DE1528372A1 - Cam drive for piston engines - Google Patents

Description

Patent attorney Dipl.-Phys. Gerhard Liedl 8 Munich 22 Steinsdorfstr. 21-22 Tel. 29 84

(- B 80 070 Ic / 59a) A 2291

Logo

BOULTON PAULAIRCRAFT LIMITED; Pendefond Lane, Codsall, nr Wolverhampton, STAFFORDSHIRE / ENGLAND

Cam drive for piston machines

The invention relates to a cam drive for piston machines with a relative Cylinder arrangement moved to the cam drive, in which η piston is displaceable are guided and with a curve guide controlling the Koiben movement, whose running surface S has identical sections, where S is a whole Number is and the number of strokes of a piston during a full cycle of movement Cylinder arrangement corresponds to the curve guide and with one half of the curve developed as a mirror image of the other and in a number is subdivided by sections, each of which corresponds to the arc lengths of around the middle correspond to a construction base circle plotted angles, in particular

009836/0178 ϊ © omgimal "

(Alt. 7 £ Ι / Λα. 2 no. T sentence 4 d «6 amendment qoe. W. 9.19SJI

according to patent (patent application km- P 11 53 -1-11.9 / B 70; ϊ <> 5 Ic / 59a).

The main patent proposes a cam drive of the type mentioned at the beginning with the restriction to Radiaikolbenmaschim-n, in which accordingly a cylinder star that is rehitely surrounded by a control pin, in which η pistons are guided radially displaceably, and a piston guide pin as a curve guide are provided. The contour of the piston guide ring is also designed as a mirror image and divided into three subsections, each extending over angles plotted around the Mir.e of the ring. Whereby with one size the angle of the partial intervals of δ 1 '' and '- the first and the third partial segment through circular arcs around the center of the ring with the radii CR and CRgebik: -! are, while the civil section is formed by a spiral curve, the radius of which, emanating from the center of the ring, has the size -R (- * - am - ί where C! J ₅ £ and ^α wit- are defined as follows:

C is the length of a m der. "Ime des Spir-albogi ...- from d-jr ring center to Spiral drawn radius street was called.

R is the stroke of the pistons in the :: κϊone than C,

L is the parameter angle l: r_ the center of the ring v..n nnem in the center of the spiral arc radius st κ. ·:;: /.U a wide range. -he spiral cutting radar beam in the range voii <to ^J

η is an integer _; the i;:, hi is less than 5, Cc is determined by the equation

Sa- in - 1). _1 if ::. odd is bsv .. 2n

S -ι (η - 2). _ if η is even.
2η

η and S have no common factor greater than 1 uiul if η and S are both even numbers, so that 2 and 'J have no common factor greater than 1, then ' 2 is an odd number greater than .'i.

Through this fixation of the contour of the piston guide ring, which controls the movement, the task is solved of keeping the ratio of the liquid flow rate / ur angular velocity to the volume of the frame piston shaft constant at every rotary position, so that in the case of an "ir ■ ri ^ mix »With the same rotational speed, the instantaneous conveyance duck is not subject to any fluctuations, while ίκι ι in the motor under the \ on.ussetzunu. that equal amounts of liquid in the inlet are du i \ -hge / t μ nk: i. An unchanged angular velocity achieves vmiiI.

For the cam drive described above, the condition is that the number of pistons η should not be less than .1 gi because rl. It is the object of the present invention to propose a cam drive of the type mentioned at the beginning, which, as well as the cam drive described above, has a constant ratio of the fluidity rate to the angular speed of the rotating part of a piston machine, but also means that it can be used on piston machines with one piston drive. ahl bn down / ι η : i enables. This task is solved by the fact that the first and the fifth of five subsections by circular arcs around the; The center of the construction base circle are formed with or correspond to the radii CR and CR, while the second and fourth subsections are formed by or correspond to a spiral, whose radius beam emanating from the center of the construction base circle has the size

009836/0178 ^

BAD ORiGlMAt

«R

and the third sub-section is formed by or corresponds to a spiral curve, the radius of which emanating from the center of the construction base circle is CR. "" 3, said C, R, _j Δ 0 P _U nd are defined as follows:

C is the length of one in the middle of the drift section (spiral arc) drawn from the center point of the constituency circle to the spiral arc Radius beam,

R is the stroke dor piston and smaller than C,

Δ is the parameter angle around the center point of the construction base circle from a radius ray lying in the middle of the third subsection (spiral arc) to another radius ray intersecting the spiral in the range from -J to · ' ^x .

c defines the third sub-section ranging from -i to -3 within the range from - 1 to χ,

where Ji and β are determined by the number of pistons η according to the conditions in the following table:

009836/0178

TABLE 1

δ> O η even> 6 α = δ =

β = O η odd "^ 5 α =" - δ =

Π δ = O, α = -f-

β = 0, η even>, 4

III δ = O, α = f η = 6 P = T "

β> O, η even ~> / 8 β = or ---

η + 1 part- _β 7t_

τ ν «^ bar by 4, 2 η η odd ^ -3

η + 3 part- _ß _ _3π

bar by 4, 2η

IVÖ> 0, α = 5-δ / ~ ... ο ^ χϊλ. η -4 (η divisible β = - + δ, ^ΛΑ

,. _Λ / through 4 η even ^ 6

η + 2 divisible = π _Γ "^ η -2 by 4"

β> O Γη + 1 divisible β = ^ + δ, δ <· Π

η odd) 3 7 through 4

η + 3 divisible β »ττ— + δ, δ <- ^. π

,,, 2η 4η

by 4

009836/0178 _Dym

BATH ORIGINAL

- 1)

It can be seen that the mathematical definition given above of the contour of the curve guide by special choice of the width ; ^{J contains} the contour of the Kolbtmirungsi inges described in the main patent. However, the definition continues to show. that if; - differs from zero »the minimum number η of pistons that can be used b / .w. Z \ alleviate aul Ά can be lowered.

For the sake of simplicity, the following is a description of the essential Sizes in the basic design circle on which the curve contour is based went out.

In the curve guidance according to the present invention, Yer.veilsectors can be vorgtse'-rm within which ~, (C ί «Δ)} - O applies, while those b.rt-v "η aui the curve: ~ guiding along the curve contour are provided, which lie outside this Verveilsectors. The area lying within the limits - β and β corresponds to a spiral point in which the change in the length of the radial beam with the Parameter angle A, τ. (CM (A)) a constant 2R; ··. ^; -it. As already mentioned above, the curve guide contour proposed by the invention is based on a base circle with radius C, from which the length of the radius beam under the parameter angle Δ is determined as a value C - f (Δ). '. is thus dt r measured angle of rotation in the grand circle starting from a reference line, and the following relationships apply in the base circle within the individual subsections:

- i door - I ^ Δν < - a

-Δ + β - - ^ sin ^^ | _T n <'for-α <Δ <- β

009S36 / Q178

iia) 2 R. for - έ =>'<

3-3

R., -,.,. ± Zi_ sin ^ 4.u <for : i <Λ · 'α

■ - η ι-ρ

R for! ν ^ < ^

Where!"·! you · big ones are already defined above.

When using the curve guide contour according to the present invention, the curve guide takes the form of a toothed rack, lni de! the values of f (A) related to the base circle are deviated from the length of the rack. ^. where r is C · f (Δ), immediately as Cartesian cooninates y. χ considered and plotted on the abscissa axis the arc lengths corresponding to ^{the angles α, ″ i'iitspreenden.}

If the curve guidance according to the invention is fixed on piston machines in an axial design, the values of 1 (>) are corresponding to the timing diagonal coordinates, r, ^. /. where, starting from the cartesian coordinates y, χ for curve guides of Sohubkolbenmachinen now \ Cf Φ) becomes ζ and χ the arc lengths r ^ win ^{corresponds to any zero radium:} ray calculated, so that the new independent coordinate c to the Place of the angle Λ occurs in the base circle and r is constant.

Taking into account the above coordinate transformations,. outgoing from the representation in the base circle, the transfer of the invention Carry out the curve guide contour on radial, axial and reciprocating piston machines. For the sake of simplicity, the further explanation is given below the relationships in the base circle, those of the arrangement in radial Koltyenmaschinen is carried out

009836/0178

BATH ORIGINAL

TC TC

The relation for f (Δ) is valid for - - <Δ ^ T * y ie over a semicircle.

3Tt
For the interval \ to ~ - - f (Δ) is defined as f ( ^π ~ ^Δ ), so that the mirror-image formation of the curve guidance results.

The above definition of the curve guide according to the invention are the possible designs with regard to the residence and work sectors. The definition also includes the applicable conditions for the Number of pistons η is determined as well as the angle set, each of a machine with one stroke per revolution of the rotating part.

There are no dwell periods in embodiments 11 and III of the cornering provided in which the piston speed is zero. In Embodiment IV, dwell periods are provided provided that their Values are small and well below those given in the last column Values lie. These dwell areas can be used under certain circumstances Improvement of the machine design may be necessary.

The given definition for f (Δ) refers to Pun.peu or engines with one stroke per revolution and η piston. Machines with more than one, namely S strokes per revolution and η piston have the required properties, provided that that

a) the number of pistons η divided by the highest common factor d of η and S, ie the so-called "reduced" number of pistons η = n corresponds to a set of the conditions listed under embodiments I to IV and

b) the function f (£) for a number of pistons η is divided into S working areas, each S times smaller than the working range in the case of one stroke per revolution are. This means that a new curve guidance function is defined by

009836/0178

the relationship C ι g (ί), where g (Δ) = f (SA) and f (Δ) has a period of 2π. If the angle Δ passes through the range from> to 2 ^, the value Δ S passes through the range from 0 to 2 π S, so that with S strokes per revolution the same piston movement is performed S times relative to the base circle. The design of the cam guide according to the invention is thus dependent on the number of strokes η or η and the number S of strokes ie revolution

The grand circle radius C, the piston stroke R and the number 1 of the piston machine set the flow rate of the pump or the torque of the motor test if z. B. a certain Fordf-rstrom achieved with a piston stroke R per revolution then reaches a pump or motor with 2, 3 or more piston strokes the same throughput or the same torque per revolution and the same rotational speed if the piston stroke is reduced proportionally to R / 2, R / 3 etc.

The embodiments of the curve guide according to the invention also have the property that they deliver constant piston accelerations and consequently cause the piston machine to operate smoothly and without jolts. Darii jr also result in machines whose number of strokes per revolution and whose number of pistons corresponds to the above condition a), where the value d is greater than i, resulting forces that combine to form a pure force couple. To change the delivery rate of a pump or the absorption amount of an engine, the cam guide of the invention may be formed as a surface in a known manner, a plurality of axially offset from one another, differently sized piston strokes R effecting Direction cam guides au ¹ .'eist.

The choice of the number of pistons η is determined by the requirements of the pump of the motor. The torque of a motor is given by the K> >] beiiflaehe

009836/0178

multiplied by the product of η, S and R. Therefore, for a given Output torque these quantities can be varied in any way if the end product remains unchanged.

In the two following tables, Table 2 gives the angles β for the spiral area and the angle 5 for the dwell sectors corresponding to the number of pistons of a pump or a motor that has one working stroke per revolution exhibit. Table 3 gives the radial distances from the center of the base circle to the piston guide ring of a pump or a motor with η 3, R a Unit and C ^ 10 units. In table 2 both ß and ο given in degrees.

Further features and advantages of the invention can be seen from the following Description of preferred embodiments of the invention based on this for example reproducing drawing.

Show it:

1 shows a diagram of the base circle and a guide ring contour built on it to represent the different sectors;

2 shows a polar diagram of a guide ring with those listed in Table 3 Measured values,

Fig. 3 3in a diagram of the base circle and a guide ring contour built on it for three strokes per revolution;

4 shows a diagram with a straight base line and one built on it Contour of a curve guide, which has the shape of a longitudinal

00S838 / 0178

direction moving rack in a piston machine with an in-line arrangement the cylinder has;

In Figure 1, the base circle 1 is shown in full lines, and the contour of the Guide ring 2 is shown in broken lines. The latter is formed by two loops, one inside and one outside of the base circle. The straight lines 3 mark the boundaries between the work and leisure clores. The straight lines 4 mark dip limits

en

between the spiral sector (- ρ to ■ »p) and the rest of the borrowed part of the labor sector; the mirror images of the straight line 4 · in the left part of the diagram are in Figure 1 not shown.

As shown, each working sector extends over an angle of 2 ^α in the center of the base circle 1, which has a radius C. The distance between the center of the base circle and a section on the contour of a guide ring is C + f (Δ). The angle that is limited in the center of the base circle by the boundaries of each dwell sector is denoted by 2 δ.

Figure 2 shows the shape of the guide ring, which according to the measured values according to Table 3 is detailed. The guide ring is matched to a pump or a motor with three pistons, with one piston stroke of a unit, the The radius of the base circle corresponds to 10 units, the working sector extends over an angle of 180, of which 2 χ 30 = 60 form the spiral sector, while 2 χ 60 = 120 correspond to the remaining parts of the labor sector. In this example of embodiment 3, the dwell sector does not exist.

Figure 3 is derived in the following way. The angles listed in table 2 are used for the design of motors or rims with S strokes per revolution

009836/0178 SAD original

the necessary data, provided that the values in the top row (i.e. the number of pistons n) are chosen as values η = n / S, i.e. where η is divided by S to get the values in this top row The values in Table 3 for η 3, S ■ - 1 automatically indicate the shape of the guide ring for every other permissible number of S strokes per revolution, provided that the numbers in the first column (angular position) are divided by S So is im Case η = 9, S - 3 the highest common factor d 3, so that η is 9/3 ■ 3 and the angular position t-n should be divided by S 3, so that the radial dimensions of the hihnmg of 9. 0000 at -30 ° to 11 0000 at <30 °. The radial dimensions thus obtained for the sector (-30 ° to * 30) are extended as mirror images to the sectors (-60 ° to -30 °) and (30 ° to 60 °); this form (-60 ° to '60 ^f ) is repeated twice ί · ίίθ ° to i 80 °). (-1HO ^Q to -60 °)

TABLE 2

Number of pistons η

3 5

9 JO

execution III angle β 30th 54 30th 12 * 22 ¹ 30th 18th δ- 0 α = π
2 or 4 5 or 36

Version IV angle B

30-6 54-δ 30 · δ 12- · έ 4 5-6 30 · δ 18 · δ

Angle δ

less than 30 18 30 38 ^ 22 ~ 30 36

7 2

009836/0178

TABLE 3

Angular position Piston stroke Radialabmessimg Racial dimensions of the cam of the cam ( ^Δ ) r Δ) IN DEGREES Δ f (A) C * f (Δ) C- f (Δ) O 0.000000 10.0000 10.0000 3 0.050000 10.0500 9.9500 6th 0.100000 10.1000 9.9000 9 0.150000 10.1500 ¹ year 8500 12th 0.200000 10.2000 9.8000 15th 0.250000 10.2500 9,7500 18th 0.300000 10.3000 9.7000 21 0.350000 10.3500 9.6500 24 0.4000OO 10.4000 9. OOOO 27 0.450000 10.4 500 9.5500 30th 0.500000 10.5000 9.5000 33 0.549-97 10.5-199 9.4501 36 0.599182 10.5992 9.4008 39 0.647255 10.6473 9.3527 42 0.693549 10.6935 9.3065 45 0.737540 10.7375 9.2625 48 0.778759 10.7788 9.2212 51 0.816808 10.8168 f). 1832 54 0.851365 10.8514 9.1486 57 0.882195 10.8822 9.1178 60 0.909155 10.9092 9.0908 63 0.932195 10.9322 l>. 0678 66 0.951365 10,951} 9.0486 69 0.966808 10,900-1 9.0332 72 0.978759 10.9788 9.0212 75 0.987540 10.9875 9.0125 78 0.993549 10.9935 9.0065 81 0.997255 10.9973 9.0027 84 0.999182 10.9992 9,0008 87 0.999897 10.9999 9,0001 90 1.000000 11.0000 9.0000

009836/0178

and fills the whole circle.

FIG. 4 shows the application of the cam guide to cylinders in an in-line arrangement. L is a guiding cycle and an arbitrarily chosen dimension which depends on the exact values of the constant force and speed of the rack in question. R is the stroke of a piston, X and Y are lit; Coordinates of a 'point on the guide contour, where X LA /.' J (Jo and Y - Rf (Δ). This means that the abscissa dimensions are proportional to the original arc lengths 2 κ C ""'3Go and the Onhnauaabi> n? -; solutions to the value of C + f (Δ) It follows that the can in response dt urlnrderliehen rectilinear displacement ι corresponding number of times on the rack outline worn cam shape in a hydraulic motor or a hydraulic pump are used, wherein the movement dei flask under. At right angles to the length of the rack, the relative longitudinal movement /. between the rack and the component supporting the piston is generated.

If η pistons are provided in the sector that covers a cam cylinder, in this way a hydraulic piston engine is created, the tmo constant Longitudinal force component and a correct speed el; * rack generated, when the pistons are exposed to a constant working pressure; the opposite applies to a hydraulic thrust piston pump.

The features previously identified in relation to radial piston pumps or motors are to be applied in a similar way to Axialkoibenbauarbeiten - .. J.en, under Consideration of the coordinate transformation mentioned above and the following considerations resulting from it.

009336/017 «

The rack design according to the invention can be applied to any of the mentioned Types of controllable feed pumps or drive motors with controllable torque are used. To achieve this, work in general said the pistons of the pump or the motor with a three-dimensional guide surface together, which is a plurality of mutually offset according to the invention Has guide elements that merge smoothly into one another. Offset to one another in one direction = ünd, which is perpendicular to the Swing axis of each piston and the direction of the working movement tines each piston relative to the guide element. With a radial bump> enlruian this distance lies along the axis of rotation, as stated above. In the linear motion type, the distance is perpendicular to both the Linear motion and to the axis of each piston. i.e. to the directions \ and y mentioned above. With the axial piston design, the distance is radial; however, there is a Π -! effect of the Kolberzvlindei aggregate technically more difficult to achieve. the result is d < r Advantage of a possibility to change the mechanical loop, aii that of the pistons applied, the force, the torque and the stroke of the piston constant which is of particular importance for frictional losses.

The formula given for the running surface of the guide element relates to only stand on the profile of the guide element in Idea! if the this profile corresponds to the outer line of the railway, which one! »unkt would be described in the central longitudinal axis of a piston if one assumes that the piston moves relative to the guide element along the path into which the guide element should force the piston. But when For example, if a sequence element is used, then the above-mentioned one is used Ideal condition not met. So that you get the required piston movement receives. the profile is designed in such a way that the formula is based on the

009836/0178 ^ ORIGINAL

Control surface refers to which the longitudinal axis of each roller passes through when the roller is moved along the profile, and this control surface would form the ideal running surface of the guide element. The actual profile will be created here by using a cutter with the same diameter as the roller and along the cutter center with an ideal tread profile moved, which is given by the formula.

009836/0178

Claims (3)

Claims f IJ Cam drive for piston machines with a cylinder arrangement that moves relative to the cam drive, in which η pistons are displaceably guided and with a cam guide that controls the piston movement, the running surface S of which has identical sections, where S is an integer and the number of strokes of a piston with a full one Cycle of movement of the cylinder arrangement relative to the curve guide and where one half of the curve development is designed as a mirror image of the other and divided into a number of sub-sections, each of which corresponds to the arc lengths of angles plotted around the center of a construction base circle, in particular according to patent (patent application P 14 53 441.9 / B 70 365 Ic / 59a) characterized in that the first and fifth of five subsections are formed by circular arcs around the center of the construction base circle with the radii CR or C + R, while the second and fourth subsections are formed by a Sp Iralkurve are formed or correspond to this, whose radius beam emanating from the center of the construction base circle has the size C-R ι α τ ρ H ν * τ [</ OC "~ S _1n '· « ο + β π (α + β) ^aui a - β for- for β ^ and the third section is formed by a spiral curve or this corresponds to the center of the construction base circle 2 Δ going radius ray has the size C + R -, where C, R, Δ, CL + ρ α and β are defined as follows: A 2291 009836/0178 C is the length of a in the middle of the third section (spiral arc) drawn from the center of the basic construction circles to the spiral arch Radius beam; R is the stroke of the pistons and is less than C; Δ is the parameter angle around the center of the construction base circle from a radius beam lying in the middle of the third section (spiral arc) to another radius intersecting the spiral ray in the range from - α to + α, β defines the third sub-section within - ß to + ß of the range from -α to + α, where α and β are represented by the number of pistons η are determined according to the conditions in the table below: 003838/0178 TABEL 6> O η even> 6 α = δ = ^ ΔΠ Π β = O η odd ^ - 5 α = ο ^ ~ 2η Π δ = 0, α = -f- β. = O, η even > 4 ΠΙ δ = O, α = - η = 6 β> O, η = 6 8th '' lHl ß = 4th
4, π
6th or 2π η even > bar
bar CQ, π β
β 3 part- η η odd> by
part-
by 2 η
3π
2η IV δ> O, α = - - δ .... a - ■ * * χ / η -4 _π η divisible β - - 5, ο <-τ— · ^π ... through 4 η straight> 6 - η + 2 divisible _ α t _t , η -2 by 4 ^r η 4η β> O η-1 divisible β = ~ * 6. 5 <ι ^ n η odd). 3 _ν through 4 η * 3 divisible S - ^ - -δ. δ < - ^ ~ - · π ... ^r 2η 4η by 4 009836/0178 2. Cam drive according to claim 1, characterized in that S Arbeltahttbe in the range 0-2 * of Δ are provided that the axial deflection of the piston from its central position is g (Δ), where g (Δ) = i (8Δ) and f (Δ) by the conditions listed in claim 1 are determined and the function g (Δ) and its form are repeated S times in each region 2 η / on Δ and that the quotient obtained by dividing the number η of pistons by the highest common factor d of η and S. , one set of the conditions according to Table 1 is sufficient. 3. Cam drive according to claim 1 or 2, characterized in that e: has a three-dimensional running surface whose on the piston parts during the relative movement, the adjacent cross-sectional area changes its shape changes a direction which is normal to the oscillatory movement and to the relative movement, such as to change the delivery rate of the pump or of the torque of the engine, the running surface can be displaced along this normal relative to the piston. 009836/0178 Blank page