DE261311C - - Google Patents

Description

IMPERIAL

PATENT OFFICE.

PATENT LETTERING

- M 261311 CLASS 46 a. GROUP

Patented in the German Empire on November 27, 1909.

Individual engines, for example internal combustion engines, in addition to the working cylinders, they also have auxiliary cylinders, e.g. B. air compressors, water pumps, condensation pumps etc. By special arrangement of these auxiliary cylinders, a balance of the mass effects in the whole System itself can be achieved. The present invention relates to prime movers,

ίο whose number of cylinders is an even multiple of Two or three and which have two or more auxiliary cylinders. It is known, four- and multi-cylinder piston machines due to the special choice of the crank angle, different Balance the weights of the operating parts and the various distances between the individual cylinders in terms of their mass effects. These Type of mass balancing is not suitable for internal combustion engines because at these both individually at the crank angle to each other because of the starting and the cylinder distances and the crank mechanism, in contrast to the steam engine, should be carried out in the same way as possible.

In the case of the four-, six- and multi-crank machines under consideration, all are cranks offset from one another at the same or almost the same angles, namely by 90 ° for the four-cylinder engine and 60 ° for the six-cylinder engine, etc.

The present invention resides in such four, six or more crank engines through the special choice of the crank sequence for the working and auxiliary cylinders, as well as through the choice of the position of the individual auxiliary cylinders to balance both with respect to mass pressure and to mass moment effects.

The engine shown as an example in Fig. 1 has four working cylinders which act on four cranks I to IV located at a distance α from one another. The position of the four working cranks relative to one another can be seen from FIG. The two outer cranks I and IV are diametrically opposed to each other; at right angles to this is the other pair of cranks II and III; the latter two cranks can also swap their designation in FIG. 2. The two auxiliary cylinders, e.g. B. two air compressors are located at both ends of the crankshaft and act on the two cranks H ₁ and H ₂ , which are also diametrically opposed to each other. The piston and rod masses acting on the working cranks I to IV generate mass pressures of the first order (i.e. without taking into account the finite length of the push rods) in the direction of the cylinder axis, which balance out due to the equality of the four crank angles and the diametrical position of two cranks .. If m is the reciprocating mass of a cylinder, r is the associated crank radius and ν is the constant circumferential

speed of the crank pin, so is the mass pressure

P = m - cos χ r

for each value of the angle of rotation χ of the crank from its dead center position. These inertial forces generate torques in the plane laid by the crank axis and the cylinder axes. The changing size of this

ίο moments of inertia is a simple cosine function and repeats itself with every revolution; the same goes for the resulting one Moment of inertia of all working cylinders. To compensate for this result-

At the same time, a moment of inertia, which is generated by the movement linkage of the two auxiliary cylinders H ₁ and H ₂ and is directed opposite to the former, is used, which is of course also a simple cosine function. Since the mutual distance b of the two auxiliary pumps or corresponding auxiliary cylinders H ₁ and H ₂ can be chosen to be sufficiently large compared to the individual distances α of the working cylinder, the movement linkages of the pumps do not need to be as large as those of the working cylinders. The angle z that the two auxiliary cranks enclose with the dead center position of the first working crank is a constant value; the same changes its sign when the two main cranks II and III are mixed up. The mass pressures generated by the linkage of the two auxiliary cylinders H ₁ and H ₂ are the same, but directed in opposite directions, so their effect is canceled out Mass moments of pressure first Order of the combined machine system balanced.

The two auxiliary cylinders H ₁ and H ₂ can also be moved closer together by placing them next to one another between the individual working cylinders or even in the middle of the crankshaft between the cranks II and III. However, when the pump spacing b is reduced, the rod masses of the pumps or the crank radii must be increased; It will therefore be advantageous for the execution to place the two pumps as far apart as possible, especially if they are to be made small.

The so-called mass effects caused by the finite length of the push rods of the second order are also mainly in the present machine system balanced. These secondary mass pressures according to the expression

P ₁ =

-γ I COS 2 X,

where I is the push rod length, are balanced in the selected four-crank system due to the four equal crank angles of 90 °. The moments of these mass pressures of the second order are also balanced, namely in that the two pairs of cranks with diametrically opposed cranks, i.e. I and IV or II and III, are arranged in the longitudinal direction of the crankshaft symmetrically to its center. Since, according to the cosine function of the double angle of rotation, these mass pressures are repeated twice in terms of magnitude and direction with each revolution, the diametrically positioned cranks of each pair of cranks result in the same and rectified mass pressures of the second order, so that no moments can be released because the crank pairs are arranged symmetrically to the shaft center are.

Since the two pump cranks H ₁ and H ₂ are also diametrically opposed to one another, their second order mass pressures are also equal to one another, ie they cancel one another out. Since they are directed in opposite directions, they do not result in a free moment of inertia. The remaining unbalanced mass pressures of the second order in the entire machine system including the auxiliary cylinder, originating from the two auxiliary pumps, are insignificant, since the moving masses at the pumps can be made relatively small. In addition, the ratio of the length of the push rod to the crank radius in the two pumps can be selected to be very large, so that these inertia forces are negligibly small.

In the same way as on the four-crank machine, the mass effects can also be achieved on the six-crank machine with six identical or almost identical crank angles. As shown in FIGS. 3 and 4, as in the case of the four-crank machine, two cranks I and VI or II and V and III and IV, which are symmetrical to the longitudinal center of the crankshaft, are diametrically opposite one another. The two cranks II and III or IV and V can also be interchanged in FIG. 4. The two auxiliary cylinders or pumps H ₁ and H ₂ are at both ends of the crankshaft and have counter-rotating cranks. The first-order moment of inertia resulting from the three pairs of cylinders, which is variable according to a cosine function, is compensated for by the first-order moment of mass pressure generated in the pair of pumps H ₁ and H _2. As in the case of the four-crank machine, it is also advantageous here to place the two pumps far apart, so that their distance b is increased and their rod mass is reduced.

Claims (1)

As with the four-crank machine in the first example, there are also in this six-crank machine both the mass pressures and the second order mass moments are fully balanced. With regard to the secondary mass effects of the pump pair, the same applies as for the Four-crank machine. For machines that do not have auxiliary cylinders ίο have for secondary purposes, the same is achieved. if you replace them with two auxiliary power cylinders specially dimensioned for the purpose of balancing sets up or only auxiliary masses going back and forth. The individual power cylinders can be the same as the auxiliary cylinders, or they can only be of the same kind, i.e. H. with the same ratio of push rod length to the crank length, but the corresponding, reciprocating masses are dimensioned so that the cylinders have the same mass forces. The arrangement described can also be used several times around the same common crankshaft be arranged around in different levels, if only the arrangement in each individual level meets the conditions set here is equivalent to. What in the foregoing of the effects of the masses going back and forth in the common cylinder plane has been said also applies to the effects of the vibrating and rotating engine parts in the planes perpendicular to the common cylinder plane. Let the acceleration components of these engine parts perpendicular to the common cylinder plane be set equal to K for a cylinder; then the formula is known from the works on mass action: K = m · - smj ;,
r where m is the mass of the push rod, ν is the crank speed, r is the crank radius and χ is the angle of rotation of the crank from its dead center position. ■ These inertial forces of the individual push rods of the power cylinder are balanced among themselves by. the diametrical position of the cranks because the individual pairs of cranks each have the same oscillating push rod masses. These inertial forces generate centrifugal moments in planes perpendicular to the common Cylinder plane; the centrifugal moment, which in this way by two diametrically arranged Cranks with otherwise the same conditions arise, is then, as from the concerned Special works known, M = a • sin χ ), where α is the distance between the two cylinder axes. This formula is a simple sine function; the same applies to a second (or a third) Pair of cylinders with diametrical cranks. The centrifugal moment of the whole crank system to be compensated is therefore the Sum of two or more sine functions. However, according to trigonometric laws, it is the sum of two (or more) sine functions itself again a simple sine function (which is known from mathematics, and therefore cannot be proven). This proves that the centrifugal forces of several pairs of cylinders (power cylinders) resulting centrifugal moment generated by an oppositely directed centrifugal moment (or two auxiliary cylinders) can be compensated, which is generated by a single pair of cylinders, provided that that its crank angle and rod mass are correctly calculated from the trigonometric formulas. This calculation shows that the crank angle and the linkage masses which are used for the cancellation of the reciprocating mass effects are calculated identically are related to the crank angle and the linkage masses which cancel out the slinging effects result. Pa τ en τ claim: Power machine whose number of cylinders or cranks is an even multiple of two or three, with being at equal or nearly equal angles to each other Cranks, characterized in that the cranks of the same oppose each other in pairs and are symmetrical are arranged to the longitudinal center of the crankshaft, and that two auxiliary cylinders are arranged whose cranks also face each other and are symmetrical to the longitudinal center of the crankshaft! 05 are ordered, and their crank position and rod masses are calculated so that the mass effects of the back and forth going engine parts in the common cylinder plane as well as the sling? the effect of the vibrating and rotating engine parts in planes perpendicular to the common cylinder plane in the described Wise to be repealed. '' 1 sheet of drawings.