CN116592393A - Combustion equipment and gas engine - Google Patents

Abstract

The invention provides a combustion device and a gas engine, which relate to the field of aerospace technology and solve the problems of large heat load in the combustion chamber, difficult cooling, large temperature gradient at the outlet of the combustion chamber, and the like. The combustion equipment has a combustion chamber, a central air intake passage and two bending passages, each bending passage includes an air intake section and a trapped vortex section communicated with the air intake section, the trapped vortex section communicates with the combustion chamber, and the central air intake section The channel communicates with the combustion chamber through the ring area surrounded by the trapped vortex section. The combustion equipment includes the first oil inlet pipeline, the second oil inlet pipeline and the first swirl structure. The first oil inlet pipeline passes through the central air inlet passage and the The combustion chamber communicates, the first swirl structure is arranged between the outer wall of the first oil inlet pipeline and the inner wall of the central air intake passage, and the second oil inlet pipeline communicates with the air intake section. The gas engine includes: a pressure stabilizing box, the above-mentioned combustion equipment and a spraying section. The combustion chamber equipment and the gas engine provided by the invention are used in the combustion chamber.

Description

Combustion equipment and gas engine

technical field

The invention relates to the field of aerospace technology, in particular to a combustion device and a gas engine.

Background technique

Today, with the rapid development of gas turbine technology, researchers have carried out in-depth research on combustion systems, and carried out research on trapped vortex combustors (Trapped Vortex Combustor, TVC), ultra-compact combustors (Ultra-Compact Combustor, UCC) and other Extensive research work in advanced combustion technologies has resulted in combustors showing the potential to significantly exceed the performance of conventional gas turbine combustors. The trapped vortex combustor is mainly composed of a pre-combustion chamber and a main combustion chamber. The pre-combustion chamber is used to stabilize the flame, and the main combustion chamber is used to provide power.

At present, the trapped vortex combustor has the advantages of simple structure design, low emission, low lean-out boundary and good high-altitude re-ignition performance. At the same time, TVC can also be used as a Rich-Burn/Quick-Quench/Lean-Burn (RQL) burner, providing a rich-fuel ignition model for the interior of the cavity, and the flow of the mainstream air Fast blending provides a fast blending lean combustion model, and applying different models to TVC can reduce NOx emissions. Even though the trapped vortex combustor has more advantages than the traditional combustor, the trapped vortex combustor is used in the concave cavity structure of the flame tube where the trapped vortex occurs, which has the problems of large heat load and difficult cooling. Problems such as large temperature gradient at the outlet of the combustion chamber.

Contents of the invention

The object of the present invention is to provide a combustion equipment and a gas engine to solve the problems of large heat load in the combustion chamber, difficult cooling and large temperature gradient at the outlet of the combustion chamber.

In the first aspect, the present invention provides a combustion device, which has a combustion chamber, a central air intake channel and two bending channels;

Each bending passage includes an intake section and a trapped vortex section connected with the intake section, the trapped vortex section communicates with the combustion chamber, and the central air intake passage communicates with the combustion chamber through the ring area surrounded by the trapped vortex section;

The combustion equipment includes a first oil inlet pipeline, a second oil inlet pipeline and a first swirl structure, the first oil inlet pipeline communicates with the combustion chamber through the central air intake passage, and the first swirl structure is arranged on the first oil inlet pipeline. Between the outer wall and the inner wall of the central air intake passage, the second oil inlet pipeline communicates with the air intake section.

Compared with the prior art, in the combustion equipment provided by the present invention, each bending channel of the combustion equipment includes an air intake section and a trapped vortex section communicated with the air intake section, the trapped vortex section communicates with the combustion chamber, and the central air intake section The channel communicates with the combustion chamber through the inner area of the ring surrounded by the vortex section, and because the first oil inlet pipeline communicates with the combustion chamber through the central air intake passage, the first swirl structure is arranged on the outer wall of the first oil inlet pipeline and the combustion chamber. Between the inner walls of the central intake passage, therefore, when the combustion chamber is in the combustion state of the small working condition, the air enters the central intake passage and mixes with the fuel in the first oil inlet pipeline to meet the combustion chamber under the small working condition Demand, the first swirl structure rotates and entrains to continuously inhale fresh oil and gas to maintain the continuous occurrence of combustion reaction. On this basis, since the second oil inlet pipeline is connected with the air intake section, when the combustion chamber is in the combustion state of the large working condition, the air enters from the central air intake channel and each bending channel at the same time, and the air enters the bending channel It is mixed with the fuel injected in the second oil inlet pipeline to form oil gas, and each bent channel includes an air intake section and a vortex segment connected with the intake section, so that when the oil flow in the bent channel exits the bent channel, it will The vortex section forms an aerodynamic stationary vortex, and under the action of the high temperature of the flame edge burned in the central intake passage, the oil and gas in the stationary vortex section are ignited, thus meeting the needs of the combustion chamber under large working conditions.

Since each bending passage includes an intake section and a vortex section communicating with the intake section, and the vortex section communicates with the combustion chamber, when the oil and gas form an aerodynamic vortex in the vortex, it will not only change the flow rate and The flow direction will also make the air and fuel in the vortex section more evenly mixed, which will make the combustion of oil and gas in the vortex section more stable. Based on this, since the trapped vortex in the trapped vortex section can burn stably, and the trapped vortex section communicates with the combustion chamber, the stable combustion of the trapped vortex section will also make the combustion in the combustion chamber more stable. In addition, since the bent channel has a trapped vortex section that communicates with the combustion chamber, an aerodynamic trapped vortex will be formed when the oil and gas are in the trapped vortex section. Cooling, therefore, this bent channel can effectively solve the problem of large heat load and difficult cooling.

At the same time, due to the combustion in the combustion chamber, the bending channel and the central intake channel contain a large amount of heat load. When the air enters the combustion chamber through the central intake channel and each bending channel respectively, the air can The bending channel performs a brief cooling, and the heat load in the central air intake channel and each bending channel can preheat the air, so that the air and fuel can be mixed quickly, which is conducive to improving the combustion efficiency of oil and gas.

In a second aspect, the present invention provides a gas engine comprising: a pressure stabilizing box, the combustion equipment described in the first aspect above, and a spraying section.

Compared with the prior art, the beneficial effect of the gas engine provided by the present invention is the same as that of the combustion equipment described in the present invention, and will not be repeated here.

Description of drawings

Further details, features and advantages of the invention are disclosed in the following description of exemplary embodiments with reference to the accompanying drawings in which:

Fig. 1 shows a kind of structural diagram of the combustion equipment of the embodiment of the present invention;

Fig. 2 shows the schematic diagram of key design variables of the combustion chamber of the embodiment of the present invention;

Fig. 3A shows the total pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention;

Fig. 3B shows the total pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention;

Fig. 3C shows the total pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idle state of the embodiment of the present invention;

Fig. 4A shows the static pressure distribution diagram of the central symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention;

Fig. 4B shows the static pressure distribution diagram of the central symmetrical longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention;

Fig. 4C shows the static pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idle state of the embodiment of the present invention;

Fig. 5A shows the velocity vector diagram of the centrally symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention;

Fig. 5B shows the velocity vector diagram of the centrosymmetric longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention;

Fig. 5C shows the velocity vector diagram of the central symmetric longitudinal section of the combustion chamber in the idle state of the embodiment of the present invention;

Fig. 6A shows the axial velocity distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention;

Fig. 6B shows the axial velocity distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention;

Fig. 6C shows the axial velocity distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idle state of the embodiment of the present invention;

Fig. 7A shows the temperature distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention;

Fig. 7B shows the temperature distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention;

Fig. 7C shows the temperature distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idle state of the embodiment of the present invention;

Fig. 8A shows the velocity profile of the outlet section of the combustion chamber in the initial state of the embodiment of the present invention;

Fig. 8B shows the velocity distribution diagram of the outlet section of the combustion chamber in the ignition state of the embodiment of the present invention;

Fig. 8C shows the velocity distribution diagram of the outlet section of the combustion chamber in the idling state of the embodiment of the present invention;

Fig. 9A shows the temperature distribution diagram of the outlet section of the combustion chamber in the initial state of the embodiment of the present invention;

Fig. 9B shows the temperature distribution diagram of the outlet section of the combustion chamber in the ignition state of the embodiment of the present invention;

Fig. 9C shows the temperature distribution diagram of the outlet section of the combustion chamber in the idling state of the embodiment of the present invention;

Fig. 10 shows another structural diagram of the main combustion chamber scheme of the embodiment of the present invention;

Fig. 11A shows the distribution diagram of the small working condition flow field of the embodiment of the present invention;

Fig. 11B shows the distribution diagram of the flow field at the design point working condition of the embodiment of the present invention;

Fig. 12A shows the distribution diagram of the temperature field in the small working condition of the embodiment of the present invention;

Fig. 12B shows the distribution diagram of the temperature field at the design point working condition of the embodiment of the present invention;

Fig. 13 shows the distribution diagram of the instantaneous outlet temperature section of the design point of the embodiment of the present invention;

Fig. 14 shows another structural diagram of the main combustion chamber scheme of the embodiment of the present invention;

Fig. 15A shows the distribution diagram of the temperature field of the small working condition of the embodiment of the present invention;

Fig. 15B shows the distribution diagram of the temperature field in the large working condition of the embodiment of the present invention;

Fig. 16 shows the distribution diagram of the large working condition flow field of the embodiment of the present invention;

Fig. 17 shows the combustion chamber exit radial temperature distribution coefficient (RTDF) diagram of the flow field temperature field and the design point under different working conditions of the embodiment of the present invention;

Fig. 18 shows the temperature field distribution diagram of the blunt body structure of the embodiment of the present invention;

Fig. 19 shows the flow field distribution diagram of the bluff body structure of the embodiment of the present invention;

Fig. 20 shows a plan diagram of the main combustion stage oil supply of the bent channel and the pre-combustion stage fuel supply of the central air intake channel according to the embodiment of the present invention;

Fig. 21 shows the plan diagram of the oil supply for the main combustion stage and the pre-combustion stage of the central intake passage for the small bend of the bending channel according to the embodiment of the present invention;

Fig. 22 shows a plan diagram of the same oil-air ratio between the bending channel and the central air intake channel according to the embodiment of the present invention;

Fig. 23 shows the oil supply scheme diagram of the small bend inlet of the bent channel according to the embodiment of the present invention;

Fig. 24 shows the form diagram of the direct coupling flame flow field between the trapped vortex section and the combustion chamber without the isolation section of the embodiment of the present invention;

Fig. 25 shows the high oil-gas ratio morphology of the flame flow field directly coupled with the short isolation section and the combustion chamber in the embodiment of the present invention;

Fig. 26 shows the form diagram of the small oil-gas ratio flame flow field directly coupled between the trapped vortex section and the combustion chamber without the isolation section of the embodiment of the present invention.

Reference signs:

101-combustion chamber, 102-central air intake channel, 103-bending channel, 104-first oil inlet pipeline, 105-second oil inlet pipeline, 106-first swirl structure, 107-outer shell, 108-folding Bending plate, 109-inner casing, 110-the third oil inlet pipeline.

Detailed ways

In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention clearer, the present invention will be further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described here are only used to explain the present invention, not to limit the present invention.

It should be noted that when an element is referred to as being “fixed” or “disposed on” another element, it may be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or indirectly connected to the other element.

In addition, the terms "first" and "second" are used for descriptive purposes only, and cannot be interpreted as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features. Thus, a feature defined as "first" and "second" may explicitly or implicitly include one or more of these features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined. "Several" means one or more than one, unless otherwise clearly and specifically defined.

In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "front", "rear", "left", "right" etc. are based on those shown in the accompanying drawings. Orientation or positional relationship is only for the convenience of describing the present invention and simplifying the description, and does not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of the present invention.

In the description of the present invention, it should be noted that unless otherwise specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection. Connection, or integral connection; can be mechanical connection or electrical connection; can be direct connection or indirect connection through an intermediary, and can be the internal communication of two elements or the interaction relationship between two elements. Those of ordinary skill in the art can understand the specific meanings of the above terms in the present invention according to specific situations.

In an aviation gas turbine engine, the main combustion chamber, as the "core" of the aero-engine consisting of "compressor-combustor-turbine", is responsible for converting the chemical energy of fuel into heat energy under the condition of high-speed gas-liquid two-phase complex turbulent flow , so as to meet the requirements of the Brayton cycle. The above-mentioned main combustion chamber can directly affect the front temperature, thrust, fuel consumption rate and working life of the engine turbine, so the core technology research work related to the main combustion chamber has important value and significance. At present, the combustion efficiency of the main combustion chamber of an aero-engine is close to 100%, the temperature of the combustion chamber can reach 1100K-1200K, and the maximum outlet temperature can reach above 2200K. , the current design of the main combustion chamber still needs to be improved and optimized.

Today, with the rapid development of gas turbine technology, researchers have carried out in-depth research on combustion systems, and carried out a lot of research work on trapped vortex combustors (TVC), ultra-compact combustors (UCC) and other advanced combustion technologies. As a result, the combustor exhibits performance potential significantly beyond that of conventional gas turbine combustors. The trapped vortex combustor (TVC) is mainly composed of a pre-combustion chamber and a main combustion chamber. The pre-combustion chamber is used to stabilize the flame, and the main combustion chamber is used to provide power.

At present, the trapped vortex combustor has the advantages of simple structure design, low emission, low lean-out boundary and good high-altitude re-ignition performance. At the same time, the TVC can also be used as a rich ignition, rapid blend and lean burn (RQL) burner, providing a rich ignition model for the interior of the cavity, and a rapid blend with the mainstream air to provide a rapid blend lean combustion model , applying different models to TVC can reduce NOx emissions. Even though the trapped vortex combustor has more advantages than the traditional combustor, the trapped vortex combustor is used in the concave cavity structure of the flame tube where the trapped vortex occurs, which has the problems of large heat load and difficult cooling. Problems such as large temperature gradient at the outlet of the combustion chamber.

Based on the above problems, the present invention provides a combustion chamber device and a gas engine to solve the problems of large heat load in the combustion chamber, difficult cooling and large temperature gradient at the outlet of the combustion chamber.

Fig. 1 shows a kind of structural diagram of the combustion equipment of the embodiment of the present invention, as shown in Fig. 1, the combustion equipment of the embodiment of the present invention has a combustion chamber 101, a central air intake passage 102 and two bending passages 103; A bending channel 103 includes an intake section and a vortex section communicating with the intake section, the vortex section communicates with the combustion chamber, and the central intake passage 102 communicates with the combustion chamber through the ring area surrounded by the vortex section, and the combustion chamber is connected to the combustion chamber. The equipment includes a first oil inlet pipeline 104, a second oil inlet pipeline 105 and a first swirl structure 106. The first oil inlet pipeline 104 communicates with the combustion chamber 101 through the central air intake passage 102, and the first swirl structure 106 is located at Between the outer wall of the first oil inlet pipeline 104 and the inner wall of the central air intake passage 102 , the second oil inlet pipeline 105 communicates with the air intake section.

In practical application, the combustion chamber is designed according to the design point parameters of the combustion chamber in Table 1 and the design variable table and their interrelationships in Table 2, forming a schematic diagram of the key design variables of the combustion chamber as shown in Figure 2.

Table 1 Combustion chamber design point parameters

status point air flow Pressure ratio T3 T4 oil gas ratio ignition 0.1058kg/s 1.3 300K 400K 0.005 idle speed 0.2117kg/s 3 450K 1000K 0.015 design point 0.3024kg/s 8 700K 1500K 0.03

Select the combustion chamber design points in Table 1 as the initial design constraints, and take the aspect ratio not greater than 1.2 and the total length of the combustion chamber not exceeding 200 mm as the geometric constraints to start the design of the single-head combustion chamber intake scheme, and generate initial parameters as shown in Table 2:

Table 2 Design variables and their relationship

Based on the above initial parameters, the flow distribution law and total pressure loss of the combustion chamber are studied, and the main combustion chamber scheme is initially iteratively generated to form a structural diagram of the combustion equipment as shown in Figure 1.

As shown in Figure 1, the combustion equipment has a combustion chamber 101, a central air intake passage 102 and two bending passages 103, the air enters the combustion chamber 101 through the central air intake passage 102 and the two bending passages 103 respectively, and due to The first oil inlet pipeline 104 communicates with the combustion chamber 101 through the central air intake passage 102, and the first swirl structure 106 is arranged between the outer wall of the first oil inlet pipeline 104 and the inner wall of the central air intake passage 102, therefore, in the combustion When the chamber is in the combustion state of the small working condition, the air enters the central air intake channel and is mixed with the fuel in the first oil inlet pipeline to meet the needs of the combustion chamber under the small working condition, and the first swirl structure rotates and entrains to continuously inhale fresh air Oil and gas sustain the combustion reaction to continue to occur. On this basis, since the second oil inlet pipeline 105 communicates with the intake section, when the combustion chamber 101 is in the combustion state of a large working condition, air enters from the central intake passage 102 and each bending passage 103 at the same time, and the air enters After the bent channel 103 is mixed with the fuel injected from the second oil inlet pipeline 105 to form oil and gas, and each bent channel 103 includes an air intake section and a vortex segment communicating with the intake section, so that the oil and gas in the bent channel When flowing out of the bending channel, an aerodynamic trapped vortex is formed in the trapped vortex section. Under the high temperature of the flame edge burned in the central intake channel, the oil and gas in the trapped vortex section are ignited, thus meeting the combustion chamber requirements under large working conditions.

Since each bending passage includes an intake section and a vortex section communicating with the intake section, and the vortex section communicates with the combustion chamber, when the oil and gas form an aerodynamic vortex in the vortex, it will not only change the flow rate and The flow direction will also make the air and fuel in the vortex section more evenly mixed, which will make the combustion of oil and gas in the vortex section more stable. Based on this, since the trapped vortex in the trapped vortex section can burn stably, and the trapped vortex section communicates with the combustion chamber, the stable combustion of the trapped vortex section will also make the combustion in the combustion chamber more stable. In addition, since the bent channel has a trapped vortex section that communicates with the combustion chamber, an aerodynamic trapped vortex will be formed when the oil and gas are in the trapped vortex section. Cooling, therefore, this bent channel can effectively solve the problem of large heat load and difficult cooling.

At the same time, due to the combustion in the combustion chamber, the bending channel and the central intake channel contain a large amount of heat load. When the air enters the combustion chamber through the central intake channel and each bending channel respectively, the air can The bending channel performs a brief cooling, and the heat load in the central air intake channel and each bending channel can preheat the air, so that the air and fuel can be mixed quickly, which is conducive to improving the combustion efficiency of oil and gas.

In an optional way, as shown in Figure 2, the height of the air intake section along the direction of the central air intake channel decreases sequentially, and when the air enters the bending channel, the air intake section follows the direction of the central air intake channel The height of the air intake section decreases successively. Here, the height of the direction of the central air intake channel can be understood as the radial dimension of the air intake section decreases successively. As the air flowing into the bending channel changes in the radial direction, the flow will The air velocity passing through the radial section is accelerated. When the air velocity is increased, the fuel molecules ejected from the second oil inlet pipeline can be sheared, so that the air and the fuel molecules ejected from the second oil inlet pipeline can be mixed more evenly.

In an optional way, the trapped vortex section is located in the ring area surrounded by the intake section and the central intake passage. Due to the bending structure of the bending passage, the sudden expansion deceleration and flow conversion of the mixed oil and gas at the outlet direction, so that the air flowing out of the bending channel forms a stationary vortex in the stationary vortex section. After the oil gas stabilizes the flow rate in the stationary vortex section, it enters the combustion chamber, and finally plays a role of stabilizing combustion in the combustion chamber.

In an optional manner, the combustion equipment further includes an outer shell, an inner shell, and a bent plate, a part of the inner shell extends into the outer shell, and the bent plate extends from the inside of the outer shell to the inside of the inner shell, The inner casing forms a combustion chamber, and the outer casing, the bending plate and the part of the inner casing extending into the outer casing form a bending passage in a bending direction.

In practical applications, part of the inner shell extends into the outer shell, and the bent plate extends from the inside of the outer shell to the inside of the inner shell. It can be understood that the bent half here can be a U-shaped structure. The bent plate may also be a bent plate of other structural forms, which is not specifically limited here. When the air enters the bending channel, since the bending plate extends from the inside of the outer casing to the inside of the inner casing in the same direction, it will have different changes in the flow direction and flow velocity of the air, and the flow velocity and flow direction of the air are different. This will lead to changes in the combustion steady state in the combustion chamber.

In an optional manner, the oil injection port of the second oil inlet pipeline is formed on the outer casing, and there is a gap between the end of the outer casing and the inner wall of the outer casing. Fuel is sprayed out from the fuel injection port of the second oil inlet pipeline on the upper body, and there is a gap between the end of the outer casing and the inner wall of the outer casing, so that the fuel is mixed with air in the gap, and the finally formed oil gas is then bent The channel flows out and enters the combustion chamber for combustion.

In another optional way, the oil injection port of the second oil inlet pipeline is formed at the end of the bent plate located at the outer casing, and there is a gap between the end of the outer casing and the inner wall of the outer casing, when the air enters the bent When channeling, fuel is sprayed out from the fuel injection port of the second fuel inlet line formed at the end of the bent plate at the end of the outer shell, and there is a gap between the end of the outer shell and the inner wall of the outer shell, so that the fuel is in the air in the gap The oil and gas finally formed flow out from the bending channel and enter the combustion chamber for combustion.

In an optional manner, the air intake section includes a first air intake section and a second air intake section, the first air intake section communicates with the second air intake section through a gap, and the bent plate forms a first air intake section with the inner wall of the outer casing. In the air intake section, the part where the inner shell extends into the outer shell and the bent plate form a second air intake section and a trapped vortex section, both of which are in communication with the combustion chamber.

During specific implementation, as shown in Figure 1, the bent plate 108 extends from the inside of the outer shell 107 to the inside of the inner shell 109, and the bent plate 108 and the inner wall of the outer shell 107 form the first air intake section, because the bent plate When 108 extends into the inside of the outer shell 107, the radial dimension of the first air intake section formed between the bent plate 108 and the inner wall of the outer shell 107 gradually decreases, so that the speed of air entering the first air intake section gradually increases , quickly flowing through the air can be quickly mixed with the fuel in the gap, so that the fuel and air are mixed more evenly, and the mixed oil and gas pass through the inner shell 109 and extend into the inner part of the outer shell to form a second bending plate 108 The air intake section flows out of the bent passage, and the oil and gas flowing out of the second air intake section accelerates at the outlet of the second air intake section due to the bent structure of the bent plate 108, and the bent plate 108 guides the oil and gas at the outlet It will change the flow velocity and direction of the oil and gas flowing out of the second intake section, and finally form a trapped vortex at the outlet of the second intake section. The oil and gas can stabilize the flow velocity and flow direction in the trapped vortex section, and finally flow into the combustion at a stable flow rate. chamber, making the combustion in the combustion chamber more stable.

In addition, when the air flows through the first air intake section and the second air intake section respectively, the fast-flowing air can take away part of the heat of the first air intake section and play a cooling effect on the first air intake section. Part of the heat in the first air intake section can preheat the air, so that the air can be quickly mixed with the fuel injected from the second oil inlet pipeline, and the fuel flow formed by the blending flows into the second air intake section , the heat in the second air intake section can preheat the oil and gas molecules, so that the oil and gas entering the combustion chamber can meet the combustion conditions, avoiding the problem that the combustion chamber loses part of the heat due to the preheating of the oil and gas, and making the combustion efficiency in the combustion chamber more efficient high.

Fig. 3 A shows the total pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention, and Fig. 3B shows the total pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention , Fig. 3C shows the total pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idling mode of the embodiment of the present invention. It can be seen from Fig. 3A～Fig. The total pressure of the symmetrical longitudinal section increases gradually, and the total pressure distribution of the central symmetrical longitudinal section in the combustion chamber is uneven.

Figure 4A shows the static pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention, and Figure 4B shows the static pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention , Fig. 4C shows the static pressure distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idling mode of the embodiment of the present invention, as can be seen from Fig. The static pressure of the symmetrical longitudinal section gradually increases, and the static pressure in the combustion chamber is unevenly distributed under different working conditions. The pressure of the central air intake channel in the combustion chamber is higher than the pressure in other parts of the combustion chamber under idling conditions.

Fig. 5 A shows the velocity vector diagram of the centrosymmetric longitudinal section of the initial state combustion chamber of the embodiment of the present invention, and Fig. 5 B shows the velocity vector diagram of the centrosymmetric longitudinal section of the combustion chamber when the ignition state of the embodiment of the present invention, Fig. 5C shows the velocity vector diagram of the central symmetric longitudinal section of the combustion chamber in the idle state of the embodiment of the present invention. From Fig. 5A to Fig. 5C, it can be seen that as the combustion state in the combustion chamber changes, the center of the combustion chamber in the combustion chamber The velocity of the symmetrical longitudinal section increases gradually, and the velocity of the centrally symmetrical longitudinal section in the combustion chamber changes with different working conditions. The flow velocity at the channel and at the outlet of the combustion chamber is greater than that at other parts of the combustion chamber.

Fig. 6A shows the axial velocity distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the initial state of the embodiment of the present invention, and Fig. 6B shows the axial velocity of the centrally symmetrical longitudinal section of the combustion chamber in the ignition state of the embodiment of the present invention Distribution diagram, Fig. 6C shows the axial velocity distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idling mode state of the embodiment of the present invention, as can be seen from Fig. 6A～Fig. The axial velocity of the centrosymmetric longitudinal section of the combustion chamber in the chamber increases gradually, and the axial velocity and flow velocity of the centrosymmetric longitudinal section of the combustion chamber in the combustion chamber is unstable.

Fig. 7 A shows the temperature distribution diagram of the central symmetric longitudinal section of the initial state combustion chamber of the embodiment of the present invention, and Fig. 7 B shows the temperature distribution diagram of the central symmetric longitudinal section of the combustion chamber when the ignition state of the embodiment of the present invention is shown, Fig. 7C shows the temperature distribution diagram of the centrally symmetrical longitudinal section of the combustion chamber in the idling mode of the embodiment of the present invention. From FIGS. 7A to 7C, it can be seen that as the combustion conditions in the combustion chamber change, the center The temperature of the symmetrical longitudinal section increases gradually, and the temperature distribution of the central symmetrical longitudinal section of the combustion chamber is uneven.

Fig. 8 A shows the velocity distribution diagram of the outlet section of the combustion chamber in the initial state of the embodiment of the present invention, Fig. 8B shows the velocity distribution diagram of the outlet section of the combustion chamber in the ignition state of the embodiment of the present invention, and Fig. 8C shows The velocity distribution diagram of the outlet section of the combustion chamber in the idling state of the embodiment of the present invention can be seen from Figures 8A to 8C, as the combustion conditions in the combustion chamber change, the velocity of the outlet section of the combustion chamber in the combustion chamber gradually increases , no matter what state the outlet section is in, the velocity of the outlet section will show the phenomenon that the middle velocity is low and the outer velocity is high, and the velocity of the outlet section of the combustion chamber is unstable.

Fig. 9A shows the temperature distribution diagram of the outlet section of the combustion chamber in the initial state of the embodiment of the present invention, Fig. 9B shows the temperature distribution diagram of the outlet section of the combustion chamber in the ignition state of the embodiment of the present invention, and Fig. 9C shows The temperature distribution diagram of the outlet section of the combustion chamber in the idling state of the embodiment of the present invention can be seen from Fig. 9A to Fig. 9C. With the change of the combustion state in the combustion chamber, the temperature distribution of the outlet section of the combustion chamber is in the ignition state. uneven.

From Figure 3A to Figure 9C, it can be seen that with the change of the combustion state of the combustion chamber, the position of the second oil inlet pipeline in the combustion chamber is unreasonable, and the fuel in the second oil inlet pipeline cannot make full use of the advantages of the bending channel. At the same time, the unreasonable design of the first oil inlet pipeline makes the fuel transportation structure and design more difficult, and the intake matching of the swirl structure is difficult. Based on the above problems, another structural diagram of the main combustion chamber scheme is generated on the basis of one version of the main combustion chamber scheme, forming another structural diagram of the main combustion chamber scheme as shown in FIG. 10 .

In view of the unreasonable position of the second oil inlet pipeline in the combustion chamber, the fuel injection port of the second oil inlet pipeline is formed on the end of the bending plate located at the outer shell, and the high-speed and high-centrifugal force of the small curvature turning process is used when the air enters the bending channel The stretching and shearing effect on fuel oil strengthens the atomization and mixing of oil and gas. At the same time, a plurality of turbulence structures are added to the second air intake section. When the oil and gas flow into the second air intake section, due to the shearing and stretching of the oil and gas by the turbulence structures, the mixing of oil and gas can be strengthened. At the same time, the high-speed flowing oil and gas will also take away part of the heat in the second air intake section, which can cool the second air intake section. In view of the unreasonable design of the first oil inlet pipeline, which makes the fuel transportation structure and design more difficult, and the intake matching of the swirl structure is difficult, by changing the head swirl structure to a two-stage axial swirl structure The center classification scheme can increase the stability of fuel and gas injection when the fuel is sprayed through the first fuel inlet pipeline.

In an optional way, the combustion equipment also includes a third oil inlet pipeline, which communicates with the combustion chamber through the central air intake passage. In order to reduce the difficulty of fuel transportation structure and design, the central air intake passage There is a third oil inlet line through which the fuel can enter the combustion chamber. It should be understood that the third oil inlet line here can be arranged along the axial direction of the central air intake passage, or can be arranged along the center. The radial direction of the air channel is set.

In an optional manner, the central air intake passage includes a plurality of air intake passages sheathed together, and there is a second swirl structure between two adjacent air intake passages, and the second swirl structure includes rings arranged on the corresponding The swirl teeth between the adjacent two intake passages and the swirler communicated with the third oil inlet pipeline.

In practical application, the central intake passage includes multiple intake passages nested together, when the air enters the combustion chamber along the multiple intake passages, there is a second swirl structure between two adjacent intake passages , the second swirl structure can generate a strong swirl to the air entering the combustion chamber, and the rotation of the swirl teeth rings arranged between two adjacent intake passages can generate a strong swirl, and the strong swirl can change the flow rate of the air and At the same time, after the air is fully mixed with the fuel injected from the first oil inlet pipeline, the mixed fuel gas enters the combustion chamber to burn more efficiently, and at the same time, the third oil inlet pipeline can provide fresh fuel gas to the combustion chamber, Under the action of the swirler, the fuel sprayed from the third oil inlet pipeline is mixed with the air. When the swirl tooth rotates to generate a strong swirl, it will entrain the surrounding air to form a recirculation area, and use the entrainment effect of the recirculation area to continuously inhale. The fresh oil and gas provided by the third oil inlet pipeline maintains the continuous occurrence of the combustion reaction, making the combustion in the combustion chamber more stable. The needs of the combustion chamber can only be met when the chamber is supplied with oil and gas.

In another optional way, the central air intake passage includes a plurality of air intake passages sheathed together, and there is a second swirl structure between two adjacent air intake passages, and the second swirl structure includes a The swirl teeth between two adjacent intake passages, or the second swirl structure includes a swirl connected to the third oil inlet pipeline. Here, it should be understood that the second swirl structure can be located between two adjacent The swirl teeth between the intake passages can also be swirlers connected to the third oil inlet pipeline. This second swirl structure is suitable for combustion under small working conditions. When the oil is sprayed from the first oil inlet pipeline or When the oil is sprayed from the third oil pipeline, the second swirl structure will make the fuel and air mix evenly. This combustion method is suitable for combustion in small working conditions, and only one of the methods can be used to realize the combustion to the combustion chamber. Oil and gas supply.

According to another structural diagram of the improved main combustion chamber scheme shown in Figure 10, the idle speed and design point working conditions of the main combustion chamber scheme are studied.

Fig. 11A shows the distribution diagram of the small working condition flow field of the embodiment of the present invention, and Fig. 11B shows the distribution diagram of the design point working condition flow field of the embodiment of the present invention. It can be seen from Fig. 11A to Fig. 11B that, with The flow rate of the oil and gas flowing out from the vortex section of the bending channel is greater than that of the oil and gas flowing out from the central air intake channel, and the flow rate of the oil and gas in the combustion chamber is stable.

Fig. 12A shows the distribution diagram of the temperature field of the small working condition of the embodiment of the present invention, and Fig. 12B shows the distribution diagram of the temperature field of the design point working condition of the embodiment of the present invention. It can be seen from Fig. 12A to Fig. 12B that as the working Due to the change of conditions, the temperature in the bending channel is higher than the temperature in the combustion chamber, and the temperature at the stationary vortex section is higher than the temperature in the bending channel, making the temperature distribution in the combustion chamber uneven.

Fig. 13 shows the distribution diagram of the instantaneous outlet temperature section of the design point of the embodiment of the present invention. It can be seen from Fig. 13 that with the change of different working conditions, the temperature in the combustion chamber is low at both ends and high in the middle, and At this time, the temperature distribution of the design point is uneven, which cannot meet the demand of the instantaneous outlet temperature of the design point.

From Figures 11A to 13, it can be seen that with the change of the combustion conditions of the combustion chamber, the central grading strategy adopted for the central intake channel of the combustion chamber has no significant impact on the performance of the combustion chamber in this scheme, and it will also increase the difficulty of design matching. The cross-section uniformity of the instantaneous outlet temperature at the design point does not meet the requirements of the instantaneous outlet temperature at the design point. Based on the above problems, the combustion chamber is improved to form another structural diagram of the main combustion chamber scheme of the embodiment of the present invention as shown in FIG. 14 .

In view of the problem in another structural diagram of the main combustion chamber scheme of the embodiment of the present invention in Figure 10, the multi-stage central air intake channel is changed to a single-stage central air intake channel, and the radial size of the central air intake channel is reduced after the improvement , the intake air volume of the central intake channel can be indirectly controlled within 10% of the total flow into the combustion chamber, and finally the cross-sectional uniformity of the instantaneous outlet temperature at the design point meets the requirements of the instantaneous outlet temperature at the design point.

Fig. 15A shows the distribution diagram of the temperature field in the small working condition of the embodiment of the present invention, and Fig. 15B shows the distribution diagram of the temperature field in the large working condition of the embodiment of the present invention. It can be seen from Fig. 15A to Fig. 15B that with different working conditions The temperature in the combustion chamber rises with the change of different working conditions. At the same time, the temperature in the combustion chamber is higher near the bending channel under small working conditions, and the temperature of the stationary vortex section is higher than that of other parts. , when the combustion working condition is converted to a large working condition, the temperature distribution in the two bending channels is uniform, and the temperature of the part near the central air intake channel in the combustion chamber is higher than the temperature of other parts in the combustion chamber, and the temperature of other parts in the combustion chamber The temperature distribution is even.

Figure 16 shows the distribution diagram of the large working condition flow field of the embodiment of the present invention. As shown in Figure 16, when the air enters the combustion chamber through the central air intake channel and the two bent channels, it flows in along the bent channels After the air is mixed with the fuel in the gap, it flows into the combustion chamber through the turbulence structure. The oil gas flow rate when it flows out of the combustion chamber is faster than that of the first intake section, and the oil gas flow out of the second intake section is formed in the vortex section. The stagnant vortex, as shown in Figure 16, the oil and gas in the inner layer of the stagnant vortex entrains the outer layer of oil and gas flowing into the combustion chamber, so that the oil and gas change the flow velocity and direction at the stagnant vortex. Oil and gas flow into the combustion chamber at a steady flow rate.

Fig. 17 shows the combustion chamber exit radial temperature distribution coefficient (RTDF) figure of the flow field temperature field and the design point under different working conditions of the embodiment of the present invention, it should be understood that the combustion chamber exit radial temperature distribution coefficient is the combustion chamber exit The total temperature of each point on the same radius of the cross-section, the ratio of the difference between the maximum average radial total temperature and the average total temperature at the outlet obtained after taking the arithmetic mean value in the circumferential direction, and the rise in the combustion room needs to be determined by the maximum heat load in the combustion chamber, It is determined when the average outlet temperature is the highest. It can be seen from Figure 17 that as the heat load in the combustion chamber increases, the radial temperature distribution coefficient of the combustion chamber outlet increases gradually. With the increase of the radial temperature distribution coefficient of the combustion chamber outlet, Effectively ensure the uniform heating in the combustion chamber.

In order to resist the impact of the air entering the central air intake passage on the combustion chamber, a blunt body is also provided at the position of the central air intake passage. It should be understood that the blunt body here can be a gas-permeable partition, and the partition There is a through hole for the first oil inlet pipeline. The blunt body can also be a deflector with an arc structure. The deflector panel can guide the air, and when the air flows into the central air intake passage, it can be evenly mixed with the fuel sprayed out of the first oil inlet pipeline, and the evenly mixed fuel gas can flow into the combustion chamber stably without damaging The combustion state of the combustion chamber is disturbed.

Fig. 18 shows the temperature field distribution diagram of the blunt body structure of the embodiment of the present invention, and Fig. 19 shows the flow field distribution diagram of the blunt body structure of the embodiment of the present invention, as can be seen from 18 to Fig. 19, in the central air inlet channel When a bluff body is provided at the entrance of the bluff body, since the bluff body can guide the air that quickly flows into the central air intake channel, the air can pass through the bluff body stably without disturbing the combustion state of the combustion chamber. Therefore, Only then will the temperature distribution in Figure 18 be uniform and the flow rate in Figure 19 more stable.

Based on the above description of the combustion chamber, the design parameters of the single head test piece of the combustion chamber are finally determined, as shown in Table 3:

Table 3 Combustion chamber design variables and their relationship

After determining the combustion design parameters of the combustion chamber, the fuel injection position of the first oil inlet pipeline, the fuel injection position of the second oil inlet pipeline and the fuel injection position of the third oil inlet pipeline are determined at the same time. Figure 20 shows the The plan diagram of the oil supply of the main combustion stage of the large bend of the bending channel and the fuel supply of the pre-combustion stage of the central air intake channel of the embodiment of the invention. Diagram of the oil supply scheme for the pre-combustion stage of the air channel, Figure 22 shows the scheme diagram of the same oil-gas ratio of the bent channel and the central intake channel in the embodiment of the present invention, Figure 23 shows the small bend inlet of the bent channel in the embodiment of the present invention The fuel supply scheme diagram, as can be seen from Figures 20 to 23, the central air intake channel in the combustion chamber can work independently to organize combustion, and can also form a coupled flame through the mutual diffusion and mixing of oil and gas mixtures, and combine the oil and gas ejected from the bending channel Tissue burning.

The fuel injection point of the combustion chamber, the fuel-air ratio of the bending channel and the fuel-gas ratio of the central intake channel are the key factors affecting the outlet temperature and combustion efficiency of the flame tube, and the injection point is close to the first intake section of the bending channel. The position can obtain better combustion efficiency, and the position close to the second air intake section can obtain better combustion stability performance. The outlet temperature distribution of the combustion chamber that meets the requirements of different tasks can also be obtained by adjusting the oil-air ratio of the bending channel and the central intake channel.

In order to ensure that oil and gas can flow into the combustion chamber more stably in the stationary vortex section, an isolation section is provided in the stationary vortex section. It should be understood that the above-mentioned isolation section can be a high temperature resistant temperature insulation plate. Figure 24 shows an embodiment of the present invention Fig. 25 shows the form diagram of flame flow field with short isolation section and direct coupling flame flow field between the vortex section and the combustion chamber of the embodiment of the present invention, Fig. 26 It shows the small oil-gas ratio morphological diagram of the direct coupling flame flow field between the stationary vortex section and the combustion chamber without the isolation section of the embodiment of the present invention. It can be seen from Fig. 24 to Fig. 26 that by adjusting the length of the isolation section, the stationary vortex section and the center can be realized. The adjustment of the intake section can meet the combustion requirements of the combustion chamber under different working conditions by adjusting the length of the isolation section of the trapped vortex section.

The present invention provides a gas engine comprising: a pressure stabilizing box, the combustion equipment described in the first aspect above, and a spraying section.

Compared with the prior art, the beneficial effect of the gas engine provided by the present invention is the same as that of the combustion equipment described in the present invention, and will not be repeated here.

Claims (10)

1. A combustion device, characterized in that, the combustion device has a combustion chamber, a central air intake passage and two bending passages; Each of the bent passages includes an air intake section and a trapped vortex section communicated with the air intake section, the trapped vortex section communicates with the combustion chamber, and the central air intake passage passes through the trapped vortex section The formed ring area communicates with the combustion chamber; The combustion equipment includes a first oil inlet pipeline, a second oil inlet pipeline and a first swirl structure, the first oil inlet pipeline communicates with the combustion chamber through the central intake passage, and the first swirl structure The flow structure is arranged between the outer wall of the first oil inlet pipeline and the inner wall of the central air intake passage, and the second oil inlet pipeline communicates with the air intake section. 2. The combustion equipment according to claim 1, characterized in that, the height of the air intake section along the direction of the central air intake channel decreases successively. 3 . The combustion equipment according to claim 1 , wherein the trapped vortex section is located in an inner area of a ring surrounded by the air intake section and the central air intake passage. 4 . 4. The combustion equipment according to claim 1, characterized in that, the combustion equipment further comprises an outer casing, an inner casing and a bent plate, part of the inner casing extends into the outer casing, and the a bent plate extending from the interior of the outer shell to the interior of the inner shell, the inner shell forming a combustion chamber, the outer shell, the bent plate and the inner shell protruding into the outer shell The part inside the body encloses the bending passage in the bending direction. 5. The combustion equipment according to claim 4, characterized in that, the fuel injection port of the second oil inlet pipeline is formed on the outer casing; or, The oil injection port of the second oil inlet pipeline is formed at the end of the bent plate located at the outer casing; There is a gap between the end of the outer shell and the inner wall of the outer shell. 6. The combustion equipment according to claim 5, wherein the intake section comprises a first intake section and a second intake section, and the first intake section and the second intake section pass through The gaps are connected. 7. The combustion equipment according to claim 6, wherein the bent plate and the inner wall of the outer shell form the first air intake section, and the inner shell extends into the inner wall of the outer shell. The part and the bent plate form a second air intake section and a trapped vortex section, and both the second air intake section and the trapped vortex section communicate with the combustion chamber. 8. The combustion equipment according to claim 1, characterized in that, the combustion equipment further comprises a plurality of turbulence structures located in the second air intake section, each of the turbulence structures along the second air intake section Intake direction distribution of segments; and/or, The combustion equipment also includes a third oil inlet pipeline, which communicates with the combustion chamber through the central air intake passage. 9. The combustion equipment according to any one of claims 1-8, characterized in that, the central air intake passage includes a plurality of air intake passages sleeved together, and the space between two adjacent air intake passages is Has a second swirl structure; The second swirl structure includes swirl teeth rings arranged between two adjacent inlet passages; and/or The second swirl structure includes a swirler communicated with the third oil inlet pipeline. 10. A gas engine, characterized by comprising: a pressure stabilizing box, the combustion equipment according to any one of claims 1-9, and a spraying section.