DE976619C - Anti-aircraft computer - Google Patents

Description

Issued on the basis of the First Transitional Act of July 8, 1949

(WiGBl. P. 175)

FEDERAL REPUBLIC OF GERMANY

ISSUED JANUARY 16, 1964

GERMAN PATENT OFFICE

PATENT LETTERING

CLASS 72 f GROUP 15 05 INTERNAT. CLASS F 07h

N 13871 c / Tsf

N.V. Hollandse Signalapparaten, Hengelo (Netherlands)

Anti-aircraft computer

Patented in the territory of the Federal Republic of Germany on September 3, 1942 Patent application published February 2, 1956 Patent issued December 12, 1963

The priority of the application in the Netherlands of September 8, 1941 has been claimed The term of protection of the patent is extended according to Law No. 8 of the Allied High Commission

The invention relates to a lead computer for controlling anti-aircraft guns, which from the continuously supplied values of the elevation angle α and the lateral angle φ as well as the ascertained slope distance e to the respective measuring point Z _m under the assumption of constant flight altitude h both the lateral angle values Δoc and the elevation angle values Δφ of the lead and the spatial angular coordinates « _s and cp _{s of} the corresponding meeting point Z _t lying in the inclined distance e _s as well as the projectile flight time T to the point of impact and the attachment angle ω determined with the help of differentiators and closed gear circles. Devices of this type are known. They can be based on various calculation processes, each of which is based on the coordinates of the measuring point which are continuously determined by the target tracking.

First, the basics for the selected calculation process are explained. Show it Fig. Ι to 3 geometric representations, ao

4 shows the basic structure of a differentiator used in the exemplary embodiment of the computer,

Fig. 5 and 6 associated geometric representations, Fig. 7 a further development of the differentiator, 8 and 9 are geometrical representations. The goal may be along the lines in Fig. 1 in elevation and move the path s shown in plan in Fig. 2

309 791/2

and, at the point in time under consideration, are at point Z _w , the measuring point. The position of the measuring point in relation to the observation point B is determined by the lateral angle φ, the elevation angle α and the inclined distance e and the assumed constant height Ä, eu is the map distance of the measuring point, ie the horizontal projection of the inclined distance e. The sizes and φ can be continuously checked by one or more visors, e.g. B. a binocular telescopic sight, and the size e or h can be determined by one or more range finders or altimeters.

If, starting from the coordinates of the measuring point Z _m , the target is shot at, then Zt is the associated meeting point. Compared to observation point B, it has the coordinates tx _s = elevation angle to the meeting point, φ ₈ = lateral angle to the meeting point, e _s = inclined distance to the meeting point and h _s = height of the meeting point. T is the associated projectile flight time.

In the interest of angle and length fair presentation of the meeting point Zt containing height triangle, this is the containing plumb line folded to point B in the plane of the drawing in Fig ι., As well as from ι in Fig. And emerges 2 registered guides. The elevation angles κ and oi _s as well as the metric height h and - with a constant target height - the same height h _s are measured against the horizontal plane laid through point B. The lateral angles φ and q> _s are set against any horizontal direction BG, z. B. against the north direction or the line observation site - gun site, measured. If the distance between the observation point and the gun point exceeds a certain amount, the resulting parallax must be taken into account. Since the z. B. can happen in a known manner, it was not discussed in detail.

If the target speed vector assumed to be horizontal is broken down into two components in and perpendicular to the horizontal projection of the sight line BZ _m , the two components are obtained, which are referred to below as the horizontal approach speed EUn and the horizontal transverse speed SU . According to FIG. 3, which otherwise corresponds to FIG. 2, when multiplied by the projectile flight time T, these two components lead from the measuring point Z _m to the meeting point Tt.

Let the elevation angle lead be denoted by Δ κ and the lateral angle lead as Δφ. The following relationships can be read from FIGS. 1 to 3:

e _k = h * cotg ex-; h = constant;

EUn =

h dK

German

sin ² « dt '

at"

■ err da- ι

dt sin

CO (2)

SU

dm
= - ~ - e-

German

e · cos «;

HU = O;

ejc - e * cos κ; CsTc = ßs * cos a _s ;

. , dm _, e · cos «

sin / I95 = - ^ - · T

dt Cg ' cos Ks

(5) (6) (7)

(10)

e _s -cos «g. . άφ

sin Δ φ = ~ - · Γ;

e ' cos oi dt

6 · cos «-

there-
~ dT

B-T

cos Δ φ =

sin α

e _s · cos

(12)

2 ^ T

e _s · cos «s. ίΖί

Cos Δ φ = I:

& · Cos α sin 2 α

tgöc =

tg «s =

tg «« =

e · cos α

A.
e _s cos Oi ₈

β · cos α

• tg «.

(14) (15) (16)

e _s · cos ί
From equation (16) can be determined

/ e _s cos a _s \

oi _s = κ - \ - Δα - τ \ κ; .

\ e · cos κ j

Equations (ii), (13), (16) and (17) are the 105th Based on the device. From the equations (11) and (13) are determined

ι. Δφ, e _s · cos 1

2.

e · cos oi

From oi and

e _g cos
e · cos

the quantity a _{s is} determined according to equation (17). From Ks and h result

and further

ω = ■ fz (oi _g \ h).

T is the projectile flight time already mentioned above and ω the essay. Both are functions of sizes Oi ₈ and h, which can be taken from the firing tables.

According to the foregoing, the target side angle φ and the

Target altitude angle <% and also their derivatives -

German

there.

and - to determine. To determine the side

(Lt

angle φ and the elevation angle «are used in the usual way with directional optics. A gear unit called ίο differentiator is used to set this directional optics, which makes the straightening work much easier for the operator, ie it carries out the straightening work essentially automatically and also forms the time derivative of the lateral angle φ and the elevation angle κ . A differentiator is provided for the side adjustment and for the height adjustment of the directional optics. The individual differentiator consists of a speed-adjustable drive and a manual drive, which at the same time forms the control element for the output speed of the automatic drive and whose setting movement is superimposed on the output movement of the automatic drive in a differential. The resulting movement is fed to the directional optics.

Fig. 4 shows an embodiment of the differentiator. The speed adjustable automatic drive consists in a friction gear, the friction disc 1 of a motor 2 with constant Speed is driven and its friction roller 3 from the center of the friction disk 1 is adjustable radially on both sides. A shaft 4, on which the roller 3 with a wedge and Groove is guided longitudinally. To adjust the roller 3, a bearing fork 5 encompassing it is used, which is held on a nut 7 guided on a spindle 6. The spindle 6 carries at one end a handwheel 8 and its other end is connected to a differential 9 via a spur gear, which is also connected on the input side to the drive 4 of the friction gear. The output shaft 10 is via a worm gear 11 with the Directional telescope 12 coupled.

The above-mentioned observation point B lies on the vertical axis of rotation of the directional telescope 12.

For the sake of simplicity, it is assumed that the directional telescope 12 can only be rotated sideways and is accordingly used to track the target in the horizon plane. Let the target move along the path s and be at the point Z _n , the measuring point, at the point in time under consideration. The point Z _m thus moves along the path s.

For the purposes of the following, the beam determined by the optical axis of the telescopic sight is referred to as the directional beam and the beam passed through the point B and the measuring point Z _m or its horizontal projection as the aiming beam. The directional telescope must therefore always be set so that the directional beam coincides with the target beam and, as a result, the target is positioned sideways in the crosshairs of the telescopic sight. If this is not the case, as indicated in FIG. 5, an angle difference arises between the directional beam BR and the target beam BZ _m. The angle φ, ie the side angle of the target beam measured against the selected reference direction, is the side angle sought.

If the target beam moves at a constant angular speed and the friction gear is set accordingly, the aiming telescope 12 is continuously tracked to the target movement via the friction roller 3, the drive 4, the differential gear 9 and the gear parts 10, 11, without a difference between the target beam and the directional beam arose. If the target beam changes its angular velocity, there is a difference between the target beam and the directional beam (see FIG. 5). Two things then have to happen. On the one hand, the angular difference that has arisen must be eliminated, and the angular speed of the directional movement must also be set to the new angular speed of the target beam. Both tasks are solved simultaneously by operating the handwheel 8, because once the directional telescope 12 is corrected directly by the angular difference between the directional beam and the target beam via the handwheel 8, the spindle 6, the spur gear, the differential gear 9 and the gear parts 10, 11. Furthermore, however, the actuation of the handwheel 8 required for this also results in a corresponding change in the radial setting of the roller 3 with respect to the friction disk 1. The starting speed of the automatic drive formed by the friction gear and the motor 2 changes, in the correct sense, as you can easily see from the drawing. Because depending on whether the angular velocity of the target beam increases or decreases, there is a positive or negative angle difference between the target beam and the directional beam. As a result, the handwheel 8 is to be operated in one sense of rotation or the other to eliminate the angular difference, with the result that the output speed of the friction gear is increased or decreased accordingly.

So it is when the angular velocity of the target beam changes and the resulting beam Angular difference is eliminated via the handwheel 8, the friction gear automatically switches to the new one Angular speed set. The angular velocity of the target beam then remains for a while constant, the friction gear alone supplies the adjustment movement again after a short loading process for the rifle scope that keeps it in line with the target.

Let us now consider the case in which the movement of the target beam is not uniform, but rather with constant angular acceleration. At the beginning of the observation, let the lateral angle of the target ray equal φ ₀ , the angular velocity

equal - J ^ - and the angle assumed to be constant

acceleration equal to -T ^ r . In this case it can

the friction gear alone no longer supplies the adjustment movement, since the angular velocity is of the target beam changes continuously. The handwheel 8 must therefore also be adjusted continuously. Designated the angle transmitted from the handwheel 8 via the gear parts 6, 9, 10, 11 to the telescopic sight

with r and, accordingly, the angular velocity of this setting movement with -, then the relation generally applies

dw dr dt dt ^

(18)

This means: If the telescopic sight 12 is kept in line with the target, the angular speed of the telescopic sight is made up of two amounts, namely the angular speed -γ- that is directly applied via the handwheel 8

the movement transmitted by the telescopic sight and from the angular velocity of the movement transmitted by the friction gear to the telescopic sight. Its angular speed is linearly dependent on the angular position of the spindle 6 with respect to the zero position and can accordingly be set equal to b · r, where b is a gear constant resulting from the transmission ratio and the speed of the motor 2. After a short break-in period, as can be shown by a calculation that has been omitted here, for the dr

impacting size - = - can be set:

German

dr
It

(IQ)

It can be seen from equation (18) that if the angular velocity of the target beam is not constant, the Angular position of the spindle 6, measured against its zero position, is not a measure of the instantaneous Angular velocity of the target beam gives, but a measure of the angular velocity that leads to the

Side angle belongs to the target -r · second before the Observation. To convince yourself of this, note that the angular acceleration of the target ray is in the unit of time. So if, according to equation (19), the handwheel 8 directly Percentage of the transmitted to the riflescope

Total angular velocity - - times the part of

Angular acceleration makes up, the reverse is the angular velocity of the friction gear the movement transmitted by the telescopic sight 12 relative to the instantaneous value of the angular velocity of the target beam by - ^ - times the angular acceleration of the aiming beam remained. But that means that the angular velocity of the The movement transmitted from the friction gear to the telescopic sight represents the angular velocity

, represents that the aiming ray possessed - second before. 'δ

The angular position of the spindle 6 therefore does not reflect the instantaneous value of the angular velocity of the target beam, but - in the case of a constant angular acceleration of the target beam - the angular velocity that the target beam had before -r second

would have.

In general, it should be noted that if the angular velocity of the target beam is not uniform, the Spindle 6 represents the angular velocity sought with a certain time delay or that the variable guided by the spindle 6 is the angular velocity of the target beam for a previous one Time is.

This time delay can be neglected without causing excessive errors in many cases.

The invention is based on the object, in order to achieve greater accuracy of the calculation result, the time delay in the representation of the angular velocity sought avoid.

This time delay in the determination of the angular velocity of the target beam can be avoided eliminate the need for the angular velocity value guided by the spindle 6 to have the associated Searches for angular coordinates, thus values of angle and angular velocity that belong to one another receives and based on these values carries out the calculation. You get those that belong together Values of angle and angular velocity using the following approach:

According to FIG. 6, the aiming ray may have the lateral angle cp ₀ and after - seconds the lateral angle φ . Then the following applies assuming a constant angular acceleration

ψ = ψο +

ψ = Ψο +

[(d <Po_
J \ dt

df-

German

· F "

Ψ = Ψο + _Ύ ·

German

(20)

(21)

(22)

If b is chosen accordingly, the last term can be neglected. You then get

German

(23)

That means: Is the goal pursued with the help of the differentiator in the manner described above and If the telescopic sight is kept in line with the target, it belongs to that determined by the differentiator Angular speed that is generated by the spindle 6

leads and was designated above with - ~~ ,

ut

the angular coordinate φ ₀ = φ —τ -P ⁵ -.

Ό Cot

The same goes for the elevation angle. For the following, one denotes the one measured in the differentiator

Lateral angular velocity and elevation angular velocity for the sake of simplicity with - ^ - or - ^,

dt dt

so are the associated angular coordinates
τ df

^φ ~ Τ "ΪΓ

respectively

X -

dx

so the following values belong together:

άφ ι df

™ ~~ b '

φ -

German dx

German dx ~ dt

In order to avoid any misunderstandings, it should be emphasized again that φ and «are the angular coordinates of the target ray in these last-mentioned expressions, while - ^ - and ™ are the

dt dt

tiator formed (and thus temporally) previous angular velocity of the lateral angle or the Elevation angle is.

The values of angles that belong to one another and are determined by the above formulas and angular velocity can be obtained in a simple manner by the addition of the shown in FIG Differentiator according to FIG. 4. According to FIG. 7, of the

Differentiator the angular velocity - ~ which is in

Ct t

7 is represented by the symbol φ for the sake of simplicity, derived via the shaft 13 connected to the spindle 6 and the associated angular coordinate via a differential gear 15 connected on the one hand to the spindle 6 and on the other hand via the shaft 14 to the shaft 10. The differential gear 15

forms the difference f - - φ, i.e. that of the angle

e _s · cos «s

e -

de ~~ dt

■ cos

U-

dx

~ dT

sin j A f

e _s · cos

e -

de

"dt

dx

¹⁰⁰ TT -; .. *

- · cos M95 -j

tg Äs =

tg μ άφ It

dx ~ It

sm 2 \ x -

ι dx \

~~ Jt)

e _s cos X ₈ (25)

(26)

de \ I ι dx

—— ^cos 1 « τ" ~ jT

dt \ b dt

The invention consists in that using equations (24) through (26) above, a number Computing devices work together in the following way:

a) A first friction calculating gear in which the change in angular velocity φ over a

speed φ belonging angular coordinate, and forwards this variable on the shaft 16 on. Of the

Factor - is determined by the appropriate choice of the gear ratio considered.

One of the arrangement according to FIG. 7, the same arrangement can be used for the vertical directional movement, that is, to determine the elevation angular velocity - £ - and the

German

associated angular coordinate χ - _; —— used

will.

The above-mentioned angular coordinates and angular velocities, as explained, do not relate to the respective measuring point Z _n ,

but on a temporal -j- second before the

Target trajectory point Z _mv lying at _{measuring point Z m} , as shown in FIGS. 8 and 9 corresponding to the representation of FIGS. 1 and 2. However, correct results are obtained if the calculation is not based on the measuring point Z _m but on the point Z _mv .

The formulas obviously remain the same as stated above, with the only difference that

instead of φ and χ the quantities φ - \ · ~~~ or χ - \ - · ~ '' b dt b dt

are to be introduced. Furthermore, instead of the projectile flight time T, in which, as is known, the destination is the distance from

Z _m to currently races to the size T -f - introduce:

because this quantity T -f- -r is the time that is the goal

Due to the cables of the distance of Z _mv to meeting currently needed. As can be overlooked, the quantities Αφ, Aa and e are also replaced by quantities . ι dw 1 μ ι dot- 1 ι de

If one introduces the aforementioned quantities into equations (11), (13) and (16), they go over to

ι df \ df ~ b Jt) ⁼⁼ lit

(24)

hand-driven shaft is introduced, while the second input of this gearbox is a constant Has speed, a first addition device is assigned to the movement of the output of the first friction calculator is added to that of the hand-operated shaft

and with its output the movement of the target perception device around its lateral angle axis controls.

b) The angular position of the hand-operated shaft of the first friction calculator and the projectile flight time T are fed to a first multiplication device which delivers the product φ · ir + ~).

c) A second friction calculation gear, in which the change in angular velocity ά over a hand-operated shaft is introduced while the second input of this gearbox has a constant speed, a second addition device is assigned which the movement of the output of the second friction calculator to that of the hand-operated Wave added and with its output the movement of the ornamental perception device controls around its vertical axis.

d) The angular position of the hand-driven shaft of the second friction calculator and the projectile flight time T are sent to a second multiplication device which delivers the product Si · (Τ + ~).

e) This value and the value α · «determined with the aid of a third addition device, which is supplied on the one hand to the elevation angle κ of the target perception device and on the other hand to the movement of the hand-operated shaft of the second friction calculating gear, is received by a curve body calculating device and calculates it

ι - ·

sin 2 «-

¹ Oi

f) A sine-cosine calculator receives this value and the value q>'\ T - \ - r \ supplied by the first multiplication device and calculates it therefrom

e - e

cos I Oi -

■ Oi

and

g) This last-mentioned value is added by a fourth addition device to the value φ - φ and obtained by means of a fifth addition device, which is supplied on the one hand with the lateral angle φ of the target perception device and, on the other hand, the movement of the hand-operated shaft of the first friction calculator

returns the angle to the point of contact <p _s . h) A cam gear receives e _s · cos oig

e -

■ Oi

Oi

■ -r'öi and returns the value

Value Δ oi + - · «to which the curve

body arithmetic device supplied value κ - τ- 'Si and supplies the elevation angle to the

χ λ ι

from the sine-cosine calculator and the value fed to the calculator for β

+ ■ i-.ά. i) A sixth addition device adds this

point oi _s .

k) Another cam mechanism receives this value of the elevation angle oi _s to the meeting point Zf as well as the target altitude h and supplies the value for the projectile flight time T and the attachment angle ω fed to the two multiplication devices.

1) A seventh adding device adds this attachment angle ω to the calculated value of the elevation angle oe _s to the point of contact.

The equations (24) to (26) can be simplified by the fact that during the measurement delay occurring changes of e and α are neglected. So you get

&s' COS Ois

e · cos oi

e _s cos 1
e cos 1

sin \ Δφ + -ϊ- ■ cos {Αφ + -η- · dt j ~ dt '\ "*" δ ·'

dw \ - = dt = ι

there-

sin2 [oi -

dot ~ dt

(27)

(28)

e _s cos oi _s β ' cos oi (29)

One selects, as it has proven to be practical, the gear constant b = 2 and sets this

COS OCs e · COS OC e _s - cos a _s

sin [Αφ +

e · cos κ

cos

[δ _ψ

αφ

It) value in equations (27) to (29), these go into

(30)

German

^d "!? + I

sm2 [oc -

ι doc \ '

tgtXg = ^ ~

e _s cos oc _s e cos κ (31)

(33)

The calculator can be based on equations (24) to (26) or (27) to (29). The lead computer shown in FIG. 10 is based - according to the entered calculation variables - on equations (30) to (32).

Fig. 10 shows the computer according to the invention and at the same time the target column with the directional optics

^a 5 installation site of the device forms point B (Fig. i, 2,3,8,9). On a horizontally erected foot with a column 20, the upper part 21 containing the directional optics and the computing gears is rotatably mounted on the side, preferably, as indicated at 22 in the drawing, with the aid of a ball bearing. The directional optics consists of two binocular directional telescopes 23 and 24, the latter of which is only partially shown in FIG. 10. The two directional telescopes have a common elevation axis 25, which is mounted on the upper part 21.

For lateral adjustment, the upper part 21 is rotated sideways relative to the fixed column 20. This lateral setting and also the height setting are each made via a differentiator as shown in FIG. 4 and 7 causes the design shown. As shown, these two differentiators can have a common Assign friction disk 26. It is driven by a motor 27 at constant speed. The friction roller 28 of the one differentiator which is in engagement with the friction disk 26 has a wedge and groove on the shaft 29 forming the output is guided and is longitudinally displaceable, but not rotatable Via the fork 30 encompassing them and the traveling nut which carries this fork and is guided on the spindle 31 32 via the shaft 33 connected to the spindle 31 and the handwheel 34 coupled to it set. The shaft 29 and that coupled to the motor 27 and accordingly at constant speed driven shaft 35 work on a differential 36, the output shaft of which is denoted by 37. The movements of the shaft 35 and the shaft 29 are superimposed on the differential 36, namely subtractive, so that the shaft 37 comes to a standstill when the shaft 29 and 35 rotate with the same amount of rotation transmitted to the differential 36 or its output shaft 37. As a result of corresponding When selecting the transmission ratios, the shaft 37 is at a standstill when the friction roller 28 is approximately in the position shown Position is, so about a quarter of the diameter of the friction disk 26 from their Center is deflected. This position in which the resulting movement on the shaft 37 is zero is the zero position of the differentiator. If from this zero position the friction roller 28 in one or deflected in another sense along the shaft 29 extending radially with respect to the friction disk 26, it then rotates the shaft 37 at a speed proportional to the deflection of the roller 28. The insertion of the Differential 36 and the shaft 35 thus only serves the purpose of the zero point of the friction roller 28 from the To relocate the center of the friction disc 26, so that, as shown, this friction disc two differentiators can be together.

The friction roller of the second differentiator is denoted by 38; it is with wedge and groove on the output forming shaft 39 extending radially to the friction disk 26 is longitudinally displaceable, but not guided in a rotatable manner and is adjusted by a fork 41 held on a traveling nut 40. the Traveling nut 40 is in turn guided on the spindle 42 and is connected to it via this Shaft 43 and the handwheel 44 coupled to it are set.

The movements of the shafts 39 and 35 are summarized in the differential 45 subtractively. the resulting movement is transmitted from the output shaft 46 of the differential 45. The differential 45 serves the same purpose as the differential 36. It thus effects in connection with its connection to the shaft 35 that the zero point of the differentiator containing the friction roller 38 is outside the center the friction disc is located, namely by about a quarter of the diameter of this friction disc.

The shaft 37 and the handwheel 34 work on the differential 47, the output shaft of which is denoted by 48 is. Accordingly, the handwheel 44 and the shaft 46 are connected to a differential 49, the output shaft of which is denoted by 50. The two differentials 47 and 49 have within the associated differentiator the same task as the differential 9 in that shown in Fig. 4 or 7 and already above described differentiator. It is thus in the differential 47 and also in the differential 49 the output movement guided by the shaft 37 and 46, respectively

of the associated friction gear combined with the movement of the handwheel 34 and 44, respectively.

The shaft 48 is via a spur gear, a shaft

51, a second spur gear and a shaft 52 a pinion 53 is switched, which meshes with a ring gear 54 attached to the column 20. Since the Shafts 52 and 51 are mounted on the upper part 21, so has a rotational movement transmitted to the pinion 53 via the parts 48, 51 and 52 with the result that the entire Upper part rotates sideways around the column 20 at rest.

The shaft 50 is on a spur gear, a shaft 55, a bevel gear, a shaft 56 on Connected to this shaft attached pinion 57, which is in engagement with a fixed to the leveling axis 25 Dental arch 58 is standing. A rotary movement of the shaft 50 is therefore via the gear parts 55, 56, 57, 58 transferred to the vertical alignment axis 25.

According to the foregoing, the handwheel 34 is the side handwheel to be operated by the elevation judge, the handwheel 44 is the elevation handwheel to be operated by the elevation judge. These two operators, one of whom observes the target via the directional telescope 23 and the other observes the target via the directional telescope 24, operate the handwheels 34 and 44 continuously so that the target is in the crosshairs of the directional optics 23, 24 remains, so that with reference to FIGS. 4 and 5, the directional beam BR is always in congruence with the target beam BZ _m . Then the shaft 48 guides the lateral angle φ relating to the measuring point Z _m (see also FIGS. 8 and 9) and the shaft 50 the elevation angle relating to the measuring point Z _m. At the same time, the shaft 33 carries the one relating to the point Z _mv (see FIGS. 8 and 9)

Lateral angular velocity -— ■ and the WeEe 43 die

German

Elevation angular velocity referring to the same point -. The to these angular velocities

Cb t

at

there.

associated angle coordinates

b - 2 - according to the above φ - - · - % - or <x - ⁰ '2 dt _

It should also be mentioned here that because of the abbreviation in the drawing instead of -— and ~~ , ά and ψ are used.

German

α, φ

The mentioned quantity φ ~ - is given in the difference

rential 59, the output shaft of which is denoted by 6o, formed, including on the input side on the one hand on the shaft 48 and on the other hand via the shafts 61 and 62

connected to the shaft 33 leading to the size

(Lt

is. To form the size « - the difference

2 (Lt

rential 63; it is on the input side of the shaft 50 and also on shafts 64 and 65 to size -r-

(L t

leading shaft 43 connected. 66 is the output shaft of the differential 63. As will become apparent from the following explanation, the shaft 67 continuously carries the projectile flight time T. The shafts 68 and 69 are connected to the shaft 67. The former also has the projectile flight time T, while the latter, due to the appropriate choice of its starting position relative to the shaft 67, has the quantity T + η- or in the fore

lying case in which & = 2, the quantity T + - -.

This variable is a multiplication gear via the shaft 70 71 and 72 respectively. The multiplication gear 71 is via its second input shaft 73 connected to the shaft 65 and thus receives

and thus delivers output

(Lt

( T + -). These

of this size the

side on the shaft 74 the size

Size is fed to a cam gear 75 on the input side, which also has the

Shaft 66 coupled shaft 76 the size α -

receives and on the output side via the shaft 77 the size

* Ίΐ ^ΛΤ

I ι d (x \

■ in 2 cc · ---: - 1

\ 2

sm.2

it)

supplies. One overlooks the fact that this expression is a function of the two arguments

iÜOC

~ dT

T + - ¹ -1 and α ² /

doc

and as a result, depending on these two arguments, can be continuously formed by a cam gear.
The multiplication gear 72 forms from the over

the wave 70 supplied variable T - \ and from the

via the second input shaft 78 supplied size - ~

(Lt

the product -Jj- · (Τ + - J and transfers this quantity

the output shaft 79 to a switching mechanism 80. This is also on the input side via the shaft 81 to the Output member of a sine-cosine gear 82 connected. The switching mechanism 80 controls a motor 83, in such a way that when the quantities supplied via the shafts 79 and 81 are the same, the motor 83 comes to a standstill and in the case of positive or negative differences between these two variables, the motor 83 in one way or the other Sense is switched on until the relevant difference is eliminated. The motor 83 operates via the shaft 84 onto a shaft 85, one end of which is connected to one input element of the sine-cosine gear 82 is. With its second input element, this sine-cosine gear is connected to the shaft 86, which in turn is coupled with a motor 87. This motor is powered by a rear derailleur 88 controlled, on the one hand to the already mentioned output shaft 77 of the cam gear 75 and on the other hand connected via the shaft 89 to the second output element of the sine-cosine gear 82 is.

In the sine-cosine gear 82, the angle is introduced via the shaft 85 and the amount of the vector is introduced via the shaft 86, which is broken down in the sine-cosine gear 82 into its sine and cosine components. The sine component is derived via shaft 81 and the cosine component via shaft 89. According to what has been said above, the quantities fed to the sine-cosine gear 82 via the motors 83 and 87 are still unknown, apart from the fact that the motor 83 introduces the angle and the motor 87 the absolute value of the vector to be broken down. On the other hand, it can be seen from the foregoing that the motors 83 and 87 are controlled by the associated switching mechanisms 80 and 88 so that the input waves of these switching mechanisms lead the same sizes. So the sine component to be removed from the sine-cosine gear 82 via the shaft 81 must be equal to the variable carried by the shaft 79 and the cosine component to be derived from the shaft 89 from the sine-cosine gear 82 must be the same as the variable carried by the shaft ¹ Jj be. Now this latter quantity represents the right-hand side of equation (31) and the quantity carried by shaft 79 represents the right-hand side of equation (30), so shaft 81 must be the left-hand side of equation (30) and shaft 89 the left-hand side Side of equation (31) lead. If one compares the left-hand sides of these two equations (30) and (31) with one another, one sees that they are in fact divided by a sine-cosine

represent drives by adding the quantity Δφ- \ ■ -jr

the angle and the size -

-the amount of the too

e · cos «

decomposing vector forms. It follows from this that the motor 83 and the gear parts coupled linearly with it have the size Aw + - · - ~ and the motor 87 and the

2 (dd

with it linearly coupled gear parts the quantity e _s · cos <Xs j -.- T.

__? ί_ drove.

e cos oc

The controls 80, 83 and 87, 88 together with the sine-cosine gear 82 and the right sides of the two equations (30) and (31) leading shafts 79 and 77 thus represent a gear arrangement , with the help of which the system of equations (30) and

(31) with regard to the two unknowns Aw H

"2,

and _f_ fgelöst _au. That of the shaft 85 e · cos oc °

The guided variable Αφ + - · —y- is fed to a differential 90, which also receives the variable φ · - ~ via the shaft 60. The two input variables

are combined additively in the differential 90, so that its output shaft 91 φ, the sum + Αφ leads, which - with a corresponding count, ie sign choice of size Δ ψ - of Figure 2 equal to the size φ _8, that is equal to the azimuth angle to the meeting point Zt. is. In the differential 92, which is connected on the one hand to the shaft 91 and on the other hand via the shaft 93 to a rotary knob, a command correction to be made by the display device 95 can be superimposed on this variable. The output shaft 96 of the differential 92 therefore carries the quantity 9 , which is possibly superimposed with a command correction φ &? _s ; it can be read on a coupled to the shaft 96 and indicated at 97 display device and by telephone or via a remote transmission system whose z. B. two-part encoder is coupled to the shaft 96 and is indicated at 98, are transmitted to the guns.

The quantity carried by the motor 87 lil ^ l ^ L ·

e · cos et

becomes a cam gear via shafts 99 and 100 101 supplied, which is also via the shaft

66, the shaft 76 and the shaft 102 are given the size χ - - · - and the size via the output shaft 103

Aa -J · -j- supplies to the switching mechanism 104. This

2 German ~

controls the motor 105 connected to the second input shaft 106 of the switching mechanism 104 is linearly coupled. The parts 104 to 106 provide a follow-up control which simulates the quantity guided by the wave 103 with energy. The shaft 106, which thus the

Quantity Ax + - ■ · - ^ - leads, is to a differential 107

connected, which is also connected on the input side to the shaft 66 and on the output side via the Wave 108 is the sum of the input variables, that is

dx

~ Jf

dx

supplies (see. Fig. 1 and 8).

The cam gear 101 is based on equation (32). If this equation were applied directly, x _s would be obtained as the output variable of the cam gear 101. In the illustrated embodiment, the cam gear 101 is based on the following development resulting from equation (32):

- Λ

ι dx \ __

dx .
Jf)

e _s cos oc e cos ix

■ - Α

Ι doc \

(33)

From Fig. 8 one reads

- x -

there

) = Δχ + - dt j

HJ

(34)

309 791/2

If you insert this value into equation (33), it changes into

A <x

there-

= arc tg doi
It

e _s cos <x β cos (X

d <x \
IT) '

(35)

This equation, in which the quantities <x 7r

2 at

e _s cos (Xs e ' cos α

the independent variables are,

is based on the cam gear ιοί. This has the advantage over the direct application of equation (32) that a part of the total value of the size <x _{s is taken} from the shaft 66 and thus the cam gear 101 only has to supply the remainder, which is important for the design and operation of the Cam body gear 101 is advantageous.

As already mentioned, the projectile flight time T is calculated as a function of the quantity h and the quantity « _s. A drum 109 is used to determine or introduce the variable Ji , which contains curves of constant distance on its circumference in an ^a 5 ' rectangular coordinate system depending on the variables tx and Ji , i.e. the relationship between the three variables e, α and Ji in the form of a family of curves. For each curve of this family of curves, the associated distance value, z. B. 21 hm, 22 hm etc., added. The rotatably mounted drum 109 is rotated via a rotary knob 110 according to one coordinate, namely according to Ji . Parallel to the drum axis, a pointer is longitudinally displaceable via a spindle 112 connected to the shaft 56 according to the second coordinate, namely according to the size <x. If the variable h were known and it were inserted after the display device 113 coupled to the rotary knob 110, then the pointer in, which is automatically set according to the variable λ, would indicate the respective inclined distance e of the target on the family of curves. Conversely, one can also use h after ex. and determine 0. That is done here. The slant distance e is measured with the aid of a range finder. The curve of the family of curves located on the drum 109, which corresponds to the measured distance value, is set using the rotary knob 110 under the tip of the pointer in; then the axis of the drum 109 has the size Ji. The setting is compared from time to time with the results of the distance measurements and corrected if necessary.

The arrangement for introducing the quantity Ji is very simple and very advantageous for performing the calculation, since the computer can work continuously, although the distance e can only be determined intermittently. The variable Ji guided by the axis of the drum 109 is displayed by the display device 113 and, via the shaft 114 coupled to the drum axis, is fed to a switching mechanism 115 which controls a motor 116. This is via the shafts 67 and 68 and shaft 116 already mentioned above

switched to a cam gear 117, which is also adjusted via the shafts 108, 118 and 119 according to the size «s. The output value of the cam gear 117 reaches the switching mechanism 115 via the shaft 120. This keeps the motor 116 switched off if the input variables supplied by the shafts 114 and 120 are the same and the motor 116 in one or the other direction of rotation if the two input variables are positive or negative switched on. The functional surface of the cam mechanism 117 is designed on the basis of the target table in such a way that it delivers the size Ji as a function of the size tx _s and the size T. Here, however, the quantity T forms the unknown; it is determined by the transmission connection shown. Since the motor 116 is controlled via the switching mechanism 115 in such a way that the shaft 120 also carries the variable h guided by the shaft 114, the shaft 67 must necessarily carry the desired variable T.

A second cam gear 121 is connected on the input side to the shaft 67 leading to size T according to the above and to the shaft 119 leading to size <x _s; via its output shaft 122, it supplies the attachment angle ω as a function of the quantities T and <x _s. It was said above in connection with equations (1) to (17) that the quantity ω results as a function of the quantities oc _s and h . Instead, as has happened here, ω can be represented as a function of the quantity oc _s and T , since T is a function of <x _s and Ji . The gear arrangement selected in the exemplary embodiment for determining the quantities T and ω has the advantage that the setting quantities for the two cam gears i ° 5 117 and 121 are taken from gear parts on which a sufficient torque is available.

The top angle ω guided by the shaft 122 is added to the angle <x _s n ° guided by the shaft 108 in the differential 123. If necessary, a command correction 8β is superimposed on this sum in a further differential 124, which is introduced via the rotary knob 125 and the shaft 126 after the display device 127 coupled to it. The tube elevation ε guided by the output shaft 128 of the differential 124 is thus obtained. This size is passed on to the guns via the, for example, two-part transmitter 129 of an electrical transmission system coupled to the shaft 128 and for control and any telephone transmission by a z. B. also two-part, coupled to the shaft 128 display device 130 is displayed.

If the guns are adjusted automatically with the help of motors and are used for this purpose controls

used, in which, as is known per se, the engine speed according to the lateral angular velocity or elevation angular velocity is controlled, these control variables can also be taken from the Computer can be derived, since the shaft 65 the altitude angular velocity and the shaft 62 the Lateral angular velocity leads. For this purpose, as indicated at 131 and 132, the shaft 62 and 65, respectively a regulating body, e.g. B. a voltage divider or a resistor, coupled.

Regarding equations (1) to (35), it should also be noted that the individual quantities must be introduced with the correct signs or the positive and accordingly the negative direction should be selected accordingly. So is z. B. to choose the count of the quantity Δ ψ of equation (30) so that this quantity is negative in the case of FIG. 2, as can be seen by comparing equation (30) with FIG. This example should also explain the remaining equations with regard to this point.

The various controls, e.g. B. 88, Sj and 80, 83 etc., can be carried out in the manner of the known follow-up controls. Preferably electrical controls are used, e.g. B. according to the structure shown in FIG. 200 is the motor, a DC motor. Its field winding 201 consists of two parts which are connected to the current source 203 via the switching device 202 and the armature in the manner shown in FIG. 11. The switching device 202 comprises a rotatably mounted switching arm 204 which is coupled to the shaft 205 and cooperates with two contact segments 206 and 207. These are attached to a disc 208 which is rotatably mounted on the same axis as the switching arm 204 and which is coupled to a shaft 209. Depending on whether the switching arm 204 makes contact at 206 or 207, the motor runs in one direction or the other, namely until the switching arm 204 has returned to the zero position with respect to the two contact segments 206, 207. The two 6g waves 205 and 209 correspond, for. B. with respect to the controller 88, 87 of FIG. 10, the shafts yy and 89, while the motor 200 corresponds to the motor 83 in this case.

If you couple the shaft of the motor 200 with one of the shafts 205 and 209, z. B. with the shaft 209, so the control shown in Fig. 11 forms a follow-up control, d. H. a control that a predetermined movement carried out by the shaft 205 with Replicates energy. FIG. 11 only shows one of the possible controls more or less schematically point out. Of course, the more sophisticated types of these controls, e.g. B. after patent 631,665, can be used. Follow-up controls are also within the computer according to Fig. 10 can be used to relieve the load on the individual computing gear.

Only the combination of all features mentioned in the patent claim is protected.

Claims (1)

Claim. Lead computer for controlling anti-aircraft guns, which from the continuously supplied values of the elevation angle α and the lateral angle φ as well as the ascertained incline distance e to the respective measuring point Zm under the assumption of constant flight altitude h both the lateral angle values Δ κ and the elevation angle values Δ φ of the lead and the spatial angular coordinates ks and cps of the corresponding meeting point Zt lying in the inclined distance es as well as the projectile flight time T to the point of impact and the attachment angle ω are determined with the aid of differentiators and closed gear circles using the following equations, cos ι Λ / ι e - · e · Cos \ K - · κ Cs 'COS Ks ϊ Λ / Γ "e-τ- · e · cos« - · κ 0 \ bbf' cos (Δ φ + -j- · ψ j = ι sm 2 · I « tg KS - tg [oc - ι Λ / ι - · e · cos ix r- · κ b J \ b es - cos according to which several computing devices work together in the following way: a) A first friction computing gear (28 to 32) into which the change in angular speed t ψ is introduced via a hand-operated shaft (33), while the second input (26) of this gear has a constant speed, a first addition device (47) is assigned, which the movement of the output (37) of the first friction calculating gear to that of the hand-operated Shaft (33) is added and with its output (48) controls the movement of the target perception device (23, 24) about its lateral angle axis. b) The angular position of the hand-operated shaft (33) of the first friction calculating gear (28 to 32) and the projectile holding time T are sent to a first multiplication device (72) which delivers the product φ · ΙΓ + -Η. c) A second friction calculating gear (38 to 42), into which the change in angular speed α is introduced via a hand-operated shaft (43), while the second input (26) of this gear has a constant speed, is assigned a second addition device (49) , which adds the movement of the output (46) of the second friction calculator to that of the hand-operated WeEe (43) and controls with its output (50) the movement of the target perception device (23, 24) about its vertical axis (25). d) The angular position of the hand-operated shaft (43) of the second friction calculating gear (38 to 42) and the projectile flight time Γ are fed to a second multiplication device (71) which delivers the product ά · ΙΓ + -τ-). e) This value and the value a determined with the aid of a third addition device (63), which is fed on the one hand to the elevation angle α of the target perception device and on the other hand to the movement of the hand-operated shaft (43) of the second friction calculating gear, is received by a cam calculating device (75) ) and from this calculates 2 «· Γ i. SU12 · «- κ f) A sine-cosine calculator (82) receives this value and the value φ · (τ + γ \) supplied by the first multiplication device (72) and uses it to calculate it · cos Oi5. E \ · cos [κ = - Friction calculator is supplied, obtained value ψ -τ- · ψ and supplies the lateral angle to the point of contact <ps. h) A cam gear (101) receives it · cos Ks cos α - from the sine-cosine calculator (82) and the value Δα + -τ- · ■ ~ · Si supplied to the calculator (75) and delivers the value 0 In Documents considered: German Patent Specifications No. 613 619, 631 665; VDI-Zeitschrift, Vol. 82, 1938, pp. 1277 to 1281. i) A sixth addition device (107) adds this value Δ α + -, - · Si to the value Oi -r which is also fed to the "0 curve body calculator (75) - · ά and returns the elevation δ angle to the meeting point ois. k) Another cam gear (121) receives this value of the elevation angle txs to the point of impact Zt as well as the target altitude h and supplies the value for the projectile flight time T and the attachment angle ω fed to the two multiplying devices. 1) A seventh adding device (123) adds this attachment angle ω to the calculated value of the elevation angle oi _s at the point of contact. For this purpose 2 sheets of drawings © 509 656/352 1.56 (309 791/2 1.64)