CN111691967A - Two-stage supercharger and engine - Google Patents
Two-stage supercharger and engine Download PDFInfo
- Publication number
- CN111691967A CN111691967A CN201910190184.5A CN201910190184A CN111691967A CN 111691967 A CN111691967 A CN 111691967A CN 201910190184 A CN201910190184 A CN 201910190184A CN 111691967 A CN111691967 A CN 111691967A
- Authority
- CN
- China
- Prior art keywords
- pressure stage
- low
- engine
- compressor
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention provides a two-stage supercharger and an engine, wherein the two-stage supercharger comprises a high-pressure stage supercharger, a high-pressure stage compressor and a high-pressure stage turbine; a low-pressure stage supercharger comprising a low-pressure stage compressor and a low-pressure stage turbine; the first bypass passage is communicated with the air inlet of the high-pressure stage turbine and the air inlet of the low-pressure stage turbine and is provided with a high-pressure stage bypass valve and a low-pressure stage bypass valve; a second bypass channel for communicating the air outlet of the low-pressure stage compressor with the air outlet of the high-pressure stage compressor, wherein a compressor bypass valve is arranged on the second bypass channel; when the rotating speed of the engine is less than a preset high rotating speed value, the bypass valve of the compressor is closed, and the high-low pressure level bypass valve is closed or the opening degree is adjustable; when the rotating speed of the engine is greater than or equal to a preset high rotating speed value, the bypass valve of the compressor is opened, and the bypass valve of the high-low pressure stage is opened. The invention realizes the switching of the working modes of the supercharger under different engine rotating speeds, thereby ensuring that the engine can simultaneously give consideration to higher low-speed torque and higher rated power and has stronger power.
Description
Technical Field
The invention relates to the technical field of engine parts, in particular to a two-stage supercharger, and further relates to an engine.
Background
The two-stage supercharger of the existing engine realizes the control of the high-low pressure stage supercharger by shunting at an exhaust gas inlet, the control mode can solve the problem of insufficient low-speed power of the engine, but the smoothness of the switching of the supercharger among working modes at different engine rotating speeds is poor, so that the engine cannot easily take into account high low-speed torque and high rated power at the same time.
Disclosure of Invention
In view of this, the present invention provides a two-stage supercharger to switch between operating modes of the supercharger at different engine speeds, so that the engine can simultaneously achieve a higher low-speed torque and a higher rated power, and the power is stronger.
Another object of the present invention is to provide an engine having the above two-stage supercharger.
In order to achieve the purpose, the invention provides the following technical scheme:
a two-stage supercharger comprising:
the high-pressure stage supercharger comprises a high-pressure stage compressor and a high-pressure stage turbine, wherein the high-pressure stage compressor is provided with a high-pressure stage compressor air inlet and a high-pressure stage compressor air outlet which is used for connecting an engine air inlet manifold, and the high-pressure stage turbine is provided with a high-pressure stage turbine air outlet and a high-pressure stage turbine air inlet which is used for connecting an engine exhaust manifold;
the low-pressure stage supercharger comprises a low-pressure stage compressor and a low-pressure stage turbine, the low-pressure stage compressor is provided with a low-pressure stage compressor air outlet connected with a high-pressure stage compressor air inlet and a low-pressure stage compressor air inlet used for being connected with an air supply device, the low-pressure stage turbine is provided with a low-pressure stage turbine air inlet and a low-pressure stage turbine air outlet, and the high-pressure stage turbine air outlet is connected with the low-pressure stage turbine air inlet;
the first bypass passage is communicated with the air inlet of the high-pressure stage turbine and the air inlet of the low-pressure stage turbine and is provided with a high-pressure stage bypass valve and a low-pressure stage bypass valve;
a second bypass channel for communicating the air outlet of the low-pressure stage compressor with the air outlet of the high-pressure stage compressor, wherein a compressor bypass valve is arranged on the second bypass channel;
when the rotating speed of the engine is lower than a preset high rotating speed value, the bypass valve of the compressor is closed, and the high-low pressure level bypass valve is closed or the opening degree of the high-low pressure level bypass valve is adjustable; and when the rotating speed of the engine is greater than or equal to the preset high rotating speed value, the compressor bypass valve is opened, and the high-low pressure stage bypass valve is opened.
Preferably, the two-stage supercharger further comprises a third bypass passage for communicating the inlet of the low-pressure stage turbine with the outlet of the low-pressure stage turbine, and the third bypass passage is provided with a waste gate valve;
when the actual boost pressure of the engine is smaller than or equal to the preset boost pressure value, the waste gas bypass valve is closed; and when the actual boost pressure of the engine is greater than the preset boost pressure value, the waste gas bypass valve is opened or the opening degree is adjustable.
Preferably, the two-stage supercharger further comprises a controller for automatically controlling the high-low pressure stage bypass valve, the compressor bypass valve, and the waste gate bypass valve.
Preferably, in the two-stage supercharger, when the engine speed is lower than a preset low speed value, the high-low pressure stage bypass valve is closed; when the rotating speed of the engine is between the preset low rotating speed value and the preset high rotating speed value, the opening degree of the high-low pressure level bypass valve is adjustable; the preset low rotation speed value is smaller than the preset high rotation speed value.
Preferably, in the two-stage supercharger, the preset low rotation speed value is 1500 rpm; the preset high rotation speed value is 3000 rpm.
Preferably, in the above two-stage supercharger, the third bypass passage is integrated in a low-pressure stage turbine housing of the low-pressure stage turbine.
Preferably, in the above two-stage supercharger, the first bypass passage is integrated in a high-pressure stage turbine housing of the high-pressure stage turbine.
Preferably, in the above two-stage supercharger, the second bypass passage is integrated on a high-pressure stage compressor casing of the high-pressure stage compressor.
As can be seen from the above technical solutions, the two-stage supercharger provided by the present invention includes: the high-pressure stage supercharger comprises a high-pressure stage compressor and a high-pressure stage turbine, the high-pressure stage compressor is provided with a high-pressure stage compressor air inlet and a high-pressure stage compressor air outlet used for being connected with an engine air inlet manifold, and the high-pressure stage turbine is provided with a high-pressure stage turbine air outlet and a high-pressure stage turbine air inlet used for being connected with an engine air outlet manifold; the low-pressure stage supercharger comprises a low-pressure stage compressor and a low-pressure stage turbine, the low-pressure stage compressor is provided with a low-pressure stage compressor air outlet connected with a high-pressure stage compressor air inlet and a low-pressure stage compressor air inlet used for connecting an air supply device, the low-pressure stage turbine is provided with a low-pressure stage turbine air inlet and a low-pressure stage turbine air outlet, and the high-pressure stage turbine air outlet is connected with the low-pressure stage turbine air inlet; the first bypass passage is communicated with an air inlet of the high-pressure stage turbine and an air inlet of the low-pressure stage turbine and is provided with a high-pressure stage bypass valve and a low-pressure stage bypass valve; a second bypass channel for communicating the air outlet of the low-pressure stage compressor with the air outlet of the high-pressure stage compressor, wherein a compressor bypass valve is arranged on the second bypass channel; when the rotating speed of the engine is lower than a preset high rotating speed value, the bypass valve of the compressor is closed, and the high-low pressure level bypass valve is closed or the opening degree is adjustable; when the rotating speed of the engine is greater than or equal to a preset high rotating speed value, the bypass valve of the compressor is opened, and the bypass valve of the high-low pressure stage is opened.
When the device is used, the air inlet of the low-pressure stage compressor is connected with the air outlet of an air filter of an air supply device, the air outlet of the high-pressure stage compressor is connected with an engine air inlet manifold, the air inlet of the high-pressure stage turbine is connected with an engine exhaust manifold, and the air outlet of the low-pressure stage turbine is connected with a waste gas exhaust pipe.
When the rotating speed of the engine is less than a preset high rotating speed value, the bypass valve of the compressor is closed, and the bypass valve of the high-low pressure stage is closed; at the moment, fresh air provided by an air filter firstly enters a low-pressure stage compressor, flows through a high-pressure stage compressor and enters an engine air inlet manifold at the air inlet side of the engine; and then the waste gas after doing work in the engine cylinder is discharged to the high-pressure stage turbine from an engine exhaust manifold on the exhaust side of the engine, and the inertia impulse force of the waste gas discharged by the engine is utilized to push the high-pressure stage turbine to rotate, so that the coaxial high-pressure stage compressor is driven to do work, the air is pressurized to do work, the air inlet pressure is increased, and the problem of insufficient low-speed power of the engine is solved. Or the bypass valve of the compressor is closed, and the opening of the high-low pressure level bypass valve is adjustable; at the moment, a part of waste gas flows through the high-low pressure stage bypass valve to enter the low-pressure stage turbine, the inertia impulsive force of the waste gas exhausted by the engine is utilized to push the low-pressure stage turbine to rotate, so that the coaxial low-pressure stage compressor is driven to do work, the air pressurization work is realized, the air inlet pressure is improved, the high-pressure stage supercharger and the low-pressure stage supercharger work in a cooperative mode, the main force is the high-pressure stage supercharger, the switching smoothness is guaranteed, the power is stably increased, and the high torque output within a large rotating speed range is guaranteed.
When the rotating speed of the engine is greater than or equal to a preset high rotating speed value, a bypass valve of the compressor is opened, and a bypass valve of a high-low pressure stage is opened; at the moment, fresh air provided by an air filter firstly enters a low-pressure stage compressor, and then most of the air flows through a bypass valve of the compressor and enters an engine air inlet manifold at the air inlet side of the engine; then most of the exhaust gas discharged from the engine exhaust manifold flows through the high-low pressure stage bypass valve to enter the low-pressure stage turbine, and the inertia impulse force of the exhaust gas discharged from the engine is utilized to push the low-pressure stage turbine to rotate, so that the coaxial low-pressure stage compressor is driven to do work, the air is pressurized and does work, the air inlet pressure is improved, that is, most of the exhaust gas does not pass through the high-pressure stage turbine, so that the loss is reduced, and the air inlet efficiency is ensured; at the moment, the high-pressure-stage supercharger still compresses air, but mainly works by the low-pressure-stage supercharger, so that the supercharger and the engine are better matched, and the control effect is better.
In conclusion, the two-stage supercharger not only solves the problem of insufficient low-speed power of the engine, but also realizes better matching between the supercharger and the engine within the whole engine rotating speed range; and utilize high-low pressure level bypass valve to realize the switching between high-pressure level booster and the low-pressure level booster, can realize the smooth-going nature of switching between the working mode of booster under different engine speed to make the engine can compromise higher low-speed moment of torsion and great rated power simultaneously, power is stronger, is applicable to the work occasion that the engine speed range is great and have higher requirements for booster smoothness and reliability.
The invention also provides an engine, which comprises an engine intake manifold, an engine exhaust manifold and a supercharger, wherein a compressed air outlet of the supercharger is connected with the engine intake manifold, an exhaust gas inlet of the supercharger is connected with the engine exhaust manifold, the supercharger is any one of the two-stage superchargers, and the two-stage supercharger has the same effect as the engine with the two-stage supercharger, so the engine is not repeated.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
FIG. 1 is a schematic diagram of a two-stage supercharger according to an embodiment of the present invention operating at engine speeds less than a predetermined high speed;
fig. 2 is a schematic diagram of the operation of the two-stage supercharger provided in the embodiment of the present invention when the engine speed is greater than or equal to the preset high speed value.
In the above FIGS. 1-2:
1-air filter, 2-low pressure stage compressor, 3-high pressure stage compressor, 4-compressor by-pass valve, 5-second by-pass channel, 6-intake manifold, 7-exhaust manifold, 8-first by-pass channel, 9-high low pressure stage by-pass valve, 10-high pressure stage turbine, 11-third by-pass channel, 12-waste gas by-pass valve, 13-low pressure stage turbine, 14-exhaust pipe.
Detailed Description
The embodiment of the invention provides a two-stage supercharger, which realizes the switching of the working modes of the supercharger under different engine rotating speeds, so that the engine can simultaneously give consideration to higher low-speed torque and higher rated power, and the power is stronger.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1-2, a two-stage supercharger according to an embodiment of the present invention includes: the high-pressure stage supercharger comprises a high-pressure stage compressor 3 and a high-pressure stage turbine 10, wherein the high-pressure stage compressor 3 is provided with a high-pressure stage compressor air inlet and a high-pressure stage compressor air outlet which is used for connecting an engine air inlet manifold 6, and the high-pressure stage turbine 10 is provided with a high-pressure stage turbine air outlet and a high-pressure stage turbine air inlet which is used for connecting an engine air outlet manifold 7; the low-pressure stage supercharger comprises a low-pressure stage compressor 2 and a low-pressure stage turbine 13, wherein the low-pressure stage compressor 2 is provided with a low-pressure stage compressor air outlet connected with a high-pressure stage compressor air inlet and a low-pressure stage compressor air inlet used for connecting an air supply device, the low-pressure stage turbine 13 is provided with a low-pressure stage turbine air inlet and a low-pressure stage turbine air outlet, and the high-pressure stage turbine air outlet is connected with the low-pressure stage turbine air inlet; the first bypass passage 8 is used for communicating an air inlet of the high-pressure stage turbine with an air inlet of the low-pressure stage turbine, and a high-low pressure stage bypass valve 9 is arranged on the first bypass passage 8; a second bypass channel 5 for communicating the air outlet of the low-pressure stage compressor with the air outlet of the high-pressure stage compressor, wherein a compressor bypass valve 4 is arranged on the second bypass channel 5; when the rotating speed of the engine is lower than a preset high rotating speed value, the compressor bypass valve 4 is closed, and the high-low pressure stage bypass valve 9 is closed or the opening degree is adjustable; when the rotating speed of the engine is greater than or equal to a preset high rotating speed value, the compressor bypass valve 4 is opened, and the high-low pressure stage bypass valve 9 is opened.
Specifically, the high-pressure stage supercharger adopts a variable-section VGT technology.
When the air purifier is applied, the air inlet of the low-pressure stage air compressor is connected with the air outlet of an air filter 1 of an air supply device, the air outlet of the high-pressure stage air compressor is connected with an engine air inlet manifold 6, the air inlet of the high-pressure stage turbine is connected with an engine exhaust manifold 7, and the air outlet of the low-pressure stage turbine is connected with an exhaust pipe 14.
As shown in fig. 1, when the engine speed is less than the preset high speed value, the compressor bypass valve 4 is closed, and the high-low pressure stage bypass valve 9 is closed; at the moment, fresh air provided by the air filter 1 firstly enters the low-pressure stage compressor 2, flows through the high-pressure stage compressor 3 and enters an engine intake manifold 6 at the engine intake side; and then, the exhaust gas which does work in the engine cylinder is discharged to the high-pressure stage turbine 10 from an engine exhaust manifold 7 at the exhaust side of the engine, and the inertia impulse force of the exhaust gas discharged by the engine is utilized to push the high-pressure stage turbine 10 to rotate, so that the coaxial high-pressure stage compressor 3 is driven to do work, the air is pressurized to do work, the air inlet pressure is increased, and the problem of insufficient low-speed power of the engine is solved. Or the bypass valve 4 of the compressor is closed, and the opening degree of the high-low pressure level bypass valve 9 is adjustable; at the moment, a part of exhaust gas enters the low-pressure stage turbine 13 through the high-low pressure stage bypass valve 9, the low-pressure stage turbine 13 is pushed to rotate by utilizing the inertia impulsive force of the exhaust gas exhausted by the engine, the coaxial low-pressure stage compressor 2 is driven to do work, the air pressurization work is realized, the air inlet pressure is improved, the high-pressure stage supercharger and the low-pressure stage supercharger work in a cooperative mode, the main force is the high-pressure stage supercharger, the switching smoothness is guaranteed, the power is stably increased, and the high torque output within a large rotating speed range is guaranteed.
As shown in fig. 2, when the engine speed is greater than or equal to the preset high speed value, the compressor bypass valve 4 is opened, and the high-low pressure stage bypass valve 9 is opened; at the moment, fresh air provided by the air filter 1 firstly enters the low-pressure stage compressor 2, and then most of the air flows through a compressor bypass valve 4 and enters an engine intake manifold 6 at the engine intake side; then most of the exhaust gas discharged from the engine exhaust manifold 7 flows through the high-low pressure stage bypass valve 9 to enter the low-pressure stage turbine 13, and the inertia impulse force of the exhaust gas discharged from the engine is used for pushing the low-pressure stage turbine 13 to rotate, so that the coaxial low-pressure stage compressor 2 is driven to do work, the air is pressurized and does work, the air inlet pressure is improved, that is, most of the exhaust gas does not pass through the high-pressure stage turbine 10, so that the loss is reduced, and the air inlet efficiency is ensured; at the moment, the high-pressure-stage supercharger still compresses air, but mainly works by the low-pressure-stage supercharger, so that the supercharger and the engine are better matched, and the control effect is better.
In conclusion, the two-stage supercharger not only solves the problem of insufficient low-speed power of the engine, but also realizes better matching between the supercharger and the engine within the whole engine rotating speed range; and utilize high-low pressure level bypass valve 9 to realize the switching between high-pressure level booster and the low-pressure level booster, can realize the ride comfort that the booster switches between the mode under different engine speed to make the engine can compromise higher low-speed moment of torsion and great rated power simultaneously, power is stronger, is applicable to the work occasion that the engine speed range is great and have higher requirements for booster ride comfort and reliability.
Preferably, the two-stage supercharger further comprises a third bypass channel 11 for communicating the inlet of the low-pressure stage turbine with the outlet of the low-pressure stage turbine, and a waste gas bypass valve 12 is arranged on the third bypass channel 11; when the actual boost pressure of the engine is less than or equal to the preset boost pressure value, the wastegate valve 12 is closed; when the actual boost pressure of the engine is greater than the preset boost pressure value, the wastegate valve 12 is opened or the opening degree is adjustable.
It should be noted that the actual engine boost pressure is detected by a pressure sensor provided on the engine intake manifold 6.
In the application process, when the actual boost pressure of the engine is smaller than or equal to the preset boost pressure value, the waste gas bypass valve 12 is closed; the exhaust gas flow discharged from the exhaust port of the high-pressure stage turbine passes through the low-pressure stage turbine 13 and is discharged from the exhaust pipe 14, so that the best supercharging capacity of the low-pressure stage supercharger is ensured; when the actual boost pressure of the engine is greater than the preset boost pressure value, the waste gas bypass valve 12 is opened or the opening degree is adjustable, and waste gas exhausted by the exhaust manifold 7 of the engine can pass through the high-pressure stage turbine 10 and the waste gas bypass 12 and is directly exhausted into the exhaust pipe 14 without doing work, so that the supercharger is prevented from overspeed due to over-supercharging.
In conclusion, the waste gas bypass valve 12 is matched with the high-low pressure stage bypass valve 9 and the compressor bypass valve 4, so that the two-stage supercharger and the engine can be better matched, and the working reliability is further improved. Of course, the present invention may be provided without the wastegate valve 12.
In order to further optimize the above technical solution, the two-stage supercharger further comprises a controller for automatically controlling the high-low pressure stage bypass valve 9, the compressor bypass valve 4 and the wastegate valve 12. The invention automatically controls the states of the three valves through the controller according to different engine rotating speeds and supercharging pressures, thereby simplifying the operation.
In the preferred technical scheme, when the rotating speed of the engine is less than a preset low rotating speed value, the high-low pressure level bypass valve 9 is closed; when the rotating speed of the engine is between a preset low rotating speed value and a preset high rotating speed value, the opening of the high-low pressure level bypass valve 9 is adjustable; the preset low rotation speed value is smaller than the preset high rotation speed value.
The invention is divided into three working modes according to different rotating speeds of the engine: when the rotating speed is low (less than a preset low rotating speed value), the bypass valve 4 of the compressor is closed, the high-low pressure stage bypass valve 9 is closed, and the high-pressure stage supercharger works; when the rotating speed is in the middle (between the preset low rotating speed value and the preset high rotating speed value), the bypass valve 4 of the compressor is closed, the opening of the high-low pressure stage bypass valve 9 is adjustable, the high-pressure stage supercharger and the low-pressure stage supercharger work cooperatively, but the main force is the high-pressure stage supercharger; when the rotating speed is high (greater than or equal to a preset high rotating speed value), the bypass valve 4 of the compressor is opened, and the bypass valve 9 of the high-low pressure stage is fully opened, so that the compressor mainly works by means of the low-pressure stage supercharger; the air inlet pressure of the engine can be better controlled, and high torque output of the engine in a large rotating speed range is ensured.
It is understood that the present invention may also be practiced without the above-mentioned preset low rotation value, and with the preset high rotation value as a boundary, so that the two-stage supercharger has two control modes.
In the above embodiment, the preset low rotation speed value is 1500 rpm; the preset high rotation value is 3000 rpm. When the engine is in a low rotating speed of about 750-; when the rotating speed of the engine is increased to 1500-3000 rpm, and the supercharging pressure reaches the preset supercharging value of the high-pressure-stage supercharger, the high-low pressure-stage bypass valve 9 is opened, and the high-pressure-stage supercharger and the low-pressure-stage supercharger work simultaneously, so that the smoothness of switching is ensured, the stable increase of power is ensured, and high torque output in a larger rotating speed range is ensured; when the engine reaches high speed, about 3000-.
According to different engine models, the preset low rotating speed value and the preset high rotating speed value can also be other numerical values, such as 1300 rpm; the preset high rotation speed value is 3200rpm, etc., and the invention is not limited in detail herein.
To simplify the construction, the third bypass duct 11 is integrated in the casing of the low-pressure stage turbine 13, and the external piping is omitted. Of course, it is also possible to provide a separate line forming the third bypass channel 11.
The first bypass duct 8 is integrated in the casing of the high-pressure stage turbine 10, eliminating the need for an external line. Of course, it is also possible to provide a separate line forming the first bypass channel 8.
The second bypass channel 5 is integrated on the high-pressure stage compressor 3 casing of the high-pressure stage compressor 3, and an external pipeline is omitted. Of course, the present invention may also be provided with a separate pipeline to form the second bypass passage 5, or the second bypass passage 5 may be integrated into the high-pressure stage compressor 3 casing of the high-pressure stage compressor 3 and the low-pressure stage compressor 2 casing of the low-pressure stage compressor 2.
The embodiment of the invention also provides an engine, which comprises an engine intake manifold 6, an engine exhaust manifold 7 and a supercharger, wherein a compressed air outlet of the supercharger is connected with the engine intake manifold 6, an exhaust gas inlet of the supercharger is connected with the engine exhaust manifold 7, the supercharger is a two-stage supercharger provided by any one of the embodiments, and the switching of the working modes of the supercharger at different engine speeds is realized, so that the engine can simultaneously give consideration to higher low-speed torque and higher rated power, and the power is stronger.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (9)
1. A two-stage supercharger, comprising:
the high-pressure stage supercharger comprises a high-pressure stage compressor (3) and a high-pressure stage turbine (10), wherein the high-pressure stage compressor (3) is provided with a high-pressure stage compressor air inlet and a high-pressure stage compressor air outlet which is used for being connected with an engine air inlet manifold (6), and the high-pressure stage turbine (10) is provided with a high-pressure stage turbine air outlet and a high-pressure stage turbine air inlet which is used for being connected with an engine exhaust manifold (7);
the low-pressure stage supercharger comprises a low-pressure stage compressor (2) and a low-pressure stage turbine (13), wherein the low-pressure stage compressor (2) is provided with a low-pressure stage compressor air outlet connected with a high-pressure stage compressor air inlet and a low-pressure stage compressor air inlet used for being connected with an air supply device, the low-pressure stage turbine (13) is provided with a low-pressure stage turbine air inlet and a low-pressure stage turbine air outlet, and the high-pressure stage turbine air outlet is connected with the low-pressure stage turbine air inlet;
a first bypass passage (8) communicating the high pressure stage turbine inlet with the low pressure stage turbine inlet, a high and low pressure stage bypass valve (9) being provided on the first bypass passage (8);
a second bypass channel (5) for communicating the air outlet of the low-pressure stage compressor with the air outlet of the high-pressure stage compressor, wherein a compressor bypass valve (4) is arranged on the second bypass channel (5);
when the rotating speed of the engine is lower than a preset high rotating speed value, the compressor bypass valve (4) is closed, and the high-low pressure level bypass valve (9) is closed or the opening degree is adjustable; when the rotating speed of the engine is greater than or equal to the preset high rotating speed value, the compressor bypass valve (4) is opened, and the high-low pressure level bypass valve (9) is opened.
2. A two-stage supercharger according to claim 1, further comprising a third bypass channel (11) communicating the low-pressure stage turbine inlet with the low-pressure stage turbine outlet, the third bypass channel (11) being provided with a wastegate valve (12);
when the actual boost pressure of the engine is less than or equal to the preset boost pressure value, the waste gas bypass valve (12) is closed; and when the actual boost pressure of the engine is greater than the preset boost pressure value, the waste gas bypass valve (12) is opened or the opening degree is adjustable.
3. A two-stage supercharger according to claim 2, further comprising a controller for automatically controlling the high and low pressure stage bypass valve (9), the compressor bypass valve (4) and the wastegate valve (12).
4. A two-stage supercharger according to claim 2, characterised in that the high-low pressure stage bypass valve (9) is closed when the engine speed is less than a preset low speed value; when the rotating speed of the engine is between the preset low rotating speed value and the preset high rotating speed value, the opening degree of the high-low pressure level bypass valve (9) is adjustable; the preset low rotation speed value is smaller than the preset high rotation speed value.
5. The two-stage supercharger of claim 4, wherein the preset low speed value is 1500 rpm; the preset high rotation speed value is 3000 rpm.
6. A two-stage supercharger according to claim 2, characterised in that the third bypass channel (11) is integrated in the low-pressure stage turbine (13) housing of the low-pressure stage turbine (13).
7. A two-stage supercharger according to claim 1, characterised in that the first bypass channel (8) is integrated in the high-pressure stage turbine (10) housing of the high-pressure stage turbine (10).
8. A two-stage supercharger according to claim 1, characterised in that the second bypass channel (5) is integrated in the high-pressure stage compressor (3) housing of the high-pressure stage compressor (3).
9. An engine comprising an engine inlet manifold (6), an engine outlet manifold (7) and a supercharger, the supercharger having a compressed air outlet connected to the engine inlet manifold (6) and an exhaust gas inlet connected to the engine outlet manifold (7), characterised in that the supercharger is a two-stage supercharger as claimed in any one of claims 1 to 8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910190184.5A CN111691967A (en) | 2019-03-13 | 2019-03-13 | Two-stage supercharger and engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910190184.5A CN111691967A (en) | 2019-03-13 | 2019-03-13 | Two-stage supercharger and engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111691967A true CN111691967A (en) | 2020-09-22 |
Family
ID=72475725
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910190184.5A Pending CN111691967A (en) | 2019-03-13 | 2019-03-13 | Two-stage supercharger and engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111691967A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112682166A (en) * | 2020-12-18 | 2021-04-20 | 合肥工业大学 | Multistage control device of turbocharger |
| CN114427493A (en) * | 2022-03-23 | 2022-05-03 | 上海汽车集团股份有限公司 | Supercharger and engine with same |
| CN114483288A (en) * | 2022-01-27 | 2022-05-13 | 重庆长安汽车股份有限公司 | Control method and system for improving transient response of supercharged engine and automobile |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62113829A (en) * | 1985-11-14 | 1987-05-25 | Nissan Motor Co Ltd | Control device for supercharge pressure in engine with two-stage supercharger |
| US20080034752A1 (en) * | 2006-06-12 | 2008-02-14 | Bodo Becker | Supercharging system for two-stage supercharging of V-type internal combustion engines |
| JP2010024878A (en) * | 2008-07-16 | 2010-02-04 | Toyota Motor Corp | Control device for internal combustion engine |
| CN101900042A (en) * | 2009-05-29 | 2010-12-01 | 通用汽车环球科技运作公司 | The system and method that is used for the pattern transformation of two-stage series sequential turbocharger |
| JP2011021504A (en) * | 2009-07-14 | 2011-02-03 | Isuzu Motors Ltd | Multi-stage supercharging apparatus |
| CN102644506A (en) * | 2011-02-21 | 2012-08-22 | 福特环球技术公司 | Method for operating a turbocharger arrangement and control unit for a turbocharger arrangement |
| CN103180582A (en) * | 2010-10-28 | 2013-06-26 | 五十铃自动车株式会社 | Turbocharge system |
| CN103233825A (en) * | 2013-04-07 | 2013-08-07 | 中国人民解放军军事交通学院 | Secondary adjustable boosting control system and control method thereof |
| CN106437880A (en) * | 2016-08-31 | 2017-02-22 | 无锡康明斯涡轮增压技术有限公司 | Turbine end structure for turbocharger |
-
2019
- 2019-03-13 CN CN201910190184.5A patent/CN111691967A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62113829A (en) * | 1985-11-14 | 1987-05-25 | Nissan Motor Co Ltd | Control device for supercharge pressure in engine with two-stage supercharger |
| US20080034752A1 (en) * | 2006-06-12 | 2008-02-14 | Bodo Becker | Supercharging system for two-stage supercharging of V-type internal combustion engines |
| JP2010024878A (en) * | 2008-07-16 | 2010-02-04 | Toyota Motor Corp | Control device for internal combustion engine |
| CN101900042A (en) * | 2009-05-29 | 2010-12-01 | 通用汽车环球科技运作公司 | The system and method that is used for the pattern transformation of two-stage series sequential turbocharger |
| JP2011021504A (en) * | 2009-07-14 | 2011-02-03 | Isuzu Motors Ltd | Multi-stage supercharging apparatus |
| CN103180582A (en) * | 2010-10-28 | 2013-06-26 | 五十铃自动车株式会社 | Turbocharge system |
| CN102644506A (en) * | 2011-02-21 | 2012-08-22 | 福特环球技术公司 | Method for operating a turbocharger arrangement and control unit for a turbocharger arrangement |
| CN103233825A (en) * | 2013-04-07 | 2013-08-07 | 中国人民解放军军事交通学院 | Secondary adjustable boosting control system and control method thereof |
| CN106437880A (en) * | 2016-08-31 | 2017-02-22 | 无锡康明斯涡轮增压技术有限公司 | Turbine end structure for turbocharger |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112682166A (en) * | 2020-12-18 | 2021-04-20 | 合肥工业大学 | Multistage control device of turbocharger |
| CN114483288A (en) * | 2022-01-27 | 2022-05-13 | 重庆长安汽车股份有限公司 | Control method and system for improving transient response of supercharged engine and automobile |
| CN114483288B (en) * | 2022-01-27 | 2023-09-12 | 重庆长安汽车股份有限公司 | Control method and system for improving transient response of supercharged engine and automobile |
| CN114427493A (en) * | 2022-03-23 | 2022-05-03 | 上海汽车集团股份有限公司 | Supercharger and engine with same |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP3817420B2 (en) | Variable rotational speed oil-free screw compressor and operation control method thereof | |
| CN111691967A (en) | Two-stage supercharger and engine | |
| CN102421999A (en) | Internal combustion engine having sequential supercharging | |
| CN110566341B (en) | Control method of series-parallel electric supercharging system | |
| CN104632356A (en) | Parallel type engine two-stage pressurization system with compressed air storage device and vehicle | |
| CN109057946B (en) | Anti-surge structure of pneumatic supercharging device for vehicle and control method thereof | |
| GB2545942A (en) | Double channel power turbine system and control method thereof | |
| CN103352754A (en) | Multi-mode large and small turbocharger diesel engine sequential supercharging structure | |
| CN110500174A (en) | The parallel electronic pressure charging system of one kind and its control method | |
| CN112031925A (en) | Electric supercharging preposed multistage mixed supercharging system for engine | |
| CN102359413B (en) | Turbocharging system | |
| CN104832221A (en) | Anti-surge system for turbocharging | |
| CN107740710B (en) | Turbine shell structure | |
| CN105508035B (en) | Supercharged diesel engine multi-mode switches pressurized construction and boosting method | |
| CN201635827U (en) | Intake system of turbocharged engine | |
| CN204253169U (en) | A kind of two independent turbine variable boost device | |
| CN102392732A (en) | Multi-valve bypass valve assembly for two stages of supercharging | |
| CN214698018U (en) | Exhaust pulse energy utilization system and turbocharger thereof | |
| CN205297731U (en) | Engine supercharging system | |
| CN205349509U (en) | Compound pressure intensifying structure in succession of supercharged diesel engine | |
| CN212583814U (en) | Successive supercharging system, engine assembly and vehicle | |
| CN212202227U (en) | Compound supercharging system of engine | |
| CN205225401U (en) | Double fluid way power turbine system | |
| CN203892005U (en) | Turbo charging mechanism with two-position two-way pulse width adjusting valve | |
| CN207406406U (en) | Two stage turbocharging system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20200922 |