CN108119235B - Isothermal compression preheating type internal combustion engine - Google Patents
Isothermal compression preheating type internal combustion engine Download PDFInfo
- Publication number
- CN108119235B CN108119235B CN201710605731.2A CN201710605731A CN108119235B CN 108119235 B CN108119235 B CN 108119235B CN 201710605731 A CN201710605731 A CN 201710605731A CN 108119235 B CN108119235 B CN 108119235B
- Authority
- CN
- China
- Prior art keywords
- cylinder
- compression
- compression cylinder
- valve
- air
- 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.)
- Active
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
- F02B75/00—Other engines
- F02B75/40—Other reciprocating-piston engines
Abstract
The invention belongs to the technical field of internal combustion engines, and particularly relates to an isothermal compression preheating type internal combustion engine. The technical problem to be solved by the invention is to reduce the heat loss of the engine by improving the structure of the engine. The technical scheme includes that the isothermal compression preheating type internal combustion engine comprises a working cylinder and a compression cylinder, wherein a compressed air cooler is arranged on the compression cylinder, a regenerative heat exchanger is arranged behind an exhaust valve of the working cylinder, and compressed air of the compression cylinder enters the working cylinder through the regenerative heat exchanger. The innovation of the invention is that: compression and work are accomplished in different cylinders. Through the work of the multi-stage compression cylinder, the air is subjected to isothermal compression and then enters the special cylinder for acting after being subjected to heat exchange and preheating with exhaust. The comprehensive transformation improves the heat efficiency of the engine, reduces energy waste, reduces exhaust emission, and reduces air pollution while improving efficiency.
Description
Technical Field
The invention belongs to the technical field of internal combustion engines, and particularly relates to an isothermal compression preheating type internal combustion engine.
Background
An internal combustion engine is a power machine, and is a heat engine that directly converts heat energy released by burning fuel inside the machine into power. At present, the most common piston type internal combustion engine is used. The piston type internal combustion engine works on the principle that fuel and air are mixed and combusted in a cylinder of the piston type internal combustion engine, and the released heat energy enables the cylinder to generate high-temperature and high-pressure fuel gas. The gas expands to push the piston to do work, and then the mechanical work is output through a crank link mechanism or other mechanisms to drive driven machinery to work, wherein the common engine and the gasoline engine are adopted. The process of moving from one end of the cylinder to the other as the piston reciprocates within the cylinder is called a stroke.
Most of common internal combustion engines are four-stroke internal combustion engines. It is divided into an intake stroke, a compression stroke, a power stroke and an exhaust stroke.
Suction stroke: the intake valve is opened, the exhaust valve is closed, the piston moves downward, and the gasoline and air mixture enters the cylinder.
Compression stroke: both the intake and exhaust valves are closed, the piston moves upward and the gasoline and air mixture is compressed. Converting mechanical energy into internal energy.
And (3) power stroke: at the end of the compression stroke, the spark plug generates an electric spark, which burns the fuel violently, producing a high temperature, high pressure gas. The high-temperature and high-pressure gas pushes the piston to move downwards, so that the crankshaft is driven to rotate to apply work to the outside. Only the working stroke in the four strokes does work outwards, and the other three strokes are all completed by the inertia of the working stroke. Converting the internal energy into mechanical energy.
Exhaust stroke: the intake valve is closed, the exhaust valve is opened, the piston moves upward, and the exhaust gas is discharged out of the cylinder.
In essence, an internal combustion engine is a process in which fuel and air are mixed and combusted to produce heat, which causes the gases to expand and be converted into mechanical energy by the expansion. Therefore, it is a process of converting chemical energy into mechanical energy. From the viewpoint of energy conservation, complete conversion of chemical energy into mechanical energy is the most desirable result, but in practice, the energy consumption of fuel generation has mainly the following paths: the engine does work, heat in exhaust, cooling system absorbs heat, mechanical loss, pumping loss, heat radiation, compression work of compression stroke and the like. The most significant loss is heat being rejected. The exhaust gas temperature of the existing internal combustion engine exceeds 500 ℃, and the exhaust gas is not utilized. Also, during the compression stroke, the compression of the gas generates heat, i.e., additional compression work is consumed. In addition, resistance consumption by the mechanical structure is also involved. Therefore, it is necessary to reduce heat loss as much as possible and improve thermal efficiency by further design.
For example, with turbocharging, average pressure is provided, phasing is improved to increase compression ratio, and thermal efficiency is improved. The fuel injection adjusting angle is used for adjusting the fuel injection advance angle along with the rotating speed and adjusting the ignition time, so that the combustion is fully carried out, and the heat efficiency is improved. Direct injection, good atomization, shortened combustion time, and improved thermal efficiency. The high-pressure common rail provides consistent oil pressure and accurate oil supply, so that the air input of the oil quantity is matched with the rotating speed, and the aims of saving oil and improving the heat efficiency are fulfilled.
The improved technical schemes are improved on the premise that the four strokes of the engine are not changed.
Disclosure of Invention
The technical problem to be solved by the invention is to reduce the heat loss of the engine by improving the structure of the engine.
The innovation of the invention is that: compression and work are accomplished in different cylinders. The air enters a special acting cylinder after being subjected to isothermal compression and heat exchange with exhaust gas for preheating.
The technical scheme includes that the isothermal compression preheating type internal combustion engine comprises a working cylinder and a compression cylinder, wherein a compressed air cooler is arranged on the compression cylinder, a regenerative heat exchanger is arranged behind an exhaust valve of the working cylinder, and compressed air of the compression cylinder enters the working cylinder through the regenerative heat exchanger.
Specifically, the isothermal compression preheating type internal combustion engine comprises a working cylinder, a compression cylinder, wherein an inlet valve, an exhaust valve and an oil injection nozzle are arranged on the working cylinder, the oil injection nozzle is connected with an oil supply system consisting of a fuel tank, a fuel oil delivery pump and a high-pressure oil pump, the exhaust valve is connected with a regenerative heat exchanger, an exhaust port of the regenerative heat exchanger is connected with a denitration catalyst and a silencer, an inlet valve and an exhaust valve are arranged on the compression cylinder, the exhaust valve of the compression cylinder is communicated with the inlet valve of the working cylinder through the regenerative heat exchanger, a front compression cylinder is further arranged on the compression cylinder, a compressed air cooler is arranged between the exhaust valve of the front compression cylinder and the inlet valve of the compression cylinder, piston connecting rods are arranged in the working cylinder, the compression cylinder and the front compression cylinder, and all the piston connecting.
The working process of the engine is as follows: air enters a front compression cylinder through air filtration to be compressed, heat generated by compressed air is cooled through a compressed air cooler, cooled gas is compressed through the compression cylinder and then preheated through a regenerative heat exchanger to enter an acting cylinder, the time and the amount of oil injection are controlled, oil injection is performed, expansion acting (piston descending) waste gas is discharged out of a cylinder (piston ascending) to be exhausted through the regenerative heat exchanger, heat is released (heat exchange is performed with air inlet), and finally the waste gas and a denitration agent reflect denitration on a catalyst and are finally discharged through a silencer.
Generally, air compression is performed in dedicated compression cylinders by 2-4 stages of compression (i.e., 2-4 compression dedicated cylinders). Except for the final stage of compression, the other stages of compression are cooled (by water cooling or ambient air cooling). Air pressure after final stage compression: 2.5 to 3.5MPa (absolute pressure), temperature: and (4) preheating to 500-1000 ℃ through a regenerative heat exchanger at 90-250 ℃, and then entering a special acting cylinder.
Compared with the four-stroke combustion working process of the existing engine, the invention has the innovation points that: compression and work are accomplished in different cylinders. Through the work of the multi-stage compression cylinder, the air is subjected to isothermal compression and then enters the special cylinder for acting after being subjected to heat exchange and preheating with exhaust. In the compression engineering, the heat generated by the compressed air is released continuously, and the energy loss caused by air compression is reduced. And before entering the acting cylinder, the heat generated by the emission of the acting cylinder is fully absorbed, the temperature of the compressed air is improved, the compressed air is more fully combusted, the combustion efficiency is higher, the comprehensive transformation improves the thermal efficiency of the engine, the energy waste is reduced, the exhaust emission is reduced, and the air pollution is reduced while the efficiency is improved.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
in the figure: 1-an air intake pipe for burning air to do work; 2-an air filter; 3-ambient air for cooling; 4-a compressed air cooler; 5-a regenerative heat exchanger; 6-a denitration catalyst; 7-a silencer; 8-a fuel tank; 9-a fuel delivery pump; 10-a high-pressure oil pump; 11-an exhaust valve; 12-a working cylinder; 13-a crankshaft; 14-an intake valve; 15-an oil nozzle; 16-a spark plug; 17-a compression cylinder; 18-a front compression cylinder; 19-a preceding compression cylinder; 20-a denitrifier electromagnetic regulating valve; 21-compressed air cooler.
Detailed Description
As shown in figure 1, the isothermal compression preheating type internal combustion engine comprises a working cylinder 12 and a compression cylinder 17, wherein the working cylinder 12 is provided with an inlet valve 14, an exhaust valve 11, an oil nozzle 15 and a spark plug 16, the oil nozzle 15 is connected with an oil supply system consisting of a fuel tank 8, a fuel oil delivery pump 9 and a high-pressure oil pump 10, the exhaust valve 11 is connected with a regenerative heat exchanger 5, an exhaust port of the regenerative heat exchanger 5 is connected with a denitration catalyst 6 and a silencer 7, an air inlet valve and an air outlet valve are arranged on the compression cylinder 17, the air outlet valve of the compression cylinder is communicated with the air inlet valve of the power cylinder 12 through the regenerative heat exchanger 5, the compression cylinder 17 is also provided with a front compression cylinder, a compressed air cooler is arranged between an exhaust valve of the front compression cylinder and an air inlet valve of the compression cylinder 17, piston connecting rods are arranged in the working cylinder 12, the compression cylinder 17 and the front compression cylinder, and all the piston connecting rods are connected with the same crankshaft 13.
The air cooler comprises two front compression cylinders, namely a front compression cylinder 18 and a front compression cylinder 19, wherein an air inlet pipe 1 is connected to an air inlet valve of the front compression cylinder 19, an air filter 2 is arranged on the air inlet pipe 1, and a compressed air cooler 4 is connected between an exhaust valve of the front compression cylinder 19 and the air inlet valve of the front compression cylinder 18.
The exhaust system of the working cylinder 12 is provided with a denitration agent electromagnetic regulating valve 20.
The number of the working cylinders 12 is two.
The invention can thus be implemented in two embodiments
Embodiment 1: the number of the working cylinders is 2, and 2 air compression cylinders are added. For a total of 4 cylinders. The air is compressed in 2 stages. The inner diameter of the special 2-stage air compression cylinder is 45-60% of that of other cylinders. The other 3 cylinders have the same bore. Under the design working condition, the thermal efficiency can reach 80 percent, the mechanical loss and the auxiliary machine consumption are deducted by 10 percent, and the total efficiency is 70 percent. The scheme is suitable for the reconstruction of the existing internal combustion engine.
Scheme 2: the number of the working cylinders is 2, the number of the compression cylinders is 3, one compression cylinder is one, two front compression cylinders are provided, the total number of the front compression cylinders is 5, and air is compressed by 3 stages. The inner diameters of the 2 special cylinders for doing work are the same. The inner diameter of the special cylinder for 1-stage air compression is 100-110% of that of the special cylinder for acting. The inner diameter of the special cylinder for 2-stage air compression is 60-65% of that of the special cylinder for acting. The inner diameter of the special 3-stage air compression cylinder is 35-38% of that of the special acting cylinder. Under the design working condition, the thermal efficiency can reach 87%, 10% of mechanical loss and auxiliary machine consumption are deducted, and the total efficiency is 77%.
The air compression is completed by 2-4 stages of compression (namely 2-4 special compression air cylinders) in a special compression air cylinder. Except for the final stage of compression, the other stages of compression are cooled (by water cooling or ambient air cooling). Air pressure after final stage compression: 2.5 to 3.5MPa (absolute pressure), temperature: and (4) preheating to 500-1000 ℃ through a regenerative heat exchanger at 90-250 ℃, and then entering a special acting cylinder.
Working process of the working cylinder: the piston is at the top dead center, the exhaust valve is closed, the intake valve is opened, air is introduced (the piston moves downwards), the air introduction is finished, the intake valve is closed (accounting for 5-9% of the volume of the cylinder), oil injection and combustion are performed, the combustion is finished (accounting for 6-12% of the volume of the cylinder), expansion work is done (the piston moves downwards to the bottom dead center), the exhaust valve is opened to exhaust (the piston moves upwards), the exhaust is finished, the exhaust valve is closed, the piston returns to the top dead center.
Temperature of gas discharged from the working cylinder: 550-1050 ℃, pressure: 0.13~0.25MPa (absolute pressure), through backheat heat exchanger give out heat (be used for preheating and admit air), the temperature: and (3) 140-290 ℃, and discharging the denitration product from the silencer after reacting with a denitration agent on the catalyst for denitration.
The special compression cylinder and the special acting cylinder adopt the same crankshaft (a large-scale unit can be divided into a plurality of shafts and connected by a coupler or a gear and a chain wheel). The fuel oil system adopts a high-pressure oil pump, an oil pipe and an oil nozzle which are commonly used by a diesel engine. Each working cylinder is provided with one oil cylinder (two cylinders can be arranged after the existing internal combustion engine is transformed). The oil injection quantity is adjusted by adjusting the oil pumping stroke of the oil cylinder. The oil injection quantity can also be adjusted by adopting an electromagnetic valve type oil injection nozzle. In general, the fuel system is the same as existing diesel engines. The fuel oil can be any combustible oil, such as diesel oil, gasoline and heavy oil. The higher the injection and combustion speeds, the higher the thermal efficiency (as is the case with the existing internal combustion engines). If gas fuels such as natural gas and the like are adopted, high-pressure compression is needed, and the pressure reaches more than 1.6 MPa. The oil nozzle is replaced by a solenoid valve type air nozzle. When the preheating temperature of the compressed air is lower than 800 ℃, the natural gas can be added into the compressed air before an air inlet valve of the special cylinder for acting, and the pressure of the natural gas is only slightly higher than that of the compressed air (2.6-3.6 MPa). Large units can adopt the scheme.
The starting mode is as follows: the starting power is the same as that of the existing internal combustion engine, and an electric motor or a pneumatic motor is adopted. Ignition is carried out by adopting a spark plug or electric heating preheating intake air ignition. Once started, fuel can auto-ignite during operation without ignition. If the fuel is natural gas, a spark plug is required to be used for ignition during operation. Since the natural gas ignition temperature is as high as 800 ℃.
The working cylinder and the cylinder cover are cooled by water cooling or water vaporization. The water vaporization cooling can properly improve the temperature of the cylinder and the cylinder cover and reduce the heat dissipation loss.
In order to prolong the service life of the working cylinder, the cylinder cover and the piston, the top of the piston is sprayed, enameled or aluminized, nitrided and ceramized on the inner surfaces of the cylinder and the cylinder cover.
The air compression cylinder and the cylinder cover are cooled by water cooling or ambient air fins. When water cooling is adopted, a cooling water system is independent, so that the cooling temperature is as low as possible.
Due to the high combustion temperature, the exhaust gas must be denitrated. The denitration agent adopts urea aqueous solution, liquid ammonia, ammonia water or other alkali liquor, and is quantitatively added into the discharged flue gas through an electronic regulating valve before the denitration catalyst. And cooled flue gas is mixed into the compressed air inlet, so that the oxygen content is reduced, the yield of nitrogen oxides is reduced, and the consumption of a denitration agent is reduced. With the increase of the environmental pressure, the flue gas of the existing internal combustion engine also needs denitration.
Claims (4)
1. The utility model provides an isothermal compression preheating-type internal-combustion engine, including acting cylinder (12), compression cylinder (17), be equipped with (14) intake valve and exhaust valve (11) and fuel sprayer (15) on acting cylinder (12), spark plug (16), fuel tank (8) are connected in fuel sprayer (15), fuel delivery pump (9), the oil feeding system of high-pressure oil pump (10) constitution, backheat heat exchanger (5) are connected in exhaust valve (11), denitration catalyst (6) and muffler (7) are connected to the gas vent of backheat heat exchanger (5), be equipped with admission valve and discharge valve on compression cylinder (17), its characterized in that: an exhaust valve of a compression cylinder (17) is communicated with an inlet valve (14) of a working cylinder (12) through a regenerative heat exchanger (5), a front compression cylinder is further arranged on the compression cylinder (17), a compressed air cooler is arranged between an exhaust valve of the front compression cylinder and an inlet valve of the compression cylinder (17), piston connecting rods are arranged in the working cylinder (12), the compression cylinder (17) and the front compression cylinder, all the piston connecting rods are connected with the same crankshaft (13), a denitration agent electromagnetic regulating valve (20) is arranged on an exhaust system of the working cylinder (12), the compression cylinder (17) has 2-4 stages, a compressed air cooler is connected between each stage, the compressed air cooler adopts air cooling or water cooling, the two front compression cylinders are respectively a front compression cylinder (18) and a front compression cylinder (19), an inlet valve of the front compression cylinder (19) is connected with an inlet pipe (1), an air filter (2) is arranged on the air inlet pipe (1), and a compressed air cooler (4) is connected between an exhaust valve of the front compression cylinder (19) and an inlet valve of the front compression cylinder (18).
2. Isothermal compression preheating internal combustion engine according to claim 1, characterized in that: the number of the working cylinders (12) is two.
3. Isothermal compression preheating internal combustion engine according to claim 1, characterized in that: the cooling mode of the compressed air cooler is air cooling or water cooling.
4. Isothermal compression preheating internal combustion engine according to claim 1, characterized in that: the air input of the working cylinder (12) is 5-10% of the volume of the cylinder; the air inlet pressure is 2.5-3.5 MPa; the inlet air temperature is 500-1000 ℃.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/CN2017/000698 WO2019018954A1 (en) | 2017-07-14 | 2017-11-22 | Isothermal compression preheating internal combustion engine |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710574757 | 2017-07-14 | ||
| CN2017105747575 | 2017-07-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108119235A CN108119235A (en) | 2018-06-05 |
| CN108119235B true CN108119235B (en) | 2020-12-04 |
Family
ID=62228114
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710605731.2A Active CN108119235B (en) | 2017-07-14 | 2017-07-24 | Isothermal compression preheating type internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN108119235B (en) |
| WO (1) | WO2019018954A1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1382901A (en) * | 2002-06-05 | 2002-12-04 | 浙江大学 | Car engine using mixture of comprssed air and fuel oil or fuel gas |
| US7201156B1 (en) * | 2005-05-24 | 2007-04-10 | Wait Irving S | Thermal transfer internal combustion engine |
| CN2934598Y (en) * | 2006-06-09 | 2007-08-15 | 王福山 | Environment-friendly energy-saving type internal combustion engine |
| CN101443535A (en) * | 2006-05-27 | 2009-05-27 | 托马斯·C·罗宾逊 | Improved engine |
| CN201377352Y (en) * | 2009-03-25 | 2010-01-06 | 王福山 | Reciprocating internal combustion engine |
| CN103244256A (en) * | 2012-02-08 | 2013-08-14 | 通用汽车环球科技运作有限责任公司 | Internal combustion engine utilizing dual compression and single expansion process |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1928333A (en) * | 2006-10-01 | 2007-03-14 | 袁辉 | Internal-combustion engine |
| US8082892B2 (en) * | 2007-10-10 | 2011-12-27 | Yuanping Zhao | High efficiency integrated heat engine-2 (HEIHE-2) |
| CN105715387B (en) * | 2016-03-07 | 2019-03-26 | 武汉理工大学 | CNG engine multi-cylinder is from inflation system and its from inflation method |
-
2017
- 2017-07-24 CN CN201710605731.2A patent/CN108119235B/en active Active
- 2017-11-22 WO PCT/CN2017/000698 patent/WO2019018954A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1382901A (en) * | 2002-06-05 | 2002-12-04 | 浙江大学 | Car engine using mixture of comprssed air and fuel oil or fuel gas |
| US7201156B1 (en) * | 2005-05-24 | 2007-04-10 | Wait Irving S | Thermal transfer internal combustion engine |
| CN101443535A (en) * | 2006-05-27 | 2009-05-27 | 托马斯·C·罗宾逊 | Improved engine |
| CN2934598Y (en) * | 2006-06-09 | 2007-08-15 | 王福山 | Environment-friendly energy-saving type internal combustion engine |
| CN201377352Y (en) * | 2009-03-25 | 2010-01-06 | 王福山 | Reciprocating internal combustion engine |
| CN103244256A (en) * | 2012-02-08 | 2013-08-14 | 通用汽车环球科技运作有限责任公司 | Internal combustion engine utilizing dual compression and single expansion process |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108119235A (en) | 2018-06-05 |
| WO2019018954A1 (en) | 2019-01-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201560839U (en) | Internal combustion stirling engine | |
| CN101900027A (en) | Adopt the internal-combustion engine of dual compression and dual expansion processes | |
| CN202811059U (en) | Piston type composite thermal power system | |
| WO2002084092A1 (en) | Method of operating reciprocating internal combustion engines, and system therefor | |
| CN101532421A (en) | A secondary expansion mixed stroke explosive motor | |
| CN101608572A (en) | A kind of have a turbo charged petrol engine | |
| CN101225765A (en) | Cylinder linkage technique for multi-cylinder internal combustion engine | |
| CN104088720B (en) | A kind of efficient heat energy power engine and work method thereof | |
| WO2016000402A1 (en) | High pressure energy storage thermal energy power machine and work-doing method therefor | |
| US11066974B2 (en) | Internal combustion engine waste heat utilization system | |
| WO2016000400A1 (en) | Efficient thermal energy power device and work-doing method therefor | |
| CN108119235B (en) | Isothermal compression preheating type internal combustion engine | |
| CN216278144U (en) | High-efficiency internal combustion engine | |
| CN201358849Y (en) | Six-stroke internal combustion and steam self-cleaning engine | |
| CN204476553U (en) | Two-stroke pure oxygen motor waste expansion mechanism | |
| CN107035517A (en) | A kind of new work engine | |
| WO2016000403A1 (en) | Thermal energy power device and work-doing method therefor | |
| CN201351527Y (en) | Air inlet and exhaust device of medium speed diesel engine | |
| CN103557070A (en) | Heat-absorption type dry ice engine | |
| CN104632362B (en) | Exhaust gas expanding mechanism for two-stroke pure oxygen engine | |
| CN102767428B (en) | Heat absorption type dry ice engine | |
| CN204082318U (en) | A kind of thermal powerplant | |
| CN204082379U (en) | A kind of efficient heat energy power engine | |
| CN107355317A (en) | A kind of internal-combustion steam engine | |
| CN104141535B (en) | Four-stroke ic formula fluid power motor |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20210825 Address after: 035400 Industrial Zone, Qiucun village, Jizhuang Township, Dingxiang County, Xinzhou City, Shanxi Province Patentee after: XINZHOU LIBO EQUIPMENT MANUFACTURING Co.,Ltd. Address before: 035400 Qiucun Industrial Park, Dingxiang County, Xinzhou City, Shanxi Province Patentee before: Zou Guoquan Patentee before: Zhang Yingchen |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20220429 Address after: 035400 Industrial Zone, Qiucun village, Jizhuang Township, Dingxiang County, Xinzhou City, Shanxi Province Patentee after: SHANXI LIGUO MAGNETIC MATERIALS Co.,Ltd. Address before: 035400 Industrial Zone, Qiucun village, Jizhuang Township, Dingxiang County, Xinzhou City, Shanxi Province Patentee before: XINZHOU LIBO EQUIPMENT MANUFACTURING CO.,LTD. |
|
| TR01 | Transfer of patent right |