DE1903047A1 - Machine for machining threads with variable pitch - Google Patents

Description

Y Λ TENT Λ NW ALIS

Dr. Ar »drϋj ■ * wski
Dr.-Inn · Honk β
43 Essen, Kelt λ ip.er Str. 36

(AmHBuptbcuicW UdUberg) Telephone 225802/03

SUD-AVIATION Sooiete Nationale de Constructions Aeronautiquea, in Paris (France)

Machine for machining threads with variable pitch.

The subject of the invention is a machine for the production of screws with variable pitch, in particular of such screws with large dimensions. Such a variable pitch is achieved according to the invention by means of a displacement of a tool carrier axis a continuously variable speed, or by means of a rotation of the workpiece also by means of a continuously variable speed, or by means of these two produced simultaneously.

Devices are known on machines, for example lathes, which have different tool carriers Allocate pre-stroke speeds or the turning speed of the workpiece, but these preset speeds remain during a Machining process constant, so this way there is no

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Variable pitch screw can be made. The task of machining a screw with changeable G-anghöhe, i.e. the task of moving a tool carrier slide a or a workpiece with a variable speed according to a precisely defined spatial law, is made by the masohine forming the subject of the invention solved.

A main feature of the invention

Machine is the separation of the power function on the one hand and the displacement function on the other hand. This separation is achieved by means of the following parts:

- a power generating equipment which fulfills the task of a spring and constantly acts on a slide in such a way that it presses it against a movable stop;

a movable stop formed by a screw and nut system;

- an arrangement for controlling the displacement and the achievement of the variable speed.

In certain embodiments of such a machine, the power is supplied by an electric motor, which runs at a constant speed and drives a pump with a variable delivery rate. This pump feeds a hydraulic motor which drives a reduction gear, the output pinion of which with one on the machine frame attached stationary rack is in engagement.

In one embodiment, the movable Stop a nut which prevents rotation and is firmly connected to the movable tool carrier slide is, as well as an associated Sohraube, which is in a translational movement compared to the machine frame is prevented.

This system with the head and mother

is self-locking, i.e. only one rotation of the screw is possible a displacement of the nut, while a force exerted on the nut parallel to the axis of the thrust Cannot make Sohraube rotate. The degree of self-locking of this system is, however, chosen in such a way that it is the Reversibility is as close as possible, so that the unlocking of the thrush opposite the one acting on the mother Translations for the required force as small as possible

0 09836/045 7

power will.

In an arrangement for controlling the

Shift and thus to achieve the variable speed includes a rotary motion imparting kinematic chain to the screw a motor, which a first Gearbox with interchangeable gears is assigned, the output axis of which is an input shaft of a differential with a constant predetermined speed. This engine is powered by a second gearbox with interchangeable gears connected to the axis of a cam, the profile of which is determined as a function of the spatial law to be established.

This cam is the button of a hydraulic

Liechen copier assigned, the working cylinder is firmly connected to a rack, which interacts with a third gear with interchangeable gears, whose output axis carries a pinion, which is connected to the cage of the differential with a toothing in The output shaft of the differential engages the screw via a fourth gearbox with interchangeable gears offset in rotation.

The main benefit of separating the lines

the displacement function and the displacement function is that the size of the variable speed generating device can be reduced.

In the case where the system is using

Screw and nut have the power function as well as the displacement function exercises, must namely to the greatest possible reduction of the torque required on the screw is the pitch the same can be reduced, resulting in the same displacement of the tool carriage to a considerable number of Turns of the screw. Since the stroke of the working cylinder controlling the rack for controlling the cage of the differential is limited, the mechanical transmission then has to be between the rack and the cage are increased, thereby reducing the power available at the output of the differential is limited.

In the training according to the invention,

in which the system with screw and nut is at the limit of reversibility, on the other hand, the one for the

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Displacement of the slide required number of revolutions the screw low. The number of arranged between the rack of the copier and the cage of the differential Gears and the translation of such a transmission are reduced, which leads to better efficiency between the power of the working cylinder and the power obtained on the screw.

Furthermore, the fact that the

Nut constantly rests against the lead screw, the achievement better accuracy when machining the thread, since the movement of the tool carrier slide is always accurate corresponds to the commands transmitted by the button of the copier in contact with its cam will.

The invention is explained below by way of example with reference to the drawing.

Fig. 1 shows in a diagrammatic

schematic representation with parts broken away, the overall view of a machine according to the invention in the working position .

Fig. 2 shows a diagram of the development of the screw thread to be produced.

3 shows the profile of the control cam in the form of a diagram.

FIG. 4 shows, in the same representation as FIG. 1, an embodiment modification of such a machine.

The machine shown contains for

Exercise of the power function a feed unit with an electric motor 1, a reservoir 2 for a liquid with a filter 3, a pump 4 with variable delivery rate, a calibrated valve 5 and a manually operated one Switching distributor 6. This unit feeds via a line 7 a hydraulic one provided with a tachometer dynamo 8a Motor 8. A return line 9 connects the motor 8 to the reservoir 2. A third line 10 connects the Motor 8 directly with the reservoir 2 and causes the backflow of the leakage currents.

The Aohse of the hydraulic motor 8 is firmly connected to a worm 12, which is connected to a worm

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_5-19U3047

kenrad 11 is in engagement, with which a shaft rotatably 13 by grooves 13a of the same at the point of the hub 11a of the Wheel 11 is connected so that the shaft 13 slide axially can. This shaft 13 is firmly connected to a pinion 14, which can come into engagement with a gear 15, which is mounted on an intermediate shaft 16, which is a pinion 17 carries, which is in engagement with a gear 18 which is attached to a hollow shaft 19, which in of the machine frame supported bearings is stored, which are not shown to simplify the drawing, this hollow shaft on one side the shaft 13 and on the opposite end a pinion 20 receives, with which one on a tool carrier slide 22 fixed rack 21 is in engagement. On this slide, the guidance of which is shown schematically by a with a slide rail of the machine bed cooperating dovetail is shown, there is a tool carrier, at the end of a cutter 23 by a not shown Motor is set in rotation, which delivers the cutting power, the carriage against an adjustable stop 24 sets, the position of which is determined as a function of the workpiece. This sleigh carries an obvious one below Nut 25, which is prevented from rotating with respect to the tool carrier slide 22. Control of the mother is not shown.

A lever 26 pivotable about an axis 27 attached to the machine frame for reversing and Speed change carries a fork 28 at its end, which grips between two shoulders 29 of the shaft 13, which allows the shaft 13 with the shaft 19 by means of a claw coupling to connect, which by the interaction of the pinion 14 and one on the corresponding side of the gear 18 formed encompassing third teeth 30 is formed to separate the shaft 13 from the shaft 19, and this latter driven by the intermediate shaft 16 as shown in the figure, for which the lever 26 can assume three different positions.

Achieving a shift with

a constantly changing speed takes place duroh the arrangement described below.

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The machine has a motor for this purpose

31 with a continuously variable e.g. between 70 rpm and 1400 rpm Speed on, on the shaft of which a tachometer dynamo 31a is attached. This motor shaft drives a pulley 35 with several grooves, which drives a corresponding belt pulley 36 with several grooves via belt 37. These pulleys are interchangeable and result in a reduction ratio of for a moment chosen as an example 1/3.

The axis of the pulley 36 is fixed

connected to a first worm 38 which cooperates with a worm wheel 39, the axis 40 of which is a worm 41, which cooperates with a worm wheel 42, which rotates fixedly with the spindle 32 carrying the pig 33 is connected, on which a split disc 34 is attached, which is opposite to a fixed not shown Pointer rotates to form an adjustment system. In the example under consideration, the transmission ratio is of the first gear with the worm 38 and the worm wheel 39 i / 60, while that by the worm 41 and the worm wheel 42 given ratio is 1/20. The total reduction is determined by the appropriate choice of pulleys 35,36. By defining the speed of the motor 31 can so the speed of the spindle 32 can be set precisely because the speed of the motor 31 is continuously variable, with a control takes place through the information supplied by the tachometer dynamo 31a.

The spindle 32 is fixed to the first

Pinion 43a of a synchronizing gear with interchangeable gears connected, and the last pinion 43 (1 of this gear 43 is firmly connected to a shaft 44 which carries a sun gear 45 of a differential 46.

Furthermore, this spindle drives the axis of rotation via a second gear 47 with exchangeable gears a cam 48, the profile of which is determined in accordance with the spatial law to be established. for this determination is a Example explained below.

With the profiled edge of this cam 48, a copy button 49 of known design cooperates, wel-

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rather interacts with a hydraulic feed, which is provided with a pump 50 and the hydraulic fluid used in a suitable manner on the two chambers of a copy working cylinder 51, the piston rod of which is firmly connected to a rack 52. This rack cooperates with the first pinion 53 <a of a gear 53 with interchangeable gears, the last wheel of which with a toothing 55 carried by the cage 54 of the differential is in engagement.

Within this cage 54 of the differential 46 are the sun gear 45 and double cylindrical planetary gears arranged with pairs of meshing gears 56 and 57, each gear 56 having the first input sun gear 45 and each gear 57 meshes with the output sun gear 58, the latter being fixed is connected to an output shaft 59. The planet gears 56 and 57 are load-bearing on them and firmly connected to the cage 54 Shafts loosely rotatable. All of these gears are chosen so that when the cage 54 is at a standstill, the ratio between of the input speed and the output speed equals the unit, i.e. the sun gears 45 and 58 on the one hand and the planet gears 56 and 57 on the other hand have the same pitch circle diameter and the same Z-like numbers.

The output shaft 59 is fixed to the

first pinion of another gear 60 connected to interchangeable gears, the output pinion fixed to the end a shaft 61a is connected, which is coaxial with the control screw spindle 61, the threaded part 61_b with the reveal mother 25 cooperates. The connection between the axis 61a and the screw spindle 61 is through a sleeve 62 keyed to the axis 61a and sliding thereon, which inside it is connected to the screw spindle 61 is firmly connected by a Schnetkenrad 63, which with the screw spindle 61 is coupled and locked by a worm 64 which meshes with the son corner wheel 63 stands and is mounted in the sleeve 62, wherein this screw 64 can be driven in any way, in particular by an independent motor, not shown.

Determining the profile of the active

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The edge of the e-docking 48 can be done as follows:

Let it be:

V is the speed of the control screw spindle 61 in rpm ρ is the pitch of the control screw spindle 61 in mm

E, the displacement of the slide 22 in mm

V is the speed of the pinion 53a in rpm P "~

D is the diameter of the pinion 53a in mm

V _{e is} the speed of rotation of the shaft 44 in rpm

V _{1 is} the speed of rotation of the cage 54 in rpm

V is the speed of the output shaft 59 in rpm r the transmission ratio of the transmission 60

T _{1 is} the transmission ratio of the transmission 53

E is the displacement of the rack 52 in mm

V is the speed of this rack 52 in mm / min

The equation for the displacement of the carriage 22 can be written:

Taking into account Willis' equation:

in which R is the gear ratio of the differential, which one is equal

is when the differential cage is locked , and the ratio y

the equation (1) can be written:

E _ch = 2 pr Jv ₁ dt - pr / V _e dt (2)

in which the expression 2 pr JV ^ dt represents the shift at variable speed, while the expression -pr JV _e dt represents the shift at constant speed.

The equation of the displacement of the rack 52 can be written:

E ₀ - / T ₀ dt (3)

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Taking into account the value of

V = π. D_ »V and the ratio

the equation (3) can be written:

E ₀ = —B- j V ₁ dt (4)

and by substituting equation (4) in the expression for the variable speed displacement, which

equals 2 p.rfv- dt, one obtains
¹ Z. D

τ? ■ '■ ■ .E (variable speed) £ i _Q = <l prr ^

Wind to show the cam

the screw thread to be produced on the workpiece 33 and thus draws the variable pitch to be achieved as a function of the pitch circle diameter D- of the screw and the change in pitch according to the points P-, Pp ···· P _n over the length of the screw, like this can be seen in particular from Fig.2. At the beginning of the pitch at point A and near the end of the same at point B ', a straight line can be drawn which represents the development of a mean constant pitch ρ obtained by the action of the gears 43 and 60. Ee it is then possible to draw a circle with any desired radius 0-A- (Fig. 3), which represents the mean constant pitch. Starting from the radius 0-A-, successive equal angles are drawn in, the unit angle α being the angle of rotation of the cam 48, which corresponds to one revolution of the spindle 32. In relation to this circle, segments are drawn on _{the radiuses determined by these successive angles, which correspond to the lengths X-, X 2} , etc., taking into account the scale factor K of the cam, which is a puncture of the greatest displacement of the display system, which is the reduction ratio of the Gear 53 determined, with these segments X-, X ₂ etc. the differences between the mean pitch and the changed pitch X ₁ = P _m - Pj »* 2 = ² _ρηι - (Pf + P2)» X _n = np _n - (Pi + P ₂ ··· ⁺ P _n ) parts of clara.

009836/0457

In the example above it is sioh

around the machining of a screw thread with variable pitch with a length of L = 4400 mm, of which 2770 mm have a constant pitch of 267 mm and 1630 mm have a variable pitch, the outer diameter D = 350 mm, the thread width 150 mm and the Thread depth 50 mm is _0. The machining can be done with a milling cutter with a diameter of 140 mm, which has ten teeth with a feed rate of 0.2 mm per tooth and rotates at a speed of 45 rpm, with a cutting speed of 20,000 mm in the minute is.

During operation, the largest is

Displacement speed V of a moving body on the part 33 1740 mm per second and the lowest speed V _Q 600 mm per second, while the real speed ν of this part is 135 rpm.

The speed V of the workpiece 33 during machining is given by the following expression:

< - (2 «· VV ^{2 +} Cir

Menu V the total feed speed of the milling cutter 23 a

is, ie 90 mm / min, and R is the mean radius of the screw for machining, ie 150 mm, can be written: V _u = 0.0737 rpm.

The speeds of the control screw spindle 61 correspond to the equation:

VV
ν o_ __u

ν - p _v 'ν

If ρ is the pitch of the control screw 61 and equal 40 mm results

V mini = 0.490 rpm

V _y maxi = 1.430 rpm

The processing time is determined by the printout

4-

given, where t is the time taken by the moving body for its displacement on the considered screw 33 needs. This results in sioh *

t _u »193 min.

009836/0457

Taking into account the time for the

At the entry and exit of the milling cutter, the cam 48 must make one revolution in a little more than 193 min · This corresponds to a reduction ratio of the gear 47 located between the spindle 32 and the cam 48 of 0.0737 x 193 = 14.2. If a ratio of 15 is selected, the cam makes one revolution with 203 minutes, and the angle α has a value of 24 ° for one revolution of the workpiece 33. In the example under consideration, the transmission 43 has four wheels, namely the wheel 43a, which is on the spindle 32 is seated and meshed with the wheel 43, b, which drives the wheel 43, which is connected to the wheel 43d attached to the shaft 44 of the differential. cooperates. The illustrated wheel 43e serves to maintain the center distance between the spindle and the input shaft of the differential in order to make the schematic representation clearer. As a function of the length of the blank, namely 4400 mm, the machining time t = 193 min and the speed of the workpiece 33, namely V _u = 0.0737 rpm, the value p _m = 309.42 is obtained for the mean constant pitch mm, so that the following equation can be written for the gear ratios:

«6

When choosing 39 teeth for 43a, 17 teeth

for 43b, 32 teeth for 43 £, and 19 teeth for 4 3d, an average constant pitch of 309.65 mm is obtained, which is acceptable. The values of X ^, X ₂ , etc. are measured on the graph drawn to scale. The entrance and exit of the cam are drawn in that the developments on both sides of the blank are lengthened, the curve B ₁ -A ₁ corresponding to a decrease in the milling cutter. The scale factor must be chosen in such a way that the possible displacement possibilities of the hydraulic reproduction system / are exceeded. According to the parameters of the copying system, the displacement at a constant maximum speed is 180 mm, and for the displacement at a variable speed, a maximum value at X ₁ of, for example, 610 mm is read off on the curve in FIG. 2. Further, when the diameter D of the pinion 53a

P ~~

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Is 60 mm and the pitch p _{y of} the control screw spindle is 40 mm, it can be written:

² py ^r ' ^r 1 ^ 610

π. D ' TW

what results:

r .T ₁ > 8.

If you choose r. r .. = 9 with a ter-

ratio of 2 for the transmission 60 and a ratio of 4.5 for the transmission 53 one obtains E = 0.26 E (variable speed), which results in a scale factor K of 0.26.

The operation of the above arrangement is then as follows:

Mean, all engines are turned off

Lever 26 is in the dead center, which corresponds to the release of the pinion 14, and the open nut 25 is disengaged is, you bring the tool carrier slide 22 and thus the milling cutter 23 by hand in such a position that the The surface lines of the milling cutter and those of the revolution cylinder formed by the workpiece is a right angle.

The controllable output stop 24 is then brought to bear on the slide 22 and blocked in this position. Thereupon, the angular position of the W _e rkstücks is thereby determined that a secured to the frame not shown controllable pointer is made to coincide with a mark of the split disc 34 and blocked in this position.

The button 49 is then with its key end of an output mark not shown in Fig. 1 at the Bred opposite cam 48, which in the present case coincides with the radius 0-A .., which on the occasion of the shape of the cam and is shown in FIG. 3.

The high pressure pump 50 is operated

set. The electric motor 1 is started and causes the pump 4 to work with a variable delivery rate and the pressurization of the liquid up to the distributor 6. The worm 64 which is in engagement with the wheel 63 is driven and effected by means of a motor (not shown) the rotation of the control screw spindle 61 such that

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the threads of the screw spindle 61 coincide exactly with those of the nut 25 which is open. This nut 25 is going through Closure made effective. By means of the distributor 6, the hydraulic motor 8 is then fed, and by changing the At the speed of the motor 1, the delivery rate of the pump 4 is set so that the motor 8 has a specified, precise speed which is obtained by the speedometer dynamo 8a exactly is shown.

By means of the divider 6, the motor

turned off, and the lever 26 is brought into the working position, i.e. in the position in which the pinion 14 with the Gear 15 is engaged. The hydraulic motor 8 is put into operation again by means of the distributor 6 and drives via the worm 12 the Sc] - ^ 3okenrad 11, which the movement transmits to the shaft 13, the pinion 14 of which is in engagement with the gear 15 via the pinion 17, the gear drives, whereby the engagement of the output pinion 20 with the rack 21 attached to the carriage 22 is established. The torque on the pinion 20 has the exertion of a force through the nut 25 on the control screw spindle 61 in the Axial direction of the same and thus a constant contact of the threads of the nut 25 on those of the screw spindle 61 to Episode. At the same time the oil pressure increases, and part of this oil exits through the calibrated valve 5 and returns to the Reservoir 2 back.

The motor of the Praeser 23 is then in

Operation is set, and the cutter is set for a first operation with the desired depth, which is determined by the geometric parameters of the screw to be produced and the materials concerned is determined. The shift of the Milling in the direction of the axis of the screw to be produced is done by hand by the user using a with a Nonius combined actuation, which are not shown.

After starting the engine 31 drives

this the pulley 35 and then via the belt 37 the pulley 36 and ultimately via the reduction gears 38, 39 and 41, 42 the spindle 32. The rotation of the motor 31 causes the spindle 32 at the same time

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Rotation of cam 48 via gearbox 47 and rotation of input shaft 44 of differential 46 via gearbox The identical planetary gear pairs 56 and 57 of the differential 54 mesh with one another first planet gear 56 is set in rotation by the sun gear 45, while the second planet gear 57 is the output sun gear set in rotation, which has the same parameters as the first has. On the one hand, the constant speed of the input shaft 44 of the differential and, on the other hand, become these planetary gears The variable rotational speed generated by the cam 48 is issued via their axes connected to the cage 54. These variable speed reproduced by the button 49 via the high pressure pump 50 and the working cylinder 51 on the rack 52 and finally with the desired translation through the gear 53 on the cage of the differential transfer.

The rotation of the input shaft of the differential at constant speed is effected in conjunction with the variable speed of its cage that is added to it, the rotation of the output shaft with variable speed and thus also that of the control screw spindle via the gear 60. This rotation of the control screw spindle 61 allows the open nut 25 and thus the slide 22 and the milling cutter 23 to be displaced continuously variable speed with the creation of a stop, which as required in function of the desired spatial law resigns ",

After this first step has been completed, the power supply to motor 31, the milling cutter, is interrupted 23 is withdrawn, the motor driving it is switched off and the hydraulic motor 8 is supplied with oil by means of of the manually operated distributor 6 is canceled · The lever 26 is returned to the dead center. The mother 25 is opened, whereby it is uncoupled from the control screw spindle 61. You then bring the lever 26 upwards, whereby the pinion 14 is connected to the gear 30, what the Rapid return of the sole 22 to its stop 24 is possible, this return producing the distributor 6 is what sioh in the direction of rotation of the hydraulic

009836/0457

- 15 see motor 8 is in reversing position.

It is straightened for a new operation

after advancing the milling cutter 23 in such a way that the identification marks coincide with their pointers, whereupon the above processes are repeated will.

In Pig. 4 shown execution

A modification of the pitch can also be achieved, but by means of a constantly changing one Speed of the blank ο

This is done using equipment

their movable mechanical arrangement attached to the end of the table of a pre-machine on the side of the part box is, while the fixed arrangement is arranged parallel to the table of the milling machine and fixed to the frame of the same connected is.

This equipment includes the fixed

Arrangement a holder 71 fastened to the frame 72 and arranged parallel to the table 73 of the milling machine, which the setting of a reproduction jig 74 allows the profile of which depends on the thread cutting work to be carried out changes. Such a gauge 74, for example made of sheet metal 2 to 3 mm thick, with a profile in the form of a continuous curve is designed in such a way that it allows the constant and constant change in the speed of the workpiece according to the desired change the pitch allows.

This arrangement, which is attached to the frame of the milling machine, is replaced by a second movable mechanical one Completed the arrangement, which is fixed to the table 73 the milling machine is connected and has a copy button 75 of known design, the trailing end of which is during the longitudinal stroke the movable arrangement is in constant contact with the profiled edge of the gauge 74 »

This button controls the movements

of a working cylinder 76, which is driven by a rack 77 is extended to which the dimensional changes of the gauge 74 are transferred. A gear 78 with interchangeable Gears receives the longitudinal movement of the rack 77 and forms it into a rotary movement with a continuously changing shape

009836/0457

vertigo > m .. _} which via ice gear ST on the cage

79 its differential 30 is transmitted. Within this cage, two revolvers with the same pitch circle diameter and the same number of teeth mesh with one another, the first planetary gear 82, which turns the sun gear 84 into rotation, which is firmly connected to the screw spindle 85, which moves the table 73 at a constant speed causes a drive means, not shown, transmits its movement to the second rotating wheel 83? which sets the output gear 36 of this differential 80 in rotation. These two rotating gears receive the constant drive speed via the cutting gear 34 and, in turn, transmit _9, since they are fixed to the cage 79 of the differential, on their not shown

80 connected axes are loosely rotatable, the constant constantly changing speed on the fixed with the sun gear 86 connected output shaft 87 of the differential.

This output shaft 87 transmits over

_s is a divider box 88 with a set of "/ on gears, which the average constant pitch of the screw to be manufactured is variable in accordance with 91, and the speed ratio determined according to the in the example described above ¥ explained else the you the sum formed by the differential 80 stemming θ Sssar.t Speed via a shaft 9G parallel to the axis of movement of the Si ropes 73 of the milling machine on a hanger hook 89. The Teilerdcoke attached to this table 73 receives the constantly changing rotational speed, which it transmits to the workpiece 91 j wsloliss swiselisii IClemsibaeksn at one of its ends ^r rcn & sn lowly shown to chuck CLSR divider Docke content 512 v / IIXL ;, ν ⁷ £, ΐ2Γ3ΐΐ-ί1 · 5: ί: tL ^ -i 3 5iiie; ii and si ⁰ s 3üd3 τοπ a likewise ^"-::: t3llt -i ^ :: -.-- ge..?": r ^ - "" - itcoL ::: pit3-2 i:;: "iij" it • i: lez Aoiisrich ".

modified

--_ 1 d-5 · t -, ": - / CJ-'r-h8-- ⁼ on 5" .J.ld31 ^; . ^: i ϊ. '' · 3Ϊ: -; ν- 2.1 S dVÜ'Sll ΘΪΪ15 BGlbst «

BATH ORIGINAL

Constant speed displacement and a variable speed displacement from a differential to be different. In addition, the I cam scanning can be used to generate a shift with variable speed by means other than hydraulic means.

Furthermore, the invention is applicable to the processing of any continuously changing surfaces, which are different from a screw thread, the The movement imparted to the blank can be different from a rotational movement.

009836/0457

Claims (1)

Patent claims:: 1 ») Machine for processing continuously * changeable surfaces, in particular, but not exclusively, of screw threads with variable pitch, characterized by devices (31, 32, 34 to. 45 he,. r ,, s / τ ,. % w ^for mutual displacement, or 86 to 89 (Fig. 4)) / a foalingT33) and a tool carrier (22, 23) with constant speed and Ad- ^. diermittel (46 »54 to 58 or 82, to 86), which to. To this constant speed add a speed that is constantly and continuously changing according to a certain spatial law. 2,) machine according to claim 1, marked ^ characterized by means (1 to 21) which are elastic; act and the displacement of a tool carrier erzeu- provide \ constricting power, and means (25 '61) of this shift form an execution enabling retractable stop, which is connected to the adding means (45, ^46, 55 to 57) is coupled and is withdrawn with a constant and continuously changing speed in accordance with the spatial law. . - "■■:" 5.) Machine according to claim 2, characterized in that an electric motor (1) with constant speed is coupled to a hydraulic pump (4) with a variable delivery rate, which in turn is connected to a hydraulic motor (8) through a switching distributor (6) which is connected to a supply line (7 or 9) * a return line (9 or 7) and a line (10) is provided for the return flow of the leakage currents, the pump (4) with variable delivery rate with a calibrated pressure relief valve (5) combined with training is made so that the hydraulic motor (8) has the power to make the displacement of one on the retractable Stop (25 »61) abutting movable body (22), e.g. a tool carrier, supplies. 4.) Machine according to claim. 3 »thereby characterized in that the movable body is a tool carrier slide (22) actuated by the hydraulic motor (8) _? the transmission between the tool carriage 009836/0487 (22) and the. Motor (8) contains a mechanical disengageable reversing and reduction device (14 to 18), the output shaft (19) of which carries a pinion (20) which is in engagement with a rack (21) which is attached to the tool carrier slide (22) _} which is provided with an open nut (25) which, at the limit of self-locking, cooperates with an associated screw spindle (61) which, together with this mirfci-er, forms the retractable stop " 5 ·) Machine according to claim 4, characterized in that the screw spindle (61). from a moving one Part C58) of a differential out of rotation becomes, in which another movable part (45) a movement is issued at a constant rate while .the third movable part (46, 56, 57) with a movement variable speed is granted, the algebraic Addition of this constant speed and this variable speed as the resultant of the desired spatial law corresponding constantly and continuously changing speed results. 6.) Machine according to claim 5, characterized in that that the second movable part (45) of the differential directly through a gear (43) with a one Spindle-bearing shaft (32) is connected, while the third movable part (46) of the same indirectly with this shaft (32) connected via a device for changing movement (48, 49, 51, 52, 53) which partially generates the spatial law is. "'-." "-" 7.) Machine according to claim 6, thereby characterized in that the device for changing movement has a crouch (48) which is connected by a gear (47) to the shaft (32) carrying the spindle, the cam track of this cam (48) cooperating with a copy button (49) which connected to a Kotor (51) which drives the third movable part (55, 46) of the differential via gears (52, 53) ;. . ^: 8 ..) machine according to claim 7, thereby marked that reduction gear or step-up gear with variable transfer behavior, in particular 009836/0457 . BATH their gears with interchangeable gears (14 to 18, 38 to 42 _y 45? 53? 6-0) _t between the hydraulic power motor (8;). "and." the corresponding pinion (20) of the rack (21), between the Motor (31) of the spindle-bearing shaft (32) and this shaft (32) between the spindle-bearing shaft (32) and the first moving part (44) of the differential, between the motor (51) of the probe and the third movable part (46) of the differential and between the stop screw head spindle (61) and the second movable part "(58) of the differential are arranged" 9 ») Machine according to claim 1 to 8, characterized characterized in that an adjustable stop (24) with the tool carrier slide (2-2) is combined that a with a reference member (34) cooperating with a pointer. who the spindle bearing shaft (32) is assigned, and that a controllable Coupling (62 to 64) between the screw spindle (61_b) and their, drive shaft (61a) is arranged. . - - ~ "'." - ■ 1G »), machine according to claim 1, characterized characterized j, "that the blank (91, Fig. 4). of the workpiece, which is carried by a movable table (73) cooperating with a drive _{screw spindle (85), is displaced in front of a fixed tool 9} with the screw spindle (85) with . the third movable part (84) of a differential is connected in order to drive the latter, while the second 'movable' part (86) of the differential is connected to a drive shaft (90) of a sub-dock (89) which the blank (91) on the table (73) ″ and the third movable part (79, 81) of the differential is coupled to the drive member (76) of a copier whose button (75) cooperates with a cam track of a lock (74), which on the is fixed frame (72) ,, when the probe is connected to the table (73), or which is inversely movable with the table (73) when the stylus (75) is stationary, the configuration is devised such ₉ that the Rotary movement of the blank (91) It becomes, which is the limited sum of the movement of the drive screw spindle (85) of the table- (73) which can be a movement with constant speed, and the movement with constant and continuous movement produced in the differential . BATH ORIGINAL - 00983670457 '. · variable speed which: from the motor (76); the copy supply is displayed, the button (75) of which follows the lock (74) is ₀ BAD ORiGfMAL 009836/0457 Lee on the side