Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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Rotary Piston Machine
The invention concerns a rotary piston machine.
In a conventional rotary piston machine (DE P 42 41 320.6;
DE G 92 18 694.7; PCT/DE 92/01025), all lines of the cycloid
component and the central component extending transverse to
and defining the operating direction pass through the point
of intersection of the axes of rotation. This limits the
expansion and compression behavior of the working chambers
and therefore adaptation of the rotary piston machine to
various working media and fields of application.
In contrast thereto, the invention, in a broad
aspect comprising a rotary piston machine operating as a
pump, a compressor, a turbine or a motor, comprising: a
casing having an inner spherical volume, and having at least
one inlet and one outlet opening, a power component having
an output shaft supported in the casing and with a drive or
output device, the power component having an output
spherical layer truncated by an output end face and an
output base surface, the center of the spherical layer lying
in the axis of rotation of the drive or output shaft and the
diameter of the spherical layer corresponding to the inner
volume of the casing, wherein the output base surface is
perpendicular to the axis of rotation and the output end
face is formed by the motion of a straight generating line,
connected to a point on the rotary axis, along a cycloid
generating curve with at Least 2 cycloids, wherein the
circle generating the cycloids, rolls along the circular
line of intersection between the output base surface and the
output spherical layer with the point on the circle forming
the cycloids moving on the surface of the spherical layer, a
blocking component connected to a blocking shaft supported
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in the casing and having a blocking spherical layer
truncated by a blocking end face and a blocking base
surface, the center of the blocking spherical layer lying on
the axis of rotation of the blocking shaft and the diameter
of the blocking spherical layer corresponding to the inner
volume of the casing, the blocking base surface of which
extends perpendicularly to the axis of the blocking shaft
and the blocking end face of which defines teeth cooperating
in mating engagement with the power component, wherein the
number of blocking component teeth differs from the number
of the power component cycloids by one, the power component
and the blocking component moving synchronously about the
rotary axes of the drive or output shaft and the blocking
shaft, the shafts being disposed at a working angle with
respect to one another, wherein working spaces are formed
between the cycloids and the teeth of the blocking component
which, with each rotation, pass through a defined maximum
and minimum determined by the cycloids, the shape of the
teeth and the working angle, characterized in that the line
generating the output end face of the power component is a
curved line in a plane extending through the rotary axis of
the drive or output shaft, has the advantage that the intake
and output behavior of the working chambers is determined by
the phase shift, to thereby reduce undesired back-flow or
mixing between the intake and output working media.
According to a further advantageous embodiment of
the invention, the phase shift from the inner to the outer
diameter is at least 360° such that the working chamber is
closed off from the surroundings at least at one angular
position of the first or second component.
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According to a further advantageous embodiment of the
invention, the amplitudes of the cycloids forming the
operating surface of the cycloid component differ from one
another. This allows additional freedom in designing the
behavior of the working chambers.
According to a further advantageous embodiment of the
invention, the working chambers are separated by a positive
fit between the sides and tops of the opposing component
teeth. Due to the different number of teeth, the tooth tops of
the Control component advance along the sides of the cycloid
component teeth to essentially eliminate fluid back-flow. In
addition, the control component can thereby be driven by the
cycloids_
According to a further advantageous embodiment of the
invention, there is no positive fit between the cycloids
forming the operating surfaces of the cycla~d carnpanent and
the control component. The machine is then a tlow machine
whose characteristics are defined by trhe impulse and mass of
the working medium. Moreover, sensitive media having
characteristics impaired by compression may also be used as
the working medium.
According to a further advantageous embodiment of the
invention, the control channel for input of the working medium
is disposed at the outer diameter, and the control channel for
output of the working medium is disposed on the inner diameter
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of the tooth structures. wring turbine or motor operation,
the impulse and mass forces generated by the working medium
are aligned with the direction of displacement of the working
chamber. This reduces leakage losses and improves efficiency.
According to a further advantageous embodiment of the
inventipn, the working positions of the axes of rotation of
the components can be changed independently of one another. Tn
accordance with the invention, additional pairs of toothed
disk structures can be incorporated. At least one of the
components has toothed gearing on its back side which
cooperate with an additional rotating component having single
or double teeth. This requires a radial seal between the
enclosing casing and these rotating components. Drive and
output may be effected in a conventional manner using shafts
or toothed wheels Connected to the rotating components or
dzsposed thexeon arid cooperating with additional drive or
output means. By changing the working positions of Che rotary
axes, the volume change in one component of the rotary piston
machine can be advanced or retarded with respect to the other
to permit graduated operation through connection of the
working chambers or for mixing.
According to an advantageous embodiment of the invention,
there are two cycloid or contr4l Components and the additional
part is disposed between the doubled components in the form of
a ring with toothed surfaces or cycloid operating surfaces.
According to a further embodiment, at least two working
chambers, on opposite sides of the ring, can be connected to
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one another. This creates e.g. a double pump or power machine,
in which a control component, With teeth on both sides, is
disposed between two absolutely synchronously rotating cycloid
components with a number of teeth differing by one tooth from
the number of teeth on the doubled components. This control
component may comprise a drive or output device in dependence
on whether it is a pump or a motor. Alternatively, the drive
and/or output may be effected via the doubled cycloid
components. The casing may serve as a stator supporting both
driven cycloid components at corresponding workzng angles
between which the Control Component, having sides with a
number of teeth differing by one tooth, freely rotates.
According to a further advantageous embodiment of the
invention, the casing or the control component has appropriate
channels for the input or output of the working media, which
may be optionally controlled during rotation. This precludes
additional valves and also effects rinsing in the centrifugal
direction.
According to a further preferred embodiment of the invention,
the radial circumference of the components is spherical, and
the components are guided on a corresponding spherical inner
surface of the casing in a radially sealing manner. This
spherical guidance permits change in the working position
without creating additional sealzng problems. This outer or
inner radially sealing, spherical working chamber wall may be
connected to the control or cycloid components and may rotate
therewith to center the components with respect to each other.
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In a further advantageous embodiment of the invention, the
rotary piston machine is a compressor with COriCrol independent
of the rotational speed effected, in particular, by changing
the phase shift of the two rotating parts relative to the
channels of the working media. In addition to the
advantageously stable centrifugal force dependence of the
moving components, the small size, and large power, the phase
shift permits continuous Control df the compression ratio,
independent of the rotational speed. Such a compressor is
particularly suitable for charging combustion engines, since
they have high, widely varying rotational speeds, since the
mass of the charger should be as small as possible (in
particular trie driven rotating masses), and since the power
must be controlled independently of the rotational speed.
Since several pairs of working chambers can operate in a
phase-shifted manne», the valve-less control in the direction
of flow (no inversion of flow) and the very high sealing
quality of the working chambers, permit the inventive
compressors to be used in pressure ranges currently accessible
to piston machines only.
In a further advantageous embodiment of the invention, the
rotary piston machine is a hydrostatic element used as a pump,
motor or transmission. These applications are advantageously
influenced by the extremely favorable relationship between the
size and volume exchange. The simple kinematics, the
rotational speed stability of the structure and the very large
rinsing channel cross-sections ensure that these machines are
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also suitable for the highest of rotational. speeds. The inner
flow resistance of the machine according t4 the invention is
extremely low. If it is used as a pump, the high inherent
stability of the components has advantageous effects. Wear is
lim~.ted to rubbing between the movable components. In
addition, the machine is suitable for the highest working
pressures. If it is used as a hydraulic motor the same
advantages obtain, in particular, the small accelerated
masses, the good starting behavior, and the high volume
efficiency_ The low constz'uction volume and the compact manner
in which the pump and the hydraulic motor can be connected is
particularly advantageous far use as a hydrostat~.c
transmission.
In a further advantageous embodiment of the invention, the
rotary piston machine is a power machine or refrigerator, in
particular, operating according to the Stirling principle,
wherein the cooperating working chambers are phase-shifted by
90°. Tao rotating cycloid components cooperate with a rotating
control Component to form Operating chamber pairs which are
each phase-shifted by 90°. One chamber is heated and the other
cooled, and a regenerator is integrated into the control
companent_ In accordance with the invention, there is no
component exchange between the warm and cool regions. The
walls of the cold and the warm working chambers are insulated
from one another despite their close spatial proximity. An
advantageous convection surface/wor3cirig chamber volume ratio
can be achieved due to the high inherent stability of the
components forming the working chamber. One of the rotating
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components may be a lineax generator driver for a Stirling
motor or a linear motor far a Stirling refrigerator. The
machine can therefore be hezZnetically sealed and designed for
very high loading pressure with low working gas leakage loss.
The phase shift defining the performance of the Stirling motor
Can be easily realized in this embodiment. In any event, the
amount of transported heat can be regulated in such a
refrigerator, irxeepeetive of the rotational speed_
Further advantages and advantageous embodiments of the
invention can be extracted from the following description, the
drawing and the claims.
An embodiment of the invention is shown in the drawing and
further described below.
Fig. 1 shows an exploded view of a drive or output component
and a blocking component;
Fig. 2 shows a drive or output component and a blockzng
component in the assembled state, including the casing;
Fig. 3 shows a top view of a cycloid tooth construction with
Cycloids and a spiral angle of approximately 170;
and
;~ig. 4 shows a top view of a corresponding tooth construction
of the blocking component with five tQeth.
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The right hand side of figure 1 shows the power component I
and the drive or output shaft 2. One end of the drive or
output shaft 2 supported in the casing (not shown) is provided
with the power component 1. The power component 1 consists of
a spherical layer 3 which is bordered by a flat base surface 4
at the drive or output shaft 2 with an end face 5 having a
spiral, cycloid toothed structure. In contrast to the
conventional cycloid canstruction, the cycloid 6 is generated
by rolling a circle along the line of intersection 7 between
spherical surface 8 and base surface 4 with the point on this
circle describing the cycloid 6 always being located on this
spherical surface 8. The cycloid 6 is the generating curve for
forming the toothed structure. A straight cycloid toothed
structure is obtained by a straight generating line moving
about a fixed point on the rotary axis of the drive ox output
shaft 2 along the generating curve 6. Instead of such a
straight generating line, a spiral generating line leads to
the spiral cycloid tooth structure of the power component
according to the invention.
The blocking component 10 shown on the left-hand side of
figure 1 has a similar geometrical shape. A shaft 11 disposed
in the casing (not shown) supports the spherically layered
blocking component 10 Which is bordered by a base surface 12
proximate the shaft 1Z and having a spherical outer surface
13. The end face i4 of the blocking component 10 comprises a
spiral tooth structure, wherein the number of teeth exceeds
the number of teeth in the cycloid 6 of the power component
by one. The shapes of the teeth correspond to the tangents to
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the cycloids 6 during the synchronous rotation of the power
component 1 and the blocking component 10. The shape of the
teeth may be selected to maintain a defined separation between
the cycloid and the teeth of the blocking component 10. In
this case, the displacement machine then becomes a flow
machine. This is advantageous if e.g. the working medium could
be damaged by compression at the sealing lines 9 or if the
impulse and mass forces of the working medium are to be used.
The rotary axes of the blocking component 10 and power
component 1 are disposed at a working angle 15 with respect to
one another. It is irrelevant to the invention whether the
cycloid tooth structure is disposed on the end face of the
power component 1 as shown herein, with the corresponding
tooth st=ructure disposed on the blocking component 10, or vice
versa.
Fig. 2 shows the power component 1 and the blocking component
in their installed position. 'I~vo sealing lines 9 between
the power component 1 and blocking component i~ are shown
(visible as contact points in the drawing). The blocking
component 10, the power component 1 and the casing 17 form
several working chambers 16 in dependence on the number of
cycloids, of which two are shown. In the rotational direction
of the power component 1 and blocking component 10 indicated
by two arrows, the working chambers 16 expand during the part
of the rotary motion shown. The volume of the working chamber
is correspondingly compressed in the second half of the
rotation (not shown). The sealing lines 9 move ~rom the
outszde to the inside or vice versa, depending on the
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to
direction o~ rotation, to thereby effect supply of the working
medium or drive of the output shaft 2. The control openings in
the Casing 17 (not shown) are located in dependence on the
requirements o~ the application. During pump operation with
supply from the Inside to the outside, the Inlet opening in
the casing I7 is located at the point where the sealing line 9
exits the inner diameter of the toothed structure. The outer
toothed structure is disposed at a position in the casing
leading to the required volume of the working chamber 16. The
power output of the rotary piston machine may be regulated for
constant rotational speed by moving the blocking component l0
relative to the power component 1_ In this case, the rotary
axis of the blocking component 10 remains on a cone-shaped
surface having a cone angle corresponding to the working angle
15.
Fig. 3 shows a simplified top view of the power component 1.
Four Spiral generating lines 18 are shown, illustrating the
structure of the spiral cycloid teeth. The generating lines 18
are located at the apex points of the cycloids. In the example
shown, the spiral angle 19 is approximately 170°.
Fig. 4 shows the corresponding generating lines 21 for the
blocking component 10. A comparison between figure 3 and
figure 4 shows the difference in the number of teeth and
illustrates the effect of the spiral tooth s>~ructure. In
contrast to a straight cycloid tooth structure, the same
working chamber may expand and compress simultaneously at its
inner and outer regions. This facilitates a plurality of
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designs to obtain a desired volumetric behavior for the
working chamber. When the spiral angle 19 subtended by the
spiral generating line is greater than 360°, each working
chamber 16 is temporarily closed at all sides during rotation
of the power component 1 and the blocking component 10. Back
flow of the working medium or cthar effects between the outlet
and the inlet side or vice versa are thexeby precluded.
All the features shown in the description, the subsequent
claims and the drawing may be essential to the invention
individually or collectively in any arbitrary combination.
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List of Reference Numbers
1. power Component
2 drive or output shaft
3 spherical layer
4 base surface of the power component
end face of the power component
6 cycloid
7 line of intersection between spherical surface and base
surface
8 spherical surface
9 sealing line between power component and blocking
component
blocking component
ii shaft
12 base surface of the blocking component
~.3 spherical surface
14 end face of the blocking componen>r
working angle
16 working chambex
1'7 Casing
18 generating lines of the power component
19 spiral angle
-
21 generating lines of the blacking component
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