U.S. patent application number 14/535346 was filed with the patent office on 2015-03-05 for turbine.
The applicant listed for this patent is Yanzhao LI, Yongtai LI, Yingxin LIU, Hang WANG, Yanxia WANG, Daojun YUAN, Zhifu ZHU. Invention is credited to Yanzhao LI, Yongtai LI, Yingxin LIU, Hang WANG, Yanxia WANG, Daojun YUAN, Zhifu ZHU.
Application Number | 20150063991 14/535346 |
Document ID | / |
Family ID | 46770744 |
Filed Date | 2015-03-05 |
United States Patent
Application |
20150063991 |
Kind Code |
A1 |
WANG; Hang ; et al. |
March 5, 2015 |
TURBINE
Abstract
A turbine, including: a volute and an impeller. The volute
includes: a volute gas inlet, a volute gas feeding flow passage,
and a volute gas outlet. The impeller includes: blades, an impeller
gas feeding flow passage, an impeller gas inlet, an impeller gas
outlet, and a partition plate. The impeller gas feeding flow
passage includes: an inner flow passage and an outer flow passage.
The impeller is disposed inside the volute. The blades are disposed
on an outer part of the impeller. The partition plate is
circumferentially disposed between the impeller gas inlet and the
impeller gas outlet. The partition plate divides the impeller gas
feeding flow passage into the inner flow passage and the outer flow
passage.
Inventors: |
WANG; Hang; (Shouguang,
CN) ; LI; Yongtai; (Shouguang, CN) ; LI;
Yanzhao; (Shouguang, CN) ; ZHU; Zhifu;
(Shouguang, CN) ; YUAN; Daojun; (Shouguang,
CN) ; WANG; Yanxia; (Shouguang, CN) ; LIU;
Yingxin; (Shouguang, CN) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
WANG; Hang
LI; Yongtai
LI; Yanzhao
ZHU; Zhifu
YUAN; Daojun
WANG; Yanxia
LIU; Yingxin |
Shouguang
Shouguang
Shouguang
Shouguang
Shouguang
Shouguang
Shouguang |
|
CN
CN
CN
CN
CN
CN
CN |
|
|
Family ID: |
46770744 |
Appl. No.: |
14/535346 |
Filed: |
November 7, 2014 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
PCT/CN2012/000714 |
May 22, 2012 |
|
|
|
14535346 |
|
|
|
|
Current U.S.
Class: |
415/187 ;
415/203 |
Current CPC
Class: |
F01D 25/24 20130101;
Y02T 10/144 20130101; F01D 9/026 20130101; Y02T 10/12 20130101;
F05D 2220/40 20130101; F02B 37/025 20130101; F02B 37/22 20130101;
F01D 9/048 20130101 |
Class at
Publication: |
415/187 ;
415/203 |
International
Class: |
F01D 9/04 20060101
F01D009/04; F01D 25/24 20060101 F01D025/24 |
Foreign Application Data
Date |
Code |
Application Number |
May 7, 2012 |
CN |
201210137082.5 |
Claims
1. A turbine, comprising: a) a volute, the volute comprising: a
volute gas inlet, a volute gas feeding flow passage, and a volute
gas outlet; and b) an impeller, the impeller comprising: blades, an
impeller gas feeding flow passage, an impeller gas inlet, an
impeller gas outlet, and a partition plate; the impeller gas
feeding flow passage comprising an inner flow passage and an outer
flow passage; wherein the impeller is disposed inside the volute;
the blades are disposed on an outer part of the impeller; the
partition plate is circumferentially disposed between the impeller
gas inlet and the impeller gas outlet; and the partition plate
divides the impeller gas feeding flow passage into the inner flow
passage and the outer flow passage.
2. The turbine of claim 1, wherein the volute gas feeding flow
passage comprises a middle partition, and the middle partition
divides the volute gas feeding flow passage into a left flow
passage and a right flow passage; the left flow passage
communicates with the inner flow passage; and the right flow
passage communicates with the outer flow passage.
3. The turbine of claim 2, wherein the left flow passage comprises
a gas outlet of the left flow passage in the vicinity of the
impeller; the right flow passage comprises a gas outlet of the
right flow passage in the vicinity of the impeller; the inner flow
passage comprises a gas inlet of the inner flow passage
corresponding to the gas outlet of the left flow passage; and the
outer flow passage comprises a gas inlet of the outer flow passage
corresponding to the gas outlet of the right flow passage.
4. The turbine of claim 3, wherein a ratio of a width W1 of the gas
inlet of the inner flow passage to a width W2 of the gas inlet of
the outer flow passage is between 0.1 and 10.
5. The turbine of claim 4, wherein the inner flow passage is a
radial inflow channel.
6. The turbine of claim 4, wherein the inner flow passage is a
Francis channel.
7. The turbine of claim 4, wherein the outer flow passage is a
radial inflow channel.
8. The turbine of claim 4, wherein the outer flow passage is a
Francis channel.
9. The turbine of claim 4, wherein a ratio of a width W3 of the gas
outlet of the inner flow passage to a width W4 of the gas outlet of
the outer flow passage is between 0.1 and 10.
10. The turbine of claim 9, wherein the blade comprises inner
blades correspondingly disposed inside the inner flow passage and
outer blades correspondingly disposed inside the outer flow
passage.
11. The turbine of claim 10, wherein a ratio of a number of the
inner blades to a number of the outer blades is between 0.2 and
6.
12. The turbine of claim 11, wherein an adjustable valve is
disposed inside the left flow passage in the vicinity of the volute
gas inlet; and the adjustable valve is connected to a control
mechanism.
13. The turbine of claim 11, wherein an adjustable valve is
disposed inside the right flow passage in the vicinity of the
volute gas inlet; and the adjustable valve is connected to a
control mechanism.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application is a continuation-in-part of International
Patent Application No. PCT/CN2012/000714 with an international
filing date of May 22, 2012, designating the United States, now
pending, and further claims priority benefits to Chinese Patent
Application No. 201210137082.5 filed May 7, 2012. The contents of
all of the aforementioned applications, including any intervening
amendments thereto, are incorporated herein by reference. Inquiries
from the public to applicants or assignees concerning this document
or the related applications should be directed to: Matthias Scholl
P.C., Attn.: Dr. Matthias Scholl Esq., 245 First Street, 18th
Floor, Cambridge, Mass. 02142.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] The invention relates to the field of turbocharging of an
internal combustion engine, and more particularly to a turbine.
[0004] 2. Description of the Related Art
[0005] A typical double-layer flow passage cross-section variable
turbocharger, as shown in FIG. 1, includes a turbine. The turbine
includes a volute 1 and an impeller 2. The volute 1 includes: a
volute gas inlet 3, a volute gas feeding flow passage, and a volute
gas outlet 4. A middle partition 5 is circumferentially disposed
inside the volute gas feeding flow passage. The middle partition 5
divides the volute gas feeding flow passage into a left flow
passage 6 and a right flow passage 7. The impeller 2 includes: an
impeller gas inlet 8, an impeller gas feeding flow passage 9, and
an impeller gas outlet 10. A valve control mechanism is disposed at
the left flow passage 6 or at the right flow passage 7 in the
vicinity of the volute gas inlet 3 for realizing single flow
passage working or double-flow passage co-working, thereby changing
the flow area of the volute flow passage.
[0006] However, in practical applications, when the motor operates
at low speeds, the efficiency of the turbine is relatively low
because only a single flow passage of the volute is utilized and
the exhaust gas discharged from the motor enters the volute gas
inlet and passes through the single flow passage to reach the gas
outlet of the single flow passage where sudden expansion of the gas
easily occurs, so that the gas entering the impeller gas feeding
flow passage from the impeller gas inlet is reduced. Also, when the
motor operates at middle or high speeds, the efficiency of the
turbine is relatively low because while both of the flow passages
of the volute are utilized, the exhaust gas discharged from the
motor enters the volute gas inlet and passes through the double
flow passages to reach the impeller gas inlet where the gas of the
two flow passages is mixed, so that a part of the kinetic energy of
the gas entering the impeller gas feeding flow passage is converted
into the potential energy.
SUMMARY OF THE INVENTION
[0007] In view of the above-described problems, it is one objective
of the invention to provide a double-area turbine for
turbocharging, the turbine being capable of reducing the sudden
expansion phenomenon of the gas at the gas outlet of the single
flow passage of the volute in conditions of small flow rate as well
as reducing the mixing phenomenon of the gas from the two flow
passages of the volute at the impeller gas inlet, therefore
improving the efficiency of the double-layer flow passage
cross-section variable turbocharger in the full range of working
conditions of the motor.
[0008] To achieve the above objective, in accordance with one
embodiment of the invention, there is provided a turbine,
comprising: a volute and an impeller. The volute comprises: a
volute gas inlet, a volute gas feeding flow passage, and a volute
gas outlet. The impeller comprises: blades, an impeller gas feeding
flow passage, an impeller gas inlet, an impeller gas outlet, and a
partition plate. The impeller gas feeding flow passage comprises an
inner flow passage and an outer flow passage. The impeller is
disposed inside the volute. The blades are disposed on an outer
part of the impeller. The partition plate is circumferentially
disposed between the impeller gas inlet and the impeller gas
outlet. The partition plate divides the impeller gas feeding flow
passage into the inner flow passage and the outer flow passage.
[0009] In a class of this embodiment, the volute gas feeding flow
passage comprises a middle partition, and the middle partition
divides the volute gas feeding flow passage into a left flow
passage and a right flow passage. The left flow passage
communicates with the inner flow passage. The right flow passage
communicates with the outer flow passage.
[0010] In a class of this embodiment, the left flow passage
comprises a gas outlet of the left flow passage in the vicinity of
the impeller. The right flow passage comprises a gas outlet of the
right flow passage in the vicinity of the impeller. The inner flow
passage comprises a gas inlet of the inner flow passage
corresponding to the gas outlet of the left flow passage. The outer
flow passage comprises a gas inlet of the outer flow passage
corresponding to the gas outlet 8 of the right flow passage.
[0011] In a class of this embodiment, a ratio of a width of the gas
inlet of the inner flow passage to a width of the gas inlet of the
outer flow passage is between 0.1 and 10.
[0012] In a class of this embodiment, the inner flow passage is a
radial inflow channel.
[0013] In a class of this embodiment, the inner flow passage is a
Francis channel.
[0014] In a class of this embodiment, the outer flow passage is a
radial inflow channel.
[0015] In a class of this embodiment, the outer flow passage is a
Francis channel.
[0016] In a class of this embodiment, a ratio of a width of the gas
outlet of the inner flow passage to a width of the gas outlet of
the outer flow passage is between 0.1 and 10.
[0017] In a class of this embodiment, the blade comprises inner
blades correspondingly disposed inside the inner flow passage and
outer blades correspondingly disposed inside the outer flow
passage.
[0018] In a class of this embodiment, a ratio of a number of the
inner blades to a number of the outer blades is between 0.2 and
6.
[0019] In a class of this embodiment, an adjustable valve is
disposed inside the left flow passage in the vicinity of the volute
gas inlet. The adjustable valve is connected to a control
mechanism.
[0020] Both the right flow passage and the outer flow passage are
normal open passages.
[0021] When a motor operates at a low rotational speed working
condition, a relatively small amount of exhaust gas is discharged
from the motor, and the adjustable valve is in a close state driven
by the control mechanism. Since either a first flow path including
the left flow passage, the gas inlet of the inner flow passage, and
the inner flow passage or a second flow path including the right
flow passage, the gas inlet of the outer flow passage, and the
outer flow passage is opened, the left flow passage, the gas inlet
of the inner flow passage, and the inner flow passage are also in
the close sate. The exhaust gas discharged from the motor only
passes through the right flow passage, the gas inlet of the outer
flow passage, and the outer flow passage to do work, so that a
sudden expansion phenomenon of the gas at the outlet of the left
flow passage is reduced, the intake pressure of the outer flow
passage is effectively increased, and the exhaust energy entering
the turbine is increased. With the increase of the intake energy of
the turbine, the energy in the exhaust gas is fully utilized, and
therefore the efficiency of the turbine and the torque output are
improved.
[0022] When the motor operates at a high rotational speed working
condition, a relatively large amount of the exhaust gas is
discharged from the motor, and the adjustable valve is in an open
state driven by the control mechanism. Because the left flow
passage, the gas inlet of the inner flow passage, and the inner
flow passage communicate with each other, and because the right
flow passage, the gas inlet of the outer flow passage, and the
outer flow passage communicate with each other, the exhaust gas
discharged from the motor separately passes through a first flow
path comprising the left flow passage, the gas inlet of the inner
flow passage, and the inner flow passage and through a second flow
path comprising the right flow passage, the gas inlet of the outer
flow passage, and the outer flow passage to do work. Thus, the
mixing phenomenon of the gas from the left flow passage and the gas
from the right flow passage at the impeller gas inlet is reduced.
The opening degree of the adjustable valve is controlled by the
control mechanism so as to reasonably allocate the gas flows
entering the two flow paths of the turbine. Since the two flow
paths of the turbine are different in flow capacity, the exhaust
pressure of the motor and the power output of the turbine can be
effectively regulated by changing the intake flow ratio between the
two flow paths of the turbine, thereby satisfying the performance
and the emission requirement of the middle and high rotational
speed working condition of the motor.
[0023] In a class of this embodiment, an adjustable valve is
disposed inside the right flow passage in the vicinity of the
volute gas inlet. The adjustable valve is connected to a control
mechanism.
[0024] Both the left flow passage and the inner flow passage are
both normal open passages.
[0025] When the motor operates at the low rotational speed working
condition, a relatively small amount of exhaust gas is discharged
from the motor, and the adjustable valve is in the close state
driven by the control mechanism. Since either a first flow path
including the left flow passage, the gas inlet of the inner flow
passage, and the inner flow passage or a second flow path including
the right flow passage, the gas inlet of the outer flow passage,
and the outer flow passage is opened, the right flow passage, the
gas inlet of the outer flow passage, and the outer flow passage are
also in the close sate. The exhaust gas discharged from the motor
only passes through the left flow passage, the gas inlet of the
inner flow passage, and the inner flow passage to do work, so that
a sudden expansion phenomenon of the gas at the outlet of the right
flow passage is reduced, the intake pressure of the inner flow
passage is effectively increased, and the exhaust energy entering
the turbine is increased. With the increase of the intake energy of
the turbine, the energy in the exhaust gas is fully utilized, and
therefore the efficiency of the turbine and the torque output are
improved.
[0026] When the motor operates at a high rotational speed working
condition, a relatively large amount of the exhaust gas is
discharged from the motor, and the adjustable valve is in an open
state driven by the control mechanism. Because the left flow
passage, the gas inlet of the inner flow passage, and the inner
flow passage communicate with each other, and because the right
flow passage, the gas inlet of the outer flow passage, and the
outer flow passage communicate with each other, the exhaust gas
discharged from the motor separately passes through a first flow
path comprising the left flow passage, the gas inlet of the inner
flow passage, and the inner flow passage and through a second flow
path comprising the right flow passage, the gas inlet of the outer
flow passage, and the outer flow passage to do work. Thus, the
mixing phenomenon of the gas from the left flow passage and the gas
from the right flow passage at the impeller gas inlet is reduced.
The opening degree of the adjustable valve is controlled by the
control mechanism so as to reasonably allocate the gas flows
entering the two flow paths of the turbine. Since the two flow
paths of the turbine are different in flow capacity, the exhaust
pressure of the motor and the power output of the turbine can be
effectively regulated by changing the intake flow ratio between the
two flow paths of the turbine, thereby satisfying the performance
and the emission requirement of the middle and high rotational
speed working condition of the motor.
[0027] Advantages according to embodiments of the invention are
summarized as follows:
[0028] The turbine volute of the invention has simple structure,
excellent succession, and relatively high casting yield. The
turbine impeller of the invention acquires high aerodynamic
efficiency and high structural strength by analysis and
optimization of the modern Computational Fluid Dynamics (CFD) and
Finite Element Analysis (FEA) technology. The impeller can be
produced by adopting the existing casting and processing devices,
which has low production cost and easily realizes engineering. In
summary, the double-area turbine is capable of effectively
satisfying the turbocharging requirement in a full range of working
condition of the motor, that is, in conditions of small flow rate,
the sudden expansion phenomenon of the gas at the gas outlet of the
single flow passage of the volute is decreased, and the efficiency
of the turbine in conditions of the small flow rate is further
improved; in conditions of normal flow rate, the mixing phenomenon
of the gas from the two flow passages of the volute at the impeller
gas inlet is decreased so as to improve the efficiency of the
turbine.
BRIEF DESCRIPTION OF THE DRAWINGS
[0029] The invention is described hereinbelow with reference to the
accompanying drawings, in which:
[0030] FIG. 1 is a structure diagram of a double-layer flow passage
cross-section variable turbocharger in the prior art;
[0031] FIG. 2 is a structure diagram of a double-area turbine in
accordance with Example 1 and Example 2;
[0032] FIG. 3 is a structure diagram of an impeller in accordance
with Example 1 and Example 2;
[0033] FIG. 4 is a right view of FIG. 3;
[0034] FIG. 5 is a structure diagram of an adjustable valve mounted
inside a left flow passage in accordance with Example 1; and
[0035] FIG. 6 is a structure diagram of an adjustable valve mounted
inside a right flow passage in accordance with Example 2.
[0036] In the drawings, the following reference numbers are used:
1. Volute; 2. Turbine impeller; 3. Volute gas inlet; 4. Volute gas
outlet; 5. Middle partition; 6. Left flow passage; 7. Right flow
passage; 8. Impeller gas inlet; 9. Impeller gas feeding flow
passage; 10. Impeller gas outlet; 11. Partition plate; 12. Inner
flow passage; 13. Outer flow passage; 14. Impeller inner blade; 15.
Impeller outer blade; 16. Gas outlet of left flow passage; 17. Gas
inlet of inner flow passage; 18. Gas outlet of right flow passage;
19. Gas inlet of outer flow passage; 20. Adjustable valve; W1.
Width of gas inlet of inner flow passage; W2. Width of gas inlet of
outer flow passage; W3. Width of gas outlet of inner flow passage;
and W4. Width of gas outlet of outer flow passage.
DETAILED DESCRIPTION OF THE EMBODIMENTS
[0037] For further illustrating the invention, examples detailing a
double-area turbine for turbocharging are described below. It
should be noted that the following examples are intended to
describe and not to limit the invention.
Example 1
[0038] As shown in FIGS. 2-3, a double-area turbine for
turbocharging comprises a volute 1 and an impeller 2 disposed
inside the volute 1. Blades are disposed at an outer part of the
impeller 2. The volute 1 comprises: a volute gas inlet 3, a volute
gas feeding flow passage, and a volute gas outlet 4.
[0039] The impeller 2 comprises: an impeller gas inlet, an impeller
gas feeding flow passage, an impeller gas outlet, and blades.
[0040] A partition plate 11 is circumferentially disposed between
the impeller gas inlet and the impeller gas outlet. The shape of
the partition plate 11 satisfies aerodynamic performance
requirements and reliability requirements.
[0041] The partition plate 11 divides the impeller gas feeding flow
passage into an inner flow passage 12 and an outer flow passage
13.
[0042] The inner flow passage 12 adopts a radial inflow channel or
Francis channel. The outer flow passage 13 is generally designed to
be a radial inflow channel and is designed to be a Francis channel
in special circumstances.
[0043] A ratio of a width W1 of the gas inlet of the inner flow
passage to a width W2 of the gas inlet of the outer flow passage is
between 0.1 and 10.
[0044] A ratio of a width W3 of the gas outlet of the inner flow
passage to a width W4 of the gas outlet of the outer flow passage
is between 0.1 and 10.
[0045] The volute gas feeding flow passage comprises a middle
partition 5. The middle partition 5 divides the volute gas feeding
flow passage into a left flow passage 6 and a right flow passage
7.
[0046] The left flow passage 6 communicates with the inner flow
passage 12. The right flow passage 7 communicates with the outer
flow passage 13.
[0047] A gas outlet of the left flow passage 6 is corresponding to
a gas inlet 17 of the inner flow passage 12. A gas outlet 18 of the
right flow passage 7 is corresponding to a gas inlet 19 of the
outer flow passage 13.
[0048] As shown in FIG. 4, the blades comprise inner blades 14
correspondingly disposed inside the inner flow passage 12 and outer
blades 15 correspondingly disposed inside the outer flow passage
13. A ratio of a number of the inner blades 14 to a number of the
outer blades 15 is between 0.2 and 6.
[0049] As shown in FIG. 5, an adjustable valve 20 is disposed
inside the left flow passage 6 in the vicinity of the volute gas
inlet 3. The adjustable valve 20 is connected to a control
mechanism. Driven by the control mechanism, the rotation of the
adjustable valve 20 is realized, so that the left flow passage 6 is
opened or closed.
[0050] When a motor operates at a low rotational speed working
condition, a relatively small amount of exhaust gas is discharged
from the motor, and the adjustable valve 20 is in a close state
driven by the control mechanism. Thus, the left flow passage 6, the
gas inlet 17 of the inner flow passage, and the inner flow passage
12 are also in the close sate. The exhaust gas discharged from the
motor only passes through the right flow passage 7, the gas inlet
19 of the outer flow passage, and the outer flow passage 13 to do
work, so that a sudden expansion phenomenon of the gas at the
outlet 16 of the left flow passage is reduced, the intake pressure
of the outer flow passage 13 is effectively increased, and the
exhaust energy entering the turbine is increased. With the increase
of the intake energy of the turbine, the energy in the exhaust gas
is fully utilized, and therefore the efficiency of the turbine and
the torque output are improved.
[0051] When the motor operates at a high rotational speed working
condition, a relatively large amount of the exhaust gas is
discharged from the motor, and the adjustable valve 20 is in an
open state driven by the control mechanism. Because the left flow
passage 6, the gas inlet 17 of the inner flow passage, and the
inner flow passage 12 communicate with each other, and because the
right flow passage 7, the gas inlet 19 of the outer flow passage,
and the outer flow passage 13 communicate with each other, the
exhaust gas discharged from the motor separately passes through a
first flow path comprising the left flow passage 6, the gas inlet
17 of the inner flow passage, and the inner flow passage 12 and
through a second flow path comprising the right flow passage 7, the
gas inlet 19 of the outer flow passage, and the outer flow passage
13 to do work. Thus, a mixing phenomenon of the gas from the left
flow passage 6 and the gas from the right flow passage 7 at the
impeller gas inlet is reduced. The opening degree of the adjustable
valve 20 is controlled by the control mechanism so as to reasonably
allocate the gas flows entering the two flow paths of the turbine.
Since the two flow paths of the turbine are different in flow
capacity, the exhaust pressure of the motor and the power output of
the turbine can be effectively regulated by changing the intake
flow ratio between the two flow paths of the turbine, thereby
satisfying the performance and the emission requirement of the
middle and high rotational speed working condition of the
motor.
Example 2
[0052] As shown in FIG. 6, the turbine of this example is different
from that in Example 1 in that the adjustable valve 20 herein is
disposed inside the right flow passage 7 in the vicinity of the
volute gas inlet 3 rather than being disposed inside the left flow
passage 6 in the vicinity of the volute gas inlet 3 in Example 1.
The adjustable valve 20 is connected to a control mechanism. The
rotation of the adjustable valve 20 can be realized driven by the
control mechanism, so that the right flow passage 7 is opened or
closed.
[0053] When the motor operates at the low rotational speed working
condition, a relatively small amount of exhaust gas is discharged
from the motor, and the adjustable valve 20 is in a close state
driven by the control mechanism. Thus, the right flow passage 7,
the gas inlet 19 of the outer flow passage, and the outer flow
passage 13 are also in the close sate. The exhaust gas discharged
from the motor only passes through the left flow passage 6, the gas
inlet 17 of the inner flow passage, and the inner flow passage 12
to do work, so that the sudden expansion phenomenon of the gas at
the outlet 18 of the right flow passage is reduced, the intake
pressure of the inner flow passage 12 is effectively increased, and
the exhaust energy entering the turbine is increased. With the
increase of the intake energy of the turbine, the energy in the
exhaust gas is fully utilized, and therefore the efficiency of the
turbine and the torque output are improved.
[0054] When the motor operates at a high rotational speed working
condition, a relatively large amount of the exhaust gas is
discharged from the motor, and the adjustable valve 20 is in an
open state driven by the control mechanism. Because the left flow
passage 6, the gas inlet 17 of the inner flow passage, and the
inner flow passage 12 communicate with each other, and because the
right flow passage 7, the gas inlet 19 of the outer flow passage,
and the outer flow passage 13 communicate with each other, the
exhaust gas discharged from the motor separately passes through a
first flow path comprising the left flow passage 6, the gas inlet
17 of the inner flow passage, and the inner flow passage 12 and
through a second flow path comprising the right flow passage 7, the
gas inlet 19 of the outer flow passage, and the outer flow passage
13 to do work. Thus, the mixing phenomenon of the gas from the left
flow passage 6 and the gas from the right flow passage 7 at the
impeller gas inlet is reduced. The opening degree of the adjustable
valve 20 is controlled by the control mechanism so as to reasonably
allocate the gas flows entering the two flow paths of the turbine.
Since the two flow paths of the turbine are different in flow
capacity, the exhaust pressure of the motor and the power output of
the turbine can be effectively regulated by changing the intake
flow ratio between the two flow paths of the turbine, thereby
satisfying the performance and the emission requirement of the
middle and high rotational speed working condition of the
motor.
[0055] While particular embodiments of the invention have been
shown and described, it will be obvious to those skilled in the art
that changes and modifications may be made without departing from
the invention in its broader aspects, and therefore, the aim in the
appended claims is to cover all such changes and modifications as
fall within the true spirit and scope of the invention.
* * * * *