Rotary expansible chamber devices – Working chamber surface expressed mathematically
Patent
1992-06-11
1994-05-31
Bertsch, Richard A.
Rotary expansible chamber devices
Working chamber surface expressed mathematically
418255, F03C 200
Patent
active
053164563
DESCRIPTION:
BRIEF SUMMARY
BACKGROUND OF THE INVENTION
The present invention relates to a slide vane machine based on the geometric principle of the conchoidal of the circle, also called Pascalian Screw, with one or multiple slide vanes per working chamber in which shape and proportions of the rotating machine parts are adjusted and optimized relative to one another based on a calculation method.
Slide vane machines of the aforementioned kind are known from the U.S. Pat. Nos. 1,994,245 and DD 46,761 and have the following constructive design:
As shown in FIG. 5, in a hollow cylinder 1 with an inner contour E corresponding to the circumferential line of the Pascalian Screw which is closed off on both ends by housing end plates a rotary piston 4 in the form of a hollow circular cylinder is supported in both housing end plates in a rotatable manner and axially oriented relative to the hollow cylinder. The axis of rotation of the rotary piston corresponds to the center M' of the central circle K' of the Pascalian Screw represented in drawings 1 and 2. From this it results that the rotary piston with the radius r.sub.Kr with its outer surface approaches the inner surface of the hollow cylinder at the approximation point 21(-xr.sub.Kr Yo)=E180.degree. to form a narrow slot.
The control shaft 8, embodied as a crankshaft, with the radius r of the base circle K is guided through the hollow rotary piston and through central openings in its end faces and is also rotatably supported within the two housing end plates, whereby the crankshaft axis corresponds to the center M of the base circle K, the crankshaft axis being arranged parallel to the axis of the rotary piston.
On the crankshaft pins of the control shaft one or two slide vanes 6 with their half length L/2 are rotatably supported. They correspond functionally to slide vane wing pairs 6f staggered by 180.degree. which are connected to form a rigid slide vane by stays 6s connected to one or two central bearing sleeves 61. Their center P corresponds to the axis of the crankshaft pins, and during the rotation of the control shaft, they follow the base circle K. The slide vanes are additionally guided in diametrically opposed longitudinal grooves 5 of the rotary piston
In machines with one slide vane per working chamber the masses due to inertia of the crankshaft pins revolving on the base circle K and of the slide vane must be compensated by two counterweights at the control shaft.
The use of more than one slide vane per working chamber allows for the compensation of the forces of inertia without counterweights, when the slide vanes have a longitudinal and transverse axial symmetry and the bifurcation of the stays 6s is arranged with the bearing sleeve 61 is arranged such that they do not overlap one another.
Since the axis of rotation of the rotary piston is at M'.sub.(xo yo) =P.sub.(xo yo), the central circle K' contacts the base circle K at P.sub.(x2r yo) =S.sub.(x2r yo), r' corresponds to 2r, and the points P and S have the same trajectory velocity and direction of rotation, the central outer toothing of the control shaft 8 with the partial circle K.sub.t may engage a central inner toothing (see, for example, the representation of FIG. 9) within one rotary piston end face with the partial circle K.sub.t '.
The ratio of the number of teeth of the outer toothing 10 to the number of teeth of the inner toothing 11 is 1:2. The toothing engagement of the control shaft with the rotary piston ensures the exact synchronous rotation of these two machine parts at the ratio 2:1 and compensates bending forces acting on the slide vanes.
The machine geometry according to the Pascalian Screw also allows for constructions without toothing engagement of the control shaft 8 with the rotary piston 4, because the course of movement of the slide vanes effects a force-controlled rotation of the rotary piston and the control shaft in the aforementioned ratio 1:2.
However, due to the torque acting on the control shaft, an additional bending moment acts on the slide vanes. The bending of the slide vanes may lea
REFERENCES:
patent: 1994245 (1935-03-01), Gette et al.
patent: 2071258 (1937-02-01), Haydock et al.
patent: 4385873 (1983-05-01), Richter
patent: 4449899 (1984-05-01), Smolinski
Bertsch Richard A.
Freay Charles G.
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