Four-way intake combined centrifugal compression and conveying method for vertical pyrolysis furnace of double pyrolysis section coal

Abstract

Four-way intake combined centrifugal compression and transportation method for double pyrolysis section vertical coal pyrolysis furnace. In a double pyrolysis section vertical coal pyrolysis furnace system with internal heat type gas-solid countercurrent heat transfer, the first combustion-supporting gas and the first fuel gas enter the main flue of the stripping section to burn after being boosted by the combined centrifugal compressor and form the first mixed gas through the first mixer, and / or enter the furnace of the coal pyrolysis furnace to burn and release heat to form an upward gas heat carrier to heat the downward pyrolyzed coal material; the combustion of the first mixed gas belongs to under-oxygen combustion, and the remaining gas is used as temperature-control gas; the temperature-regulating gas enters the furnace through the temperature-regulating gas channel of the low-temperature pyrolysis section after being boosted by the combined centrifugal compressor to reduce the temperature of the upward gas; the lower pre-cooling gas enters the furnace through the pre-cooling gas channel of the semi-coke pre-cooling section after being boosted by the combined centrifugal compressor to reduce the temperature of the downward semi-coke. The combined centrifugal compressor is driven by one prime mover, and the four centrifugal compressors start and stop simultaneously, reliably controlling the flow rates of the four-way gases and realizing safe and stable production.

Description

Technical Field

[0001] The invention relates to a four-way air intake combined centrifugal compression and transportation method for a double-pyrolysis-section coal vertical pyrolysis furnace. In a double-pyrolysis-section coal vertical pyrolysis furnace system with internal heat gas-solid countercurrent heat transfer, a first combustion-aiding gas and a first fuel gas are pressurized by a combined centrifugal compressor and then formed into a first mixed gas by a first mixer, which enters a main fire channel of a stripping section for combustion and / or enters a furnace of a coal pyrolysis furnace for combustion to release heat to form an upward gas heat carrier to heat and pyrolyze the descending coal material; the combustion of the first mixed gas belongs to oxygen-deficient combustion, and the remaining gas is used as temperature-control gas; the temperature-adjusting gas is pressurized by a combined centrifugal compressor and then enters the furnace through a temperature-adjusting gas channel of a low-temperature pyrolysis section to reduce the temperature of the ascending gas; the lower pre-cooling gas is pressurized by a combined centrifugal compressor and then enters the furnace through a pre-cooling gas channel of a semi-coke pre-cooling section to reduce the temperature of the descending semi-coke; the combined centrifugal compressor uses a prime mover to drive four centrifugal compressors to start and stop at the same time, and the four-way gas flow is reliably controlled to achieve safe and stable production. Background Art

[0002] The present invention relates to an internally heated moving bed vertical coal pyrolysis furnace, which refers to a moving bed vertical coal pyrolysis furnace which uses at least the flue gas of the main fire channel combustion gas of the pyrolysis furnace as a gas heat carrier to pyrolyze coal.

[0003] The coal pyrolysis furnace of the present invention can be simultaneously provided with a system for providing external heat to the pyrolysis section (preheating section and / or pyrolysis section and / or stripping section); in the external heat supply system, the high-temperature gas flowing through the heat source material channel of the external heat supply system does not enter the furnace of the pyrolysis furnace, and the heat source material channel of the external heat supply system indirectly transfers heat to the furnace of the coal dry distillation zone of the pyrolysis furnace through the heat transfer wall surface.

[0004] The present invention relates to an internal heating type moving bed coal vertical pyrolysis furnace, which may or may not be provided with a semi-coke cooling section and a coke quenching section as required.

[0005] The present invention relates to the compression and transportation process of the component gases of the combustion gas used in the main fire channel of an internally heated moving bed vertical coal pyrolysis furnace, namely, the combustion-supporting gas and the combustion gas, and also to the compression and transportation of the temperature-regulating gas in the low-temperature pyrolysis section; the main fire channel refers to the fire channel from which most of the internal heating heat supply of the internally heated moving bed vertical coal pyrolysis furnace comes.

[0006] In the coal pyrolysis section of the present invention, the first mixed fuel gas burns in the main fire channel and / or enters the furnace of the coal pyrolysis furnace to burn and release heat to form flue gas which goes upward as a gas heat carrier to heat and pyrolyze the descending coal.

[0007] In the northwest of my country, Xinjiang Uygur Autonomous Region, Inner Mongolia Autonomous Region, and northern Shaanxi, there are abundant long flame coal, non-sticky coal, and weakly sticky coal with low ash, low sulfur, and high volatility. The coal can produce high-yield coal tar and high-yield coal gas through low-temperature pyrolysis or low-temperature dry distillation, and at the same time produce a certain quality of low-temperature pyrolysis semi-coke. The hydrogen, carbon monoxide, and methane contained in the coal gas can be used to extract hydrogen and methane. Coal tar can be used to extract phenols and hydrogenate to produce clean oil products. Pyrolysis semi-coke can be used as a reducing agent for ferroalloy coke and calcium carbide coke, and can also be used as a blast furnace injection material instead of metallurgical coke. At present, the semi-coke (or semi-coke) production capacity of low-temperature pyrolysis devices for low-grade coal in China is about 100 million tons, forming an industry, which mainly adopts a vertical pyrolysis furnace with an internal heat gas heat carrier, and uses the hot waste gas (flue gas and circulating coal gas heat carrier) generated by the under-oxygen combustion of coal gas (the combustion-supporting gas is air) to directly heat the coal for pyrolysis.

[0008] The national standard GB / T25212-2010, classification of varieties and grades of semi-coke products, stipulates the standard values ​​of each grade of each performance index of semi-coke. It can be seen that sometimes the index values ​​are very small, but the grades are completely different; for example, the fixed carbon index FCd of semi-coke is between 74.01% and 92.00%, and each increase of 2% means a grade increase; for example, the volatile matter index Vdaf of semi-coke is between 15.00% and 4.00%, and each decrease of 5% means a grade increase; the increase in grade means that the performance and scope of application are improved. The price of products has been significantly improved, and the difference in product prices is huge. For example, the volatile matter index Vdaf of lignite has been reduced from 7.0% (5.01% to 10.00% range, belonging to V-2 grade) to 4.5% (≤5.00% range, belonging to V-1 grade), which is one grade higher. The difference in product price is 100 to 150 yuan / ton or even higher. Since pyrolysis semi-coke is the pyrolysis product with the highest yield, the output value has increased greatly. For example, for a lignite production plant with an annual output of 1 million tons, the sales volume can differ by 100 to 150 million yuan / year or even higher.

[0009] In fact, if the low-temperature pyrolysis process can be ensured to proceed normally and the volatile matter of semi-coke can be further reduced reasonably, the following beneficial effects will be produced:

[0010] ① Improve the yield of high-value products (coal gas and tar) and increase output value;

[0011] ② Reduce the volatile matter content of lignite, increase the strength of lignite, increase the price of lignite, and increase the output value.

[0012] Under the conditions of a single pyrolysis stage pyrolysis furnace or essentially a single pyrolysis stage pyrolysis furnace, taking low-rank coal as an example, when the final pyrolysis temperature is 600-900°C, the increase in coal gas yield is particularly significant; the pyrolysis time directly affects the pyrolysis degree and product distribution of low-rank coal. The extension of the pyrolysis time will increase the degree of secondary cracking of tar, thereby resulting in a decrease in tar yield and an increase in coal gas yield.

[0013] Under the same coal conditions, a higher pyrolysis final temperature is required to reduce the volatile matter of blue coke. However, the conventional method of increasing the pyrolysis final temperature (such as forming medium-temperature pyrolysis) will inevitably lead to the transformation of low-temperature pyrolysis into medium-temperature pyrolysis. More heavy volatiles in the coal are thermally condensed into coke (i.e., burned), resulting in a decrease in the yield of coal tar. The higher the pyrolysis final temperature, the easier it is for the tar to undergo secondary cracking. When the pyrolysis final temperature is higher than a certain optimal value (which varies depending on the type of coal), the secondary cracking reaction of tar increases dramatically, resulting in a decrease in the actual tar yield, while the coal gas yield increases. This The steam thermal cracking rate and thermal condensation rate of coal tar increase (i.e., it loses hydrogen and becomes heavier), which will also deteriorate the quality of tar, increase the difficulty of hydrogenation and reduce its use value. In general, for low-rank coal with high volatile matter, compared with low-temperature pyrolysis (high coal tar yield and light oil quality, low coal gas yield, and high volatile matter of lignite), medium-temperature pyrolysis (low coal tar yield and heavy oil quality, higher coal gas yield, and low volatile matter of lignite) is less economical. This leads to the prevalence of low-temperature pyrolysis technology, while medium-temperature pyrolysis technology is rarely used (only used in occasions where more coal gas is produced).

[0014] Therefore, a double pyrolysis stage coal dry distillation process is needed. Under the premise of ensuring the low-temperature pyrolysis operation effect, a stripping section is added to reduce the volatile matter content of the semi-coke; the main burner at the bottom of the stripping section provides hot flue gas, and temperature-regulating gas is sprayed into the bottom of the low-temperature pyrolysis section to lower the temperature of the rising gas; the lower pre-cooling air enters the furnace through the pre-cooling air channel of the semi-coke pre-cooling section to lower the temperature of the descending semi-coke and recover heat.

[0015] The first common problem of the current low-grade coal internal heating low-temperature pyrolysis device is that the volatile matter of the lignite is too high and the strength of the lignite is too low. In the existing technical solutions, the final pyrolysis temperature must be increased to reduce the volatile matter of the lignite, which will inevitably cause tar burning. This is mainly caused by the control method of the pyrolysis temperature field. The temperature field of the pyrolysis zone of the current lignite furnace is gradually increasing along the descending direction of the coal material. There is no rising gas temperature sudden drop type double pyrolysis section internal heating type moving bed coal vertical pyrolysis furnace or pyrolysis operation mode. In fact, there is no low-temperature pyrolysis section and medium-temperature pyrolysis section with independent and flexible control of each pyrolysis temperature. The medium-temperature pyrolysis section is used to ensure the reduction of the volatile matter of the lignite, and the low-temperature pyrolysis section with independent temperature control is used to improve the yield and quality of tar.

[0016] The second common problem of the current low-rank coal internal heating medium and low temperature pyrolysis device is that the nitrogen content in the coal gas is about 50%, the hydrogen and methane content is low, the calorific value is low, and it is rich in light hydrocarbons, oxygen, hydrogen sulfide, organic sulfur, ammonia and water vapor, etc. The cost of hydrogen recovery and methane recovery is high, and the utilization value is low, which to a certain extent restricts the processing and comprehensive utilization of effective gas (hydrogen, methane) in the coal gas, limits the use value of effective gas in the coal gas, and reduces the efficiency of the device. The main reason is that the combustion control of high-purity combustible gas coal gas and oxygen-enriched or pure oxygen is difficult, and poor treatment causes the coal sintering and agglomeration at the outlet of the fire channel wind brick, and the flue gas is uneven, resulting in uneven temperature in the pyrolysis furnace, and the quality of blue carbon cannot be guaranteed, resulting in the inability to produce. What's more, once excessive oxygen-enriched or pure oxygen is introduced into the pyrolysis furnace, deflagration or even detonation will occur, forming a vicious accident of furnace explosion. One of the reasons is the lack of process equipment and control methods for controlling the excessive introduction of oxygen into the pyrolysis furnace.

[0017] When air is used as the combustion-supporting gas in an internally heated moving bed vertical coal pyrolysis furnace, the effective gas volume concentration in the coal gas is very low. Table 1 shows the coal gas composition corresponding to the combustion-supporting gas of different coal pyrolysis furnaces. It is a set of typical coal gas production data of a coal low-temperature pyrolysis device in Hami, Xinjiang Uygur Autonomous Region. Compared with the pure combustion reaction of combustible components and oxygen, the non-combustible gas (mainly nitrogen) from air becomes the cooling component of the combustion process and its volume flow rate is 3.77 times that of oxygen. The non-combustible gas (H 2 O、CO 2 、N 2 ,) are also cooling components in the combustion process, and the circulating coal gas that is artificially arranged to exceed the combustion ratio is also a cooling component in the combustion process. In this way, the normal value of the combustion flue gas temperature in the fire channel is about 650-900°C. If the combustion is carried out according to the chemical equivalent, the calculation results are shown in Table 2. The flue gas temperature and volume expansion ratio of the chemical equivalent combustion process of coal gas under different working conditions, the flue gas temperature is about 1694°C, and the short-term high temperature can be borne by high alumina bricks or silica bricks. The volume expansion ratio of the combustion raw gas to the combustion flue gas is 5.70, which can form a low-intensity deflagration.

[0018] For an internally heated moving bed vertical coal pyrolysis furnace, assuming that oxygen-enriched oxygen with an oxygen volume concentration of 34.71% and a carbon dioxide volume concentration of 65.29% is used as the combustion-supporting gas, the estimated value of the effective gas volume concentration in the coal gas is shown in Table 1. Under the accident state (excessive addition of combustion-supporting gas), combustion is carried out according to the chemical equivalent. The calculation results are shown in Table 2. The flue gas temperature can reach 2633°C, and the volume expansion ratio of the combustion raw gas to the combustion flue gas is 8.09, which will form a deflagration. This shows that under the accident state, the danger has increased significantly.

[0019] In the internal heating moving bed coal vertical pyrolysis furnace, it is assumed that pure oxygen is used as the combustion-supporting gas. The estimated value of the effective gas volume concentration in the coal gas is shown in Table 1. Under the accident state (excessive addition of combustion-supporting gas), combustion is carried out according to the chemical equivalent. The calculation results are shown in Table 3. The flue gas temperature and volume expansion ratio of the chemical equivalent combustion process of coal gas and pure oxygen. The flue gas temperature is expected to reach about 4316℃, and the volume expansion ratio of the combustion raw gas to the combustion flue gas is 11.47. Due to the high flame propagation speed in the high hydrogen concentration fuel gas, deflagration or detonation is very likely to occur, which may cause furnace wall rupture accidents or furnace explosion catastrophic accidents.

[0020] Table 1 Gas composition corresponding to different coal pyrolysis furnace combustion gases

[0021]

[0022] Table 2 Flue gas temperature and volume expansion ratio during chemical equivalent combustion of coal gas under different working conditions

[0023]

[0024] Table 3 Flue gas temperature and volume expansion ratio of chemical equivalent combustion process of coal gas and pure oxygen

[0025]

[0026] The above calculation has theoretical prediction deviations of gas composition, and its flue gas composition and temperature may also have slight deviations, but this does not affect the basic correctness of the analysis conclusions.

[0027] Therefore, when using oxygen-enriched oxygen or pure oxygen as the combustion-supporting gas in an internally heated moving bed vertical coal pyrolysis furnace, the hidden dangers of deflagration and detonation must be eliminated, and the appropriate temperatures of different distillation sections should also be reliably controlled. Since the mixer feed (the first combustion-supporting gas and the first fuel gas) of the main fire channel (also called the main gas chamber) of the existing internally heated moving bed vertical coal pyrolysis furnace is compressed and transported by independent combustion-supporting gas centrifugal compressors and coal gas centrifugal compressors, it is impossible to ensure that they are started and stopped at the same time. Therefore, under the condition that the coal gas for the combustion channel is reduced or stopped while the combustion-supporting gas for the combustion channel continues to be fed, the combustion-supporting gas for the combustion channel is formed. The uncontrollable gas will cause malignant accidents such as deflagration or detonation in the combustion channel and nearby furnace area of ​​the pyrolysis furnace. The present invention is proposed to avoid such accidents or potential accidents. The basic concept is that the combustion-supporting gas for the combustion channel must enter together with the gas in the expected proportion, and the temperature-adjusting gas must also enter the bottom of the low-temperature pyrolysis section of the furnace at the same time to accurately control the temperature of the low-temperature distillation section (to prevent the temperature from being too high), thereby becoming a basic safety guarantee measure for the coal pyrolysis device to use oxygen-enriched oxygen or pure oxygen as the combustion-supporting gas. This requirement implies that a combined compressor is needed to synchronously pressurize and deliver several gases, and start and stop them at the same time.

[0028] The concept of the present invention is: a four-way air intake combined centrifugal compression and transportation method for a double-pyrolysis-stage coal vertical pyrolysis furnace, in which a double-pyrolysis-stage coal vertical pyrolysis furnace system with internal heat gas-solid countercurrent heat transfer exists, a first combustion-aiding gas and a first fuel gas are pressurized by a combined centrifugal compressor and then passed through a first mixer to form a first mixed gas that enters the main fire channel of the distillation section for combustion and / or enters the furnace of the coal pyrolysis furnace for combustion to release heat to form an upward gas heat carrier to heat and pyrolyze the descending coal material; the combustion of the first mixed gas is oxygen-deficient combustion, and the remaining gas is used as temperature-control gas; the temperature-adjusting gas is pressurized by a combined centrifugal compressor and then passes through the temperature-adjusting gas channel of the low-temperature pyrolysis section to enter the furnace to reduce the temperature of the ascending gas; the lower pre-cooling gas is pressurized by a combined centrifugal compressor and then passes through the pre-cooling gas channel of the semi-coke pre-cooling section to enter the furnace to reduce the temperature of the descending semi-coke, and the combined centrifugal compressor uses a prime mover to drive four centrifugal compressors to start and stop at the same time, reliably controlling the four-way gas flow rate to achieve safe and stable production.

[0029] Several patent documents on combined centrifugal compressors involving multiple centrifugal compressors are described below. Their mechanical structures and functions can be used for reference by the present invention if they are suitable and available.

[0030] Chinese Patent ZL201210361133.2 A single-shaft plus multi-shaft carbon dioxide centrifugal compressor includes a double-shaft drive device, the left shaft of the double-shaft drive device is directly connected to the single-shaft low-pressure cylinder by a diaphragm coupling, and the right shaft of the double-shaft drive device is connected to the multi-shaft high-pressure cylinder by a diaphragm coupling; CO 2 The gas enters from the first-stage impeller of the single-shaft low-pressure cylinder, undergoes four-stage compression, flows out from the fourth-stage outlet pipe of the low-pressure cylinder and enters the first-stage impeller of the multi-shaft high-pressure cylinder, and then is discharged from the 3rd and 4th-stage impeller outlet of the multi-shaft high-pressure cylinder after four-stage compression and enters the subsequent process system; the present invention saves more than 10% energy compared with the traditional single-shaft + single-shaft model, and has higher safety and stability than foreign multi-shaft carbon dioxide compressors. The multi-stage centrifugal compressor of the invention is used for a gas, namely CO 2 The gas is compressed in multiple stages in series.

[0031] Chinese Patent ZL201410351897.2 discloses a multi-stage centrifugal compressor, which reduces the thrust load generated on the output shaft, and has high efficiency and high mechanical reliability. The multi-stage centrifugal compressor comprises: an input shaft (4) driven by an engine; a main gear (20) provided on the input shaft (4); a cannon (21) meshing with the main gear (20); an output shaft (5) provided with the cannon (21); a first-stage centrifugal impeller (11) provided at one end of the output shaft (5); and a second-stage centrifugal impeller (12) provided at the other end of the output shaft (5) and located on the downstream side of the flow of the fluid than the first-stage centrifugal impeller (11). Furthermore, the outer diameter (D1) of the first-stage centrifugal impeller (11) is set larger than the outer diameter (D2) of the second-stage centrifugal impeller (12). The multi-stage centrifugal compressor of the invention is used for multi-stage series compression of a gas.

[0032] Chinese Patent ZL201480030156.2 discloses a centrifugal compressor, comprising: a drive shaft (2) for rotational driving; a drive gear (11) connected to the drive shaft (2); driven gears (12, 13) for obtaining the rotation transmitted by the drive gear (11); a driven shaft (3) extending to both ends of the driven gears (12, 13) in the direction of the central axis; a first compression section (41) disposed on the first end side of the driven shaft (3) in the direction of the central axis; a second compression section (42) disposed on the second end side of the driven shaft (3) in the direction of the central axis; and a pressure adjustment section (7) for uniformly adjusting the pressure of the ejection side space of the fluid in the first compression section (41) and the pressure of the ejection side space of the fluid in the second compression section (42). The multi-stage centrifugal compressor of the invention is used for multi-stage series compression of a gas.

[0033] The method of the present invention has not been reported.

[0034] The purpose of the invention is to propose a four-way air intake combined with centrifugal compression and transportation method for a double-pyrolysis-stage coal vertical pyrolysis furnace. Summary of the invention

[0035] The four-way air intake combined with centrifugal compression and transportation method of the double-pyrolysis-stage coal vertical pyrolysis furnace of the present invention is characterized by:

[0036] ⑴ Double pyrolysis stage coal vertical pyrolysis furnace

[0037] The coal pyrolysis furnace is a vertical coal pyrolysis furnace with double pyrolysis sections and internal heating and moving bed. The coal entering the pyrolysis furnace passes through at least a preheating section, a low-temperature pyrolysis section, a stripping section, and a semi-coke precooling section during its downward process, and gradually becomes preheated coal, low-temperature pyrolysis semi-coke, stripping semi-coke, and precooling semi-coke.

[0038] In the furnace of the pyrolysis furnace, the stripping section is located below the low-temperature pyrolysis section, and the space of the stripping section is connected to the space of the low-temperature pyrolysis section;

[0039] In the furnace of the pyrolysis furnace, the semi-coke pre-cooling section is located below the stripping section, and the space of the semi-coke pre-cooling section is connected with the space of the stripping section;

[0040] In the low-temperature pyrolysis section, the heat source of the low-temperature pyrolysis section is provided by the initial gas heat carrier of the low-temperature pyrolysis section rising in the low-temperature pyrolysis section; a temperature-adjusting gas distribution channel is arranged at the bottom of the low-temperature pyrolysis section, and the temperature-adjusting gas distribution channel discharges the temperature-adjusting gas into the furnace cavity; the temperature-adjusting gas entering the furnace cavity is mixed with the upward stripping section output gas from the stripping section to become the initial gas heat carrier of the low-temperature pyrolysis section, and the temperature of the initial gas heat carrier of the low-temperature pyrolysis section is at least 100°C lower than the temperature of the stripping section output gas;

[0041] In the low-temperature pyrolysis section, the temperature-adjusting gas distribution channel is located in the lower coke layer and / or outside the lower coke layer of the low-temperature pyrolysis section;

[0042] In the low-temperature pyrolysis section, the gas heat carrier of the low-temperature pyrolysis section moves upward, countercurrently contacts with the preheated coal from the preheating section to reduce the temperature and mix with the net coal gas produced by low-temperature pyrolysis to become the output gas of the low-temperature pyrolysis section; the output gas of the low-temperature pyrolysis section enters the preheating section; the preheated coal moving downward gradually heats up to perform low-temperature pyrolysis, reducing the volatile matter to become low-temperature semi-coke; the low-temperature semi-coke moves downward and is discharged from the low-temperature pyrolysis section to enter the stripping section;

[0043] In the stripping section, most or all of the heat source of the stripping section is provided by the gas heat carrier rising in the stripping section; a main fire channel is arranged at the bottom of the stripping section; the stripping heat supply gas discharged from the main fire channel goes upward, countercurrently contacts with the descending low-temperature pyrolysis semi-coke from the low-temperature pyrolysis section to reduce the temperature and mix with the stripping net product gas to become the output gas of the stripping section; the output gas of the stripping section enters the low-temperature pyrolysis section; the descending low-temperature pyrolysis semi-coke gradually heats up and deeply pyrolyzes, reducing the volatile matter to become stripping semi-coke; the stripping semi-coke is discharged from the stripping section;

[0044] The main fire channel of the stripping section is located in the lower coke layer of the stripping section and / or outside the lower coke layer;

[0045] In the semi-coke pre-cooling section, most or all of the cold source of the semi-coke pre-cooling section is provided by the pre-cooling gas heat carrier rising in the semi-coke pre-cooling section; a pre-cooling gas channel is arranged at the bottom of the semi-coke pre-cooling section; the pre-cooling gas discharged from the pre-cooling gas channel goes upward, countercurrently contacts with the downward stripping semi-coke from the stripping section to increase the temperature and mix with the net coal gas produced by the semi-coke pre-cooling section to become the output gas of the semi-coke pre-cooling section; the output gas of the semi-coke pre-cooling section goes upward into the stripping section and mixes with the stripping heating gas discharged from the main fire channel and then continues to go upward; the output gas of the semi-coke pre-cooling section enters the stripping section; the downward stripping semi-coke gradually cools down to become pre-cooled semi-coke; the pre-cooled semi-coke is discharged from the semi-coke pre-cooling section;

[0046] A pre-cooling gas channel is located in the lower coke layer and / or outside the lower coke layer of the semi-coke pre-cooling section;

[0047] The coal internal heating moving bed vertical pyrolysis furnace is composed of a single-hole, two-hole or multi-hole carbonization chamber; at least one side of each hole carbonization chamber is provided with a temperature regulating gas distribution channel, a main fire channel, and a pre-cooling gas distribution channel;

[0048] An air outlet is arranged on the temperature regulating air distribution duct, an air outlet is arranged on the main fire duct, and an air outlet is arranged on the pre-cooling air distribution duct;

[0049] A coal distribution plate is provided on the upper part of the pyrolysis chamber, and a riser is provided on the top of the pyrolysis chamber; the riser discharges the primary coal gas from the pyrolysis furnace;

[0050] ⑵ Four-way air intake combined with centrifugal compression and delivery

[0051] In the combined centrifugal compressor, a prime mover is used to drive the first combustion-aid gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor, and the first combustion-aid gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor work in a manner of starting, running, and stopping at the same time;

[0052] The prime mover of the combined centrifugal compressor transmits power to the first combustion-assisting gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor via a power transmission mechanism;

[0053] The first combustion-supporting gas is pressurized by the first combustion-supporting gas centrifugal compressor of the combined centrifugal compressor to become the first combustion-supporting gas after pressurization; the first fuel gas is pressurized by the first fuel gas centrifugal compressor of the combined centrifugal compressor to become the first fuel gas after pressurization;

[0054] The first combustion-supporting gas after pressure increase and the first fuel gas after pressure increase pass through the first mixer to become the first mixed gas; the first mixed gas enters the main fire channel for combustion and / or enters the furnace of the coal pyrolysis furnace for combustion to release heat to form a gas heat carrier that moves upward, and heats and pyrolyzes the descending coal material; the ratio of the volume of the first fuel gas entering the first mixer to the volume of the first fuel gas of the chemical combustion equivalent of the first combustion-supporting gas entering the first mixer is defined as the first fuel gas fuel supply ratio K1, K1≥1.15;

[0055] The temperature-controlled gas is pressurized by the temperature-controlled gas centrifugal compressor of the combined centrifugal compressor to become the pressurized temperature-controlled gas;

[0056] After the pressure is increased, the temperature-adjusting gas enters the temperature-adjusting gas distribution channel, enters the furnace through the distribution port of the temperature-adjusting gas distribution channel connected to the furnace, contacts with the upward hot gas and the downward carbon material, and reduces the temperature of the upward gas;

[0057] The pre-cooled air is boosted by the pre-cooled air centrifugal compressor of the combined centrifugal compressor to become boosted pre-cooled air;

[0058] After the pressure is increased, the precooling gas enters the precooling gas distribution channel, enters the furnace through the gas distribution port of the precooling gas distribution channel connected to the furnace, contacts with the descending carbon material to reduce the temperature of the descending stripping semi-coke, and contacts with the ascending gas that exists or does not exist;

[0059] The temperature-adjusted gas is the purified gas obtained from the primary gas of the pyrolysis furnace through a purification process including at least the steps of cooling, deoiling and dehydrating;

[0060] The first fuel gas is a purified gas obtained by a purification process of the primary gas from the pyrolysis furnace, which includes at least the steps of cooling, deoiling and dehydrating;

[0061] Pre-cooled gas is purified gas obtained from the primary gas from the pyrolysis furnace through a purification process that includes at least the steps of cooling, deoiling and dehydrating.

[0062] The first structural scheme of the combined centrifugal compressor of the present invention is:

[0063] The combined centrifugal compressor uses a dual output shaft prime mover;

[0064] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0065] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0066] The first gear is meshed with the main gear of the first transmission machine;

[0067] a second gear meshing with the main gear of the first transmission machine;

[0068] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0069] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0070] A first fuel gas centrifugal compressor A is arranged on one side of the first gear output shaft, and a first fuel gas centrifugal compressor B is arranged on the other side of the first gear output shaft;

[0071] The first fuel gas is divided into two paths with the same flow rate, entering the first fuel gas centrifugal compressor A and the first fuel gas centrifugal compressor B respectively;

[0072] A temperature regulating air centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling air centrifugal compressor is arranged on the other side of the second gear output shaft;

[0073] The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

[0074] The second structural scheme of the combined centrifugal compressor of the present invention is:

[0075] The combined centrifugal compressor uses a dual output shaft prime mover;

[0076] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0077] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0078] The first gear is meshed with the main gear of the first transmission machine;

[0079] a second gear meshing with the main gear of the first transmission machine;

[0080] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0081] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0082] A temperature-controlled air centrifugal compressor A is arranged on one side of the output shaft of the first gear, and a temperature-controlled air centrifugal compressor B is arranged on the other side of the output shaft of the first gear;

[0083] The temperature-controlled gas is divided into two routes with the same flow rate, entering the temperature-controlled gas centrifugal compressor A and the temperature-controlled gas centrifugal compressor B respectively;

[0084] A pre-cooling gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft;

[0085] The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

[0086] The third structural scheme of the combined centrifugal compressor of the present invention is:

[0087] The combined centrifugal compressor uses a dual output shaft prime mover;

[0088] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0089] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0090] The first gear is meshed with the main gear of the first transmission machine;

[0091] a second gear meshing with the main gear of the first transmission machine;

[0092] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0093] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0094] A pre-cooling air centrifugal compressor A is arranged on one side of the output shaft of the first gear, and a pre-cooling air centrifugal compressor B is arranged on the other side of the output shaft of the first gear;

[0095] The pre-cooling air is divided into two routes with the same flow rate, entering the pre-cooling air centrifugal compressor A and the pre-cooling air centrifugal compressor B respectively;

[0096] A temperature-adjusting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft;

[0097] The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

[0098] The fourth structural scheme of the combined centrifugal compressor of the present invention is:

[0099] The combined centrifugal compressor uses a dual output shaft prime mover;

[0100] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0101] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0102] The first gear is meshed with the main gear of the first transmission machine;

[0103] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0104] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0105] The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving;

[0106] A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine;

[0107] a second gear meshing with the main gear of the second transmission machine;

[0108] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0109] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a temperature-regulating gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0110] The fifth structural scheme of the combined centrifugal compressor of the present invention is:

[0111] The combined centrifugal compressor uses a dual output shaft prime mover;

[0112] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0113] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0114] The first gear is meshed with the main gear of the first transmission machine;

[0115] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0116] A pre-cooling air centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting air centrifugal compressor is arranged on the other side of the first gear output shaft;

[0117] The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving;

[0118] A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine;

[0119] a second gear meshing with the main gear of the second transmission machine;

[0120] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0121] A first combustion-assistant gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0122] The sixth structural scheme of the combined centrifugal compressor of the present invention is:

[0123] The combined centrifugal compressor uses a dual output shaft prime mover;

[0124] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0125] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0126] The first gear is meshed with the main gear of the first transmission machine;

[0127] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0128] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0129] The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving;

[0130] A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine;

[0131] a second gear meshing with the main gear of the second transmission machine;

[0132] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0133] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0134] The seventh structural scheme of the combined centrifugal compressor of the present invention is:

[0135] The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission;

[0136] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0137] A main gear, disposed on the input shaft of the first transmission machine;

[0138] The first gear meshes with the main gear;

[0139] The second gear meshes with the main gear;

[0140] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0141] The second gear output shaft is used to set the second gear;

[0142] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0143] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a temperature-regulating gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0144] The eighth structural scheme of the combined centrifugal compressor of the present invention is:

[0145] The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission;

[0146] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0147] A main gear, disposed on the input shaft of the first transmission machine;

[0148] The first gear meshes with the main gear;

[0149] The second gear meshes with the main gear;

[0150] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0151] The second gear output shaft is used to set the second gear;

[0152] A pre-cooling air centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting air centrifugal compressor is arranged on the other side of the first gear output shaft;

[0153] A first combustion-assistant gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0154] The ninth structural scheme of the combined centrifugal compressor of the present invention is:

[0155] The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission;

[0156] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0157] A main gear, disposed on the input shaft of the first transmission machine;

[0158] The first gear meshes with the main gear;

[0159] The second gear meshes with the main gear;

[0160] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0161] The second gear output shaft is used to set the second gear;

[0162] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0163] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0164] In the present invention, generally, the first combustion-supporting gas entering the combined centrifugal compressor comes from the first combustion-supporting gas buffer tank;

[0165] The operating pressure of the first combustion-supporting gas buffer tank is lower than the pressure at the outlet of the first mixer connected to the main fire channel.

[0166] In the present invention, usually, a first combustion-supporting gas emergency interlock cut-off valve is arranged on the pipeline of the first combustion-supporting gas after the boost is discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the first combustion-supporting gas emergency interlock cut-off valve is interlocked and closed;

[0167] A first fuel gas emergency interlock cut-off valve is provided on the pipeline of the pressurized first fuel gas discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the first fuel gas emergency interlock cut-off valve is interlocked and closed;

[0168] An emergency interlock shut-off valve for the temperature-regulating gas is provided on the pipeline for the pressurized temperature-regulating gas discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the emergency interlock shut-off valve for the temperature-regulating gas is shut off by interlock.

[0169] In the present invention, generally, the first combustion-supporting gas entering the combined centrifugal compressor comes from the first combustion-supporting gas buffer tank;

[0170] The operating pressure of the first combustion-supporting gas buffer tank is lower than the pressure at the outlet of the first mixer connected to the main fire channel;

[0171] An overpressure interlock cut-off valve of the first combustion-supporting gas buffer tank is arranged on the pipeline from which the first combustion-supporting gas buffer tank is discharged to the combined centrifugal compressor. Once the pressure of the first combustion-supporting gas buffer tank is higher than the pressure at the outlet of the first mixer, the overpressure interlock cut-off valve of the first combustion-supporting gas buffer tank is interlocked and closed.

[0172] In the present invention, usually, the first combustion-supporting gas is oxygen-enriched gas with an oxygen volume concentration higher than 35%, and a carbon dioxide volume concentration higher than 60%.

[0173] In the present invention, usually, the air flow temperature at 300 mm above the air outlet of the temperature regulating air distribution channel of the low-temperature pyrolysis section is used as the qualitative temperature of the initial gas heat carrier of the low-temperature pyrolysis section;

[0174] In the stripping section, the gas flow temperature at a point 300 mm below the gas outlet of the temperature-adjusting gas distribution channel of the low-temperature pyrolysis section is taken as the qualitative temperature of the output gas of the stripping section;

[0175] The temperature of the low-temperature pyrolysis semi-coke 300 mm above the outlet of the temperature-adjusting gas distribution channel of the low-temperature pyrolysis section is taken as the qualitative temperature of the low-temperature pyrolysis section;

[0176] The temperature of the stripping semi-coke 300mm above the outlet of the main fire channel of the stripping section is taken as the qualitative temperature of the stripping section;

[0177] The coal fed into the pyrolysis furnace is low-rank coal;

[0178] In the preheating section, the temperature of the discharged preheated coal is 180-370°C;

[0179] The qualitative temperature of the low-temperature pyrolysis section is 430-680°C; the qualitative temperature of the initial gas heat carrier in the low-temperature pyrolysis section is at least 200°C lower than the qualitative temperature of the output gas in the stripping section;

[0180] The qualitative temperature of the stripping section is 700-1000°C, and is 100-450°C higher than the qualitative temperature of the low-temperature pyrolysis section;

[0181] Each carbonization chamber is wide at the top and narrow at the bottom, with a variable cross section in the middle. The temperature-adjusting gas distribution channel and the main fire channel are arranged in the narrow cavity section below the narrowing transition section in the middle of the carbonization chamber.

[0182] The volatile matter of the stripping char is at least 2.0 weight percent lower than the volatile matter of the low-temperature pyrolysis char;

[0183] The volatile matter of the stripped semi-coke is less than 4.95 wt%.

[0184] In the present invention, usually, the coal pyrolysis furnace is provided with a semi-coke quenching section below the pre-cooling section.

[0185] In the present invention, the coal pyrolysis furnace can be provided with an external heating system at the same time. The high-temperature gas flowing through the heat transfer channel of the external heating system does not enter the furnace of the pyrolysis furnace. The heat transfer channel of the external heating system indirectly transfers heat to the furnace of the coal dry distillation zone of the pyrolysis furnace through the heat transfer wall surface.

[0186] In the present invention, usually, the first fuel gas supply ratio K1, K1 is 1.5-5.0.

[0187] In the present invention, usually, each centrifugal compressor is a single-stage centrifugal compressor.

[0188] In the present invention, usually, the impeller of the first combustion-aid gas centrifugal compressor adopts an impeller with an additional extended impeller area, which reduces the overall fluid load on the integrated output shaft by increasing the area and gas pressure of the back side of the first combustion-aid gas centrifugal compressor impeller disk.

[0189] In the present invention, usually, the prime mover is an electric motor or a turbine.

[0190] In the present invention, usually, the output shaft of the prime mover is connected to the rotating shaft of the centrifugal compressor impeller or the input shaft of the transmission by direct connection or connection through a coupling.

[0191] In the present invention, usually, the main gear and the pinion are helical gears;

[0192] The rotation direction of the helical gear is set so that the gear load acting on the pinion in the axial direction and the fluid load acting on the corresponding output shaft in the axial direction are in opposite directions. BRIEF DESCRIPTION OF THE DRAWINGS

[0193] Figure 1 It is a schematic diagram of the structure and function of the first combustion-aiding gas centrifugal compressor of the present invention provided with an additional extended impeller area.

[0194] Figure 2 yes Figure 1 A partial enlarged view of the flow passage in the additional extended impeller area.

[0195] Figure 3 It is a schematic diagram of a power transmission mechanism (speed regulator) of a combined centrifugal compressor and a configuration mode of a centrifugal compressor according to the present invention.

[0196] Figure 4 It is a schematic diagram of the structure of a double-pyrolysis-stage pyrolysis furnace.

[0197] In order to facilitate explanation, the sizes and shapes of some components in the drawings are sometimes distorted or partially enlarged.

[0198] Figure 1 , Figure 2 Description of the mark in:

[0199] The rotating shaft 703, the first combustion-supporting gas centrifugal compressor 720, the first impeller 721, the back panel 722, the hub portion 723, the through hole 723a, the main blade 724, the first centrifugal compressor housing 726, the side 726a, the space portion 727, the suction port 727a, the main discharge port 727b, the flow path 727c, the insertion port 728, the electric motor rotor 730, the bearing 740L, the motor housing 745, the rotor space portion 745b, the heat sink 746, the bearing housing 750, the protruding step portion 751, the face portion 752, the bolt 753, the additional extended impeller area flow channel 220, the extended annular body 7221, the outer edge blade 221, and the auxiliary exhaust port 225.

[0200] Figure 3 Description of the mark in:

[0201] Speed ​​increaser unit 100, first combustion-assisting gas centrifugal compressor C1 (centrifugal impeller 1001, impeller diameter D1), temperature-regulating gas centrifugal compressor C2 (centrifugal impeller 2001, impeller diameter D2), first fuel gas centrifugal compressor C3 (centrifugal impeller 3001, impeller diameter D3), pre-cooling gas centrifugal compressor C4 (centrifugal impeller 4001, impeller diameter D4), input shaft 4, main gear 20, pinion gears 21, 22, output shaft 5, thrust rings 66, 67, output shaft 6, thrust rings 68, 69, housing 101, composite bearings 60, 61, gaps 70, 71, 72, gear load Fp1, gear load Fp2, combined load F, fluid loads Fi1, Fi2, Fi3, Fi4.

[0202] Figure 4 Description of the mark in:

[0203] Figure 4 The pyrolysis furnace part shown in the figure is provided with a preheating section, a low-temperature pyrolysis section, a stripping section, a direct air cooling section, and a coke quenching section. The five cavity spaces of the preheating section, the low-temperature pyrolysis section, the stripping section, the direct air cooling section, and the coke quenching section are directly vertically connected.

[0204] Figure 4 The pyrolysis furnace shown is composed of a plurality of porous carbonization chambers 1000. Each carbonization chamber 1000 is wide at the top and narrow at the bottom, and the middle cross section is a variable cross section.

[0205] Figure 4 The pyrolysis furnace part numbers are described as follows

[0206] Riser 9005, furnace top distribution plate 9006, low-temperature pyrolysis section 9008, channel 9009, gas delivery pipe 9009M, gas distribution brick 9010, main fire channel 9012, combustion gas mixer 9012M, gas distribution brick 9013, channel 9015, endothermic gas delivery pipe 9015M, gas distribution brick 9016, quenching water main pipe and distribution pipe 9019, refractory brick 9050, thermocouple 9060, furnace protection iron piece 9080; interface FJM between preheating section and low-temperature pyrolysis section.

[0207] Figure 4 The material numbers inside the medium pyrolysis furnace are described as follows:

[0208] LM represents the cold coal material in the upper part of the preheating section of the pyrolysis furnace;

[0209] RM represents the hot coal material in the lower part of the preheating section of the pyrolysis furnace;

[0210] DWBJ represents the low-temperature pyrolysis semi-coke discharged from the lower part of the low-temperature pyrolysis section;

[0211] TLBJ represents the stripping semi-coke discharged from the lower part of the stripping section;

[0212] QLBJ represents the gas-cooled semi-coke discharged from the lower part of the direct gas-cooling section;

[0213] XHBJ indicates the post-quenching semi-coke discharged from the lower part of the quenching section.

[0214] The low-temperature pyrolysis section 9008 includes a wide horizontal cross-section section, namely, an upper section 9081 of the low-temperature pyrolysis section, a variable cross-section transition section, namely, a middle section 9082 of the low-temperature pyrolysis section, and a narrow horizontal cross-section section, namely, a lower section 9083 of the low-temperature pyrolysis section.

[0215] In the low-temperature pyrolysis section 9008, the temperature-regulating cooling gas distribution part is composed of a channel 9009, a gas delivery pipe 9009M whose main body is arranged in the channel, a gas distribution brick 9010, etc.

[0216] In the stripping section, the stripping hot flue gas distribution part is composed of a main fire channel 9012, a combustion gas mixer 9012M whose main body is arranged in the channel, a gas distribution brick 9013, etc.

[0217] In the direct air cooling section, the heat absorbing gas distribution part of the direct air cooling section is composed of a channel 9015, a heat absorbing gas conveying pipe 9015M whose main body is arranged in the channel, a gas distribution brick 9016, etc.

[0218] The quenching section is provided with a quenching water main pipe and a distribution pipe 9019. DETAILED DESCRIPTION

[0219] The following describes a coal vertical pyrolysis furnace

[0220] Coal distillation is the process of coal being decomposed by heat in an airtight condition to produce coal tar, semi-coke, distillation gas and water. According to the different final heating temperatures, coal distillation is roughly divided into three types: low-temperature distillation (500-600℃), medium-temperature distillation (600-900℃), and warm distillation (900-1100℃). According to different heating methods, coal distillation furnaces can be divided into external heating, internal heating, and simultaneous internal and external dual heating. At present, internal heating furnaces are widely used and are divided into gas heat carrier and solid heat carrier distillation furnaces. Gas heat carrier distillation furnaces mainly include Lurgi three-stage furnace, Anshan Thermal Energy Research Institute Co., Ltd. of China Steel Group, and pyrolysis furnaces developed by Shenmu County Sanjiang Coal Chemical Co., Ltd.

[0221] The medium and low temperature coal pyrolysis process has mild processing conditions, low investment and low production cost. When processing high volatile low-rank coal, the medium and low temperature pyrolysis process enriches the hydrogen in the coal into tar and coal gas with a large output, and obtains carbon-rich semi-coke, thereby producing products with higher value. The usual coal pyrolysis device includes coal preparation, pyrolysis, raw coal gas purification, coal gas recycling, phenol-containing wastewater pretreatment and other sections.

[0222] Although specific optimal targeted operating conditions need to be determined for different types of coal and different product properties, and these operating conditions have a wide range, the main changes in low-rank coal during the entire heating process of medium and low-temperature coal pyrolysis have the following regularity in a general sense, and the temperature stage division is vague:

[0223] ① Drying and degassing stage, corresponding to the preheating stage of the present invention, is usually from room temperature to about 300°C; in this stage, the appearance of the coal does not change significantly, low-rank coal such as lignite undergoes decarboxylation reaction above about 200°C, and starts pyrolysis reaction at about 300°C, while bituminous coal and anthracite generally do not change much at this stage; dehydration mainly occurs before 120°C, and degassing (mainly removing carbon dioxide, methane and nitrogen adsorbed by coal and enclosed in pores) is roughly completed around 200°C; the solid product of this stage is preheated coal or dried coal;

[0224] ② Active thermal decomposition stage (about 300 to about 600°C), corresponding to the low-temperature pyrolysis stage of the present invention, this stage is mainly characterized by depolymerization and decomposition reactions, coal is bonded into semi-coke, and a series of changes occur, coal begins to soften at about 300°C, and coal gas and tar are precipitated, the tar amount is the largest around about 450°C, and the gas precipitation amount is the largest at about 450 to about 600°C; the composition of coal gas is mainly gaseous hydrocarbons except for pyrolysis products water, carbon monoxide and carbon dioxide, so the calorific value is relatively high; the solid product of this stage is low-temperature pyrolysis semi-coke; one of the main purposes of the present invention is to controllably realize the optimized low-temperature pyrolysis operation stage to prevent the high-temperature gas in the stripping section from entering the low-temperature pyrolysis section to form tar burn-off;

[0225] ③ Thermal polycondensation stage (about 700 to about 1000°C) This is the stage where low-temperature pyrolysis semi-coke becomes stripping semi-coke or even coke, which corresponds to the stripping stage of the present invention, and is mainly based on thermal polycondensation reaction. The amount of tar precipitated is very small, and the volatile matter is mainly coal gas. After 700°C, the coal gas component is mainly hydrogen. In this stage, the aromatic nucleus is significantly enlarged, the arrangement is regularized, the structure is dense, and the colloid undergoes polycondensation and solidification reaction to form semi-coke. From low-temperature pyrolysis semi-coke to stripping semi-coke, on the one hand, a large amount of coal gas is precipitated from the semi-coke, and the volatile content is reduced. On the other hand, the semi-coke itself shrinks in volume, increases in true density, and increases in strength. One of the main purposes of the present invention is to controllably realize the optimized stripping pyrolysis operation stage, and in the process of reducing and improving the strength of semi-coke and reducing the volatile matter of semi-coke, less tar is produced (because it is mostly coal tar) and more coal gas (high value) is produced.

[0226] The field of the present invention belongs to coal pyrolysis process, generally belongs to medium-low temperature coal pyrolysis process, especially belongs to medium-low temperature coal pyrolysis process of high volatile low-rank coal. The difference from other coal pyrolysis processes is that a low-temperature pyrolysis section and a stripping pyrolysis section that produces less tar and more gas are set.

[0227] The pyrolysis furnace and system of the present invention are generally suitable for processing low-rank coal such as long flame coal, non-sticky coal, weakly sticky coal or lignite, and are particularly suitable for processing high-volatile low-rank coal. They have good economy, can optimize the operation of the low-temperature pyrolysis section, improve the tar yield, can optimize the operation of the distillation section, reduce the volatile matter of semi-coke, and improve the semi-coke strength, and can also adapt to the oxygen-rich or pure oxygen combustion-supporting gas conditions to produce coal gas with low nitrogen concentration, and have the characteristics of simple system, flexible operation and high thermal efficiency.

[0228] The goal of the present invention is that "the first combustion-supporting gas for the main fire channel must enter synchronously with the first fuel gas in an expected volume ratio, and at the same time, the temperature-adjusting gas in an expected volume ratio enters the furnace of the low-temperature pyrolysis section." The specific solution is: in combination with a centrifugal compressor, a prime mover is set to drive the centrifugal compressors of the three gas routes to start, operate, and stop at the same time.

[0229] The combined centrifugal compressor of the present invention can have a prime mover of any suitable type, such as an electric motor or a steam turbine.

[0230] When the combined centrifugal compressor of the present invention uses a transmission machine, the connection mode between the output shaft and the input shaft can be any suitable mode, such as direct connection or connection with a coupling.

[0231] The prime mover of the combined centrifugal compressor of the present invention can be a double output shaft type or a single output shaft type.

[0232] The power transmission mechanism adopted by the prime mover of the combined centrifugal compressor of the present invention can be any effective power transmission mechanism.

[0233] When the combined centrifugal compressor of the present invention adopts a dual-output shaft type prime mover, in the case where the second output shaft of the prime mover is connected to the impeller rotor shaft of the first combustion-aided gas centrifugal compressor, the power transmission mechanism can be any effective power transmission mechanism, and at least the following principle solutions (including 3 specific solutions) are available:

[0234] A dual-output-shaft prime mover is used, wherein the first output shaft of the prime mover is connected to the input shaft of the first transmission machine, and the output shaft of the first transmission machine is used to drive the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor;

[0235] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0236] A main gear, disposed on the input shaft of the first transmission machine;

[0237] The first gear meshes with the main gear;

[0238] The second gear meshes with the main gear;

[0239] A first gear output shaft, used to set the first gear and form a left side of the first gear output shaft and a right side of the first gear output shaft;

[0240] A second gear output shaft, used to set the second gear and form a left side of the second gear output shaft and a right side of the second gear output shaft;

[0241] A single-stage centrifugal compressor A for specific gas is arranged on one side of the output shaft of the first gear, and a single-stage centrifugal compressor B for specific gas is arranged on the other side of the output shaft of the first gear;

[0242] The specific gas is selected from one of the first fuel gas, the temperature-adjusting gas, and the pre-cooling gas, and the remaining two gases become the specific remaining gas;

[0243] The specific gas is divided into two routes with the same flow rate, entering the specific gas centrifugal compressor A and the specific gas centrifugal compressor B respectively;

[0244] A single-stage centrifugal compressor for one specific residual gas is arranged on one side of the second gear output shaft, and a single-stage centrifugal compressor for another specific residual gas is arranged on the other side of the second gear output shaft;

[0245] In this configuration of the output of the first impeller, the operating parameters of the centrifugal compressor A for a specific gas and the centrifugal compressor B for a specific gas are exactly the same, so the axial fluid thrusts on the impeller shafts generated by the pressure difference between the front and rear impellers of the two centrifuges are opposite in direction and equal in magnitude, that is, the axial forces cancel each other out, so that the dynamic balance performance of the first transmission machine is good;

[0246] In this configuration of the output shaft of the second gear, usually, since the conveying medium of the centrifugal compressor of one specific residual gas and the centrifugal compressor of another specific residual gas are the same circulating coal gas (same molecular weight, same temperature, same pressure), and the pressure difference of the centrifugal compressor of the specific residual gas and the centrifugal compressor of the other specific residual gas is almost equal (and very small), the axial fluid thrust acting on the impeller shaft caused by the pressure difference before and after the two centrifugal impellers is opposite in direction and almost equal in magnitude, that is, most of the axial forces cancel each other out, so that the dynamic balance performance of the first transmission machine is good;

[0247] The second output shaft of the prime mover is connected to the impeller rotor shaft of the first combustion-assisting gas centrifugal compressor; this type can refer to Chinese patent ZL201480069099.9 multi-stage electric centrifugal compressor (the prime mover is a dual-output shaft electric motor) and Chinese patent ZL201210361133.2 (the prime mover can be a dual-output shaft steam turbine).

[0248] When the combined centrifugal compressor of the present invention adopts a dual-output shaft type prime mover, the power transmission mechanism can be any effective power transmission mechanism; the first output shaft of the prime mover is connected to the first transmission device, and the second output shaft of the prime mover is connected to the second transmission device; the first transmission device is provided with an output shaft, and a centrifugal compressor is arranged on each of the two sides; the second transmission device is provided with an output shaft, and a centrifugal compressor is arranged on each of the two sides. In this case, at least the following principle solutions (including 3 specific solutions) are available:

[0249] A first transmission machine input shaft connected to a first output shaft of a prime mover;

[0250] A first transmission machine main gear, provided on the input shaft of the first transmission machine;

[0251] A first transmission gear wheel meshing with the first transmission main gear;

[0252] A second transmission machine input shaft connected to a second output shaft of the prime mover;

[0253] A second transmission machine main gear, provided on the input shaft of the first transmission machine;

[0254] A second transmission gear wheel meshing with the second transmission main gear;

[0255] In the case where the impeller rotor shaft of the first combustion-aid gas centrifugal compressor is arranged on one side of the second transmission output shaft, a single-stage specific gas centrifugal compressor is arranged on the other side of the second transmission output shaft;

[0256] The specific gas is selected from one of the first fuel gas, the temperature-adjusting gas, and the pre-cooling gas, and the remaining two gases become the specific remaining gas;

[0257] The specific gas is divided into two routes with the same flow rate, entering the specific gas centrifugal compressor A and the specific gas centrifugal compressor B respectively;

[0258] A single-stage centrifugal compressor for one specific residual gas is arranged on one side of the first transmission output shaft, and a single-stage centrifugal compressor for another specific residual gas is arranged on the other side of the first transmission output shaft;

[0259] In this configuration of the output of the first transmission, the operating parameters of the centrifugal compressor A for a specific gas and the centrifugal compressor B for a specific gas are exactly the same, so the axial fluid thrusts on the impeller shafts generated by the pressure difference between the front and rear impellers of the two centrifuges are opposite in direction and equal in magnitude, that is, the axial forces cancel each other out, so that the dynamic balance performance of the first transmission is good;

[0260] In this configuration of the output shaft of the first transmission device, usually, since the conveying medium of the centrifugal compressor of one specific residual gas and the centrifugal compressor of another specific residual gas are the same circulating coal gas (same molecular weight, same temperature, same pressure), and the pressure difference of the centrifugal compressor of the specific residual gas and the centrifugal compressor of the other specific residual gas is almost equal (and very small), the axial fluid thrust acting on the impeller shaft caused by the pressure difference before and after the two centrifugal impellers is opposite in direction and almost equal in magnitude, that is, most of the axial forces cancel each other out, so that the dynamic balance performance of the first transmission device is good;

[0261] The configuration mode of the output shaft of the second transmission device, the first combustion-supporting gas centrifugal compressor and the centrifugal compressor of the specific gas, due to the large difference in gas molecular weight (the ratio of the molecular weight of the first combustion-supporting gas to the molecular weight of the specific gas is about 1.25-1.70), when the pressure difference is similar or the pressure difference of the combustion-supporting gas centrifugal compressor is smaller, the impeller diameter of the first combustion-supporting gas centrifugal compressor is smaller, and the impeller area is smaller. The axial fluid thrust acting on the impeller shaft caused by the pressure difference before and after the two centrifugal impellers is opposite in direction and unequal in magnitude, that is, the direction of the remaining axial force after the axial forces cancel each other out is the same as the direction of the fluid load on the impeller of the temperature-controlled gas centrifugal compressor. In this way, the direction of the axial gear load received by the output shaft of the second transmission device is opposite to the direction of the fluid load on the impeller of the temperature-controlled gas centrifugal compressor, so as to offset part of the axial load, reduce the total value of the axial load, and improve the dynamic balance performance of the second transmission device;

[0262] In order to reduce the unbalanced fluid load (total fluid load) on the output shaft of the above-mentioned second transmission and improve the overall efficiency of the combined centrifugal compressor, the present invention proposes a scheme for setting an additional extended impeller area for the impeller of the first combustion-supporting gas centrifugal compressor, and by increasing the area and gas pressure on the back side of the impeller disk of the first combustion-supporting gas centrifugal compressor, the overall fluid load on the integrated output shaft can be reduced to zero as much as possible.

[0263] When the combined centrifugal compressor of the present invention adopts a single output shaft type prime mover, the power transmission mechanism of the combined centrifugal compressor of the present invention can be any effective power transmission mechanism, and can refer to the multi-stage centrifugal compressor of Chinese patent ZL201410351897.2. At least the following principle schemes (including 3 specific schemes) are available:

[0264] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0265] A main gear, disposed on the input shaft of the first transmission machine;

[0266] The first gear meshes with the main gear;

[0267] The second gear meshes with the main gear;

[0268] A first gear output shaft, used to set the first gear and form a left side of the first gear output shaft and a right side of the first gear output shaft;

[0269] A second gear output shaft, used to set the second gear and form a left side of the second gear output shaft and a right side of the second gear output shaft;

[0270] A single-stage first auxiliary gas centrifugal compressor is arranged on one side of the second gear output shaft, and a single-stage specific gas centrifugal compressor is arranged on the other side of the second gear output shaft;

[0271] The specific gas is selected from one of the first fuel gas, the temperature-adjusting gas, and the pre-cooling gas, and the remaining two gases become the specific remaining gas;

[0272] A single-stage centrifugal compressor for one specific residual gas is arranged on one side of the first gear output shaft, and a single-stage centrifugal compressor for another specific residual gas is arranged on the other side of the first gear output shaft;

[0273] In this configuration of the output of the first impeller, the conveying medium of the centrifugal compressor of one specific residual gas and the centrifugal compressor of another specific residual gas are the same circulating coal gas (same molecular weight, same temperature, same pressure), and the pressure difference of the centrifugal compressor of the specific residual gas and the centrifugal compressor of the other specific residual gas is almost equal (and very small), so the axial fluid thrust acting on the impeller shaft caused by the pressure difference before and after the two centrifugal impellers is opposite in direction and almost equal in magnitude, that is, most of the axial forces cancel each other out, so that the dynamic balance performance of the first transmission machine is good;

[0274] In this configuration mode of the second gear output shaft, due to the large difference in gas molecular weights (the ratio of the first gas-supporting gas molecular weight to the temperature-regulating gas molecular weight is about 1.25-1.70), when the pressure difference is similar or the pressure difference of the gas-supporting gas centrifugal compressor is smaller, the impeller diameter of the first gas-supporting gas centrifugal compressor is smaller and the impeller area is smaller. The axial fluid thrust acting on the impeller shaft caused by the pressure difference before and after the two centrifugal impellers is opposite in direction and unequal in magnitude, that is, the direction of the remaining axial force after the axial forces cancel each other out is the same as the direction of the fluid load on the impeller of the temperature-regulating gas centrifugal compressor. This requires that the direction of the axial gear load received by the output shaft of the second transmission machine is opposite to the direction of the fluid load on the impeller of the temperature-regulating gas centrifugal compressor, so as to offset part of the axial load, reduce the total value of the axial load, and improve the dynamic balance performance of the second transmission machine;

[0275] In order to reduce the unbalanced fluid load (total fluid load) on the output shaft of the second gear and improve the overall efficiency of the combined centrifugal compressor, the present invention proposes a scheme for setting an additional extended impeller area for the impeller of the first combustion-supporting gas centrifugal compressor, and by increasing the area and gas pressure on the back side of the impeller disk of the first combustion-supporting gas centrifugal compressor, the overall fluid load on the integrated output shaft can be reduced to zero as much as possible.

[0276] Figure 1 A cross-sectional view showing the partial structure of the first combustion-assisting gas centrifugal compressor and the motor of the two-stage electric centrifugal compressor is used to illustrate the structure and function of the additional extended impeller area of ​​the first combustion-assisting gas centrifugal compressor. The structure and function of other parts can be replaced in a variety of ways, or in other words, Figure 1 The structure and function of the first auxiliary gas centrifugal compressor provided with an additional extended impeller area can be applied to the first auxiliary gas centrifugal compressor of any suitable combined centrifugal compressor of the present invention.

[0277] like Figure 1 As shown, the two-stage electric centrifugal compressor is composed of a rotating shaft 703 that is rotatably supported, a first combustion-supporting gas centrifugal compressor 720 with a single-stage impeller is installed on the left end side of the rotating shaft 703, and a first fuel gas centrifugal compressor ( Figure 1 not shown).

[0278] like Figure 1 As shown, the first combustion-supporting gas centrifugal compressor 720 has a first impeller 721 installed on the left side of the rotating shaft 703 and a first centrifugal compressor casing 726 surrounding the first impeller 721. The first centrifugal compressor casing 726 has a space portion 727 that accommodates the first impeller 721 so as to rotate freely inside. An intake port 727a for sucking in air opens at the other end side of the space portion 727, and a flow path 727c that is connected to the intake port 727a and bends toward the circumferential direction of the first combustion-supporting gas centrifugal compressor 720 is formed in the radial direction of the space portion 727. 727c is a channel for gas to flow to 727c, and is also the main channel for gas to discharge from the compressor impeller chamber. The discharge port 727b connected to the flow path 727c is located at one end portion in the width direction of the first centrifugal compressor casing 726, that is, Figure 1 The end portion on the paper side is open. The intake air flowing in from the suction port 727a is compressed and heated by the first impeller 721, flows through the flow path 727c, and is discharged from the discharge port 727b.

[0279] like Figure 1As shown, an insertion port 728 that can insert the first impeller 721 and is circular when viewed from the side opens at one end side of the first centrifugal compressor housing 726. The insertion port 728 opens larger than the first impeller 721 to expose a portion of the flow path 727c. The side surface 726a of the first centrifugal compressor housing 726 on the side of the insertion port 728 is formed in a flat shape and is formed in a circular ring shape when viewed from the side.

[0280] like Figure 1 As shown, the first impeller 721 has a disc-shaped back plate 722, a truncated cone-shaped hub portion 723 protruding from one side of the back plate 722 in a direction orthogonal to the back plate 722 and integrally provided with the back plate 722, and a plurality of blades 724 integrally provided from the outer peripheral surface of the hub portion 723 to the back plate 722. A through hole 723a is provided in the central portion of the hub portion 723; one end of the through hole 723a is inserted into the rotating shaft 703, so that the first impeller 721 rotates integrally with the rotating shaft 703.

[0281] Generally, simply from the process requirements, the intake pressure and main exhaust pressure of the first centrifugal compressor and the second centrifugal compressor are the same, but the molecular weight of the first combustion-supporting gas is greater than the molecular weight of the first fuel gas. Therefore, compared with the impeller diameter of the first fuel gas centrifugal compressor, the diameter of the first impeller 721 is smaller.

[0282] The left side of the rotating shaft 703 extending from both sides of the electric motor rotor is provided with a bearing 740L, which may be a grease-type rolling bearing. The bearing 740L is disposed in a bearing housing 750 .

[0283] The bearing housing 750 is annular, and has an insertion hole 750a in the center thereof into which the rotating shaft 703 can be inserted, and a bearing mounting hole 750b (not shown) having a larger inner diameter than the insertion hole 750a is provided on the second centrifugal compressor side of the insertion hole 750a. A bearing 740L (not shown) is mounted in the bearing mounting hole 750b, and the rotating shaft 703 is inserted into the bearing 740L, and the rotating shaft 703 is rotatably supported via the bearing 740L.

[0284] The end of the bearing housing 750 on the first combustion-supporting gas centrifugal compressor 720 side is provided with a protruding step 751 which is fitted with the insertion port 728 of the first centrifugal compressor housing 726 and is annular in shape when viewed from the side, and an annular surface portion 752 which is opposite to and in contact with the side surface 726a of the first centrifugal compressor housing 726 is provided on the radially outer side of the protruding step 751. The bearing housing 750 is integrally fixed to the first centrifugal compressor housing 726 via bolts 753 inserted into the first centrifugal compressor housing 726.

[0285] A rotor space 745b (partially shown) rotatably surrounding the electric motor rotor is provided at the right end of the motor housing 745. A plurality of heat sinks 746 extending radially outward are provided on the outer periphery of the motor housing 745 to dissipate heat generated from the electric motor rotor 730 or the bearing 740L to the outside.

[0286] The electric motor rotor 730 is a rotor of the electric motor, and receives a driving force from a motor coil (not shown) to rotate the rotating shaft 703 at a high speed.

[0287] like Figure 1 , Figure 2 As shown, the protruding step 751 and the first centrifugal compressor casing 726 constitute an additional extended impeller area flow channel 220, which accommodates the outer circular body 7221 of the circular plate-shaped back panel 722 of the first impeller 721 and a plurality of outer edge blades 221 arranged on the outer circular body 7221; on the back side of the circular plate-shaped back panel 722 and the outer circular body 7221 is a gas chamber on the back side of the impeller, which generates an axial fluid load pointing to the suction port 727a on the circular plate-shaped back panel 722 and the outer circular body 7221.

[0288] like Figure 2 As shown, the protruding step 751 and the first centrifugal compressor casing 726 constitute an additional extended impeller area flow channel 220, which accommodates the outer circular ring body 7221 of the circular plate-shaped back panel 722 of the first impeller 721 and a plurality of outer edge blades 221 arranged on the outer circular ring body 7221; the auxiliary exhaust port 225 is the exhaust port of the additional extended impeller area flow channel 220.

[0289] like Figure 2 As shown, the gap between the back side of the circular plate-shaped back panel 722 and the outer annular body 7221 and the protruding step 751 is the impeller back air chamber BV, which generates an axial fluid load pointing to the suction port 727a on the circular plate-shaped back panel 722 and the outer annular body 7221; due to the energy applied by the rotation of the outer edge blades 221, the gas pressure of the auxiliary exhaust port 225 is higher than the gas pressure of the main exhaust port. Therefore, compared with not using the outer annular body 7221 and the outer edge blades 221, the axial fluid load pointing to the suction port 727a generated by the circular plate-shaped back panel 722 and the outer annular body 7221 is greatly increased. In order to save energy, the width of the outer edge blades 221 is reduced as much as possible, that is, the exhaust volume of the auxiliary exhaust port 225 is reduced.

[0290] Since the initial pressure of the oxygen-rich first combustion-supporting gas is usually higher than the pressure of the first fuel gas, the control value of the pressure difference of the first combustion-supporting gas is usually lower than the pressure difference of the first fuel gas to save power consumption. At this time, the diameter of the impeller of the centrifugal compressor of the first combustion-supporting gas will be much smaller than that of the centrifugal compressor of the first fuel gas, and it is not suitable to use Figure 1 A technical solution is used to reduce the axial fluid load. A suitable solution is that the first fuel gas centrifugal compressor adopts two-stage or multi-stage compression so that the diameter of the last-stage impeller of the first fuel gas centrifugal compressor is substantially the same as the diameter of the impeller of the first auxiliary gas centrifugal compressor.

[0291] Figure 3 It is a schematic diagram of a power transmission mechanism (speed regulator) of a combined centrifugal compressor and a configuration mode of a centrifugal compressor according to the present invention.

[0292] like Figure 3 The combined centrifugal compressor unit shown in the figure uses a single output shaft prime mover, a transmission machine (speed regulator) and is provided with two output shafts, and four centrifugal compressors are arranged. It is also a horizontal cross-sectional structural diagram of the power transmission mechanism. Figure 3 It is used to account for the axial fluid load on the output shaft and the gear load acting in the thrust direction due to the meshing of the main gear and pinion.

[0293] Figure 3 The combined centrifugal compressor shown has: an engine (not shown); a transmission machine, i.e., a speed increaser part 100, which transmits the rotational driving force of the engine; a first combustion-supporting gas centrifugal compressor C1, a temperature-adjusting gas centrifugal compressor C2, a first fuel gas centrifugal compressor C3, and a pre-cooling gas centrifugal compressor C4.

[0294] like Figure 3 As shown, an input shaft 4 of a speed-increasing gear part 100, which is usually a speed-increasing gear, is connected to a rotating shaft (not shown) of an engine via a coupling (not shown). A main gear 20, which is a large gear, is mounted on the input shaft 4. Two pinion gears 21 and 22, which are small gears, are meshed with the main gear 20. From the viewpoint of reducing vibration and noise, it is recommended that the main gear 20 and the pinion gears 21 and 22 use helical gears with a larger meshing ratio than spur gears.

[0295] like Figure 3 As shown, the pinion 21 and the output shaft 5 are formed integrally, and the input shaft 4 and the output shaft 5 are arranged in parallel. In addition, the pinion 21 can also be made into a separate body from the output shaft 5, and they can be fixed to the output shaft 5. On the output shaft 5, thrust rings 66 and 67 of a substantially cylindrical shape are fixed by shrink fitting.

[0296] like Figure 3 As shown, the pinion 22 and the output shaft 6 are formed integrally, and the input shaft 4 and the output shaft 6 are arranged in parallel. In addition, the pinion 22 can also be made separate from the output shaft 6 and fixed to the output shaft 6. On the output shaft 6, thrust rings 68 and 69 of a substantially cylindrical shape are fixed by shrink fitting.

[0297] like Figure 3As shown, the input shaft 4, the output shafts 5 and 6, the main gear 20, the pinion wheels 21 and 22, and the thrust rings 66 to 69 are components of the speed increaser 100 and are housed in a housing 101. The housing 101 is a horizontal plane split structure, and is divided into an upper housing and a lower housing by a plane substantially equal to a horizontal plane including the central axes of the input shaft 4 and the output shafts 5 and 6. The upper housing and the lower housing are joined together by bolts (not shown).

[0298] like Figure 3 As shown, the input shaft 4 and the main gear 20 are rotatably supported by composite bearings 60 and 61 held by the housing 101. The composite bearings 60 and 61 are bearings that receive radial (radial) loads (radial loads) and thrust (axial) loads (thrust loads).

[0299] like Figure 3 As shown, the output shaft 5 provided with the cannon 21 is rotatably supported by radial bearings 62, 63 (not shown) not shown and held by the housing 101; the output shaft 6 provided with the cannon 22 is rotatably supported by radial bearings 64, 65 (not shown) not shown and held by the housing 101; the thrust load acting on the output shaft 5 is borne and supported by thrust rings 66, 67, and the main gear 20 is clamped by the thrust rings 66, 67 with a gap 71 between them; the thrust load acting on the output shaft 6 is borne and supported by thrust rings 68, 69, and the main gear 20 is clamped by the thrust rings 68, 69 with a gap 72 between them.

[0300] like Figure 3 As shown, in order to lubricate the composite bearings 60, 61, radial bearings (not shown) of the output shafts 5, 6, thrust rings 66 to 69, the main gear 20 and the pinion wheels 21, 22, etc., lubricating oil is supplied from a lubricating oil system (not shown) and returned to an oil tank (not shown) provided at the bottom of the engine.

[0301] like Figure 3 As shown, the clearance 70 of the sliding surfaces in the thrust direction between the input shaft 4 and the main gear 20 and the composite bearings 60 and 61 is appropriately set as required, for example, about 0.2 mm. During the stable operation of the combined centrifugal compressor, one of the composite bearings 60 and 61 contacts the sliding surface of the main gear 20, and the other composite bearing maintains a clearance with the sliding surface of the main gear 20. However, when the combined centrifugal compressor is started or stopped, and the combined centrifugal compressor is operated beyond the operating limit range of the small flow area called surge, the composite bearing that contacts and slides with the main gear 20 varies depending on the operating state at that time.

[0302] like Figure 3As shown, the output shaft 5 and the pinion 21 are radially supported by radial bearings 62 and 63 (not shown). On the other hand, the output shaft 5 and the pinion 21 are supported in the thrust direction by thrust rings 66 and 67.

[0303] like Figure 3 As shown, the output shaft 6 and the pinion 22 are radially supported by radial bearings 64 and 65 (not shown). On the other hand, the output shaft 6 and the pinion 22 are supported in the thrust direction by thrust rings 68 and 69.

[0304] like Figure 3 As shown, the thrust rings 66 and 67 have the following structure, that is, they are shrink-fitted on the output shaft 5 in a manner of sandwiching the main gear 20 with a gap 71, and are in contact with the main gear 20 at the sliding surfaces located on the inner side of each axial direction. The surface distance between the sliding surface of the thrust ring 66 and the sliding surface of the thrust ring 67 is larger than the surface distance between the two sliding surfaces of the main gear 20, for example, by about 0.2 mm. That is, the gap 71 between the sliding surfaces of the main gear 20 and the thrust rings 66 and 67 in the thrust direction is, for example, about 0.2 mm. During the stable operation of the combined centrifugal compressor, either the thrust ring 66 or the thrust ring 67 is in contact with the sliding surface of the main gear 20, and the sliding surface of the other thrust ring maintains a gap with the sliding surface of the main gear 20. In addition, the thrust rings 66 and 67 maintain a gap of about 2 to 3 mm with the housing 101 and do not contact.

[0305] like Figure 3 As shown, the thrust rings 68 and 69 have the following structure, that is, they are shrink-fitted on the output shaft 6 in a manner of sandwiching the main gear 20 with a gap 72, and are in contact with the main gear 20 at the sliding surfaces located on the inner side of each axial direction. The surface distance between the sliding surface of the thrust ring 68 and the sliding surface of the thrust ring 69 is larger than the surface distance between the two sliding surfaces of the main gear 20, for example, by about 0.2 mm. That is, the gap 72 between the sliding surfaces of the main gear 20 and the thrust rings 68 and 69 in the thrust direction is, for example, about 0.2 mm. During the stable operation of the combined centrifugal compressor, either the thrust ring 68 or the thrust ring 69 is in contact with the sliding surface of the main gear 20, and the sliding surface of the other thrust ring maintains a gap with the sliding surface of the main gear 20. In addition, the thrust rings 68 and 69 maintain a gap of about 2 to 3 mm with the housing 101 and do not contact.

[0306] like Figure 3The combined centrifugal compressor shown has: an input shaft 4 driven by an engine; a main gear 20 provided on the input shaft 4; cannons 21 and 22 meshing with the main gear 20; and an output shaft 5 provided with the cannon 21 and an output shaft 6 provided with the cannon 22. On one side of the output shaft 6, a centrifugal impeller 1001 (the impeller back side 16, the impeller diameter D1) of the first assisting gas centrifugal compressor C1 is provided, and on the other side of the output shaft 6, a centrifugal impeller 2001 (the impeller back side 17, the impeller diameter D2) of the temperature regulating gas centrifugal compressor C2 is provided.

[0307] like Figure 3 As shown, the impeller is subjected to fluid thrust, the output shaft is subjected to fluid thrust and gear load, and the main gear 20 is subjected to gear load and combined load.

[0308] like Figure 3 As shown, a centrifugal impeller 1001 of the first combustion-supporting gas centrifugal compressor C1 is arranged on one side of the output shaft 6, a protective cover housing 111 (not shown) covers the outer side of the centrifugal impeller 1001, and a housing 101 (not shown) covers the back side 16 of the centrifugal impeller 1001. In addition, a shaft sealing device 15 (not shown) is arranged between the housing 101 and the output shaft 6 to prevent the compressed fluid from leaking out of the first combustion-supporting gas centrifugal compressor C1. The temperature-adjusting gas centrifugal compressor C2, the first fuel gas centrifugal compressor C3, and the pre-cooling gas centrifugal compressor C4 have similar structures.

[0309] like Figure 3 As shown, since the first fuel gas centrifugal compressor C3 and the pre-cooling gas centrifugal compressor C4 are centrifugal compressors with almost the same parameters such as gas molecular weight, inlet temperature, inlet pressure, pressure difference, etc., their impeller diameters are basically the same, and the axial net fluid loads Fi3 and Fi4 acting on the output shaft 5 by these two impellers 3001 and 4001 are almost equal in magnitude and opposite in direction, so the axial net fluid load on the output shaft 5 is very small or even almost zero.

[0310] like Figure 3 As shown, in the configuration of the output shaft of the gear 22, the first combustion-supporting gas centrifugal compressor C1 and the temperature-regulating gas centrifugal compressor C2 have a large difference in gas molecular weight (the ratio of the first combustion-supporting gas molecular weight to the temperature-regulating gas molecular weight is about 1.25-1.70). Under the condition of similar pressure difference or smaller pressure difference of the combustion-supporting gas centrifugal compressor, the impeller diameter of the first combustion-supporting gas centrifugal compressor is smaller and the impeller area is smaller. The axial fluid thrust acting on the impeller shaft caused by the pressure difference before and after the two centrifuge impellers is opposite in direction and unequal in magnitude, that is, the direction of the remaining axial force after the axial forces cancel each other out is the same as the direction of the fluid load on the impeller of the temperature-regulating gas centrifugal compressor. Therefore, the direction of the axial gear load on the output shaft of the gear 22 is required to be opposite to the direction of the fluid load on the impeller of the temperature-regulating gas centrifugal compressor, so as to cancel part of the axial load, reduce the total value of the axial load, and improve the dynamic balance performance of the transmission machine.

[0311] like Figure 3 As shown, in order to reduce the unbalanced fluid load (overall fluid load) on the output shaft of the above-mentioned gear 22 and improve the overall efficiency of the combined centrifugal compressor, the present invention proposes a solution for setting an additional extended impeller area for the impeller of the first combustion-aiding gas centrifugal compressor, and by increasing the area and gas pressure on the back side of the impeller disk of the first combustion-aiding gas centrifugal compressor, the overall fluid load on the integrated output shaft is reduced to zero as much as possible.

[0312] like Figure 3 As shown in the figure, the main gear 20 provided on the input shaft 4 and the pinion 21 provided on the output shaft 5 mesh and rotate when viewed from above, and the main gear 20 rotates clockwise when viewed from the opposite side of the engine as shown by the arrow in the figure. The main gear 20 is a left-handed helical gear with teeth inclined to the upper left when viewed from the side with the axis serving as the rotation center facing the vertical direction, and the pinion 21 is a right-handed helical gear with teeth inclined to the upper right when viewed from the side with the axis serving as the rotation center facing the vertical direction.

[0313] like Figure 3 As shown, the pinion 21 receives a gear load Fp2 in the thrust direction from the main gear 20 to the right. As a reaction to this, the main gear 20 receives a gear load (equal to Fp2) in the thrust direction from the pinion 21 to the left.

[0314] like Figure 3 As shown, the pinion 22 receives a gear load Fp1 in the thrust direction from the main gear 20 to the right. As a reaction to this, the main gear 20 receives a gear load (equal to Fp1) in the thrust direction from the pinion 22 to the left.

[0315] like Figure 3 As shown, the gear load Fp1 and the gear load Fp2 form a combined load F on the main gear 20 .

[0316] Figure 3 In the embodiment, the tooth rotation direction of the helical gear of the main gear 20 (not the rotation direction of the output shaft) can be left-handed or right-handed, and correspondingly, the tooth rotation direction of the helical gears of the pinion gears 21 and 22 (not the rotation direction of the output shaft) can be right-handed or left-handed.

[0317] Figure 3 The structure and assembly relationship shown in can be adjusted according to specific circumstances.

[0318] The following description Figure 4 The structure of the pyrolysis furnace is shown.

[0319] like Figure 4The pyrolysis furnace system shown only shows the structure of the characteristic part of the present invention, the coal charging box arranged at the upper part of the preheating section and the upper feed valve and lower discharge valve of the coal charging box, the coal charging hopper arranged at the upper part of the coal charging box, the coke discharge box arranged at the lower part of the quenching section and the upper feed valve and lower discharge valve of the coke discharge box, and the process medium pipeline connected to the pyrolysis furnace are not shown in the figure.

[0320] exist Figure 4 The internal heating vertical furnace shown is composed of a porous carbonization chamber 1000, gas distribution bricks 9010, 9013, 9016 are arranged at different positions of the carbonization chamber 1000, the vertical furnace is built of refractory bricks 9050, a combustion gas mixer 9012M, a gas delivery pipe 9009M, and an endothermic gas delivery pipe 9015M are arranged on the side of the furnace body, a thermocouple 9060 is arranged in an appropriate coal layer or semi-coke layer, and furnace protection iron parts 9080 are arranged around the furnace body.

[0321] The circulating cold coal gas is the purified coal gas after the raw coal gas discharged from the pyrolysis furnace is cooled, separated, dehydrated, deoiled and other treatment steps that may be required, and is usually pressurized by a fan to maintain the circulating flow of the coal gas.

[0322] Coke quenching water is fresh water or deeply purified water from wastewater obtained during the cooling, separation and dehydration of raw coal gas, and its water quality meets the requirements of national standards and specifications.

[0323] The following combination Figure 4 , detailed description Figure 4 The working process of the pyrolysis furnace system is shown, and the related external systems are briefly described.

[0324] The following is a detailed description Figure 4 The process and process objectives of each functional section of the pyrolysis furnace are shown.

[0325] Figure 4 The pyrolysis furnace shown adopts the operation mode that the fuel gas is mixed with the combustion-supporting gas and then enters the mixing chamber, and then is sprayed into the furnace through the gas distribution bricks. That is, the pyrolysis furnace is used as a flue gas generator, thereby saving the investment in a special flue gas generator and reducing the heat dissipation loss of the furnace body. It is a basic measure to simplify the pyrolysis system.

[0326] Figure 4The pyrolysis furnace shown in the figure has a preheating section at the top of the pyrolysis furnace cavity, which preheats the coal and dries the coal at a moderate temperature rise rate, and at the same time recovers the heat energy of the ascending hot coal gas (usually with a temperature of 300-450°C) discharged from the low-temperature pyrolysis section to reduce the energy consumption of the coal preheating process, reduce the temperature and volume flow of the coal gas leaving the pyrolysis furnace, filter the dust in the coal gas, and adsorb the asphalt droplets in the coal gas; if the ascending hot coal gas discharged from the low-temperature pyrolysis section is directly discharged from the pyrolysis furnace with the raw coal gas, during the process of coal gas cooling, separation, and oil collection, the coal gas contains too much tar asphalt and cannot be effectively recovered, and the energy consumption of the cooling process is increased, which will also aggravate the thermal condensation of tar. , and a large volume of coal gas will carry more dust and asphalt, causing the channel to be blocked; on the other hand, if the coal entering the furnace directly contacts the ascending hot coal gas discharged from the low-temperature pyrolysis section for dehydration and drying, a large amount of water will quickly convert into water vapor to expand and explode the coal particles to produce a large amount of pulverized coal; therefore, the preheating section is a necessary and important heating process with a suitable temperature rise rate, especially for coal with medium moisture content (such as coal with a moisture content of 10 to 28% by weight). Of course, coal with too high moisture content (such as coal with a moisture content of more than 35% by weight) is more suitable for an independent drying process, and then the dried coal is introduced into the pyrolysis furnace of the present invention. The operating temperature of the preheating section also needs to be strictly and flexibly controlled. Therefore, it is necessary to arrange thermocouples to monitor the temperature at the bottom and top coal seams of the expected preheating section, and even multiple thermocouple measuring points need to be set at different heights at the bottom of the expected preheating section. The flow rate and temperature of the temperature-regulating cooling gas in the low-temperature pyrolysis section can be adjusted in time according to the monitored temperature of the preheating section, and even the flow rate and temperature of the input gas in the distillation section can be adjusted, and even the flow rate of the input gas in the direct air cooling section can be adjusted. Of course, the volume of the preheating section must be large enough or the residence time of the coal preheating process must be long enough to meet the operating time requirements of the preheating or drying process, and there should be a certain margin to adapt to fluctuations in operating conditions. The overall operating goal is to fully recover the heat of the ascending hot coal gas discharged from the low-temperature pyrolysis section, heat the coal, and reduce the water content of the coal to below the expected value.

[0327] The operating temperature of the preheating section and the volume of the preheating section (coal preheating residence time) are determined by the production target, i.e., the moisture content by weight of the preheated coal discharged from the preheating section and the temperature of the coal after preheating. They are affected by the flow, moisture and temperature of the coal entering the furnace, as well as by multiple factors such as the temperature of the gas heat carrier and the flow of the gas heat carrier. The ideal moisture content by weight of the preheated coal discharged from the preheating section is usually less than 6.0%, generally less than 5.0%, and preferably less than 4.0%. The temperature of the coal after preheating is usually 180-370°C, generally 200-350°C, and preferably 200-320°C.

[0328] Figure 4The pyrolysis furnace shown in the figure has a low-temperature pyrolysis section arranged below the preheating section, which is used to perform low-temperature pyrolysis on the preheated coal to reduce its volatile matter and maximize the tar yield. At the same time, it is necessary to prevent the high-temperature gas from the distillation section from invading the low-temperature pyrolysis section, causing actual medium-temperature pyrolysis and causing tar burnout. This requires strict and flexible control of the temperature of the low-temperature pyrolysis process. Therefore, the temperature-regulating cooling gas distribution element arranged at the bottom of the low-temperature pyrolysis section is required to have a certain flexible adjustment range. It is necessary to strictly monitor the upper and lower operating temperatures of the mixing area, and adjust the flow rate and temperature of the temperature-regulating cooling gas in time according to the monitored temperature. Of course, the volume of the low-temperature pyrolysis section must be large enough or the residence time of the preheated coal must be long enough to meet the operating time requirements of the heat transfer and pyrolysis process of the low-temperature pyrolysis section, and there should be a certain margin to adapt to fluctuations in operating conditions. The overall operating goal is to fully extract tar and ensure that the low-temperature semi-coke is burned through without being undercooked.

[0329] The operating temperature of the low-temperature pyrolysis section and the volume of the low-temperature pyrolysis section (residence time of the coal after preheating) are determined by the production target, i.e., the volatile matter weight content of the low-temperature pyrolysis semi-coke discharged from the low-temperature pyrolysis section, and are affected by the flow rate, moisture, volatile matter, temperature of the preheated coal, and the temperature of the gas heat carrier, the flow rate of the gas heat carrier, and other factors; the ideal volatile matter weight content of the low-temperature pyrolysis semi-coke is 8.50% to 12.50% or 6.50% to 8.50%. The temperature of the low-temperature semi-coke discharged from the low-temperature pyrolysis section is usually 430 to 680°C, generally 460 to 650°C, and preferably 500 to 650°C.

[0330] Figure 4 In the pyrolysis furnace shown, a stripping section is arranged below the low-temperature pyrolysis section, which is used to deeply pyrolyze the low-temperature semi-coke to reduce its volatile matter, and at the same time prevent the stripping section from producing too much tar pitch and hope to produce more coal gas. That is to say, the low-temperature semi-coke needs to be quickly heated up in the upper bed layer in the stripping section to enter a higher temperature pyrolysis process. Therefore, the gas temperature of the upper bed layer in the stripping section is still very high, usually at least 150°C higher than the mixed gas temperature at the bottom of the low-temperature pyrolysis section. In this way, the gas temperature of the upper bed layer in the stripping section needs to be strictly monitored, and the flow rate and temperature of the stripping hot flue gas need to be adjusted in time according to the monitored temperature; of course, the volume of the stripping section (the residence time of the low-temperature pyrolysis semi-coke) must be large enough or the residence time of the low-temperature semi-coke must be long enough to meet the operating time requirements of the heat transfer pyrolysis process in the stripping section, and there should be a certain margin to adapt to the fluctuation of the operating conditions and ensure that the stripping semi-coke is burned through and not undercooked.

[0331] The operating temperature of the stripping section and the volume of the stripping section (residence time of the low-temperature pyrolysis semi-coke) are determined by the production target, i.e., the weight content of volatile matter in the stripping semi-coke discharged from the stripping section, and are affected by the flow rate, volatile matter, temperature of the low-temperature pyrolysis semi-coke, as well as the temperature of the gas heat carrier, the flow rate of the gas heat carrier and other factors; the ideal weight content of volatile matter in the stripping semi-coke is 3.00% to 4.95% or less than 3.00%. The temperature of the stripping semi-coke discharged from the stripping section is usually 700 to 1000°C, generally 750 to 950°C, and preferably 800 to 950°C.

[0332] Figure 4 The pyrolysis furnace shown in the figure is provided with a direct air cooling section below the stripping section for recovering the heat energy of the hot stripping coke discharged from the stripping section. In this way, the operating value of the maximum final temperature of the stripping section can be flexibly increased as needed to ensure that the volatile matter content of the stripping coke is lower than the expected upper limit. This operating mode can prevent the consumption of a large amount of gas due to increasing the maximum final temperature of the stripping section. For the case where the gas comes from the separated gas of the raw coal gas of the pyrolysis furnace, this scheme can increase the yield of the external effective gas. Of course, the volume of the direct air cooling section must be large enough or the residence time of the stripping coke must be long enough to meet the operating time requirements of the heat transfer in the cooling process of the stripping coke, and there should be a certain margin to adapt to the fluctuation of the operating conditions and ensure that the stripping coke is cooled thoroughly.

[0333] The operating temperature and volume of the direct air cooling section are determined by the production target, i.e., the temperature of the stripping coke discharged from the direct air cooling section, and are affected by the flow rate and temperature of the stripping coke, as well as by multiple factors such as the temperature of the gas heat carrier and the flow rate of the gas heat carrier. The ideal temperature of the stripping coke discharged from the direct air cooling section is usually 150-400°C, generally 180-350°C, and preferably 200-300°C. Under economic conditions, the temperature of the coke discharged from the direct air cooling section should be reduced as much as possible to reduce the water consumption in the coke quenching section.

[0334] Because the ideal temperature of the semi-coke after quenching is 70-90℃, if such a low temperature is achieved by circulating gas cooling, the volume of the quenching section will be too large, the height and weight of the pyrolysis furnace will increase too much, the gas circulation pressure difference will increase greatly, and the pressure at the bottom of the pyrolysis furnace will increase greatly, resulting in a decrease in safety, which will lead to a significant increase in investment and energy consumption, which is uneconomical. On the other hand, an inert gas barrier is required below the direct gas cooling section to prevent atmospheric air from entering the direct gas cooling section and to prevent the gas in the direct gas cooling section from leaking into the atmospheric air.

[0335] Figure 4In the pyrolysis furnace shown, a quenching section using water is arranged below the direct air cooling section to achieve thorough quenching. Since the endothermic process of water quenching mainly utilizes the latent heat of evaporation of water, very little water is required. Such a quenching section has a very small volume, which can reduce investment, reduce the height of the quenching section, and reduce the weight of the quenching section. The steam generated by the quenching enters the direct air cooling section as a gas heat carrier. Of course, the volume of the quenching section must be large enough or the quenching time must be long enough to meet the operational needs of heat transfer and pyrolysis in the quenching section. There should be a certain margin to adapt to fluctuations in operating conditions and ensure that the semi-coke is cooled thoroughly without being caught (i.e., the semi-coke core is cooled to a certain limiting temperature).

[0336] In particular, the present invention is suitable for the working condition where the combustion-supporting gas is oxygen-rich or pure oxygen.

[0337] The total residence time of the coal from entering the pyrolysis furnace to leaving the pyrolysis furnace to become stripping coke, and the residence time of each stage vary according to the specific properties of the coal, the requirements for the volatile matter content of the stripping coke, and the expected yield of low-temperature dry distillation tar. Usually, the total residence time of the coal in the pyrolysis furnace is 4 to 15 hours, generally 5 to 12 hours.

[0338] Typically, the stripping coke discharged from the coke discharge box of the pyrolysis furnace is collected and transported to the coke storage bin.

[0339] According to the needs, in the preheating section of the pyrolysis furnace, the hot flue gas drying of the pyrolysis furnace coal can be carried out. The working method is as follows, but this working method is not preferred:

[0340] Between the preheating section and the low-temperature pyrolysis section of the pyrolysis furnace, a vertical preheating section lower coal material pipe is arranged, and the preheating section lower coal material pipe forms a pressure difference on the low-temperature pyrolysis section gas to prevent the low-temperature pyrolysis section gas from ascending, and the operating pressure of the preheating section of the pyrolysis furnace is slightly greater than the operating pressure of the low-temperature pyrolysis section;

[0341] In the preheating section of the pyrolysis furnace, a hot flue gas distribution pipe is arranged at the bottom. The hot flue gas goes up and contacts with the coal material going down in the preheating section of the pyrolysis furnace to transfer heat, so that the water in the coal material evaporates and then enters the upward drying gas. The drying gas is discharged from the upper part of the preheating section of the pyrolysis furnace; the dried coal material enters the low-temperature pyrolysis section of the pyrolysis furnace through the coal material pipe at the lower part of the preheating section;

[0342] A small amount of hot flue gas enters the top of the low-temperature pyrolysis section of the pyrolysis furnace from the preheating section of the pyrolysis furnace;

[0343] The hot flue gas entering the bottom of the preheating section of the pyrolysis furnace can be the hot flue gas provided by an independent flue gas generator, or the hot flue gas generated by the indirect cooling section of the stripping semi-coke of the pyrolysis furnace.

[0344] The characteristic parts of the present invention are described below.

[0345] The four-way air intake combined with centrifugal compression and transportation method of the double-pyrolysis-stage coal vertical pyrolysis furnace of the present invention is characterized by:

[0346] ⑴ Double pyrolysis stage coal vertical pyrolysis furnace

[0347] The coal pyrolysis furnace is a vertical coal pyrolysis furnace with double pyrolysis sections and internal heating and moving bed. The coal entering the pyrolysis furnace passes through at least a preheating section, a low-temperature pyrolysis section, a stripping section, and a semi-coke precooling section during its downward process, and gradually becomes preheated coal, low-temperature pyrolysis semi-coke, stripping semi-coke, and precooling semi-coke.

[0348] In the furnace of the pyrolysis furnace, the stripping section is located below the low-temperature pyrolysis section, and the space of the stripping section is connected to the space of the low-temperature pyrolysis section;

[0349] In the furnace of the pyrolysis furnace, the semi-coke pre-cooling section is located below the stripping section, and the space of the semi-coke pre-cooling section is connected with the space of the stripping section;

[0350] In the low-temperature pyrolysis section, the heat source of the low-temperature pyrolysis section is provided by the initial gas heat carrier of the low-temperature pyrolysis section rising in the low-temperature pyrolysis section; a temperature-adjusting gas distribution channel is arranged at the bottom of the low-temperature pyrolysis section, and the temperature-adjusting gas distribution channel discharges the temperature-adjusting gas into the furnace cavity; the temperature-adjusting gas entering the furnace cavity is mixed with the upward stripping section output gas from the stripping section to become the initial gas heat carrier of the low-temperature pyrolysis section, and the temperature of the initial gas heat carrier of the low-temperature pyrolysis section is at least 100°C lower than the temperature of the stripping section output gas;

[0351] In the low-temperature pyrolysis section, the temperature-adjusting gas distribution channel is located in the lower coke layer and / or outside the lower coke layer of the low-temperature pyrolysis section;

[0352] In the low-temperature pyrolysis section, the gas heat carrier of the low-temperature pyrolysis section moves upward, countercurrently contacts with the preheated coal from the preheating section to reduce the temperature and mix with the net coal gas produced by low-temperature pyrolysis to become the output gas of the low-temperature pyrolysis section; the output gas of the low-temperature pyrolysis section enters the preheating section; the preheated coal moving downward gradually heats up to perform low-temperature pyrolysis, reducing the volatile matter to become low-temperature semi-coke; the low-temperature semi-coke moves downward and is discharged from the low-temperature pyrolysis section to enter the stripping section;

[0353] In the stripping section, most or all of the heat source of the stripping section is provided by the gas heat carrier rising in the stripping section; a main fire channel is arranged at the bottom of the stripping section; the stripping heat supply gas discharged from the main fire channel goes upward, countercurrently contacts with the descending low-temperature pyrolysis semi-coke from the low-temperature pyrolysis section to reduce the temperature and mix with the stripping net product gas to become the output gas of the stripping section; the output gas of the stripping section enters the low-temperature pyrolysis section; the descending low-temperature pyrolysis semi-coke gradually heats up and deeply pyrolyzes, reducing the volatile matter to become stripping semi-coke; the stripping semi-coke is discharged from the stripping section;

[0354] The main fire channel of the stripping section is located in the lower coke layer of the stripping section and / or outside the lower coke layer;

[0355] In the semi-coke pre-cooling section, most or all of the cold source of the semi-coke pre-cooling section is provided by the pre-cooling gas heat carrier rising in the semi-coke pre-cooling section; a pre-cooling gas channel is arranged at the bottom of the semi-coke pre-cooling section; the pre-cooling gas discharged from the pre-cooling gas channel goes upward, countercurrently contacts with the downward stripping semi-coke from the stripping section to increase the temperature and mix with the net coal gas produced by the semi-coke pre-cooling section to become the output gas of the semi-coke pre-cooling section; the output gas of the semi-coke pre-cooling section goes upward into the stripping section and mixes with the stripping heating gas discharged from the main fire channel and then continues to go upward; the output gas of the semi-coke pre-cooling section enters the stripping section; the downward stripping semi-coke gradually cools down to become pre-cooled semi-coke; the pre-cooled semi-coke is discharged from the semi-coke pre-cooling section;

[0356] A pre-cooling gas channel is located in the lower coke layer and / or outside the lower coke layer of the semi-coke pre-cooling section;

[0357] The coal internal heating moving bed vertical pyrolysis furnace is composed of a single-hole, two-hole or multi-hole carbonization chamber; at least one side of each hole carbonization chamber is provided with a temperature regulating gas distribution channel, a main fire channel, and a pre-cooling gas distribution channel;

[0358] An air outlet is arranged on the temperature regulating air distribution duct, an air outlet is arranged on the main fire duct, and an air outlet is arranged on the pre-cooling air distribution duct;

[0359] A coal distribution plate is provided on the upper part of the pyrolysis chamber, and a riser is provided on the top of the pyrolysis chamber; the riser discharges the primary coal gas from the pyrolysis furnace;

[0360] ⑵ Four-way air intake combined with centrifugal compression and delivery

[0361] In the combined centrifugal compressor, a prime mover is used to drive the first combustion-aid gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor, and the first combustion-aid gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor work in a manner of starting, running, and stopping at the same time;

[0362] The prime mover of the combined centrifugal compressor transmits power to the first combustion-assisting gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor via a power transmission mechanism;

[0363] The first combustion-supporting gas is pressurized by the first combustion-supporting gas centrifugal compressor of the combined centrifugal compressor to become the first combustion-supporting gas after pressurization; the first fuel gas is pressurized by the first fuel gas centrifugal compressor of the combined centrifugal compressor to become the first fuel gas after pressurization;

[0364] The first combustion-supporting gas after pressure increase and the first fuel gas after pressure increase pass through the first mixer to become the first mixed gas; the first mixed gas enters the main fire channel for combustion and / or enters the furnace of the coal pyrolysis furnace for combustion to release heat to form a gas heat carrier that moves upward, and heats and pyrolyzes the descending coal material; the ratio of the volume of the first fuel gas entering the first mixer to the volume of the first fuel gas of the chemical combustion equivalent of the first combustion-supporting gas entering the first mixer is defined as the first fuel gas fuel supply ratio K1, K1≥1.15;

[0365] The temperature-controlled gas is pressurized by the temperature-controlled gas centrifugal compressor of the combined centrifugal compressor to become the pressurized temperature-controlled gas;

[0366] After the pressure is increased, the temperature-adjusting gas enters the temperature-adjusting gas distribution channel, enters the furnace through the distribution port of the temperature-adjusting gas distribution channel connected to the furnace, contacts with the upward hot gas and the downward carbon material, and reduces the temperature of the upward gas;

[0367] The pre-cooled air is boosted by the pre-cooled air centrifugal compressor of the combined centrifugal compressor to become boosted pre-cooled air;

[0368] After the pressure is increased, the precooling gas enters the precooling gas distribution channel, enters the furnace through the gas distribution port of the precooling gas distribution channel connected to the furnace, contacts with the descending carbon material to reduce the temperature of the descending stripping semi-coke, and contacts with the ascending gas that exists or does not exist;

[0369] The temperature-adjusted gas is the purified gas obtained from the primary gas of the pyrolysis furnace through a purification process including at least the steps of cooling, deoiling and dehydrating;

[0370] The first fuel gas is a purified gas obtained by a purification process of the primary gas from the pyrolysis furnace, which includes at least the steps of cooling, deoiling and dehydrating;

[0371] Pre-cooled gas is purified gas obtained from the primary gas from the pyrolysis furnace through a purification process that includes at least the steps of cooling, deoiling and dehydrating.

[0372] The first structural scheme of the combined centrifugal compressor of the present invention is:

[0373] The combined centrifugal compressor uses a dual output shaft prime mover;

[0374] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0375] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0376] The first gear is meshed with the main gear of the first transmission machine;

[0377] a second gear meshing with the main gear of the first transmission machine;

[0378] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0379] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0380] A first fuel gas centrifugal compressor A is arranged on one side of the first gear output shaft, and a first fuel gas centrifugal compressor B is arranged on the other side of the first gear output shaft;

[0381] The first fuel gas is divided into two paths with the same flow rate, entering the first fuel gas centrifugal compressor A and the first fuel gas centrifugal compressor B respectively;

[0382] A temperature regulating air centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling air centrifugal compressor is arranged on the other side of the second gear output shaft;

[0383] The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

[0384] The second structural scheme of the combined centrifugal compressor of the present invention is:

[0385] The combined centrifugal compressor uses a dual output shaft prime mover;

[0386] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0387] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0388] The first gear is meshed with the main gear of the first transmission machine;

[0389] a second gear meshing with the main gear of the first transmission machine;

[0390] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0391] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0392] A temperature-controlled air centrifugal compressor A is arranged on one side of the output shaft of the first gear, and a temperature-controlled air centrifugal compressor B is arranged on the other side of the output shaft of the first gear;

[0393] The temperature-controlled gas is divided into two routes with the same flow rate, entering the temperature-controlled gas centrifugal compressor A and the temperature-controlled gas centrifugal compressor B respectively;

[0394] A pre-cooling gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft;

[0395] The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

[0396] The third structural scheme of the combined centrifugal compressor of the present invention is:

[0397] The combined centrifugal compressor uses a dual output shaft prime mover;

[0398] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0399] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0400] The first gear is meshed with the main gear of the first transmission machine;

[0401] a second gear meshing with the main gear of the first transmission machine;

[0402] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0403] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0404] A pre-cooling air centrifugal compressor A is arranged on one side of the first gear output shaft, and a pre-cooling air centrifugal compressor B is arranged on the other side of the first gear output shaft;

[0405] The pre-cooling air is divided into two routes with the same flow rate, entering the pre-cooling air centrifugal compressor A and the pre-cooling air centrifugal compressor B respectively;

[0406] A temperature-adjusting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft;

[0407] The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

[0408] The fourth structural scheme of the combined centrifugal compressor of the present invention is:

[0409] The combined centrifugal compressor uses a dual output shaft prime mover;

[0410] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0411] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0412] The first gear is meshed with the main gear of the first transmission machine;

[0413] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0414] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0415] The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving;

[0416] A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine;

[0417] a second gear meshing with the main gear of the second transmission machine;

[0418] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0419] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a temperature-regulating gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0420] The fifth structural scheme of the combined centrifugal compressor of the present invention is:

[0421] The combined centrifugal compressor uses a dual output shaft prime mover;

[0422] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0423] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0424] The first gear is meshed with the main gear of the first transmission machine;

[0425] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0426] A pre-cooling air centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting air centrifugal compressor is arranged on the other side of the first gear output shaft;

[0427] The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving;

[0428] A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine;

[0429] a second gear meshing with the main gear of the second transmission machine;

[0430] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0431] A first combustion-assistant gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0432] The sixth structural scheme of the combined centrifugal compressor of the present invention is:

[0433] The combined centrifugal compressor uses a dual output shaft prime mover;

[0434] The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving;

[0435] A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine;

[0436] The first gear is meshed with the main gear of the first transmission machine;

[0437] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0438] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0439] The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving;

[0440] A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine;

[0441] a second gear meshing with the main gear of the second transmission machine;

[0442] A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft;

[0443] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0444] The seventh structural scheme of the combined centrifugal compressor of the present invention is:

[0445] The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission;

[0446] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0447] A main gear, arranged on the input shaft of the first transmission machine;

[0448] The first gear meshes with the main gear;

[0449] The second gear meshes with the main gear;

[0450] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0451] The second gear output shaft is used to set the second gear;

[0452] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0453] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a temperature-regulating gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0454] The eighth structural scheme of the combined centrifugal compressor of the present invention is:

[0455] The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission;

[0456] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0457] A main gear, disposed on the input shaft of the first transmission machine;

[0458] The first gear meshes with the main gear;

[0459] The second gear meshes with the main gear;

[0460] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0461] The second gear output shaft is used to set the second gear;

[0462] A pre-cooling air centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting air centrifugal compressor is arranged on the other side of the first gear output shaft;

[0463] A first combustion-assistant gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0464] The ninth structural scheme of the combined centrifugal compressor of the present invention is:

[0465] The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission;

[0466] The input shaft of the first transmission machine is connected to the output shaft of the prime mover;

[0467] A main gear, disposed on the input shaft of the first transmission machine;

[0468] The first gear meshes with the main gear;

[0469] The second gear meshes with the main gear;

[0470] A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft;

[0471] The second gear output shaft is used to set the second gear;

[0472] A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting gas centrifugal compressor is arranged on the other side of the first gear output shaft;

[0473] A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the second gear output shaft.

[0474] In the present invention, generally, the first combustion-supporting gas entering the combined centrifugal compressor comes from the first combustion-supporting gas buffer tank;

[0475] The operating pressure of the first combustion-supporting gas buffer tank is lower than the pressure at the outlet of the first mixer connected to the main fire channel.

[0476] In the present invention, usually, a first combustion-supporting gas emergency interlock cut-off valve is arranged on the pipeline of the first combustion-supporting gas after the boost is discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the first combustion-supporting gas emergency interlock cut-off valve is interlocked and closed;

[0477] A first fuel gas emergency interlock cut-off valve is provided on the pipeline of the pressurized first fuel gas discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the first fuel gas emergency interlock cut-off valve is interlocked and closed;

[0478] An emergency interlock shut-off valve for the temperature-regulating gas is provided on the pipeline for the pressurized temperature-regulating gas discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the emergency interlock shut-off valve for the temperature-regulating gas is shut off by interlock.

[0479] In the present invention, generally, the first combustion-supporting gas entering the combined centrifugal compressor comes from the first combustion-supporting gas buffer tank;

[0480] The operating pressure of the first combustion-supporting gas buffer tank is lower than the pressure at the outlet of the first mixer connected to the main fire channel;

[0481] An overpressure interlock cut-off valve of the first combustion-supporting gas buffer tank is arranged on the pipeline from which the first combustion-supporting gas buffer tank is discharged to the combined centrifugal compressor. Once the pressure of the first combustion-supporting gas buffer tank is higher than the pressure at the outlet of the first mixer, the overpressure interlock cut-off valve of the first combustion-supporting gas buffer tank is interlocked and closed.

[0482] In the present invention, usually, the first combustion-supporting gas is oxygen-enriched gas with an oxygen volume concentration higher than 35%, and a carbon dioxide volume concentration higher than 60%.

[0483] In the present invention, usually, the air flow temperature at 300 mm above the air outlet of the temperature regulating air distribution channel of the low-temperature pyrolysis section is used as the qualitative temperature of the initial gas heat carrier of the low-temperature pyrolysis section;

[0484] In the stripping section, the gas flow temperature at a point 300 mm below the gas outlet of the temperature-adjusting gas distribution channel of the low-temperature pyrolysis section is taken as the qualitative temperature of the output gas of the stripping section;

[0485] The temperature of the low-temperature pyrolysis semi-coke 300 mm above the outlet of the temperature-adjusting gas distribution channel of the low-temperature pyrolysis section is taken as the qualitative temperature of the low-temperature pyrolysis section;

[0486] The temperature of the stripping semi-coke 300mm above the outlet of the main fire channel of the stripping section is taken as the qualitative temperature of the stripping section;

[0487] The coal fed into the pyrolysis furnace is low-rank coal;

[0488] In the preheating section, the temperature of the discharged preheated coal is 180-370°C;

[0489] The qualitative temperature of the low-temperature pyrolysis section is 430-680°C; the qualitative temperature of the initial gas heat carrier in the low-temperature pyrolysis section is at least 200°C lower than the qualitative temperature of the output gas in the stripping section;

[0490] The qualitative temperature of the stripping section is 700-1000°C, and is 100-450°C higher than the qualitative temperature of the low-temperature pyrolysis section;

[0491] Each carbonization chamber is wide at the top and narrow at the bottom, with a variable cross section in the middle. The temperature-adjusting gas distribution channel and the main fire channel are arranged in the narrow cavity section below the narrowing transition section in the middle of the carbonization chamber.

[0492] The volatile matter of the stripping char is at least 2.0 weight percent lower than the volatile matter of the low-temperature pyrolysis char;

[0493] The volatile matter of the stripped semi-coke is less than 4.95 wt%.

[0494] In the present invention, usually, the coal pyrolysis furnace is provided with a semi-coke quenching section below the pre-cooling section.

[0495] In the present invention, the coal pyrolysis furnace can be provided with an external heating system at the same time. The high-temperature gas flowing through the heat transfer channel of the external heating system does not enter the furnace of the pyrolysis furnace. The heat transfer channel of the external heating system indirectly transfers heat to the furnace of the coal dry distillation zone of the pyrolysis furnace through the heat transfer wall surface.

[0496] In the present invention, usually, the first fuel gas supply ratio K1, K1 is 1.5-5.0.

[0497] In the present invention, usually, each centrifugal compressor is a single-stage centrifugal compressor.

[0498] In the present invention, usually, the impeller of the first combustion-aid gas centrifugal compressor adopts an impeller with an additional extended impeller area, which reduces the overall fluid load on the integrated output shaft by increasing the area and gas pressure of the back side of the first combustion-aid gas centrifugal compressor impeller disk.

[0499] In the present invention, usually, the prime mover is an electric motor or a turbine.

[0500] In the present invention, usually, the output shaft of the prime mover is connected to the rotating shaft of the centrifugal compressor impeller or the input shaft of the transmission by direct connection or connection through a coupling.

[0501] In the present invention, usually, the main gear and the pinion are helical gears;

[0502] The rotation direction of the helical gear is set so that the gear load acting on the pinion in the axial direction and the fluid load acting on the corresponding output shaft in the axial direction are in opposite directions.

Claims

1. Four-way air intake combined with centrifugal compression and transportation method for double-pyrolysis-stage coal vertical pyrolysis furnace, Features: ⑴ Double pyrolysis stage coal vertical pyrolysis furnace The coal pyrolysis furnace is a vertical coal pyrolysis furnace with double pyrolysis sections and internal heating and moving bed. The coal entering the pyrolysis furnace passes through at least a preheating section, a low-temperature pyrolysis section, a stripping section, and a semi-coke precooling section during its downward process, and gradually becomes preheated coal, low-temperature pyrolysis semi-coke, stripping semi-coke, and precooling semi-coke. In the furnace of the pyrolysis furnace, the stripping section is located below the low-temperature pyrolysis section, and the space of the stripping section is connected to the space of the low-temperature pyrolysis section; In the furnace of the pyrolysis furnace, the semi-coke pre-cooling section is located below the stripping section, and the space of the semi-coke pre-cooling section is connected with the space of the stripping section; In the low-temperature pyrolysis section, the heat source of the low-temperature pyrolysis section is provided by the initial gas heat carrier of the low-temperature pyrolysis section rising in the low-temperature pyrolysis section; a temperature-adjusting gas distribution channel is arranged at the bottom of the low-temperature pyrolysis section, and the temperature-adjusting gas distribution channel discharges the temperature-adjusting gas into the furnace cavity; the temperature-adjusting gas entering the furnace cavity is mixed with the upward stripping section output gas from the stripping section to become the initial gas heat carrier of the low-temperature pyrolysis section, and the temperature of the initial gas heat carrier of the low-temperature pyrolysis section is at least 100°C lower than the temperature of the stripping section output gas; In the low-temperature pyrolysis section, the temperature-adjusting gas distribution channel is located in the lower coke layer and / or outside the lower coke layer of the low-temperature pyrolysis section; In the low-temperature pyrolysis section, the gas heat carrier of the low-temperature pyrolysis section moves upward, countercurrently contacts with the preheated coal from the preheating section to reduce the temperature and mix with the net coal gas produced by low-temperature pyrolysis to become the output gas of the low-temperature pyrolysis section; the output gas of the low-temperature pyrolysis section enters the preheating section; the preheated coal from the preheating section gradually heats up to perform low-temperature pyrolysis, reducing the volatile matter to become low-temperature semi-coke; The low-temperature semi-coke flows downward out of the low-temperature pyrolysis section and enters the stripping section; In the stripping section, most or all of the heat source of the stripping section is provided by the gas heat carrier rising in the stripping section; a main fire channel is arranged at the bottom of the stripping section; the stripping heat supply gas discharged from the main fire channel goes upward, countercurrently contacts with the descending low-temperature pyrolysis semi-coke from the low-temperature pyrolysis section to reduce the temperature and mix with the stripping net product gas to become the output gas of the stripping section; the output gas of the stripping section enters the low-temperature pyrolysis section; the descending low-temperature pyrolysis semi-coke gradually heats up and deeply pyrolyzes, reducing the volatile matter to become stripping semi-coke; the stripping semi-coke is discharged from the stripping section; The main fire channel of the stripping section is located in the lower coke layer of the stripping section and / or outside the lower coke layer; In the semi-coke pre-cooling section, most or all of the cold source of the semi-coke pre-cooling section is provided by the pre-cooling gas heat carrier rising in the semi-coke pre-cooling section; a pre-cooling gas channel is arranged at the bottom of the semi-coke pre-cooling section; the pre-cooling gas discharged from the pre-cooling gas channel goes upward, countercurrently contacts with the downward stripping semi-coke from the stripping section to increase the temperature and mix with the net coal gas produced by the semi-coke pre-cooling section to become the output gas of the semi-coke pre-cooling section; the output gas of the semi-coke pre-cooling section goes upward into the stripping section and mixes with the stripping heating gas discharged from the main fire channel and then continues to go upward; the output gas of the semi-coke pre-cooling section enters the stripping section; the downward stripping semi-coke gradually cools down to become pre-cooled semi-coke; the pre-cooled semi-coke is discharged from the semi-coke pre-cooling section; A pre-cooling gas channel is located in the lower coke layer and / or outside the lower coke layer of the semi-coke pre-cooling section; The coal internal heating moving bed vertical pyrolysis furnace is composed of a single-hole, two-hole or multi-hole carbonization chamber; at least one side of each hole carbonization chamber is provided with a temperature regulating gas distribution channel, a main fire channel, and a pre-cooling gas distribution channel; An air outlet is arranged on the temperature regulating air distribution duct, an air outlet is arranged on the main fire duct, and an air outlet is arranged on the pre-cooling air distribution duct; A coal distribution plate is provided on the upper part of the pyrolysis chamber, and a riser is provided on the top of the pyrolysis chamber; the riser discharges the primary coal gas from the pyrolysis furnace; ⑵ Four-way air intake combined with centrifugal compression and delivery In the combined centrifugal compressor, a prime mover is used to drive the first combustion-aid gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor, and the first combustion-aid gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor work in a manner of starting, running, and stopping at the same time; The prime mover of the combined centrifugal compressor transmits power to the first combustion-assisting gas centrifugal compressor, the first fuel gas centrifugal compressor, the temperature-adjusting gas centrifugal compressor, and the pre-cooling gas centrifugal compressor via a power transmission mechanism; The first combustion-supporting gas is pressurized by the first combustion-supporting gas centrifugal compressor of the combined centrifugal compressor to become the first combustion-supporting gas after pressurization; the first fuel gas is pressurized by the first fuel gas centrifugal compressor of the combined centrifugal compressor to become the first fuel gas after pressurization; The first combustion-supporting gas after pressure increase and the first fuel gas after pressure increase pass through the first mixer to become the first mixed gas; the first mixed gas enters the main fire channel for combustion and / or enters the furnace of the coal pyrolysis furnace for combustion to release heat to form a gas heat carrier that moves upward, and heats and pyrolyzes the descending coal material; the ratio of the volume of the first fuel gas entering the first mixer to the volume of the first fuel gas of the chemical combustion equivalent of the first combustion-supporting gas entering the first mixer is defined as the first fuel gas fuel supply ratio K1, K1≥1.15; The temperature-controlled gas is pressurized by the temperature-controlled gas centrifugal compressor of the combined centrifugal compressor to become the pressurized temperature-controlled gas; After the pressure is increased, the temperature-adjusting gas enters the temperature-adjusting gas distribution channel, enters the furnace through the distribution port of the temperature-adjusting gas distribution channel connected to the furnace, contacts with the upward hot gas and the downward carbon material, and reduces the temperature of the upward gas; The pre-cooled air is boosted by the pre-cooled air centrifugal compressor of the combined centrifugal compressor to become boosted pre-cooled air; After the pressure is increased, the precooling gas enters the precooling gas distribution channel, enters the furnace through the gas distribution port of the precooling gas distribution channel connected to the furnace, contacts with the descending carbon material to reduce the temperature of the descending stripping semi-coke, and contacts with the ascending gas that exists or does not exist; The temperature-adjusted gas is the purified gas obtained from the primary gas of the pyrolysis furnace through a purification process including at least the steps of cooling, deoiling and dehydrating; The first fuel gas is a purified gas obtained by a purification process of the primary gas from the pyrolysis furnace, which includes at least the steps of cooling, deoiling and dehydrating; Pre-cooled gas is purified gas obtained from the primary gas from the pyrolysis furnace through a purification process that includes at least the steps of cooling, deoiling and dehydrating.

2. The method according to claim 1, Features: The combined centrifugal compressor uses a dual output shaft prime mover; The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving; A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine; The first gear is meshed with the main gear of the first transmission machine; a second gear meshing with the main gear of the first transmission machine; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft; A first fuel gas centrifugal compressor A is arranged on one side of the first gear output shaft, and a first fuel gas centrifugal compressor B is arranged on the other side of the first gear output shaft; The first fuel gas is divided into two paths with the same flow rate, entering the first fuel gas centrifugal compressor A and the first fuel gas centrifugal compressor B respectively; A temperature regulating air centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling air centrifugal compressor is arranged on the other side of the second gear output shaft; The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

3. The method according to claim 1, Features: The combined centrifugal compressor uses a dual output shaft prime mover; The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving; A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine; The first gear is meshed with the main gear of the first transmission machine; a second gear meshing with the main gear of the first transmission machine; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft; A temperature-controlled air centrifugal compressor A is arranged on one side of the output shaft of the first gear, and a temperature-controlled air centrifugal compressor B is arranged on the other side of the output shaft of the first gear; The temperature-controlled gas is divided into two routes with the same flow rate, entering the temperature-controlled gas centrifugal compressor A and the temperature-controlled gas centrifugal compressor B respectively; A pre-cooling gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft; The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

4. The method according to claim 1, Features: The combined centrifugal compressor uses a dual output shaft prime mover; The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving; A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine; The first gear is meshed with the main gear of the first transmission machine; a second gear meshing with the main gear of the first transmission machine; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft; A pre-cooling air centrifugal compressor A is arranged on one side of the first gear output shaft, and a pre-cooling air centrifugal compressor B is arranged on the other side of the first gear output shaft; The pre-cooling air is divided into two routes with the same flow rate, entering the pre-cooling air centrifugal compressor A and the pre-cooling air centrifugal compressor B respectively; A temperature-adjusting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft; The second output shaft of the dual-output shaft prime mover is connected to the impeller shaft of the first combustion-aid gas centrifugal compressor.

5. The method according to claim 1, Features: The combined centrifugal compressor uses a dual output shaft prime mover; The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving; A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine; The first gear is meshed with the main gear of the first transmission machine; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the first gear output shaft; The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving; A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine; a second gear meshing with the main gear of the second transmission machine; A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft; A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a temperature-regulating gas centrifugal compressor is arranged on the other side of the second gear output shaft.

6. The method according to claim 1, Features: The combined centrifugal compressor uses a dual output shaft prime mover; The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving; A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine; The first gear is meshed with the main gear of the first transmission machine; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; A pre-cooling air centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting air centrifugal compressor is arranged on the other side of the first gear output shaft; The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving; A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine; a second gear meshing with the main gear of the second transmission machine; A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft; A first combustion-assistant gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft.

7. The method according to claim 1, Features: The combined centrifugal compressor uses a dual output shaft prime mover; The first output shaft of the dual output shaft prime mover is connected to the input shaft of the first transmission machine for driving; A main gear of the first transmission machine is arranged on the input shaft of the first transmission machine; The first gear is meshed with the main gear of the first transmission machine; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting gas centrifugal compressor is arranged on the other side of the first gear output shaft; The second output shaft of the dual output shaft prime mover is connected to the input shaft of the second transmission machine for driving; A main gear of the second transmission machine is arranged on the input shaft of the second transmission machine; a second gear meshing with the main gear of the second transmission machine; A second gear output shaft, used to set the second gear and form one side of the second gear output shaft and the other side of the second gear output shaft; A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the second gear output shaft.

8. The method according to claim 1, Features: The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission; The input shaft of the first transmission machine is connected to the output shaft of the prime mover; A main gear, disposed on the input shaft of the first transmission machine; The first gear meshes with the main gear; The second gear meshes with the main gear; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; The second gear output shaft is used to set the second gear; A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the first gear output shaft; A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a temperature-regulating gas centrifugal compressor is arranged on the other side of the second gear output shaft.

9. The method according to claim 1, Features: The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission; The input shaft of the first transmission machine is connected to the output shaft of the prime mover; A main gear, disposed on the input shaft of the first transmission machine; The first gear meshes with the main gear; The second gear meshes with the main gear; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; The second gear output shaft is used to set the second gear; A pre-cooling air centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting air centrifugal compressor is arranged on the other side of the first gear output shaft; A first combustion-assistant gas centrifugal compressor is arranged on one side of the second gear output shaft, and a first fuel gas centrifugal compressor is arranged on the other side of the second gear output shaft.

10. The method according to claim 1, Features: The combined centrifugal compressor uses a single output shaft prime mover to drive the first transmission; The input shaft of the first transmission machine is connected to the output shaft of the prime mover; A main gear, disposed on the input shaft of the first transmission machine; The first gear meshes with the main gear; The second gear meshes with the main gear; A first gear output shaft, used to set the first gear and form one side of the first gear output shaft and the other side of the first gear output shaft; The second gear output shaft is used to set the second gear; A first fuel gas centrifugal compressor is arranged on one side of the first gear output shaft, and a temperature-adjusting gas centrifugal compressor is arranged on the other side of the first gear output shaft; A first combustion-supporting gas centrifugal compressor is arranged on one side of the second gear output shaft, and a pre-cooling gas centrifugal compressor is arranged on the other side of the second gear output shaft.

11. The method according to claim 1, Features: The first combustion-supporting gas entering the combined centrifugal compressor comes from the first combustion-supporting gas buffer tank; The operating pressure of the first combustion-supporting gas buffer tank is lower than the pressure at the outlet of the first mixer connected to the main fire channel.

12. The method according to claim 11, Features: A first combustion-supporting gas emergency interlock cut-off valve is provided on the pipeline of the first combustion-supporting gas after the boost is discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the first combustion-supporting gas emergency interlock cut-off valve is interlocked and closed; A first fuel gas emergency interlock cut-off valve is provided on the pipeline of the pressurized first fuel gas discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the first fuel gas emergency interlock cut-off valve is interlocked and closed; An emergency interlock shut-off valve for the temperature-regulating gas is provided on the pipeline for the pressurized temperature-regulating gas discharged from the combined centrifugal compressor. Once the combined centrifugal compressor loses power, the emergency interlock shut-off valve for the temperature-regulating gas is shut off by interlock.

13. The method according to claim 1, Features: The first combustion-supporting gas entering the combined centrifugal compressor comes from the first combustion-supporting gas buffer tank; The operating pressure of the first combustion-supporting gas buffer tank is lower than the pressure at the outlet of the first mixer connected to the main fire channel; An overpressure interlock cut-off valve of the first combustion-supporting gas buffer tank is arranged on the pipeline from which the first combustion-supporting gas buffer tank is discharged to the combined centrifugal compressor. Once the pressure of the first combustion-supporting gas buffer tank is higher than the pressure at the outlet of the first mixer, the overpressure interlock cut-off valve of the first combustion-supporting gas buffer tank is interlocked and closed.

14. The method according to claim 1, Features: The first combustion-supporting gas is oxygen-enriched oxygen with an oxygen volume concentration higher than 35% and a carbon dioxide volume concentration higher than 60%.

15. The method according to claim 1, Features: The air flow temperature at 300mm above the outlet of the temperature regulating air distribution channel of the low-temperature pyrolysis section is taken as the qualitative temperature of the initial gas heat carrier of the low-temperature pyrolysis section; In the stripping section, the gas flow temperature at a point 300 mm below the gas outlet of the temperature-adjusting gas distribution channel of the low-temperature pyrolysis section is taken as the qualitative temperature of the output gas of the stripping section; The temperature of the low-temperature pyrolysis semi-coke 300 mm above the outlet of the temperature-adjusting gas distribution channel of the low-temperature pyrolysis section is taken as the qualitative temperature of the low-temperature pyrolysis section; The temperature of the stripping semi-coke 300mm above the outlet of the main fire channel of the stripping section is taken as the qualitative temperature of the stripping section; The coal fed into the pyrolysis furnace is low-rank coal; In the preheating section, the temperature of the discharged preheated coal is 180-370°C; The qualitative temperature of the low-temperature pyrolysis section is 430-680°C; the qualitative temperature of the initial gas heat carrier in the low-temperature pyrolysis section is at least 200°C lower than the qualitative temperature of the output gas in the stripping section; The qualitative temperature of the stripping section is 700-1000°C, and is 100-450°C higher than the qualitative temperature of the low-temperature pyrolysis section; Each carbonization chamber is wide at the top and narrow at the bottom, with a variable cross section in the middle. The temperature-adjusting gas distribution channel and the main fire channel are arranged in the narrow cavity section below the narrowing transition section in the middle of the carbonization chamber. The volatile matter of the stripping char is at least 2.0 weight percent lower than the volatile matter of the low-temperature pyrolysis char; The volatile matter of the stripped semi-coke is less than 4.95 wt%.

16. The method according to claim 1 or 15, Features: The coal pyrolysis furnace has a semi-coke quenching section below the pre-cooling section.

17. The method according to claim 1, Features: The coal pyrolysis furnace is also provided with an external heating system. The high-temperature gas flowing through the heat transfer channel of the external heating system does not enter the furnace of the pyrolysis furnace. The heat transfer channel of the external heating system indirectly transfers heat to the furnace of the coal dry distillation zone of the pyrolysis furnace through the heat transfer wall.

18. The method according to claim 1, Features: The first fuel gas supply ratio K1, K1 is 1.5~5.

0.

19. The method according to claim 1, Features: Each centrifugal compressor is a single-stage centrifugal compressor.

20. The method according to claim 5 or 6 or 7 or 8 or 9 or 10, Features: The impeller of the first combustion-aided gas centrifugal compressor adopts an impeller with an additional extended impeller area, which reduces the overall fluid load on the integrated output shaft by increasing the area and gas pressure of the back side of the first combustion-aided gas centrifugal compressor impeller disk.

21. The method according to claim 1, Features: The prime mover is an electric motor or a turbine.

22. The method according to claim 1, Features: The connection between the output shaft of the prime mover and the rotating shaft of the centrifugal compressor impeller or the input shaft of the transmission is direct connection or connection through a coupling.

23. The method according to claim 2 or 3 or 4 or 5 or 6 or 7 or 8 or 9 or 10, Features: The main gear and pinion are helical gears; The rotation direction of the helical gear is set so that the gear load acting on the pinion in the axial direction and the fluid load acting on the corresponding output shaft in the axial direction are in opposite directions.

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