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EP 1 887 184 B1 |
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EUROPEAN PATENT SPECIFICATION |
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Mention of the grant of the patent: |
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27.03.2013 Bulletin 2013/13 |
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Date of filing: 26.07.2007 |
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International Patent Classification (IPC):
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Rotary positive displacement control apparatus
Rotationsverdrängungs - Steuerungsvorrichtung
Appareil de commande de déplacement positif rotatif
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Designated Contracting States: |
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AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO
SE SI SK TR |
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Priority: |
31.07.2006 CN 200610104010 25.10.2006 US 585942
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Date of publication of application: |
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13.02.2008 Bulletin 2008/07 |
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Proprietor: Liung Feng Industrial Co Ltd |
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Taipei Hsien (TW) |
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Inventors: |
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- Chung, Tien-tung
Tu-Cheng Shih, Taipei
Hsien (TW)
- Lin, Heng-l
Tu-Cheng Shih, Taipei
Hsien (TW)
- Hsu, Tsang-lin
Tu-Cheng Shih, Taipei
Hsien (TW)
- Lin, Jin-de
Tu-Cheng Shih, Taipei
Hsien (TW)
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(74) |
Representative: Adamson Jones |
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BioCity Nottingham
Pennyfoot Street Nottingham
Nottinghamshire NG1 1GF Nottingham
Nottinghamshire NG1 1GF (GB) |
(56) |
References cited: :
EP-A2- 0 860 585 DE-A1- 19 527 277
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WO-A1-96/16251 DE-U1- 20 107 293
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Note: Within nine months from the publication of the mention of the grant of the European
patent, any person may give notice to the European Patent Office of opposition to
the European patent
granted. Notice of opposition shall be filed in a written reasoned statement. It shall
not be deemed to
have been filed until the opposition fee has been paid. (Art. 99(1) European Patent
Convention).
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BACKGROUND OF THE INVENTION
1. FIELD OF THE INVENTION
[0001] The present invention relates to a rotary positive displacement control apparatus,
and particularly to a rotary positive displacement apparatus operating by ways of
a periodic process of suction, expansion, compression, exhaust, and can be adapted
to engines, vacuum pumps, internal combustion machines, compressors and rotary positive
displacements.
2. RELATED ART
[0002] Generally, a concept of supercharging is that force air into an intake port of a
sealing chamber which is equipped with multiple rotors rotating continuously and meshing
with each other, in which air flows through a transmitting chamber and is compressed
after rotation of the rotors and turns to be high pressure air, then air is discharged
from the exhaust port. Due to such operation cycle, air is of high compression ratio.
The character of high compression ratio can be used to apparatuses like engines, vacuum
pumps, internal combustion machines and compressors and so on for improving working
performance, lowering oil consumption, and reducing air pollution. Related structure
of supercharging apparatus has been disclosed in numerous prior arts, such as
U.S. Pat. Nos. 4,008,693,
4,321,897,
4,512,302,
4,813,388,
4,825,827,
5,329,900,
6,129,067,
6,481,410.
[0003] However, in prior arts there are still some disadvantages to the periodic operation
process of suction, expansion, compression and exhaust. Those disadvantages lower
the working performance of the apparatuses. That is, in prior arts, during periodic
operation process, residual gases remain because of incomplete exhaust, even though
the apparatus runs with a rotary positive displacement cannot avoid remaining residual
gases. As a result, the apparatus cannot have a well efficiency in providing power
and a longer lifespan. Moreover, power output of some apparatuses, such as engines,
is transmitted through crankshafts, while the quality of the crankshafts will affect
process of operation; if the crankshafts are of poor quality, the accuracy of dynamic
balance is no longer accurate, which will cause unstable performance, shorten lifespan,
and increase unnecessary power consumption.
SUMMARY OF THE INVENTION
[0004] Accordingly, an object of the present invention is to provide a rotary positive displacement
control apparatus, which can completely discharge residual gases and transmit power
without crankshafts, that is, a rotary positive displacement control apparatus of
the present invention can provide high pressure air during process of compression
and can directly transmit combustion expansion power in order to increase operation
efficiency and enhance power output.
[0005] Another object of the present invention is to provide a rotary positive displacement
control apparatus which can be axially or radially extended or can be extended with
whole system.
[0006] To achieve the above-mentioned objects, a rotary positive displacement control apparatus
of the present invention includes a transmission assembly, at least a compression
assembly, a buffer assembly and an expansion assembly, the buffer assembly disposed
between the compression and expansion assembly. The compression assembly includes
multiple compression rotors with lobes intermeshing with each other, and the expansion
assembly includes expansion rotors with lobes intermeshing with each other. An intake
and exhaust ports are respectively located at the compression assembly and expansion
assembly. A first and second intake slots are respectively disposed on opposite sides
of the compression assembly, wherein the first intake slot is corresponding to an
initial seal zone where the compression rotors initially intermesh with each other.
The second intake slot is defined within three curves, including: an arc of a base
circle of one of the compression rotors (said arc drawn with a minimum radius of the
compression rotor), a profile curve of the lobe of the compression rotor being tangent
to said arc of the base circle, and a maximum curve of the adjoining compression rotor
drawn with a maximum radius thereof and being tangent to said arc of the base circle.
[0007] The expansion rotor of the expansion assembly has a first concavity corresponding
to the first exhaust slot, the first concavity being defined by following steps:
as the intermeshing expansion rotors rotate up to a combustion area, designate a point
Q at circumference of the base circle of one of the expansion rotors, the point Q
corresponding to the combustion area, and draw a line QO by connecting the point Q
and a center O of the base circle; then rotate the expansion rotor backwards till
a recess of the lobe is against a tip of a lobe of an adjoining expansion rotor where
a point S is defined as an intersection of the tip and the recess of the lobe, and
a point P is defined as an intersection of a projecting curve of the lobe of the adjoining
expansion rotor and the recess of the lobe, and then respectively connect the point
S and P to the center O, whereby an angle SOP and angle SOQ are formed and subject
to change on rotation of the expansion rotors. Take the angle SOP as two times large
as the angle SOQ, then make an angle bisector of the angle SOP intersect the profile
of the expansion rotor at a point R to form an angle bisector OR; connect point R
and S to form a curve SR; draw an arc about the center O to intersect a line SO and
line RO to form an arc C; whereby, the first concavity is defined within an area of
the curve SR, the arc C, the line SO and line RO.
[0008] The buffer assembly has a buffer chamber being able to efficiently lead compressed
gases to the expansion assembly; meanwhile, residual gases s can be discharged from
a first and second exhaust slots both disposed on the expansion assembly. The buffer
chamber can adjust air compression ratio during process of compression.
BRIEF DESCRIPTION OF THE DRAWINGS
[0009] Figs. 1 and 2 are respectively a perspective exploded view and perspective assembled
view of the first embodiment of the present invention;
[0010] Figs. 3A to 3H are schematic views illustrating a process of operation of a compression
assembly of the first embodiment;
[0011] Figs. 4A to 4F are schematic views illustrating a process of operation of a buffer
assembly of the first embodiment;
[0012] Figs. 5A to 5C are schematic views illustrating a process of operation of an expansion
assembly of the first embodiment;
[0013] Fig. 6 is a perspective exploded view of the second embodiment of the present invention;
[0014] Figs. 7A to 7D are schematic views illustrating a process of operation of a compression
assembly of the second embodiment;
[0015] Figs. 8A to 8C are schematic views illustrating a process of operation of a buffer
assembly of the second embodiment;
[0016] Figs. 9A to 9C are schematic views showing illustrating a process of operation of
an expansion assembly of the second embodiment;
[0017] Fig. 10 is a perspective exploded view of the third embodiment of the present invention;
[0018] Figs. 11A to 11C are plane views of the fourth embodiment of the present invention
mainly illustrating a base, a second casing and a third casing of a buffer assembly;
[0019] Fig. 12 is a plane view of the fourth embodiment of the present invention illustrating
compression rotors intermeshing with each other;
[0020] Fig. 13 is a plane view of the fourth embodiment of the present invention illustrating
expansion rotors intermeshing with each other;
[0021] Figs. 14A to 14F are schematic views of the fourth embodiment of the present invention
illustrating a process of operation of exhausting, intaking and ignition; and
[0022] Figs. 15 to Figs. 17A and B another embodiment illustrating compression rotors and
expansion rotors arranged in different phasing angle.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0023] With respect to Fig. 1, the first embodiment of the present invention applied to
an engine 1, the engine 1 includes a transmission assembly 2, a compression assembly
3, an expansion assembly 4, a buffer assembly 5, and a supply assembly 6, wherein
the transmission assembly 2 includes a axial base 20, a plurality of transmission
members pivotally mounted on the axial base 20; in the first embodiment the transmission
members are a first gear 210, a second gear 211 being engaged with each other, and
a plurality of transmission shafts 22 being parallel to each other for carrying the
first and second gears 210, 211.
[0024] The compression assembly 3 includes a sealing first chamber 30, a first intake slot
31 and a second intake slot 32, wherein the sealing first chamber 30 includes a first
housing 301 sealed by a first casing 302 and a second casing 303 from opposite sides
of the first housing 301, the first housing 301 having a compression chamber 304 which
accommodates a plurality of compression rotors 33, 34 intermeshing with each other
and respectively pivotally mounted to the transmission shafts 22. Each compression
rotor 33, 34 has three identical projecting lobes being evenly spaced around the compression
rotor 33, 34. An intake port 305 is defined on the first housing 301 and communicates
with the compression chamber 304 for taking air in. The first and second casings 302,
303 respectively have a plurality of coupling holes 306, 307 corresponding to the
transmission shafts 22 carrying the first and second gears 210, 211 thereon.
[0025] Referring to Fig. 3A, the first intake slot 31 is corresponding to an initial seal
zone 90 where the compression rotors 33, 34 initially intermesh with each other.
[0026] Referring to Figs. 3E to 3G, a profile of the second intake slot 32 is defined within
three curves, comprising: an arc of a base circle 340 of one of the compression rotors
34 (said arc 340 drawn with a minimum radius of the compression rotor 34), a profile
curve 342 of the lobe 341 of the compression rotor 34 being tangent to said arc of
the base circle 340, and a maximum curve 330 of the adjoining compression rotor 33
drawn with a maximum radius thereof and being tangent to said arc of the base circle
340.
[0027] Referring back to Fig. 1, the expansion assembly 4 includes a sealing second chamber
40, a first exhaust slot 41 and a second exhaust slot 42, wherein the sealing second
chamber 40 includes a second housing 401 sealed by a third casing 402 and a fourth
casing 403, the second housing 401 having a expansion chamber 404 which accommodates
a plurality of expansion rotors 43, 44 intermeshing with each other and respectively
pivotally mounted to the transmission shafts 22, each expansion rotor 43, 44 has three
identical projecting lobes 431, 441 being evenly spaced around the expansion rotor
43, 44, the lobes 431, 441 projecting in counter direction to the lobes 331, 341 of
the compression rotors 33, 34. A rotating direction of the compression rotors 33,
34 and expansion rotors 43, 44 are the same, of which a rotating ratio is 1:1. An
exhaust port 405 is disposed on the second housing 401 and communicates with the expansion
chamber 404 for discharging air. The third and fourth casings 402, 403 respectively
have a plurality of coupling holes 406, 407 corresponding to the transmission shafts
22 carrying the first and second gears 210, 211 thereon.
[0028] Referring to Figs. 4A to 4C, a first concavity 45 is defined on the lobe 441 of the
expansion rotor 44. A profile of the first concavity 45 is defined by following steps:
As shown in Fig. 4A, when the intermeshing expansion rotors 43, 44 rotate to a combustion
area 91, designate a point Q at circumference of the base circle of one of the expansion
rotors 44 (as shown in Fig. 4B); the point Q is corresponding to the combustion 91
as shown in Fig. 4A, and draw a line QO by connecting the point Q and a center O of
the base circle, then rotate the expansion rotor 44 backwards till the recess of the
lobe 441 is against a tip of a lobe 431 of an adjoining expansion rotor 43 where a
point S is defined as an intersection of the tip and the recess of the lobe 441, and
a point P is defined as an intersection of a projecting curve of the lobe 431 of the
adjoining expansion rotor 43 and the recess of the lobe 441, and then respectively
connect the point S and P to the center O, whereby an angle SOP and angle SOQ are
formed and subject to change on rotation of the expansion rotors 43, 44. Referring
to Fig. 4C, take the angle SOP as two times large as the angle SOQ, then make an angle
bisector of the angle SOP intersect the profile of the expansion rotor 44 at a point
R to form an angle bisector OR, and connect point R and S to form a curve SR; draw
an arc about the center O to intersect a line SO and line RO to form an arc C; whereby,
the first concavity 45 is defined within an area of the curve SR, the arc C, the line
SO and line RO.
[0029] Referring to Figs. 4A and 4E, the first exhaust slot 41 is defined within an area
of the arc C, the line QO and SO, and a segment of the profile of the expansion rotor
44 being taken as the combustion area 91 appears.
[0030] Referring to Fig. 5C, the second exhaust slot 42 is disposed on the sealing second
chamber 40 with respect to an ultimate seal zone 92 where the expansion rotors 43,
44 ultimately intermesh with each other for discharging residual gases.
[0031] Referring bank to Fig. 1 in combination with Fig. 3H, the buffer assembly 5 is disposed
between the compression and expansion rotors 3, 4 and has a base 50 having a first
buffer chamber 501 corresponding to the second intake slot 32 and the first exhaust
slot 41, and a plurality of coupling holes 502 being respectively coaxial to the coupling
holes 306, 307, 406, 407.
[0032] The supply assembly 6 includes a fuel injection means 60 and a spark plug 61 both
disposed on the fourth casing 403 with respect to the ultimate seal zone 92 where
the expansion rotors 43, 44 ultimately intermesh with each other ; accordingly, a
gasoline engine is produced. (While the supply assembly includes only a fuel injection
means 60, a diesel engine ejecting directly interiorly is produced). Furthermore,
in the present embodiment, the fuel injection means 60 and the spark plug 61 are disposed
in the expansion chamber in a radial or axial direction with respect to a seal zone
where the expansion rotors intermesh with each other.
[0033] Referring to Figs. 3A to 3D, the present invention in operation, negative pressure
area is generated in the compression chamber 304 as the compassion rotors 33, 34 begin
rotating, and air is sucked in from the intake port 305 (as shown in Fig. 3B). Due
to the shape of the compression rotors 33, 34, a seal zone 90 is generated as the
compression rotors 33, 34 rotate initially. The seal zone 90 will become vacuum if
there is no air filled in. In order to avoid the vacuum situation, air can be admitted
from the first intake slot 31 into the seal zone 90 (as shown in Fig. 3A). During
the process of rotation of the compression rotors 33, 34, filled air is transported
as two parts which will mix together and be compressed in the end of transporting
(as shown in Fig. 3C). Meanwhile, air will be discharged through the second intake
slot 32 into the first buffer chamber 501 (as shown in Fig. 3D). Particularly, opening
of the second intake slot 32 is determined by the compression rotor 32, that is, the
second intake slot 32 is close because it is covered due to rotation of the compression
rotors 33, 34; in turn, the second intake slot is open, and air is admitted into the
first buffer chamber 501. On the other hand, in order to prevent the second intake
slot 32 from being opened too early, which may cause compression ratio of the first
buffer chamber 501 higher than that of the compressed air, and air returns to the
compression chamber 304, a shape and location of the second intake slot 32 are taken
into account.
[0034] Referring to Figs. 3E to 3G, the present invention in manufacture, first, rotate
the compression rotors 33, 34 to a position where compression ratio of the compressed
air and the first buffer chamber 501 is the same (as shown in Fig. 3E), then the second
intake slot 32 will open as the compression rotors 33, 34 keep rotating, and air will
be forced into the buffer chamber 501, therefore, the profile curve 342 of the lobe
341 of the compression rotor 34 indicates an appropriate location to decide opening
of the second intake slot 32. Above all, the second intake slot 32 cannot be located
at left side of a path of rotation the maximum curve 330, otherwise air will return
to the compression chamber 304. Furthermore, the second intake slot 32 cannot be located
inside the arc of the base circle 340 of the compression rotors 34 (said arc 340 drawn
with a minimum radius of the compression rotor 34) because the second intake slot
32 will always be covered and lose functions thereof. Accordingly, the shape and location
of the second intake slot 32 can be defined by the above-described three curves: the
arc of the base circle 340 of the compression rotors 34, the profile curve 342 being
tangent to the arc 340, and the maximum curve 330 of the compression rotor 33.
[0035] Referring to Fig. 3H, the first buffer chamber 501 communicates with the second intake
slot 32 and the first exhaust slot 41 and can maintain air pressure as a pressure
value which is slightly bigger than a pressure value resulted from actual explosion.
When the compression rotors 33, 34 keep rotating, the compressed air will be discharged
into the first buffer chamber 501 to keep a high pressure value. On the other hand,
when the first exhaust slot 41 is open, pressure from the first buffer chamber 501
will force air flowing rapidly into the expansion chamber 404.
[0036] Accordingly, when the air flows into the expansion chamber 404, the fuel supply means
injects fuel to mix with the compressed air, meanwhile, the spark plug is ready to
be ignited to make explosions. In case the first exhaust slot 41 is not close during
the explosions, air will flow back to the buffer chamber 501, and such result is not
expected. Referring to Figs. 4C to 4F, when the expansion rotors 43, 44 rotate as
shown in Fig. 4D, the tip of the lobe 431 of the expansion rotor 43 is against the
first concavity 45; as a result, an opening to the first concavity 45 is formed around
the tip of the lobe 431. In process of rotation (as shown in Fig. 4B), the tip of
the lobe 431 is positioned at the point S, an edge of the first concavity 45, and
the expansion rotors 43, 44 intersect at point P, whereby, a close area SRP is formed.
Keep rotation, the first concavity 45 overlaps with the first exhaust slot 41, and
the compressed air flows from the buffer chamber 501 into the combustion area 91.
Before explosion, the first concavity 45 travels across the first exhaust 41 (as shown
in Fig. 4E), at the same time, the combustion area 91 is spaced away the buffer chamber
501, and the fuel injection means 60 injects fuel to mix with the compressed air,
the spark plug 61 igniting mixed air in the combustion area 91 to cause explosions.
By means of vaporization of fuel and vortexes generated from a high-pressure air stream,
air and fuel can be mixed completely. The explosions cause combustion gas being expanded
and impel rotation of the expansion rotors 43, 44.
[0037] Referring to 5A to 5C, after explosions, residual gas is divided into two parts and
discharged from the below exhaust port 405 (as shown in Figs. 5A and 5B). Due to the
shape of the expansion rotors 43, 44, the ultimate seal zone 92 is generated at the
time ultimate discharge occurs, and wasted gas can be completely discharged from the
second exhaust slot 42 (as shown in Fig. 5C)
[0038] Moreover, number of the intermeshing compression and expansion rotors can be increased
to three to enhance power of the engine and to maintain power transmitting in stable;
accordingly, number of transmission shaft is also three. Fig. 6 illustrates the second
embodiment of the present invention applied to an engine 1' as it is used in the first
embodiment. The engine 1' includes the transmission shaft 2', the compression assembly
3', the expansion assembly 4', the buffer assembly 5' and the supply assembly 6';
a marked difference of the first and second embodiments is number of the compression
and expansion rotors in the second embodiment is increased, which influences location
of the intake port, the first and second intake slot, the exhaust port, the first
and second exhaust slot. Referring to Fig. 7A to 7D, the transmission assembly 2'
includes the first, second and third gears 210', 211', 212'. The compression assembly
3' includes the first, second and third compression rotors 33', 34', 35', intermeshing
with one another and rotating in a direction of an arrow. The intake port 305' is
located above where the compression rotors 33', 34' intermesh with each other. The
intake port 305" is located under where the compression rotors 34', 35' intermesh
with each other. The first intake slots 31', 31" are respectively disposed on the
initial seal zone 90' where the compression rotors 33', 34' and 34', 35' initially
intermesh with each other. The second intake slot 32', 32", as shown in Fig. 7D, are
disposed on the second casing 303' corresponding to the middle compression rotor 34',
wherein the increasing second intake 32" is formed by duplicating and rotating the
second intake 32' about the center of the compression rotor 34'. The profile of the
second intake slot 32', 32" is generated by the same ways as described before in the
first embodiment.
[0039] Referring to Figs. 8A to 8C, the expansion assembly has the expansion rotors 43',
44', 46' intermeshing with one another and rotating in a direction of an arrow as
same as the direction of the compression rotors 33', 34', 35'. However, lobes of the
expansion rotors 43', 44', 46' disposed in counter direction to lobes of the compression
rotors 33', 34', 35'. The exhaust port 405' is located under where the expansion rotors
43', 44' intermesh with each other. The exhaust port 405" is located above where the
expansion rotors 44', 46' intermesh with each other. The first exhaust slots 41',
41" are disposed on the third casing 402' corresponding to the expansion rotor 44',
wherein the increasing first exhaust slot 41" is formed by duplicating and rotating
the first exhaust slot 41'. The profile of the first exhaust slots 41', 41" is generated
by the same ways as described before in the first embodiment. The second exhaust slots
42', 42" are respectively disposed on the ultimate seal zone 92' where the expansion
rotors 43', 44' and 44', 46' ultimately intermesh with each other.
[0040] Further referring to Fig. 10, the third embodiment of the present invention includes
multiple sets of the rotary positive displacement control apparatus 1 of the first
embodiment coupled with one another, each set of the rotary positive displacement
control apparatus 1 having the fuel injections assembly 6 to improve power output.
On the other hand, the present invention can be varied by adjusting number of the
compression and the expansion rotors to be in a ratio of 1:2 and adding one more set
of the compression assembly and the buffer assembly to maintain discharge in stable.
Moreover, the compression rotors 33, 34 and expansion rotors 43, 44 have the same
lobe number and rotor thickness or have the same rotor thickness but different number
of the lobes, for example, the thickness of the compression and expansion rotors is
the same, but the number of the lobes can be 3, 4 or 5 and so on; alternatively, the
thickness of the rotors can be different but the number of the lobes is the same or
both the number of lobes and the rotor thickness are different to each other and the
number of lobes configured at a ratio of 1:2 between the compression and expansion
rotors 33, 34 and 43, 44, for example, the compression rotor and the expansion rotor
have the same thickness, but the compression rotor has three lobes while the expansion
rotor has six lobes, or both the number of lobes and rotor thickness are different
to each other.
[0041] Further referring to Figs. 11A to 11B, the fourth embodiment of the present invention,
the differences among the present embodiment and the above-mentioned first to third
embodiments are shown in Fig. 11A, the base 50" with respect to the second intake
slot 32 (as labeled in Fig. 1) further including a second buffer chamber 511". The
second and first buffer chambers 511", 501" respectively have two communicating openings
508", 509" and 518", 519", functions of the two pairs of communication openings are
the same as that of the second intake slot 32(as labeled in Fig. 1). The second casing
303" as shown in Fig. 11B has the second intake 32" communicating with the first buffer
chamber 501", and a first extension hole 321" communicating with the second buffer
chamber 511". The third casing 402" as shown in Fig. 11C has the first exhaust slot
41" communicating with the first buffer chamber 501", and a second extension hole
411" communicating with the second buffer chamber 511".
[0042] Referring to Fig. 12, each lobe of the compression rotor 34" defines a second second
concavity 45" thereon, the second concavity 45" is defined by the same way as the
first concavity 45. An exhaust leading channel 38" is defined on the adjoining compression
rotor 33" intermeshing with the compression rotor 34" of the second concavity 45",
the exhaust leading channel 38" including a first opening 381" and a second opening
382" communicating with the first opening 381", wherein the first opening 381" is
defined on outer edges of the lobes of the compression rotor 33", and the second opening
382" is defined on inner regions of the base circle of the compression rotor 33" (as
labeled 340 in Fig. 3E). Similarly, as shown in Fig. 13, an intake leading channel
49" is defined on the adjoining expansion rotor 43" intermeshing with the expansion
rotor 44" of the first concavity 45, the intake leading channel 49" including a first
opening 491" and a second opening 492" communicating with the first opening 491",
wherein the first opening 491" is defined on outer edges of the lobes of the expansion
rotor 43", and the second opening 492" is defined on inner regions of the base circle
(referring to Fig. 4A) of the expansion rotor 43".
[0043] Further referring to Figs. 14A to 14F, to conduct the process of compressing and
exhausting air, first, adjust the two intermeshing compression rotors 33", 34" to
a position where pressure is suitable for communicating with the first and second
buffer chambers 501", 511" and is able to compress air (as shown in Fig. 14A). When
the compression rotors 33", 34" rotate, air is flowing into the first extension hole
321" from the second opening 382" of the exhaust leading channel 38" and then is exhausted
(as shown in Figs. 14B and 14C); in the mean time, air is flowing through the second
intake slot 32" from the second concavity 45" of the compression rotor 34" and then
is exhausted. As air compression is completed, the second intake slot 32" is veiled
by the compression rotor 34", the first extension hole 321" is veiled by the compression
rotor 33". In other words, air is exhausted from the exhaust leading channel 38" and
the second concavity 45" while the compression rotors 33", 34" are rotating. At the
time that air is being compressed and exhausted as illustrated in Figs. 14D to 14F,
the expansion rotors 43", 44' are driven simultaneously, and from the first opening
491" of the intake leading channel 49" of the expansion rotor 43" air is flowing through
the second extension hole 411", and from the first concavity 45 of the expansion rotor
44" air is flowing through the first exhaust slot 41 " and into the combustion area
91 " (as shown in Fig. 14E). As air exhaust is completed, the first exhaust slot 41"
is veiled by the expansion rotor 44", the second extension hole 411" is veiled by
the expansion rotor 43" (as shown in Fig. 14F), whereby air is apart from the combustion
area 91" to be ignited to explode.
[0044] Accordingly, it makes clear from the illustration of the fourth embodiment that after
adding the second buffer chamber 511", the second concavity 45", the first and the
second extension holes 321", 411", the exhaust leading channel 38" and the intake
leading channel 49", the loads of the compression rotors 33", 34" and the expansion
rotors 43", 44" are significantly decreased, so the performance is increased and can
provide better efficiency and performance than the aforementioned first, second, third
embodiments.
[0045] Further referring to Fig. 15 to Fig. 17A and 17B, the compression rotors 33, 34 and
the expansion rotors 43, 44 in the aforementioned embodiments can be arranged in different
phase angle, such as 0 degree and 30 degree, 0 degree and 48 degree, 0 degree and
60 degree, namely, the compression rotors and the expansions can be arranged in different
phase angle depending on the practical use.
[0046] It is understood that the invention may be embodied in other forms without departing
from the scope thereof as defined by the appended claims.
1. A rotary positive displacement control (1) apparatus, comprising a transmission assembly
(2), a compression assembly (3), a buffer assembly (5) and an expansion assembly (4),
wherein
the transmission assembly (2) includes an axial base (20), a plurality of transmission
members (210, 211) pivotally mounted on the axial base (20) and gearing with each
other, and a plurality of transmission shafts (22) for carrying the transmission members
(210, 211);
the compression assembly (3) including a sealing first chamber (30) which defines
a compression chamber (304) therein and has an intake port (305) communicating with
the compression chamber (304) for taking air in, multiple compression rotors (33,
34) pivotally mounted to the transmission shafts (22) and accommodated in the compression
chamber (304), the compression rotors (33, 34) intermeshing with each other, each
compression rotor (33, 34) having at least one lobe, a first intake slot (31), and
a second intake slot (32) respectively disposed on opposite sides of the first chamber
(30), wherein the first intake slot (31) is corresponding to an initial seal zone
(90) where the compression rotors (33, 34) initially intermesh with each other;
the buffer assembly (5) disposed between the compression assembly (3) and the expansion
assembly (4) and having a base and a first buffer chamber corresponding to the second
intake slot (32);
the expansion assembly (4) including a sealing second chamber (40) which defines an
expansion chamber (404) therein and having an exhaust port communicating with the
expansion chamber (404) for discharging air, a first exhaust slot (41) disposed thereon
and corresponding to the buffer chamber, multiple expansion rotors (43, 44) pivotally
mounted to the transmission shafts (22) and accommodated in the expansion chamber
(404), the expansion rotors (43, 44) intermeshing with each other, each expansion
rotor (43, 44) having at least one lobe (431, 441), the lobe (431, 441) disposed in
counter direction to the lobe of the compression rotors and having a first concavity
corresponding to the first exhaust slot, characterised by a second exhaust slot (42) disposed on the sealing second chamber (40) and corresponding
to an ultimate seal zone (92) where the expansion rotors (43, 44) ultimately intermesh
with each other.
2. The rotary positive displacement control apparatus as claimed in claim 1, wherein
the plurality of transmission members comprise at least a first gear, a second gear,
and transmission shafts for carrying the gears, each gear being engaged with each
other.
3. The rotary positive displacement control apparatus as claimed in either claim 1 or
claim 2, wherein a profile of the second intake slot is defined within three curves,
comprising: an arc of a base circle of one of the compression rotors (said arc drawn
with a minimum radius of the compression rotor), a profile curve of the lobe of the
compression rotor being tangent to said arc of the base circle, and a maximum curve
of the adjoining compression rotor drawn with a maximum radius thereof and being tangent
to said arc of the base circle.
4. The rotary positive displacement control apparatus as claimed in claim 3, wherein
the sealing first chamber is comprised of a first housing having the compression chamber
and the intake port thereon, and a first casing and a second casing sealing the first
housing respectively from opposite direction, the first and second casings having
coupling holes corresponding to the transmission shafts.
5. The rotary positive displacement control apparatus as claimed in any preceding claim,
wherein the compression and expansion rotors are identical in shape and have the same
lobe number and rotor thickness or have the same rotor thickness but different number
of the lobes, for example, the thickness of the compression and expansion rotors is
the same, but the number of the lobes can be 3, 4 or 5 and so on; alternatively, the
thickness of the rotors can be different but the number of the lobes is the same or
both the number of lobes and the rotor thickness are different to each other and the
number of lobes configured at a ratio of 1:2 between the compression and expansion
rotors, for example, the compression rotor and the expansion rotor have the same thickness,
but the compression rotor has three lobes while the expansion rotor has six lobes,
or both the number of lobes and rotor thickness are different to each other.
6. The rotary positive displacement control apparatus as claimed in claim 5, wherein
when the number of the lobes of the compression and expansion rotors is at a ratio
of 1:2, one more set of the compression assembly and the buffer assembly is required
for maintaining exhaust.
7. The rotary positive displacement control apparatus as claimed in claim 4, wherein
the sealing second chamber includes a second housing having the expansion chamber
and the exhaust port thereon, and a third casing and a fourth casing both sealingly
assembled on opposite sides of the second housing, the third and fourth casings having
coupling holes corresponding to the transmission shafts.
8. The rotary positive displacement control apparatus as claimed in claim 7, wherein
the first concavity of the lobe of the expansion rotor is defined by following steps:
as the intermeshing expansion rotors rotate up to a combustion area, designate a point
Q at circumference of the base circle of one of the expansion rotors, the point Q
corresponding to the combustion area, and draw a line QO by connecting the point Q
and a center O of the base circle; then rotate the expansion rotor backwards till
a recess of the lobe is against a tip of a lobe of an adjoining expansion rotor where
a point S is defined as an intersection of the tip and the recess of the lobe, and
a point P is defined as an intersection of a projecting curve of the lobe of the adjoining
expansion rotor and the recess of the lobe, and then respectively connect the point
S and P to the center O, whereby an angle SOP and angle SOQ are formed and subject
to change on rotation of the compassion rotors. Take the angle SOP as two times large
as the angle SOQ, then make an angle bisector of the angle SOP intersect the profile
of the expansion rotor at a point R to form an angle bisector OR; connect point R
and S to form a curve SR; draw an arc about the center O to intersect a line SO and
line RO to form an arc C; whereby, the first concavity is defined within an area of
the curve SR, the arc C, the line SO and line RO.
9. The rotary positive displacement control apparatus as claimed in claim 8, wherein
a profile of the first exhaust slot is defined within an area of the arc C, the line
QO and SO, and a segment of the profile of the expansion rotor being taken as the
combustion area appears.
10. The rotary positive displacement control system and apparatus as claimed in any preceding
claim, a profile of the second intake slot is defined within three curves, comprising:
an arc of a base circle of one of the compression rotors (said arc drawn with a minimum
radius of the compression rotor), a profile curve of the lobe of the compression rotor
being tangent to said arc of the base circle, and a maximum curve of the adjoining
compression rotor drawn with a maximum radius thereof and being tangent to said arc
of the base circle, wherein the additional second intake slot is added as number of
the compression rotor is more than two.
11. The rotary positive displacement control apparatus as claimed in any preceding claim
8-10, having a duplicate second exhaust slot rotated about the center O when the number
of compression rotors is more than two.
12. The rotary positive displacement control apparatus as claimed in any preceding claim,
further comprising a supplying assembly including a fuel injection means and a spark
plug both disposed in the expansion chamber in a radial or axial direction with respect
to a seal zone where the expansion rotors intermesh with each other.
13. The rotary positive displacement control apparatus as claimed in any preceding claim,
further comprising a fuel injection means disposed in the expansion chamber with respect
to a seal zone where the expansion rotors intermesh with each other.
14. The rotary positive displacement control apparatus as claimed in any preceding claim,
further comprising a power transmitting assembly including at least a motor pivotally
mounted to the transmission assembly.
15. The rotary positive displacement control apparatus as claimed in claim 2, wherein
the transmission assembly is coupled with multiple control systems in series in longitudinal
direction.
16. The rotary positive displacement control apparatus as claimed in claim 15, wherein
each control system includes a fuel injection means and a spark plug both disposed
in the expansion chamber in a radial or axial direction with respect to a seal zone
where the expansion rotors intermesh with each other.
17. The rotary positive displacement control apparatus as claimed in claim 15, wherein
each control system includes a fuel injection means disposed in the expansion chamber
in a radial or axial direction with respect to a seal zone where the expansion rotors
intermesh with each other.
18. The rotary positive displacement control apparatus as claimed in claim 1 or 9, further
comprising a second concavity formed on the compression rotor corresponding to the
second intake slot, the second concavity defined by the same way as the first concavity
of the lobe of the expansion rotor, an exhaust leading channel defined on the adjoining
compression rotor intermeshing with said compression rotor of said second concavity,
the exhaust leading channel including a first opening and a second opening communicating
with the first opening.
19. The rotary positive displacement control apparatus as claimed in claim 18, wherein
an intake leading channel defined on the adjoining expansion rotor intermeshing with
said expansion rotor of said concavity, the exhaust leading channel including a first
opening and a second opening communicating with the first opening.
20. The rotary positive displacement control apparatus as claimed in claim 19, wherein
the base further has a second buffer chamber corresponding to the second intake slot.
21. The rotary positive displacement control apparatus as claimed in claim 20, wherein
each of the first and second buffer chambers has two communicating openings.
22. The rotary positive displacement control apparatus as claimed in claim 21, wherein
the first opening of the exhaust leading channel is defined on outer edges of the
lobes of the compression rotor, and the second opening is defined on inner regions
of the base circle of the compression rotor.
23. The rotary positive displacement control apparatus as claimed in claim 22, wherein
the first opening of the intake leading channel is defined on outer edges of the lobes
of the expansion rotor, and the second opening is defined on inner regions of the
base circle of the expansion rotor.
24. The rotary positive displacement control apparatus as claimed in claim 23, wherein
the second casing having a first extension hole communicating with the second buffer
chamber.
25. The rotary positive displacement control apparatus as claimed in claim 24, wherein
the third casing having a second extension hole communication with the second buffer
chamber.
26. The rotary positive displacement control apparatus as claimed in any preceding claim,
wherein the compression rotor and the expansion rotor can be arranged in different
phase angle.
27. The rotary positive displacement control apparatus as claimed in claim 18, wherein
the compression rotor and the expansion rotor can be arranged in different phase angle.
1. Rotationsverdrängungssteuervorrichtung (1), die eine Getriebeanordnung (2), eine Verdichtungsanordnung
(3), eine Pufferanordnung (5) und eine Ausdehnungsanordnung (4) umfasst, wobei:
die Getriebeanordnung (2) eine axiale Basis (20), eine Vielzahl von Getriebeelementen
(210, 211), die schwenkbar an der axialen Basis (20) montiert sind und miteinander
kämmen, und eine Vielzahl von Getriebewellen (22) zum Tragen der Getriebeelemente
(210, 211) beinhaltet,
die Verdichtungsanordnung (3) eine abdichtende erste Kammer (30) beinhaltet, die eine
Verdichtungskammer (304) in ihr definiert und Folgendes hat: eine mit der Verdichtungskammer
(304) kommunizierende Einlassöffnung (305) zum Aufnehmen von Luft, mehrere Verdichtungsläufer
(33, 34), die schwenkbar an den Getriebewellen (22) montiert und in der Verdichtungskammer
(304) aufgenommen sind, wobei die Verdichtungsläufer (33, 34) ineinandergreifen, wobei
jeder Verdichtungsläufer (33, 34) wenigstens einen Läuferflügel hat, eine erste Einlassaussparung
(31) und eine zweite Einlassaussparung (32), die jeweils an einander entgegengesetzten
Seiten der ersten Kammer (30) angeordnet sind, wobei die erste Einlassaussparung (31)
einer Anfangsdichtungszone (90) entspricht, wo die Verdichtungsläufer (33, 34) anfänglich
ineinandergreifen,
die Pufferanordnung (5) zwischen der Verdichtungsanordnung (3) und der Ausdehnungsanordnung
(4) angeordnet ist und eine Basis und eine der zweiten Einlassaussparung (32) entsprechende
erste Pufferkammer hat,
die Ausdehnungsanordnung (4) eine abdichtende zweite Kammer (40) beinhaltet, die darin
eine Ausdehnungskammer (404) definiert, und Folgendes hat: eine mit der Ausdehnungskammer
(404) kommunizierende Auslassöffnung zum Ablassen von Luft hat, eine erste Auslassausparung
(41), die daran angeordnet ist und der Pufferkammer entspricht, mehrere Ausdehnungsläufer
(43, 44), die schwenkbar an den Getriebewellen (22) montiert sind und in der Ausdehnungskammer
(404) aufgenommen sind, wobei die Ausdehnungsläufer (43, 44) miteinander kämmen, wobei
jeder Ausdehnungsläufer (43, 44) wenigstens einen Läuferflügel (431, 441) hat, wobei
der Läuferflügel (431, 441) in der Gegenrichtung zum Läuferflügel der Verdichtungsläufer
angeordnet ist und eine erste Höhlung hat, die der ersten Ausdehnungsaussparung entspricht,
dadurch gekennzeichnet, dass an der abdichtenden zweiten Kammer (40) eine zweite Ausdehnungsaussparung (42) angeordnet
ist und einer Endabdichtungszone (92) entspricht, wo die Ausdehnungsläufer (43, 44)
am stärksten kämmen.
2. Rotationsverdrängungssteuervorrichtung nach Anspruch 1, wobei die Vielzahl von Getriebeelementen
wenigstens ein erstes Zahnrad, ein zweites Zahnrad und Getriebewellen zum Tragen der
Zahnräder aufweist, wobei die Zahnräder jeweils miteinander in Eingriff sind.
3. Rotationsverdrängungssteuervorrichtung nach Anspruch 1 oder Anspruch 2, wobei ein
Profil der zweiten Einlassaussparung in drei Kurven definiert ist, umfassend: einen
Bogen eines Grundkreises von einem der Verdichtungsläufer (wobei der genannte Bogen
mit einem Mindestradius des Verdichtungsläufers gezogen wird), eine Profilkurve des
Läuferflügels des Verdichtungsläufers, die zum genannten Bogen des Grundkreises tangential
ist, und eine maximale Kurve des angrenzenden Verdichtungsläufers, die mit einem maximalen
Radius davon gezogen wird und zu dem genannten Bogen des Grundkreises tangential ist.
4. Rotationsverdrängungssteuervorrichtung nach Anspruch 3, wobei die dichtende erste
Kammer ein erstes Gehäuse mit daran befindlicher Verdichtungskammer und Einlassöffnung
umfasst und ein erstes Verkleidungsteil und ein zweites Verkleidungsteil das erste
Gehäuse von jeweils entgegengesetzten Richtungen her abdichten, wobei das erste und
das zweite Verkleidungsteil den Getriebewellen entsprechende Verbindungslöcher haben.
5. Rotationsverdrängungssteuervorrichtung nach einem der vorhergehenden Ansprüche, wobei
der Verdichtungs- und der Ausdehnungsläufer eine identische Gestalt haben und die
gleiche Läuferflügelzahl und Läuferdicke haben oder die gleiche Läuferdicke, aber
eine unterschiedliche Läuferflügelzahl haben, wobei zum Beispiel die Dicke des Verdichtungs-
und des Ausdehnungsläufers gleich ist, aber die Zahl der Läuferflügel 3, 4 oder 5
und so weiter sein kann, alternativ die Dicke der Läufer verschieden sein kann, aber
die Zahl der Läuferflügel gleich ist oder die Zahl der Läuferflügel und die Läuferdicke
beide verschieden sind und die Zahl der Läuferflügel in einem Verhältnis von 1:2 zwischen
Verdichtungs- und Ausdehnungsläufer gestaltet sind, wobei zum Beispiel der Verdichtungsläufer
und der Ausdehnungsläufer die gleiche Dicke haben, aber der Verdichtungsläufer drei
Läuferflügel hat, während der Ausdehnungsläufer sechs Läuferflügel hat, oder die Läuferflügelzahl
und die Läuferdicke beide verschieden sind.
6. Rotationsverdrängungssteuervorrichtung nach Anspruch 5, wobei, wenn die Zahl der Läuferflügel
des Verdichtungs- und des Ausdehnungsläufers im Verhältnis von 1:2 ist, zum Aufrechterhalten
der Auslassleistung ein weiterer Satz der Verdichtungsanordnung und der Pufferanordnung
erforderlich ist.
7. Rotationsverdrängungssteuervorrichtung nach Anspruch 4, wobei die dichtende zweite
Kammer ein zweites Gehäuse mit daran befindlicher Ausdehnungskammer und Auslassöffnung
hat und ein drittes Verkleidungsteil und ein viertes Verkleidungsteil aufweist, die
beide dichtend an einander entgegengesetzten Seiten des zweiten Gehäuses angebracht
sind, wobei das dritte und das vierte Verkleidungsteil den Getriebewellen entsprechende
Verbindungslöcher haben.
8. Rotationsverdrängungssteuervorrichtung nach Anspruch 7, wobei die erste Höhlung des
Läuferflügels des Ausdehnungsläufers durch die folgenden Schritte definiert wird:
beim Herandrehen der kämmenden Ausdehnungsläufer hin zu einem Verbrennungsbereich,
Bestimmen eines Punkts Q am Umfang des Grundkreises von einem der Ausdehnungsläufer,
wobei der Punkt Q dem Verbrennungsbereich entspricht, und Ziehen einer Linie QO durch
Verbinden des Punktes Q und einer Mitte O des Grundkreises, dann Rückwärtsdrehen des
Ausdehnungsläufers, bis eine Ausnehmung des Läuferflügels an einer Spitze eines Läuferflügels
eines angrenzenden Ausdehnungsläufers anliegt, wo ein Punkt S als Schnittpunkt der
Spitze und der Ausnehmung des Läuferflügels definiert wird und ein Punkt P als ein
Schnittpunkt einer vorspringenden Kurve des Läuferflügels des angrenzenden Ausdehnungsläufers
und der Ausnehmung des Läuferflügels definiert wird, und dann jeweils Verbinden von
Punkt S und P mit der Mitte O, wodurch ein Winkel SOP und ein Winkel SOQ gebildet
werden und bei Drehung der Verdichtungsläufer Veränderungen unterliegen, Annehmen
des Winkels SOP als zweimal so groß wie der Winkel SOQ, dann eine Winkelhalbierenden
des Winkels SOP das Profils des Ausdehnungsläufers an einem Punkt R schneiden lassen,
um eine Winkelhalbierende OR zu bilden, Verbinden von Punkt R und S, um eine Kurve
SR zu bilden, Ziehen eines Bogens um die Mitte O, um eine Linie SO und eine Linie
RO zu schneiden, um einen Bogen C zu bilden, wodurch die erste Höhlung in einem Bereich
der Kurve SR, des Bogens C, der Linie SO und der Linie RO definiert wird.
9. Rotationsverdrängungssteuervorrichtung nach Anspruch 8, wobei ein Profil der ersten
Auslassaussparung in einem Bereich des Bogens C, der Linie QO und der Linie SO definiert
wird und ein Segment des Profils des Ausdehnungsläufers, das als der Verbrennungsbereich
angenommen wird, erscheint.
10. Rotationsverdrängungssteuersystem und -vorrichtung nach einem der vorhergehenden Ansprüche,
wobei ein Profil der zweiten Einlassaussparung innerhalb von drei Kurven definiert
wird, umfassend: einen Bogen eines Grundkreises von einem der Verdichtungsläufer (wobei
der genannte Bogen mit einem Mindestradius des Verdichtungsläufers gezogen wird),
eine Profilkurve des Läuferflügels des Verdichtungsläufers, die zu dem genannten Bogen
des Grundkreises tangential ist, und eine maximale Kurve des angrenzenden Verdichtungsläufers,
die mit einem maximalen Radius davon gezogen wird und zu dem genannten Bogen des Grundkreises
tangential ist, wobei die zusätzliche zweite Einlassaussparung addiert wird, da die
Verdichtungsläuferzahl größer als zwei ist.
11. Rotationsverdrängungssteuervorrichtung nach einem der vorhergehenden Ansprüche 8 bis
10, die eine um die Mitte O gedrehte duplizierte zweite Auslassaussparung hat, wenn
die Verdichtungsläuferzahl größer als zwei ist.
12. Rotationsverdrängungssteuervorrichtung nach einem der vorhergehenden Ansprüche, die
ferner eine Zuführanordnung einschließlich einer Kraftstoffeinspritzvorrichtung und
einer Zündkerze aufweist, die beide in der Ausdehnungskammer in einer radialen oder
axialen Richtung in Bezug auf eine Dichtungszone angeordnet sind, wo die Ausdehnungsläufer
miteinander kämmen.
13. Rotationsverdrängungssteuervorrichtung nach einem der vorhergehenden Ansprüche, die
ferner eine Kraftstoffeinspritzvorrichtung aufweist, die in der Ausdehnungskammer
in Bezug auf eine Dichtungszone angeordnet ist, wo die Ausdehnungsläufer miteinander
kämmen.
14. Rotationsverdrängungssteuervorrichtung nach einem der vorhergehenden Ansprüche, die
ferner eine kraftübertragende Anordnung aufweist, die wenigstens einen schwenkbar
an der Getriebeanordnung montierten Motor beinhaltet.
15. Rotationsverdrängungssteuervorrichtung nach Anspruch 2, wobei die Getriebeanordnung
in Längsrichtung mit mehreren Steuersystemen in Reihe gekoppelt ist.
16. Rotationsverdrängungssteuervorrichtung nach Anspruch 15, wobei jedes Steuersystem
eine Kraftstoffeinspritzvorrichtung und eine Zündkerze aufweist, die beide in der
Ausdehnungskammer in einer radialen oder axialen Richtung in Bezug auf eine Dichtungszone
angeordnet sind, wo die Ausdehnungsläufer miteinander kämmen.
17. Rotationsverdrängungssteuervorrichtung nach Anspruch 15, wobei jedes Steuersystem
eine Kraftstoffeinspritzvorrichtung aufweist, die in der Ausdehnungskammer in einer
radialen oder axialen Richtung in Bezug auf eine Dichtungszone angeordnet sind, wo
die Ausdehnungsläufer miteinander kämmen.
18. Rotationsverdrängungssteuervorrichtung nach Anspruch 1 oder 9, die ferner eine zweite
an dem Verdichtungsläufer ausgebildete Höhlung aufweist, die der zweiten Einlassaussparung
entspricht, wobei die zweite Höhlung auf die gleiche Weise wie die erste Höhlung des
Läuferflügels des Ausdehnungsläufers definiert wurde, wobei ein Auslassleitungskanal
an dem angrenzenden Verdichtungsläufer definiert ist, der mit dem genannten Verdichtungsläufer
der genannten zweiten Höhlung kämmt, wobei der Auslassleitungskanal eine erste Öffnung
und eine mit der ersten Öffnung kommunizierende zweite Öffnung aufweist.
19. Rotationsverdrängungssteuervorrichtung nach Anspruch 18, wobei ein Einlassleitungskanal
an dem angrenzenden Verdichtungsläufer definiert ist, der mit dem genannten Verdichtungsläufer
der genannten Höhlung kämmt, wobei der Auslassleitungskanal eine erste Öffnung und
eine mit der ersten Öffnung kommunizierende zweite Öffnung aufweist.
20. Rotationsverdrängungssteuervorrichtung nach Anspruch 19, wobei die Basis ferner eine
zweite Pufferkammer hat, die der zweiten Einlassaussparung entspricht.
21. Rotationsverdrängungssteuervorrichtung nach Anspruch 20, wobei die erste und die zweite
Pufferkammer jeweils zwei Kommunikationsöffnungen haben.
22. Rotationsverdrängungssteuervorrichtung nach Anspruch 21, wobei die erste Öffnung des
Auslassleitungskanals an Außenrändern der Lüfterflügel des Verdichtungsläufers definiert
ist und die zweite Öffnung an inneren Regionen des Grundkreises des Verdichtungsläufers
definiert ist.
23. Rotationsverdrängungssteuervorrichtung nach Anspruch 22, wobei die erste Öffnung des
Einlassleitungskanals an Außenrändern der Lüfterflügel des Ausdehnungsläufers definiert
ist und die zweite Öffnung an inneren Regionen des Grundkreises des Ausdehnungsläufers
definiert ist.
24. Rotationsverdrängungssteuervorrichtung nach Anspruch 23, wobei das zweite Verkleidungsteil
ein erstes Verlängerungsloch hat, das mit der zweiten Pufferkammer kommuniziert.
25. Rotationsverdrängungssteuervorrichtung nach Anspruch 24, wobei das dritte Verkleidungsteil
ein zweites Verlängerungsloch hat, das mit der zweiten Pufferkammer kommuniziert.
26. Rotationsverdrängungssteuervorrichtung nach einem der vorhergehenden Ansprüche, wobei
der Verdichtungsläufer und der Ausdehnungsläufer in verschiedenen Phasenwinkeln angeordnet
sein können.
27. Rotationsverdrängungssteuervorrichtung nach Anspruch 26, wobei der Verdichtungsläufer
und der Ausdehnungsläufer in verschiedenen Phasenwinkeln angeordnet sein können.
1. Appareil de commande à déplacement positif rotatif (1), comprenant un ensemble de
transmission (2), un ensemble de compression (3), un ensemble tampon (5) et un ensemble
d'expansion (4), où
l'ensemble de transmission (2) comprend une base axiale (20), une pluralité d'éléments
de transmission (210, 211) montés pivotants sur la base axiale (20) et s'engrenant
les uns avec les autres, et une pluralité d'arbres de transmission (22) destinés à
porter les éléments de transmission (210, 211),
l'ensemble de compression (3) comprend une première chambre d'étanchéité (30) qui
définit une chambre de compression (304) dans celui-ci et qui possède un port d'admission
(305) communiquant avec la chambre de compression (304) de façon à aspirer de l'air,
plusieurs rotors de compression (33, 34) montés pivotants sur les arbres de transmission
(22) et logés dans la chambre de compression (304), les rotors de compression (33,
34) s'engrenant les uns avec les autres, chaque rotor de compression (33, 34) possédant
au moins un lobe, une première fente d'admission (31) et une deuxième fente d'admission
(32) disposées respectivement sur des côtés opposés de la première chambre (30) où
la première fente d'admission (31) correspond à une zone d'étanchéité initiale (90)
dans laquelle les rotors de compression (33, 34) s'engrènent initialement les uns
avec les autres,
l'ensemble tampon (5) est disposé entre l'ensemble de compression (3) et l'ensemble
d'expansion (4) et possède une base et une première chambre tampon correspondant à
la deuxième fente d'admission (32),
l'ensemble d'expansion (4) comprend une deuxième chambre d'étanchéité (40) qui définit
une chambre d'expansion (404) dans celle-ci et possède un port d'échappement communiquant
avec la chambre d'expansion (404) de façon à évacuer de l'air, une première fente
d'échappement (41) disposée sur celui-ci et correspondant à la chambre tampon, plusieurs
rotors d'expansion (43, 44) montés pivotants sur les arbres de transmission (22) et
logés dans la chambre d'expansion, les rotors d'expansion (43, 44) s'engrenant les
uns avec les autres, chaque rotor d'expansion (43, 44) possédant au moins un lobe
(431, 441), le lobe (431, 441) étant disposé à contre-sens du lobe des rotors de compression
et possédant une première concavité correspondant à la première fente d'échappement,
caractérisé par une deuxième fente d'échappement (42) disposée sur la deuxième chambre d'étanchéité
(40) correspondant à une zone d'étanchéité finale (92) dans laquelle les rotors d'expansion
(43, 44) s'engrènent finalement les uns avec les autres.
2. Appareil de commande à déplacement positif rotatif selon la Revendication 1, où la
pluralité d'éléments de transmission comprend au moins un premier engrenage, un deuxième
engrenage et des arbres de transmission destinés à porter les engrenages, chaque engrenage
étant en prise avec les autres.
3. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
1 ou 2, où un profil de la deuxième fente d'admission est défini à l'intérieur de
trois courbes, comprenant : un arc d'un cercle de base de l'un des rotors de compression
(ledit arc étant tracé avec un rayon minimal du rotor de compression), une courbe
de profil du lobe du rotor de compression étant tangente audit arc du cercle de base,
et une courbe maximale du rotor de compression voisin étant tracée avec un rayon maximal
de celui-ci et étant tangente audit arc du cercle de base.
4. Appareil de commande à déplacement positif rotatif selon la Revendication 3, où la
première chambre d'étanchéité se compose d'un premier logement possédant la chambre
de compression et le port d'admission sur celui-ci, et un premier boîtier et un deuxième
boîtier scellant le premier logement respectivement à partir d'une direction opposée,
les premier et deuxième boîtiers possédant des orifices de couplage correspondant
aux arbres de transmission.
5. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
précédentes, où les rotors de compression et d'expansion sont identiques en termes
de forme et possèdent le même nombre de lobes et la même épaisseur de rotor ou possèdent
la même épaisseur de rotor mais un nombre différent de lobes, par exemple, l'épaisseur
des rotors de compression et d'expansion est la même, mais le nombre de lobes peut
être 3, 4 ou 5 et ainsi de suite ; dans une variante, l'épaisseur des rotors peut
être différente mais le nombre de lobes est le même ou à la fois le nombre de lobes
et l'épaisseur de rotor sont différents les uns des autres et le nombre de lobes est
configuré selon un rapport de 1:2 entre les rotors de compression et d'expansion,
par exemple, le rotor de compression et le rotor d'expansion possèdent la même épaisseur,
mais le rotor de compression possède trois lobes tandis que le rotor d'expansion possède
six lobes, ou à la fois le nombre de lobes et l'épaisseur de rotor sont différents
les uns des autres.
6. Appareil de commande à déplacement positif rotatif selon la Revendication 5, où, lorsque
le nombre de lobes des rotors de compression et d'expansion est d'un rapport de 1:2,
un jeu supplémentaire de l'ensemble de compression et de l'ensemble tampon est nécessaire
pour maintenir l'échappement.
7. Appareil de commande à déplacement positif rotatif selon la Revendication 4, où la
deuxième chambre d'étanchéité comprend un deuxième logement possédant la chambre d'expansion
et le port d'échappement sur celui-ci, et un troisième boîtier et un quatrième boîtier
tous les deux assemblés de manière étanche sur des côtés opposés du deuxième logement,
les troisième et quatrième boîtiers possédant des orifices de couplage correspondant
aux arbres de transmission.
8. Appareil de commande à déplacement positif rotatif selon la Revendication 7, où la
première concavité du lobe du rotor d'expansion est définie par les opérations suivantes
:
tandis que les rotors d'expansion engrenés pivotent jusqu'à une surface de combustion,
désignez un point Q sur la circonférence du cercle de base de l'un des rotors d'expansion,
le point Q correspondant à la surface de combustion, et tracez une ligne QO en reliant
le point Q et un centre O du cercle de base ; ensuite faites pivoter le rotor d'expansion
dans le sens contraire jusqu'à ce qu'un renfoncement du lobe soit contre une pointe
d'un lobe d'un rotor d'expansion voisin où un point S est défini en tant qu'intersection
de la pointe et du renfoncement du lobe, et un point P est défini en tant qu'intersection
d'une courbe faisant saillie du lobe du rotor d'expansion voisin et du renfoncement
du lobe, et ensuite joignez respectivement les points S et P au centre O, grâce à
quoi un angle SOP et un angle SOQ sont formés et soumis à changement par la rotation
des rotors de compression. Considérez l'angle SOP deux fois plus grand que l'angle
SOQ, ensuite faites intersecter une bissectrice d'angle de l'angle SOP avec le profil
du rotor d'expansion à un point R de façon à former une bissectrice d'angle OR ; joignez
les points R et S de façon à former une courbe SR, tracez un arc autour du centre
O de façon à intersecter une ligne SO et une ligne RO de façon à former un arc C ;
grâce à quoi, la première concavité est définie à l'intérieur d'une surface de la
courbe SR, de l'arc C, de la ligne SO et de la ligne RO.
9. Appareil de commande à déplacement positif rotatif selon la Revendication 8, où un
profil de la première fente d'échappement est défini à l'intérieur d'une surface de
l'arc C, de la ligne QO et de la ligne SO, et un segment du profil du rotor d'expansion
qui est considéré en tant que surface de combustion apparaît.
10. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
précédentes, où un profil de la deuxième fente d'admission est défini à l'intérieur
de trois courbes, comprenant : un arc d'un cercle de base de l'un des rotors de compression
(ledit arc étant tracé avec un rayon minimal du rotor de compression), une courbe
de profil du lobe du rotor de compression étant tangente audit arc du cercle de base
et une courbe maximale du rotor de compression voisin étant tracée avec un rayon maximal
de celui-ci et étant tangente audit arc du cercle de base, où la deuxième fente d'admission
additionnelle est ajoutée si le nombre de rotors de compression est supérieur à deux.
11. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
8 à 10 possédant un doublon de la deuxième fente d'échappement pivotée autour du centre
O lorsque le nombre de rotors de compression est supérieur à deux.
12. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
précédentes, comprenant en outre un ensemble d'alimentation comprenant un moyen d'injection
de carburant et une bougie d'allumage, les deux étant disposés dans la chambre d'expansion
dans une direction radiale ou axiale par rapport à une zone d'étanchéité où les rotors
d'expansion s'engrènent les uns avec les autres.
13. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
précédentes, comprenant en outre un moyen d'injection de carburant disposé dans la
chambre d'expansion par rapport à une zone d'étanchéité où les rotors d'expansion
s'engrènent les uns avec les autres.
14. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
précédentes, comprenant en outre un ensemble de transmission d'énergie comprenant
au moins un moteur monté pivotant sur l'ensemble de transmission.
15. Appareil de commande à déplacement positif rotatif selon la Revendication 2, où l'ensemble
de transmission est couplé à plusieurs systèmes de commande en série dans une direction
longitudinale.
16. Appareil de commande à déplacement positif rotatif selon la Revendication 15, où chaque
système de commande comprend un moyen d'injection de carburant et une bougie d'allumage,
les deux étant disposés dans la chambre d'expansion dans une direction axiale ou radiale
par rapport à une zone d'étanchéité où les rotors d'expansion s'engrènent les uns
avec les autres.
17. Appareil de commande à déplacement positif rotatif selon la Revendication 15, où chaque
système de commande comprend un moyen d'injection de carburant disposé dans la chambre
d'expansion dans une direction axiale ou radiale par rapport à une zone d'étanchéité
où les rotors d'expansion s'engrènent les uns avec les autres.
18. Appareil de commande à déplacement positif rotatif selon la Revendication 1 ou 9,
comprenant en outre une deuxième concavité formée sur le rotor de compression correspondant
à la deuxième fente d'admission, la deuxième concavité étant définie de la même manière
que la première concavité du lobe du rotor d'expansion, un canal d'amenée d'échappement
défini sur le rotor de compression voisin s'engrenant avec ledit rotor de compression
de ladite deuxième concavité, le canal d'amenée d'échappement comprenant une première
ouverture et une deuxième ouverture communiquant avec la première ouverture.
19. Appareil de commande à déplacement positif rotatif selon la Revendication 18, où un
canal d'amenée d'admission défini sur le rotor d'expansion voisin s'engrène avec ledit
rotor d'expansion de ladite concavité, le canal d'amenée d'échappement comprenant
une première ouverture et une deuxième ouverture communiquant avec la première ouverture.
20. Appareil de commande à déplacement positif rotatif selon la Revendication 19, où la
base possède en outre une deuxième chambre tampon correspondant à la deuxième fente
d'admission.
21. Appareil de commande à déplacement positif rotatif selon la Revendication 20, où chacune
des première et deuxième chambres tampons possède deux ouvertures de communication.
22. Appareil de commande à déplacement positif rotatif selon la Revendication 21, où la
première ouverture du canal d'amenée d'échappement est définie sur des bordures extérieures
des lobes du rotor de compression, et la deuxième ouverture est définie sur des zones
intérieures du cercle de base du rotor de compression.
23. Appareil de commande à déplacement positif rotatif selon la Revendication 22, où la
première ouverture du canal d'amenée d'admission est définie sur des bordures extérieures
des lobes du rotor d'expansion et la deuxième ouverture est définie sur des zones
intérieures du cercle de base du rotor d'expansion.
24. Appareil de commande à déplacement positif rotatif selon la Revendication 23, où le
deuxième boîtier possède un premier orifice d'extension communiquant avec la deuxième
chambre tampon.
25. Appareil de commande à déplacement positif rotatif selon la Revendication 24, où le
troisième boîtier possède un deuxième orifice d'extension communiquant avec la deuxième
chambre tampon.
26. Appareil de commande à déplacement positif rotatif selon l'une quelconque des Revendications
précédentes, où le rotor de compression et le rotor d'expansion peuvent être agencés
selon un angle de phase différent.
27. Appareil de commande à déplacement positif rotatif selon la Revendication 18, où le
rotor de compression et le rotor d'expansion peuvent être agencés selon un angle de
phase différent.
REFERENCES CITED IN THE DESCRIPTION
This list of references cited by the applicant is for the reader's convenience only.
It does not form part of the European patent document. Even though great care has
been taken in compiling the references, errors or omissions cannot be excluded and
the EPO disclaims all liability in this regard.
Patent documents cited in the description