipped with a common electric motor. The box is designed so that it requires as few technological operations as possible in terms of production and has as few changed elements as possible in terms of technological utility, provided that the box is intended for the entire type series of machines of one type. Securing the gear rows on the work spindles of the machine and the feed and rapid feed output speeds of the box is achieved variably and by means of interchangeable gear wheels.

Description

Gearbox, especially for multi-spindle lathes of one type, whose part for driving the working spindles and the part for driving, feeds and rapid travels are equipped with a common electric motor. The casing is designed to require as few technological operations as possible and to exhibit as few technologically usable features as possible, provided that the casing is designed for the entire range of machines of one type.

The security of the rows on the machine working spindles as well as the feed and quick-feed output speeds of the housing is achieved by variable and interchangeable gears.

for multi-spindle lathes of one type

AND

Giant. 1

The invention relates to a gearbox, in particular for multi-spindle lathes of the same type.

Efforts to streamline the production of mass-produced products lead primarily through the constructional relationship of individual sizes or types, which is intended to use as few types and dimensions of their individual elements as possible. The aim, through standardization, is to unify elements or components, even groups or functional units, so that they are applicable to all members of a single product line.

These efforts are often hampered by the difference in functions of the technological use of such products. Typical representatives of such products are machine tools and the larger they have. the universality of their technological use or usability, the more the conditions requiring often the same effect, result or functional output to be achieved by other means as for types adjacent to a given type of one type series. This then disrupts the effort to reduce the number of unified elements applicable to the entire typoive product line, which adversely affects the economic parameters of their production. The solution to these problems therefore falls within the direct connection of technology and economy.

One of the units that considerably influence not only technologically useful, but also technologically production characteristics of the machine and economics of their production are gearboxes, units often very complex, containing more shafts, their bearings and gear wheels, the larger be the technological universality of their use. Typical examples of machine tools where these conditions are particularly prominent are multi-spindle lathes in which the series does not only include types differing in performance and size, but also types processing both bar and piece material.

The effort to achieve the highest possible unification of gearbox components for such machines affects not only their parts for driving the machine spindles, but also the parts of the machines for driving their displacements and leads in particular to the fact that at least the closest machine types are equipped with one gearbox. . This can practically only be realized on two adjacent machine types of the same series, so another type and size of the gearbox needs to be designed and manufactured for the next pair of adjacent types. In some cases, parts of the gearbox can be used to drive the feeds for a plurality of members of one type series, but this possibility is greatly complicated by the dependence of these displacements on the speed of the working spindles of the machine.

The purpose of the invention is to shift the design of the gearbox of universal machine tools and in particular multi-threading lathes to the next higher degree, so that the number of dimensions of their individual structural elements realizing kinematic chains of working spindle drives and machine feeds is further reduced and technology. naturally without any restrictions on the technical applicability and working possibilities of machines of the whole type series.

SUMMARY OF THE INVENTION The transmission housing consisting of a machine spindle drive part and a feed and rapid traverse part of its working slides equipped with a common electric drive motor has a first shaft of the work spindle drive part provided with a clutch kinematically coupled to a second a second shaft with a third shaft with interchangeable gears having a transmission which can be used once as a quick-change gear and a second time as a poimala gear, the third shaft, coupled with a hollow kinematically can be coupled with a shaft coaxially mounted in the hollow main shaft for the second output speed adjustable on the selected working spindles of the machine, alternatively either the same gear size as the larger interchangeable gear, or a smaller gear identical to the smaller gear between the second shaft and the third shaft, forming double-coupled gears with the pairs of these interchangeable gears, or another pair of interchangeable gears; the shaft of the feed section is bound by continuous engagement for the individual members of the directly designed gear wheels with the second shaft of the work spindle drive section and the second shaft of the feed section - divided into two coaxial independent rotating parts - by two pairs of permanently engaging gears, one pair fixedly connected to the shafts of the wheels and a second pair of gears separated from the first pair by a freely rotatable mounting between two parts of the second shaft of this feed part, whose third shaft - again divided into two parts rotating parts independently of one another - is coupled to the previous second shaft by moving interchangeable gear wheels and by one of the interchangeable pairs of gear wheels movably connecting opposite independently rotating parts of these shafts, of which one independently rotating part is kinematically connected via a counter the shaft coupled to the third shaft is again one of the variable interchangeable pairs of gears, one of the three non-interchangeable gears of a double-coupled transmission with one clutch shaft clutch coupled by the other with its counter shaft a second pair of gears, which clutch shaft is coupled of wheels, which can be switched by one of the couplings for feed or rapid traverse, and with the co-engaged wheels with the drive shaft fitted with the brake and through its · conical pastor and a bevel gear with a worm shaft engaging the worm wheel of the feed shaft.

The advantages and progress of this gearbox construction for universal machine tools, in particular for multi-spindle lathes of the same type series, is that it allows different offset of the working spindle speed rows at the same feed rate for a given working spindle speed. The sizes of the rapid feeds for individual members of the type series can be changed by replaceable wheels according to the requirements of the duty cycle. For the given rotational stage of the working spindles, the same working feeds can also be achieved for individual members of the machine series by means of interchangeable wheels. This design also allows the number of shaft axles and the number of gears to be reduced while maintaining a given number of revolutions of the working spindles by a number of feeds and rapid travels. In addition, the housing is designed for both single and dual output speeds, which can be optionally selected for individual machine spindles in accordance with the machining technology requirements of the component.

These advantages will be further exemplified by the description of a particular transmission housing for multi-spindle automatic lathes, which is one example of the application of the present invention to machine tools. This particular example of application of the invention is shown in the drawings, in which: FIG. 1 is a sectional view of the gearbox; FIG. 2 is a partial sectional view showing an alternative embodiment of a two output speed housing optionally selectable on any machine spindle; 3 is a diagram of the entire gearbox - its parts for driving the working spindle speed and for driving feeds and rapid travels.

The gearbox drive according to the invention is derived from an electric motor 1 (FIG. 1), whose pulley 2 together with the second large pulley 3 and V-belts 4 implementing the reduction gear 11 transmits the torque to the first shaft I of the machine working spindle. (The shaft is used to indicate the shafts.) This first shaft 1 is provided with a clutch S1 to switch on and off the housing drive and is coupled to the second shaft II of the same housing part by a pair of interchangeable gears 11,21. The working spindles of a machine of a four-member type series require four pairs of these interchangeable wheels, so chosen that the gears i2, i3, i4, i5 formed by them, essentially always slowly, form a geometrically graduated series which is intended to move within the required range output speed of working spindles according to technological requirements of individual members of the type series of machines.

From the second shaft II to the third shaft III of this part of the gearbox, the torque is transmitted by a pair of interchangeable gears 22, 32. Due to their interchangeability, these gears 22, 32 form a gearing once (Fig. 1) and a second gearing to slow I6 (FIG. 3). Other gears may be used to fill the range between the speeds of the third shaft III produced by one gear 16 and the second gear 16 - although not shown in the diagram in FIG. 3, but not drawn, which will again be realized by interchangeable gears having a total number of pairs including gears. 22, 32 - according to the diagram of the gearbox of FIG. 3, i.e. according to the described example of a particular application of the invention - is ten. The third shaft III is kinematically coupled to the hollow main shaft IV by a constant transmission 17 of the toothed coils 31, 41, so that the output number of rotations of the main shaft IV is identical to the number of rotations of the third shaft III. It can be seen from the diagram shown in Fig. 3 that these pairs of interchangeable gears form together with the gears 18 and the geometry series. It is also apparent from this diagram that from the main shaft IV the speed is transmitted to the working spindles by yet another fixed gear i8, which is no longer shown in FIG. 1, since this represents only a section through the gearbox and does not affect the coupling directly. <with machine working spindles.

An alternative solution for dual speed adjustable on any working spindle of the machine is the dashed complement in Fig. 1 and the fully illustrated situation in Fig. 2. It can be seen that the second solid shaft IVa is simultaneously guided through the hollow main shaft IVa. shaft III of the machine spindle drive part can be connected by either the same gear 141 (FIG. 1) as the larger interchangeable gear 22 or the smaller gear 32 from a pair of interchangeable gear 22, 32 between the second shaft II and the third shaft III, forming double-coupled gears with pairs of these interchangeable gears 22, 32. The coupling can naturally also be realized by another pair of interchangeable gears 33, 143 (Fig. 2), which no longer form double-coupled gears.

The drive of the feeds and rapid travels of the individual working slides of the machine is derived by the second part of the gearbox from the second shaft II, whose parts for driving the machine spindles. . First / shaft 'V' of this. the sliding part of the gearbox is coupled to the second shaft 11 of the drive / spindle part by the permanently engaging gears 23 and 53, their transmission being selected in each case on the first one; In the shifting shaft of the gearbox, all the members of a single machine series produced the same speed. Thus, for each member of the type-machine series, this transmission is different, so in the transmission diagram of FIG. 3, four, the -181, i82, 183 and? Gears are plotted for the described example of a series of several spindle automatic lathes; 184. This first shaft in the feed section is connected to the second shaft VI of the same gear housing part by two pairs of permanently engaging wheels of different gears, thereof; for this reason, the second shaft VI is divided into two. s.pu-. o-se ,; independent, rotating parts Via, Vib ./(pbr..1). “One of these .- pairs is toothed! 51, 61, of which the first gear 51 of the coupling is connected to the first shaft in the ladle portion of the transmission. cabinets, occupies;, with; The first part of the second shaft is formed by a gearwheel 6.1. The second, the twin, is formed; toothed; around; 52 coupled to the first shaft V of this; sliding parts of gearbox-gear. and second, toothed fly 62, second parts Vib; the second, his. VI. The first pair of toothed wheels · 31 ,; 61 creates; a reduction gear i51 and a second pair of toothed wheels 52, 62. conversion to '; 1.52..Tito. The shaft 11 produces two revolutions, which are then transmitted to the third shaft V1 (FIG. 11), which is again divided into two coaxial independently of each other, the rotary parts 11a and 14b. the transmission takes place with a dual path once, the speed of the third shaft (VII) being generated for the working feeds and the second for its speed for rapid traversing. / Pairs of interchangeably interchangeable gear wheels: 63 · 73, / with a transfer applicable once as a low speed i63? And a second as: a transmission to fast (FIG. 3).

r to /; '; ..: y -.' · /; // · '/// ‘i63;. ·' /

The rapid traverse speed is then provided by a set of variable interchangeable gears 64, 74 on the independently rotatable parts Vib and V1b of the second shaft Vi and the third shaft V1 of the shift part of the gearbox. Referring to the transmission diagram of FIG. 3, it is evident that this set of variable interchangeable gears 64, 74 is in the present case three-membered - thus representing three pairs with gears iS4, IBS, iB6. The feed speed is then transmitted to the master shaft from the third shaft. shaft. VIII, with a set. interchangeable gears 71, 81 with a transmission which can be used as a low-speed transmission 17.1 and a second as a transmission;

Introduction to Fast —— ..

To cover the required number of output feed speeds, there are other interchangeable wheels in the set to realize the gears 172, Ϊ73, 174, i75, i76, Ϊ77, i78 and their reciprocal values

1 1 1 1

Í72. I73 i78 i74 175 i76.

and the i79 transmission, which is a 1: 1 transmission. From the countershaft V111, the speed is transmitted to the clutch shaft IX, on the one hand, by the rapid traverse clutch S2, whose gear dimension 92. it is in direct engagement with the gear shaft 82 of the countershaft VIII, which is driven by the gearwheel 72 of the shear part V1 of the third shaft VII of the feed section of the gearbox, on the other hand to the displacement clutch S3- whose gear 93 directly engages the gear. 83 countershaft VIII. Switching of the sliding clutch S3, possibly the bellows. of the S2 clutch with rotation of the master! shaft VIII is transmitted to the clutch shaft IX, whose fixed gear 91 engages with an equally large toothed wheel 101 of the drive shaft X equipped with a brake 5. The gear wheels 91, 101 are thus realized a 1: 1 conversion i9, while By means of the gears 83, 93, a reduction gear 110 is provided between the output shaft V1H and the clutch shaft IX. The speed of the drive shaft X is further reduced by the bevel gears, namely the bevel pinion 102 and the bevel gear 112 of the shaft XI of the worm 113 which engages the worm gear 114 '(Fig. J) of the sliding shaft XII. The pinion 102 and the bevel gear 112 are the reduction gears 111 and the gearing 112 and the worm gear 113 and the worm gear 114 are also a reduction gear.

By having feeds and /.rychloposuvy derived from the shaft speed of the transmission case which is secured a drive _operating: the machine spindle, the feed rate thus depends also on the speed těchto- working machine spindle. In the lower part of the transmission diagram in FIG. 3, the ranges of the individual speed ranges of the working spindles are indicated. 01, 02, 03, 04 machines of the given type series, where the plurality of feeds P1 and the plurality of P2 rapid travels are shown in the upper part of this diagram.

Claims (1)

Gearbox, in particular for multi-spindle lathes of one type, consisting of a part for driving the working spindles and a part for driving the feeds and rapid travels of the working slides, both parts of which are equipped with a common driving electric motor. of the spindles - provided with a clutch (S1) - is connected kinematic to the second shaft (II) of the same part by one of the four pairs of interchangeable gears (11, 21) and this second shaft (II) with the third shaft (III) interchangeable gears (22, 32) with a transmission that can be used as a quick-change gear and a second as a slow-down gear, the third shaft (III) coupled kinematic to the hollow main shaft (IV) by a permanent gear transmission (31, 41) for one output speed of working spindles, can be connected with shaft (IVa) in the hollow main shaft (IV), for the second output speed adjustable on the selected working spindles of the machine, alternatively - be the same size. a gear (141), such as a larger interchangeable gear (22), or a smaller gear identical to a smaller gear (32) from a pair of interchangeable interchangeable gears (22, 32) between the second shaft (II) and the third shaft (III), forming double-coupled gears with pairs of these interchangeable wheels (2.2, 32), or another pair of interchangeable gears (33, 143), while the first shaft (V) of the feed part is coupled with continuous engagement. directly designated gears (23, 53) with a second shaft (II) of the drive portion OF THE INVENTION with working spindles and a second shaft (VI) of the drive part - divided into two coaxially independent rotating parts (Via, VIb) - by two pairs of permanently engaged gear wheels, namely one pair fixedly connected to the shafts (51, 61) and the other a pair of gears (52, 62) separated from the first pair by a freely rotatable mounting between the two parts (Via, VIb) of the second shaft (VI) of this feed part, the third shaft (VII) again divided into two coaxial parts Is coupled to the preceding second shaft (VI) by a fixed transmission of the interchangeable gear wheels (63, 73) and by one of the interchangeable pairs of gear wheels (64, 74) movably connecting opposite independently rotatable parts (VIb, Vllb) of these shafts, of which one independently rotatable part (Vllb) is kinematically connected via a the lohioive shaft (VIII), coupled to the third shaft (VII), is again one of the variable interchangeable pairs of gears (71, 81), one triple non-interchangeable gears (72, 82, 92) of the double coupled gear with one clutch (S2) a shaft (IX) coupled by its second clutch (S3) to the countershaft (VIII) by a second pair of gears (83, 93), which spiro-shaft (IX) is coupled by a gear (91), switchable optionally one of the clutches (S3, S2) for ¹ feed or rapid traverse, and the co-engaged wheels (101) with the drive shaft (X) provided with the brake (5) and by means of its bevel pinion (102) and bevel gear (112) with worm shaft (113) engaging the worm wheel (114) of the feed shaft (XII).