DE2646532A1 - PISTON MACHINE - Google Patents

Description

Applicant: Balcke-Dürr AG, Hornberger Straße 2, 4030 Ratingen

"Reciprocating engine"

The invention relates to a reciprocating piston engine with at least one on a crank pin on a bend of a crankshaft via a sliding joint and one Piston engaging connecting rod with a mass balance of the inertia forces of the oscillating weights. She prefers to but not exclusively, use as a reciprocating compressor for all gases.

It is well known to compensate for free oscillating To arrange mass forces a so-called differential gear. In this arrangement are located below the crankshaft two flyweights, one of which is driven by the crankshaft and the flyweight that is coaxial with it rotates in the opposite direction. These are half heavy or unbalanced gears. Because the flyweights are coaxial • lying next to each other and turning in opposite directions, their horizontal force components cancel each other out. Compensate at the same time the flyweights are the vertical vibrations of the crankshaft. The differential only compensates for the 1st order free mass forces.

It is also known that the disruptive effects of free inertia forces of the 1st and 2nd order in the crank mechanism a mass balance, i.e. suppressing a suitable arrangement of counterweights (Lueger, "Lexikon der Technik" Vol. 1 "Fundamentals of mechanical engineering" (1960), pages 275-280). In the cited paper are the formulas for determining the torque for a slider crank and also the formulas for determining the inertia forces are given. For the proviso that

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To eliminate the free inertial forces through mass balancing, however, there are no more detailed constructive details. The example said opposed piston engine comprises a compensating piston, which leads to a complex construction and to on the other hand, the complete compensation of the gas forces in addition to the mechanical forces in the full adjustment range of the motor is necessary.

Based on a reciprocating piston engine of the type mentioned at the outset, the invention is based on the object To achieve a compensation of the free oscillating inertia forces of the 1st and 2nd order with the desired compact design.

The solution to this problem is that according to the invention on the crankshaft, symmetrical to the point of application of the reciprocating piston, one from the crankshaft opposite to the reciprocating piston moving, with its mass on the reciprocating piston and the inertial forces of the 1st order and 2nd order oscillating with the reciprocating piston coordinated balance weight is articulated.

The counterweight is thus carried along on a straight path of movement, opposite to the reciprocating piston. The connecting rod _{length I 1 of} the reciprocating piston is equal to the connecting rod length I ₂ of the counterweight, and the lifting rod ratios A- ₁ and Λ ₂ , ie the quotients from the respective length of the connecting rod or push rod to the respective crank radius ¹ , are the same. By choosing the balance weight, a full compensation of the free oscillating inertia forces of the first and second order can advantageously be achieved.

The crankshaft is expediently bent three times in the area of the reciprocating piston or the counterweight, the counterweight is hinged to the two outer crank pins via connecting rods. This arrangement is advantageously attached at a single-crank reciprocating compressor.

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The crankshaft is preferably mounted on the crank webs assigned to the two outer bends. This results in the surprising advantage that the reciprocating piston machine, which is preferably designed in a vertical installation has an extremely small extent in the direction of the crankshaft. It is known that the deflection of the shaft increases uniform load with the third power of the free length between two support points. The arrangement of a balance weight must therefore first because of possible other disturbing forces acting on the reciprocating piston and taking into account the possibly different gas forces appear questionable in the full setting range. With the through storage up The extremely small free wavelength achieved by the crank webs, however, poses no problem. Rather, it results in a vibration-free running, a saving on foundations, an expansion of the speed setting range upwards and consequently a smaller volume and weight as well as a favorable performance-cost ratio.

The invention is explained in more detail below with reference to an embodiment shown in the drawing. Show it:

Fig. 1 schematically shows a section parallel to the crankshaft of a reciprocating piston engine and a partial plan view and

FIG. 2 shows a section transversely to the crankshaft of the reciprocating piston machine according to FIG. 1 and a partial plan view.

The exemplary embodiment relates to a single-crank reciprocating compressor vertical installation type. They are only for the present Context of essential elements shown; The further structure of such a single-crank reciprocating compressor is z. B. by the type HTS 230 from the company Maschinenbau-AG Balcke, Wormser Str. 109, $ 71 Frankenthal / Pfalz, Federal Republic of Germany , known.

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The lift or compressor piston located in the upper part 1 of the machine engages via a universal joint / with a cross head bolt 3 and a connecting rod 4 seated on the latter a middle crank pin 5 a middle bend one Crankshaft 6 on. A balance weight 7 is via two connecting rods articulated on the two outer crank pins 8 and 9 10 and 11 coupled to the crankshaft 6.

The crankshaft 6 is on the two outer bends of the crank webs 12 and 13 associated with the triple cranked crankshaft 6.

A flywheel 14 is also located on the shaft.

A sliding guide 15 is provided for the balance weight 7. (Fig. 2). The connecting rod _{length I 1 of} the connecting rod 4 is equal to the connecting rod length I _{2 of} the connecting rods 10 and 11.

When the reciprocating piston moves, the counterweight 7 is carried along in the opposite direction. If you transfer the respective Vector image for the inertial forces of the 1st and 2nd order in a time diagram, e.g. for a movement segment between the lower and the upper limit position can be seen when they are superimposed of the respective vibrations that there is complete compensation. The corresponding arithmetical determination results from Lueger (see above).

From Fig. 1 it can be seen that the storage on the crank webs 12 and 13, a minimal extent of Machine or the crankshaft results in the horizontal direction.

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Empty soap ^ 6 -

Claims (4)

Expectations 1.) Reciprocating engine with at least one on a crank pin at a bend of a crankshaft via a straight sliding joint and a connecting rod engaging reciprocating piston with a mass balance of the inertia forces of the oscillating weights, characterized in that on the crankshaft (6), symmetrical to the point of application of the reciprocating piston, one of the Crankshaft (6) moved opposite to the reciprocating piston, with its mass on the reciprocating piston and the oscillating with the reciprocating piston Mass forces I. order and II. Order balanced balancing weight (7) is articulated. 2. Reciprocating piston machine according to claim 1, characterized by a triple in the area of the reciprocating piston or the counterweight cranked crankshaft (6), the balance weight (7) on the two outer crank pins (8, 9) over Connecting rods (10, 11) is articulated. 3. Reciprocating piston machine according to claim 1 or 2, characterized in that that the crankshaft (6) is mounted on the crank webs (12, 13) assigned to the two outer cranks is. 4. Reciprocating piston machine according to claim 1 or the following, characterized through vertical installation. 809816/0209