Gasification pressure regulating device and control method thereof

Abstract

The application discloses a kind of gasification pressure regulating device and control method thereof, belong to automobile gas supply system technical field.The shell of the device is sequentially arranged with first gasification cavity, liquid cooling cavity and second gasification cavity along height direction, liquid cooling cavity is between two gasification cavities and is fluidly isolated and heat conduction connection with two thereof;Liquefied gas inlet and gas outlet are provided on the shell, and a communication passage is provided in the shell to communicate the two gasification cavities, and an adjustable valve for adjusting gas flow is provided on the communication passage.Liquid fuel gas sequentially flows through first gasification cavity, communication passage and second gasification cavity, and is indirectly heat-exchanged with the cooling liquid in the liquid cooling cavity throughout the process to be gasified;The control method limits the maximum opening of the adjustable valve in stages according to the cooling liquid temperature.The application has long heat exchange path, sufficient gasification and compact structure, and can avoid liquid fuel gas entering the engine during cold start.

Description

Technical Field

[0001] This invention belongs to the technical field of automotive gas supply systems, specifically relating to a gasification pressure regulating device and its control method. Background Technology

[0002] With the adjustment of energy structure and increasingly stringent emission regulations, vehicles using liquefied natural gas (LPG) and other liquefied fuels (including "oil-to-gas" vehicles that have been retrofitted with gas supply systems) have been widely used. The vaporization pressure regulating device is the core component of the gas supply system. Its function is to reduce the pressure of the high-pressure liquefied gas stored in the gas cylinder and heat it to vaporize it, supplying gaseous gas to the engine at a stable pressure and flow rate.

[0003] Existing vaporization pressure regulating devices mostly employ a combination structure of a spring diaphragm pressure regulating mechanism and a single-stage hydrothermal vaporization chamber: high-pressure liquefied gas enters a single vaporization chamber after being depressurized by a throttle valve. The chamber wall is in close contact with the coolant passage of the engine for heat exchange. After a single-pass flow within the vaporization chamber, the gas is regulated and output by the diaphragm pressure regulating mechanism. In this type of structure, the flow path of the gas from the inlet to the outlet is relatively short, and the heat exchange area with the heat source is limited, generally resulting in incomplete vaporization. Especially under cold start conditions in winter, when the engine coolant temperature is close to ambient temperature and the heat source supply is severely insufficient, the liquefied gas enters the engine without sufficient vaporization, easily causing problems such as an overly rich air-fuel mixture, difficulty starting, cylinder flooding, knocking, and erosion of the cylinder wall lubricating oil film, damaging the engine.

[0004] Furthermore, some existing technologies, in order to improve integration, form the connecting channel between the upper and lower vaporization chambers inside the shell sidewall. While this type of built-in sidewall channel eliminates the need for external piping, it suffers from the following coupling defects:

[0005] Under cold conditions, the sidewall metal becomes an external cold bridge. The liquid gas in the downward channel is pre-cooled before reaching the lower vaporization chamber, resulting in an earlier flash point in the lower layer, abnormal gas content in the gas and liquid phases, and imbalance in primary vaporization. The upward channel and the liquid cooling chamber are only adjacent through the wall, and the heat transfer capacity is limited. The two-phase medium continues to lose temperature during the ascent, and the gas and liquid phases undergo gravity separation, forming a pulsating feed with intermittent liquid column blockage and gas mass breakthrough. Therefore, the upper vaporization chamber does not receive a uniform two-phase flow, but rather a low-temperature, high-liquid-content, pulsating discrete feed.

[0006] Within a labyrinthine flow channel with a fixed cross-section, the volume expansion of the gas and liquid phases cannot match the flow channel cross-section, resulting in both a low-speed liquid accumulation zone and a high-speed droplet entrainment zone. When the gas converges towards the central pressure regulating valve port, residual droplets directly impact the valve port sealing surface and undergo secondary condensation in the valve port area far from the heat source, causing the diaphragm to harden at low temperatures and the sealing surface to become condensed. Simultaneously, the pulsating flow distorts the pressure signal received by the pressure regulating diaphragm, triggering positive feedback oscillations in the valve port opening and causing output pressure fluctuations.

[0007] The aforementioned defects are particularly prominent in vehicles converted from gasoline to natural gas, because the aftermarket system lacks an independent preheating device. During cold starts, the coolant temperature is close to the ambient temperature, and the vibrations during vehicle operation further exacerbate the instability of the gas-liquid interface and the sloshing of the liquid column. Summary of the Invention

[0008] To address the technical problems in existing technologies, such as insufficient vaporization of liquefied gas, pressure loss and heat dissipation during gas transfer between functional chambers, and easy entry of liquefied gas into the engine under cold start conditions, this invention provides a vaporization pressure regulating device and its control method.

[0009] The technical solution adopted in this invention is as follows:

[0010] A vaporization pressure regulating device includes a housing. A first vaporization chamber, a liquid-cooled chamber, and a second vaporization chamber are sequentially arranged along the height direction within the housing. The liquid-cooled chamber is located between the first and second vaporization chambers. Both the first and second vaporization chambers are fluidly isolated from the liquid-cooled chamber but thermally connected. The housing has a liquefied gas inlet and a gas outlet. The liquefied gas inlet communicates with the first vaporization chamber, and the gas outlet communicates with the second vaporization chamber. A communication channel connecting the first and second vaporization chambers is provided within the housing. An adjustable valve is also provided on the housing for regulating the flow rate of the fuel gas flowing into the second vaporization chamber from the communication channel.

[0011] Furthermore, a downstream channel is formed within the first vaporization chamber, and the downstream channel is a meandering and extending channel; the liquefied gas inlet is connected to the starting end of the downstream channel, and the connecting channel is connected to the ending end of the downstream channel.

[0012] Furthermore, the connecting channel includes a first channel and a second channel that are interconnected. Both the first channel and the second channel are arranged adjacent to the liquid cooling cavity and are fluidly isolated from the liquid cooling cavity. One end of the second channel is connected to the end of the lower flow channel, and the other end of the second channel is connected to one end of the first channel. The other end of the first channel forms an opening leading to the second vaporization cavity, and the adjustable valve is used to adjust the cross-sectional area of ​​the opening.

[0013] Furthermore, an inner vaporization channel and an outer vaporization channel are formed within the second vaporization chamber. The opening of the first channel leads to the inner vaporization channel, and the inner vaporization channel is connected to the outer vaporization channel. The gas outlet is connected to the outer vaporization channel.

[0014] Furthermore, the housing includes a top cover, a vaporization section, a liquid cooling section, and a bottom cover; the vaporization section is superimposed on one side of the liquid cooling section, the inner vaporization channel and the outer vaporization channel are formed on the surface of the vaporization section facing the liquid cooling section, and the top cover is provided on the side of the vaporization section facing away from the liquid cooling section; a liquid cooling groove is formed on the surface of the liquid cooling section facing the vaporization section, and the liquid cooling groove constitutes the liquid cooling cavity; a lower flow channel is formed on the surface of the liquid cooling section facing away from the vaporization section, and the bottom cover is sealed on this surface of the liquid cooling section; the surfaces of the vaporization section and the liquid cooling section in contact with each other constitute a heat-conducting partition.

[0015] Furthermore, an annular sealing ring is provided on the outer ring of the surfaces of the vaporization section and the liquid cooling section that are in contact with each other.

[0016] Furthermore, a partition is provided inside the liquid cooling tank, which divides the liquid cooling tank into a series-connected flow channel area; an inlet and a coolant pipe communicating with the liquid cooling tank are provided on the same side wall of the liquid cooling part, and the coolant enters the liquid cooling tank from the inlet, flows through the entire flow channel area and then flows out from the coolant pipe.

[0017] Furthermore, the housing is an integral structure, with the first vaporization chamber, the liquid cooling chamber, the second vaporization chamber, and the connecting channel all integrally formed inside the housing.

[0018] Furthermore, the adjustable valve includes a valve core and an operating end that is throttledly connected to the valve core; the valve core is disposed corresponding to the opening, and the operating end penetrates the housing and extends beyond the housing; the operating end is used to receive external pressing or turning force to drive the valve core to change the communication cross-sectional area of ​​the opening.

[0019] Furthermore, the lower flow channel is formed by staggered ribs, and the surface of the ribs is provided with heat-conducting fins; and / or, heat-conducting fins are provided on the heat-conducting wall surfaces between the first vaporization chamber and the liquid cooling chamber, and between the second vaporization chamber and the liquid cooling chamber.

[0020] On the other hand, the present invention also provides a vaporization pressure regulation control method, applied to any of the above-mentioned vaporization pressure regulation devices, the method comprising: acquiring the temperature of the coolant in the liquid cooling chamber; when the temperature of the coolant is lower than a first threshold, limiting the maximum opening of the adjustable valve to a first opening value; when the temperature of the coolant is not lower than the first threshold and is lower than a second threshold, gradually increasing the maximum opening limit of the adjustable valve as the temperature of the coolant increases according to a preset temperature-opening mapping curve; when the temperature of the coolant is not lower than the second threshold, releasing the maximum opening limit of the adjustable valve, and adjusting the opening of the adjustable valve according to the engine speed, throttle opening, or intake manifold pressure.

[0021] Furthermore, the method further includes: obtaining the gas temperature at the gas outlet; when the gas temperature is lower than a reference value corresponding to the current temperature of the coolant, and the duration exceeds a preset duration, reducing the opening of the adjustable valve until the gas temperature recovers to above the reference value; the reference value is the gas temperature value corresponding to the current temperature of the coolant in a temperature mapping table calibrated in advance through experiments.

[0022] The beneficial effects of this invention are as follows:

[0023] (1) The first vaporization chamber, the liquid cooling chamber and the second vaporization chamber are arranged sequentially along the height direction inside the shell of the present invention. The liquid gas flows through the two vaporization chambers located on both sides of the liquid cooling chamber. The heat exchange path is extended by a factor of two. The gas can exchange heat indirectly with the coolant in the liquid cooling chamber through the heat-conducting wall during the entire flow process. The vaporization is sufficient, the space utilization is high and the structure is compact.

[0024] (2) The two vaporization chambers of the present invention are connected by a connecting channel set inside the shell, eliminating the need for external pipelines and avoiding pressure loss and heat loss caused by external pipelines;

[0025] (3) The adjustable valve of the present invention directly adjusts the cross-sectional area of ​​the opening of the connecting channel to the second vaporization chamber. After the gas is throttled, it enters the second vaporization chamber to complete deep vaporization. The adjustment is convenient and the output pressure is stable.

[0026] (4) The control method of the present invention limits the maximum opening of the adjustable valve in stages according to the temperature of the coolant in the liquid cooling chamber, so that the gas supply rate matches the heat source supply capacity, and avoids the liquid gas from entering the engine without vaporization under cold start conditions, thus protecting the engine; at the same time, it can identify liquid entrainment in the output gas and actively reduce the opening to ensure the vaporization quality of the output gas.

[0027] (5) In view of the coupling chain defects caused by the built-in connecting channel in the side wall of the shell, the present invention sets an inclined guide plate, a guide notch, a buffer liquid accumulation cavity and a return hole in the second channel to make the rising two-phase flow generate swirling separation and return the liquid phase to the primary vaporization chamber for re-vaporization, which effectively suppresses the phase separation pulsation caused by thermal break in the upward channel. The various structures cooperate and work together to ensure the dryness and pressure stability of the output gas.

[0028] (6) The control method of the present invention not only limits the flow in stages according to the coolant temperature to match the heat source supply capacity, but also identifies liquid entrainment and actively intervenes by real-time monitoring of the outlet gas temperature, and identifies the upstream channel phase separation abnormality by bandpass filtering of pressure pulsation and adaptively adjusts the valve opening and PID parameters, so that the control strategy matches the specific structural failure mode of the device, and realizes closed-loop control from passive flow limiting to active diagnosis-adaptive adjustment. Attached Figure Description

[0029] Figure 1 This is a side view of the gasification pressure regulating device in its assembled state in an embodiment of the present invention;

[0030] Figure 2 This is a first isometric view of the gasification pressure regulating device in its assembled state in an embodiment of the present invention;

[0031] Figure 3 This is a top view of the gasification pressure regulating device in its assembled state in an embodiment of the present invention;

[0032] Figure 4 This is a second isometric view of the gasification pressure regulating device in its assembled state in an embodiment of the present invention;

[0033] Figure 5 This is an isometric view of the vaporization pressure regulating device after the top cover is removed in an embodiment of the present invention;

[0034] Figure 6 This is a top view of the vaporization pressure regulating device in this embodiment of the invention after the top cover has been removed;

[0035] Figure 7 This is an isometric view of the vaporization pressure regulating device in this embodiment of the invention after the top cover has been removed;

[0036] Figure 8 This is an isometric view of the liquid cooling section of the vaporization pressure regulating device in an embodiment of the present invention;

[0037] Figure 9 This is a schematic diagram of the liquid cooling section and the vaporization section of the vaporization pressure regulating device in a split state according to an embodiment of the present invention;

[0038] Figure 10 This is a schematic diagram of the bottom plan of the liquid cooling section of the vaporization pressure regulating device in an embodiment of the present invention;

[0039] Figure 11 This is an isometric view of the bottom of the liquid cooling section of the vaporization pressure regulating device in an embodiment of the present invention.

[0040] In the diagram: 1-Top cover, 2-Vaporization section, 3-Liquid cooling section, 4-Bottom cover, 5-Coolant pipe, 6-Operating end, 7-Gas outlet, 8-Liquefied gas inlet, 9-Adjustable valve, 10-Inner vaporization channel, 11-Outer vaporization channel, 12-First channel, 13-Second channel, 14-Liquid cooling tank, 15-Liquid inlet, 16-Downstream channel. Detailed Implementation

[0041] The present invention will be further explained below with reference to the accompanying drawings and specific embodiments.

[0042] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. The components of the embodiments of this application described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0043] Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely to illustrate selected embodiments of the application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application.

[0044] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0045] In the description of this application, it should be noted that the use of terms such as "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer" to indicate orientation or positional relationships is based on the orientation or positional relationships shown in the accompanying drawings, or the orientation or positional relationships commonly used when the product is in use. These terms are used solely for the convenience of describing this application and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application. Furthermore, the use of terms such as "first" and "second" in the description of this application is only used to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0046] Furthermore, the use of terms such as "horizontal" and "vertical" in the description of this application does not imply that the component is required to be absolutely horizontal or suspended, but rather that it can be slightly tilted. For example, "horizontal" simply means that its direction is more horizontal than "vertical," and does not mean that the structure must be completely horizontal, but can be slightly tilted.

[0047] In the description of this application, it should also be noted that, unless otherwise expressly specified and limited, the terms "set up," "install," "connect," and "link" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0048] Example 1:

[0049] like Figures 1 to 4 As shown, this embodiment discloses a vaporization pressure regulating device, which is generally rectangular in shape. Its shell is formed by stacking and fixing the top cover 1, the vaporization part 2, the liquid cooling part 3 and the bottom cover 4 in a vertical direction.

[0050] The top cover 1 is positioned above the vaporization section 2, which overlaps the upper side of the liquid cooling section 3. The bottom cover 4 seals the lower side of the liquid cooling section 3. Mounting holes are provided at corresponding positions of the top cover 1, vaporization section 2, liquid cooling section 3, and bottom cover 4. Each part is fixedly connected by bolts passing through the mounting holes. Alternatively, a long screw can be used to vertically pass through the top cover 1, vaporization section 2, liquid cooling section 3, and bottom cover 4 to fasten all four parts at once.

[0051] After the vaporization section 2, the liquid cooling section 3 and the bottom cover 4 are stacked, three functional cavities are arranged sequentially along the height direction inside the shell: the first vaporization cavity located on the lower side, the liquid cooling cavity located in the middle and the second vaporization cavity located on the upper side. The liquid cooling cavity is located between the two vaporization cavities. Both vaporization cavities are fluidly isolated from the liquid cooling cavity and are connected by heat conduction through the heat-conducting wall surface.

[0052] As an example, the liquid cooling section 3 has external dimensions of 120mm × 100mm × 35mm, and the vaporization section 2 and the bottom cover 4 are both 10mm thick.

[0053] like Figures 5 to 7 As shown, the vaporization section 2 is a plate-shaped component, and a recessed groove is provided on its lower surface facing the liquid cooling section 3. The groove is divided by a partition provided in the vaporization section 2 into an inner vaporization channel 10 located in the central area and an outer vaporization channel 11 arranged around the inner vaporization channel 10.

[0054] The central area of ​​the inner vaporization channel 10 is used to accommodate the valve core of the adjustable valve 9. The inner vaporization channel 10 and the outer vaporization channel 11 are connected by a through hole opened on the partition. After the gas diffuses in the inner vaporization channel 10, it flows into the outer vaporization channel 11 through the through hole. As an example, the groove depth on the lower surface of the vaporization section 2 is 6 mm, and the groove width of both the inner vaporization channel 10 and the outer vaporization channel 11 is 8 mm to 12 mm.

[0055] The cross-sectional areas of the inner vaporization channel 10 and the outer vaporization channel 11 gradually increase along the direction of gas flow. Specifically, the cross-sectional area of ​​the inner vaporization channel 10 gradually increases linearly or exponentially from its inlet, which connects to the upper opening of the first channel 12, to its through-hole, which connects to the outer vaporization channel 11; similarly, the cross-sectional area of ​​the outer vaporization channel 11 gradually increases from its through-hole, which connects to the inner vaporization channel 10, to its end, which connects to the gas outlet 7. As an example, the cross-sectional area at the inlet of the inner vaporization channel 10 is 60 mm². 2 The cross-sectional area at the outlet is 120mm². 2 The cross-sectional area at the inlet of the external vaporization duct 11 is 80 mm², and the cross-sectional area at the outlet is 160 mm². 2 The gradually increasing cross-sectional area is used to match the volume expansion of the gas-liquid two-phase medium during the endothermic vaporization process, so that the flow velocity of the gas in the inner vaporization channel 10 and the outer vaporization channel 11 is maintained in the range of 0.5 m / s to 3 m / s.

[0056] like Figure 8 As shown, the liquid cooling section 3 is a rectangular block component with a certain thickness, which is the core of the heat exchange of the entire device. A recessed liquid cooling groove 14 is formed on the upper surface of the liquid cooling section 3 facing the vaporization section 2, and the liquid cooling groove 14 constitutes the above-mentioned liquid cooling cavity.

[0057] A partition is provided inside the liquid cooling tank 14, which divides the liquid cooling tank 14 into two connected flow channel regions. On the same side wall of the liquid cooling section 3, there is a liquid inlet 15 and a coolant pipe 5 that are connected to the liquid cooling tank 14. Both the liquid inlet 15 and the coolant pipe 5 are pipe fittings with external threads and a nominal diameter of 10 mm. They are respectively connected to the beginning and end of the two flow channel regions.

[0058] Due to the obstruction of the baffle, the coolant entering from the inlet 15 can only flow completely through the entire liquid cooling tank 14 along the flow channel area before flowing out from the coolant pipe 5. That is, the coolant flows unidirectionally and in series within the liquid cooling tank 14. The lower surface of the vaporization section 2 is in direct contact with the upper surface of the liquid cooling section 3, and their contact surface forms a heat-conducting baffle. The lower surface of the vaporization section 2 also acts as a cover to seal the liquid cooling tank 14. An annular sealing groove is formed on the outer ring of the upper surface of the liquid cooling section 3, and an annular sealing ring is installed in the groove. The material of the annular sealing ring is nitrile rubber or fluororubber, and the assembly compression is 20% to 30% to prevent coolant leakage. The heat of the coolant in the liquid cooling tank 14 is conducted upward to the inner vaporization channel 10 and the outer vaporization channel 11 through this heat-conducting baffle. As an example, the depth of the liquid cooling tank 14 is 15 mm.

[0059] like Figure 10 and Figure 11As shown, the liquid cooling section 3 has a recessed lower flow channel 16 on its lower surface facing away from the vaporization section 2. The lower flow channel 16 is divided by multiple staggered ribs to form a labyrinthine meandering flow channel, so as to extend the flow path of the liquid gas and increase the contact area between the gas and the heat-conducting wall. Heat-conducting fins can also be provided on the surface of the ribs to further increase the heat exchange area.

[0060] The lower flow channel 16 constitutes the flow channel within the first vaporization chamber. The bottom cover 4 is detachably fixed to the liquid cooling section 3 by bolts and seals the lower flow channel 16. A metal-graphite composite sealing gasket is provided between the bottom cover 4 and the liquid cooling section 3. The detachable connection method facilitates the periodic removal of the bottom cover 4 to clean the impurities accumulated in the lower flow channel 16.

[0061] The heat from the coolant in the liquid cooling tank 14 is conducted downwards through the body of the liquid cooling section 3 to the lower flow channel 16. As an example, the depth of the lower flow channel 16 is 8 mm, the height of the ribs is 8 mm, and the spacing between adjacent ribs is 10 mm to 15 mm.

[0062] like Figures 5 to 7 as well as Figure 9 As shown, a liquefied gas inlet 8 is provided on the side wall of the shell. The liquefied gas inlet 8 is a pipe joint with external threads, which extends inward and connects to the starting end of the lower flow channel 16.

[0063] The interior of the liquid cooling section 3 is formed with a first channel 12 and a second channel 13 that penetrate its upper and lower surfaces. For example, the aperture of the first channel 12 and the second channel 13 is 8 mm. The first channel 12 and the second channel 13 are arranged adjacent to the liquid cooling tank 14 and are isolated from the coolant in the liquid cooling tank 14 and do not come into direct contact with each other. Heat is transferred only through the wall of the liquid cooling section 3.

[0064] The lower opening of the second channel 13 is connected to the end of the downflow channel 16, and the upper opening of the second channel 13 is connected to the lower end of the first channel 12. The first channel 12 extends upward, and its upper opening is located in the central area of ​​the inner vaporization channel 10, forming the entrance for the gas to enter the inner vaporization channel 10.

[0065] As an improvement, the inner wall of the second channel 13 is provided with 2 to 4 inclined guide vanes arranged at intervals along its circumference. The angle between the guide vanes and the axis of the second channel 13 is 25° to 35°, and the height of the guide vanes is 1 mm to 2 mm. This causes the gas-liquid two-phase flow entering the second channel 13 from the end of the lower channel 16 to generate swirling motion during the upward process. Under the action of centrifugal force, the liquid phase is thrown towards the channel wall of the second channel 13, and the gas phase is concentrated in the central area of ​​the channel and transported upward.

[0066] The second channel 13 has a guide notch at the root of the guide vane on its channel wall. The guide notch has a depth of 0.3 mm to 0.8 mm and a width of 0.5 mm to 1.2 mm, which is used to guide the liquid phase adhering to the wall downward. A buffer liquid accumulation chamber is provided at the junction of the upper end of the second channel 13 and the lower end of the first channel 12. The buffer liquid accumulation chamber is a cavity formed by the local radial expansion of the second channel 13. Its diameter is 10 mm to 14 mm, its depth is 3 mm to 5 mm, and its volume is 15% to 25% of the total volume of the second channel 13. A reflux hole is provided at the bottom of the buffer liquid accumulation chamber. The reflux hole has a diameter of 1.5 mm to 2 mm. The reflux hole extends downward and communicates with the starting section of the lower flow channel 16 or the heat exchange wall near the liquid cooling tank 14, so that the liquid phase accumulated in the buffer liquid accumulation chamber flows back to the heated area of ​​the lower flow channel 16 through the reflux hole to re-vaporize.

[0067] Gas outlet 7 is located on the side wall of the shell and is a pipe joint with external threads, which is connected to the end of the outer vaporization channel 11. Thus, after the gas enters from the liquefied gas inlet 8, it flows sequentially through the downstream channel 16, the second channel 13, the first channel 12, the inner vaporization channel 10 and the outer vaporization channel 11, and finally flows out from gas outlet 7.

[0068] In all the above-mentioned flow channels, the gas does not come into direct contact with the coolant. Instead, it exchanges heat indirectly with the coolant in the liquid cooling tank 14 through the heat-conducting wall. Since the first channel 12 and the second channel 13 are formed inside the liquid cooling section 3 and are adjacent to the liquid cooling tank 14, the gas can continue to absorb heat from the coolant during the transfer and transportation between the upper and lower cavities. No external pipeline is required, thus avoiding pressure loss and heat dissipation.

[0069] The adjustable valve 9 is an integral component, including a valve seat, a valve core, and an operating end 6 that is drivenly connected to the valve core. The valve seat is press-fitted into the valve seat hole in the central area of ​​the inner vaporization channel 10, and the valve core is installed in the valve seat and is opposite to the upper opening of the first channel 12. When the valve core moves vertically, it changes the cross-sectional area of ​​the connection between the upper opening of the first channel 12 and the inner vaporization channel 10, and the stroke of the valve core is 0 to 3 mm.

[0070] An inertial liquid-retaining ring is provided below the valve port of the adjustable valve 9. The inertial liquid-retaining ring is an annular component with an inner diameter larger than the outer diameter of the valve core, forming an annular flow channel between the inertial liquid-retaining ring and the valve core. After the gas flows out from the upper opening of the first channel 12, it undergoes a flow direction change of approximately 180° under the guidance of the inertial liquid-retaining ring before entering the valve port. Due to its greater inertia than the gas phase, the liquid droplets collide with the wall of the inertial liquid-retaining ring during the change of direction and are intercepted. A return groove is provided on the wall of the inertial liquid-retaining ring, which extends circumferentially along the inertial liquid-retaining ring and slopes downward to guide the intercepted liquid phase back into the outer vaporization channel 11.

[0071] The heat-conducting partition between the vaporization section 2 and the liquid cooling section 3 extends upward with localized heating microfins. These microfins extend into the area below the valve port of the adjustable valve 9 to supplement heat to this area and suppress secondary condensation of residual heavy components at the valve port sealing surface. The localized heating microfins have a height of 3mm to 6mm and a thickness of 1mm to 2mm, and 4 to 8 fins are evenly arranged along the circumference of the valve port.

[0072] The diaphragm of the adjustable valve 9 is located on the side of the vaporization section 2 facing away from the liquid cooling section 3 (i.e., in the space between the top cover 1 and the vaporization section 2). A heat insulation gasket is provided between the diaphragm and the second vaporization chamber. The heat insulation gasket is made of polyimide or polytetrafluoroethylene and has a thickness of 0.3mm to 0.8mm. It is fitted around the outer periphery of the operating end 6 and sandwiched between the diaphragm and the diaphragm seat. It is used to block the direct heat conduction of the low-temperature gas to the diaphragm and slow down the hardening and creep of the diaphragm under low-temperature conditions.

[0073] The housing is also equipped with a pressure sensing channel. The pressure tapping point of the pressure sensing channel is located in the gas phase stabilization zone downstream of the valve port of the adjustable valve 9. This gas phase stabilization zone is the gas gas convergence area downstream of the inertial liquid-blocking ring. Due to the interception effect of the inertial liquid-blocking ring, the liquid content in this area is extremely low, and it is in a single-phase gas phase state. The pressure sensing channel is equipped with a damping orifice with a diameter of 0.5mm to 1.5mm, which is used to filter out the high-frequency pressure pulsations transmitted to the pressure tapping point by the gas-liquid two-phase flow, so that the pressure signal received by the diaphragm is a low-frequency average pressure.

[0074] The operating end 6 is a vertically extending rod that passes through the vaporization section 2 and the top cover 1 and protrudes from the upper surface of the top cover 1. It is used to receive external pressing or turning operations. Pressing or turning the operating end 6 will drive the valve core to actuate, thereby regulating the gas flow rate and thus the pressure of the output gas. The operating end 6 can extend to the cab via a flexible shaft, cable, or connecting rod for manual operation by the driver; it can also be connected to a drive mechanism such as a stepper motor for automatic drive by the vehicle's computer; in a configuration that combines both, the driver can still directly control the valve core via the operating end 6 if the drive mechanism fails.

[0075] In this embodiment, the coolant flow and the gas flow are independent of each other during operation. The coolant flow is as follows: the high-temperature coolant heated by the engine in the engine cooling system enters the liquid cooling tank 14 through the inlet 15, flows unidirectionally through the entire liquid cooling tank 14 under the guidance of the baffle and releases heat, and then returns to the engine cooling system through the coolant pipe 5.

[0076] The gas flow process is as follows: High-pressure liquefied gas enters the lower channel 16 from the liquefied gas inlet 8, flows meanderingly within the labyrinthine lower channel 16, absorbs heat conducted downwards by the liquid cooling section 3, increases in temperature, and undergoes throttling flash evaporation, completing primary gasification; After the two-phase medium flows to the end of the lower channel 16, it enters the second channel 13 through the lower opening and flows upwards, then enters the first channel 12, continuously absorbing the coolant in the liquid cooling tank 14 through the wall of the liquid cooling section 3 during the flow process. Heat; when the medium reaches the upper opening of the first channel 12, it enters the inner vaporization channel 10 after being throttled by the adjustable valve 9. The throttling and pressure reduction cause the residual liquid phase to flash further. Subsequently, the medium diffuses in the inner vaporization channel 10 and enters the outer vaporization channel 11 through the through holes on the partition. During the flow in the inner vaporization channel 10 and the outer vaporization channel 11, it continues to fully absorb heat through the heat-conducting partition between the vaporization section 2 and the liquid cooling section 3. Finally, the combustion gas merges into the gas outlet 7 at the end of the outer vaporization channel 11 and is output to the engine.

[0077] It should be noted that the degree of gasification at each stage is related to the operating conditions: under normal operating conditions with a high coolant temperature, most of the medium has been vaporized when it flows to the end of the lower channel 16. The remaining liquid phase is throttled and flashed by the adjustable valve 9, and then undergoes deep vaporization in the inner vaporization channel 10 and the outer vaporization channel 11. Under cold start conditions with a low coolant temperature, the proportion of primary vaporization decreases, the proportion of liquid phase in the medium increases, and the vaporization process relies more on the inner vaporization channel 10 and the outer vaporization channel 11. At this time, by limiting the opening of the adjustable valve 9 to reduce the gas supply rate, it can be ensured that the output gas is still in a gaseous state.

[0078] Under any of the above operating conditions, the liquefied gas flows from the liquefied gas inlet 8 to the gas outlet 7, passing through the primary vaporization in the lower channel 16, the transfer and transportation between the second channel 13 and the first channel 12, the throttling flash evaporation of the adjustable valve 9, and the deep vaporization in the inner vaporization channel 10 and the outer vaporization channel 11. Throughout the entire process, it indirectly exchanges heat with the coolant in the liquid cooling tank 14.

[0079] The inclined guide vanes in the second channel 13 cause the rising two-phase flow to swirl. Under the action of centrifugal force, the liquid phase adheres to the wall and returns to the lower channel 16 for re-vaporization through the guide notch-buffered liquid accumulation chamber-return hole, thereby breaking the formation of continuous liquid column in the second channel 13 and suppressing the pulsating feeding mechanism of liquid column blockage and gas mass breakthrough. The gradually expanding cross-section flow channels of the inner vaporization channel 10 and the outer vaporization channel 11 keep the flow velocity uniform throughout the entire flow channel range, avoiding droplet sedimentation in the low-speed zone and droplet entrainment in the high-speed zone. The inertial liquid-blocking ring intercepts residual droplets and prevents them from impacting the valve port sealing surface. The heat insulation gasket protects the diaphragm from direct heat conduction by the low-temperature gas. The damping pressure tapping channel filters out pressure pulsation. All the structures cooperate and work together to ensure the dryness and pressure stability of the output gas.

[0080] Example 2:

[0081] The difference between this embodiment and Embodiment 1 lies in the construction of the shell; the rest of the structure, connection relationship, and working process are the same as in Embodiment 1.

[0082] In this embodiment, the shell is an integral structure. The first vaporization chamber, the liquid cooling chamber and the second vaporization chamber are integrally formed along the height direction inside the shell. That is, the lower flow channel 16, the liquid cooling tank 14, the inner vaporization channel 10, the outer vaporization channel 11, the first channel 12 and the second channel 13 are all integrally formed inside the shell. The liquefied gas inlet 8, the gas outlet 7, the liquid inlet 15 and the coolant pipe 5 are directly opened on the side wall of the shell.

[0083] A one-piece housing can be manufactured in the following ways:

[0084] Firstly, casting is used, with sand cores or lost foam forming the cavities and flow channels within the mold, and aluminum alloy gravity casting or low-pressure casting is used for integral forming.

[0085] Secondly, by machining, various flow channels and passages are drilled and milled inward on the side of the solid blank. The process holes formed by machining are sealed by screwing in plugs or welding plugs after the flow channels are formed.

[0086] Third, additive manufacturing is used, which involves layer-by-layer deposition of materials through selective laser melting. The materials are aluminum alloy or 316L stainless steel. After forming, the internal support is removed and the airtightness is tested.

[0087] The adjustable valve 9 is mounted on a one-piece housing as follows: a threaded mounting hole is pre-drilled at the top of the housing corresponding to the center of the inner vaporization channel 10. The valve seat of the adjustable valve 9 is press-fitted onto the stepped surface within the mounting hole. The valve core is inserted through the mounting hole and aligned with the upper opening of the first channel 12. An O-ring seal is provided between the operating end 6 and the mounting hole, and it is secured with a lock nut. The one-piece housing eliminates the assembly process between components and the interlayer seals, resulting in higher overall structural strength and sealing reliability, as well as smaller size and weight, making it suitable for vehicles with high requirements for installation space and weight.

[0088] Example 3:

[0089] This embodiment provides alternative and enhanced implementation methods for some structures in the above-mentioned device. Each method can be used individually or in combination.

[0090] Regarding the fixing method: In addition to using bolts or long screws to connect the top cover 1, vaporization section 2, liquid cooling section 3 and bottom cover 4, solder foil can be applied to the contact surface and then placed in a vacuum brazing furnace for overall brazing, or diffusion welding can be used for permanent connection to further improve sealing performance and thermal conductivity.

[0091] Regarding the flow channel shape: In addition to the labyrinthine flow channel formed by interlaced ribs, the lower flow channel 16 can also be formed by continuous spiral baffles to form a spiral flow channel with a spiral pitch of 15mm to 20mm to further extend the flow path; the baffles in the liquid cooling tank 14 can be corrugated baffles with a corrugation amplitude of 3mm to 5mm and a wavelength of 10mm to 15mm to increase the heat exchange area on the coolant side; the surface of the vaporization section 2 facing the liquid cooling section 3, i.e. the surface of the heat-conducting baffle located on the side of the second vaporization chamber, can be provided with heat-conducting fins extending into the inner vaporization channel 10 and the outer vaporization channel 11. The height of the heat-conducting fins is 3mm to 5mm, the spacing between adjacent fins is 2mm to 4mm, and the fins are arranged along the gas flow direction to increase the heat exchange area on the gas side without significantly increasing the flow resistance.

[0092] Regarding alternative implementations of heat conduction connections: In addition to achieving the heat conduction connection between the first vaporization chamber, the second vaporization chamber, and the liquid cooling chamber through a shared heat-conducting wall surface, heat-conducting columns or heat pipes can also be embedded inside the shell. One end of the heat-conducting column or heat pipe contacts the wall surface of the liquid cooling chamber, and the other end contacts the wall surface of the corresponding vaporization chamber, so as to form an additional heat conduction path between the two.

[0093] Regarding the channel location: the first channel 12 and the second channel 13 are not limited to being formed inside the liquid cooling section 3. They can also be formed inside the vaporization section 2, or partially formed in the vaporization section 2 and partially formed in the liquid cooling section 3, as long as they are isolated from the coolant in the liquid cooling tank 14 and arranged adjacently to maintain heat transfer.

[0094] Regarding vibration resistance enhancement: In response to the continuous vibration and attitude changes during vehicle aftermarket use, 3 to 5 anti-sway baffles are spaced apart along the axial direction inside the second channel 13. The anti-sway baffles are circular pieces with notches, the area of ​​which is one-third of the cross-sectional area of ​​the second channel 13. The notches of adjacent anti-sway baffles are staggered by 180 degrees. The anti-sway baffles are fixed to the channel wall of the second channel 13 by interference fit or are integrally formed with the second channel 13. The anti-sway baffles break the continuity of the liquid column in the channel, suppressing the liquid column swaying and feeding pulsation caused by vehicle driving vibration.

[0095] The top and two sides of the ribs of the lower flow channel 16 are provided with serrated microribs. The tooth height of the microribs is 0.5mm to 1mm and the tooth pitch is 1mm to 2mm. The tooth tip is perpendicular to the mainstream direction of the gas flow to suppress surface waves of the liquid film, enhance the adhesion of the liquid phase, and reduce droplet splashing caused by vibration.

[0096] Regarding cold start enhancement: To address the low coolant temperature and insufficient heat source during cold starts in winter, the liquid cooling section 3 contains a phase change heat storage material cavity. This cavity is located within the solid area between the liquid cooling tank 14 and the lower flow channel 16, and consists of an annular cavity surrounding the liquid cooling tank 14 or multiple cylindrical cavities arranged in an array, with a wall thickness of 1.5mm to 2mm. After vacuuming, the cavity is encapsulated with paraffin-based phase change heat storage material with a phase change temperature of 50℃ to 60℃, filling 85% to 90% of the cavity volume, leaving space for thermal expansion. During normal vehicle operation, the heat from the coolant melts the phase change heat storage material to store heat. During cold starts, the phase change heat storage material solidifies and releases heat, compensating for heat loss in the liquid cooling tank 14 and the lower flow channel 16, buffering the insufficient heat during the cold start phase, and shortening the recovery time of vaporization capacity.

[0097] As a replacement or supplement to the aforementioned phase change heat storage material cavity, a temperature-sensing variable cross-section mechanism can also be provided within the body of the liquid cooling section 3. Specifically: a transition cavity is provided at the end of the pipe section extending inward from the liquefied gas inlet 8. The volume of the transition cavity is approximately 2 to 3 times the volume of the inlet pipe section, and the transition cavity is connected to the starting end of the lower flow channel 16. A temperature-sensing boss is provided on the side wall of the liquid cooling section 3, adjacent to the liquid cooling tank 14. A bimetallic strip or shape memory alloy element is installed in the temperature-sensing boss, and its free end drives a butterfly baffle or slide valve baffle located in the transition cavity via a micro-connecting rod, thereby changing the effective flow cross-sectional area of ​​the transition cavity. When the coolant temperature decreases, the temperature-sensing element drives the baffle to reduce the effective flow cross-sectional area of ​​the transition cavity, thereby reducing the flow rate of the liquefied gas and prolonging its heat exchange time in the primary vaporization cavity. When the coolant temperature increases, the temperature-sensing element drives the baffle to increase the effective flow cross-sectional area, thereby reducing pressure loss and adapting to high flow rate requirements. The temperature-sensing variable cross-section mechanism and the opening adjustment of the adjustable valve 9 constitute a two-stage flow matching system of flow channel cross-section and valve opening.

[0098] Regarding passive temperature sensing regulation: The valve core of the adjustable valve 9 can also be directly driven by the temperature sensing element to achieve passive regulation that automatically changes the cross-sectional area of ​​the upper opening of the first channel 12 according to the coolant temperature.

[0099] Specifically, one end of the bimetallic strip is fixed to a temperature-sensing protrusion adjacent to the liquid cooling tank 14 on the liquid cooling section 3 to sense the temperature of the coolant. The free end of the bimetallic strip is connected to the valve core via a lever with a transmission ratio of 2:1 to 3:1 to amplify the displacement of the bimetallic strip. Alternatively, a shape memory alloy spring and a bias spring are arranged opposite each other. When the coolant temperature changes, the force balance position of the two springs moves, causing the valve core to change the communication cross-sectional area of ​​the opening. This passive adjustment method can serve as a redundancy or alternative to the electronic control adjustment method.

[0100] Example 4:

[0101] This embodiment provides a gasification pressure regulation control method, applied to the gasification pressure regulation device of any of the above embodiments. The device is equipped with a control unit, a coolant temperature sensor, a gas temperature sensor, a gas pressure sensor, and a drive mechanism; the control unit is a vehicle computer or an independent gas control unit; the coolant temperature sensor is an NTC thermistor, located in the liquid cooling tank 14 or at the coolant pipe 5; the gas temperature sensor is located at the gas outlet 7; the gas pressure sensor is located at the gas outlet 7 and is used to detect the pressure of the output gas; the drive mechanism is a stepper motor or a proportional electromagnetic actuator, connected to the operating end 6 of the adjustable valve 9. The method includes the following steps:

[0102] S1: The control unit acquires the operating parameters of the device in real time. The sampling period for coolant temperature is 100ms; the sampling period for gas pressure is 10ms. The sampled signals are subjected to RC hardware filtering and moving average software filtering. The moving average window is 20 sampling points to cover the dominant cycle of the feeding pulsation and filter out high-frequency pressure pulsations. The operating parameters may also include the gas temperature at gas outlet 7, engine speed, and throttle opening.

[0103] S2: When the coolant temperature is below the first threshold, the control unit determines that the vehicle is in a cold start or insufficient heat source condition and enters the cold start flow limiting mode: The control unit limits the maximum opening of the adjustable valve 9 to the first opening value through the drive mechanism, forcibly reducing the supply rate of liquefied gas, so that the gas supply is matched with the limited heat supply, and preventing liquefied gas from penetrating the device and entering the engine without vaporization. As an example, the first threshold is set to 40°C, and the first opening value is set to 15% of the maximum opening of the adjustable valve 9.

[0104] S3: When the coolant temperature rises to a level not lower than the first threshold and lower than the second threshold, for example, in the range of 40℃ to 60℃, the control unit gradually increases the maximum opening limit of the adjustable valve 9 according to the preset temperature-opening mapping curve as the coolant temperature increases. This mapping curve is a piecewise linear interpolation curve, and its calibration method is as follows: On the test bench, the coolant temperature is stabilized at calibration points of 40℃, 45℃, 50℃, 55℃, and 60℃ respectively. At each calibration point, the opening of the adjustable valve 9 is gradually increased. The maximum opening corresponding to the gas outlet 7 when there is no liquid entrainment is taken as the opening limit of that calibration point, and linear interpolation is performed between adjacent calibration points. As an example, the maximum opening limits corresponding to the calibration points of 40℃, 45℃, 50℃, 55℃, and 60℃ are 15%, 30%, 50%, 75%, and 100% of the maximum opening, respectively. Since the gasification rate changes non-linearly with temperature, in the temperature range where the gasification rate decreases rapidly, the calibration points are arranged more densely and the increase in the opening limit is more gradual, so that the gas supply always matches the heat source supply capacity.

[0105] S4: When the coolant temperature is not lower than the second threshold, for example, reaching 60℃, the control unit determines that the heat source is sufficient, releases the full opening restriction of the adjustable valve 9, and enters the normal adjustment mode: the control unit uses the target pressure of the output gas as the set value and the filtered gas pressure at the gas outlet 7 as the feedback value to perform closed-loop adjustment, and corrects the target pressure according to the engine speed, throttle opening, or intake manifold pressure. The closed-loop adjustment adopts the PID algorithm, and the proportional coefficient, integral time, and derivative time are tuned on the bench. As an example, the proportional coefficient is 0.5 to 2.0, the integral time is 0.1s to 1s, the derivative time is 0 to 0.1s, and the control cycle is 100ms. To avoid oscillation, when the pressure deviation enters the neighborhood of the target range, it switches to small step fine adjustment and sets an adjustment dead zone of ±2kPa.

[0106] As a supplement to the normal regulation mode, the control unit also monitors and analyzes the gas pressure signal at gas outlet 7 in real time. The control unit first processes the pressure signal through a bandpass filter with a passband frequency of 0.5Hz to 5Hz, covering the dominant frequency range of liquid column pulsation, filtering out high-frequency noise and DC steady-state components; then, it calculates the peak-to-peak value of the filtered signal within a 3-second sliding window. When the peak-to-peak value exceeds a preset pulsation threshold (e.g., ±8kPa) and lasts for more than 3 seconds, the control unit determines that a severe phase separation pulsation has occurred in the upstream connecting channel (i.e., liquid column blockage-gas mass breakthrough pulsation in the second channel 13). In response to this determination, the control unit performs the following adaptive adjustment operations: actively reducing the current opening of the adjustable valve 9 by 5% to 15% to reduce the gas supply rate and alleviate the liquid column load in the upstream channel; at the same time, increasing the integral time of the PID controller to 1.5 to 2 times the original value to reduce the response speed of the control system to the pulsation signal and avoid misinterpreting the pulsation as a pressure change and causing over-adjustment; when the pressure pulsation amplitude falls below the preset pulsation threshold and remains stable for 5 seconds, the control unit gradually restores the opening of the adjustable valve 9 to the target value of the normal adjustment mode and restores the PID parameters to the original set value.

[0107] S5: In normal adjustment mode, the control unit monitors the gas temperature at gas outlet 7 in real time. If the gas temperature is lower than the reference value corresponding to the current coolant temperature, and the duration exceeds a preset duration, such as 5 seconds, it is determined that there is liquid entrainment in the output gas, i.e., insufficient vaporization. The reference value is the gas temperature value corresponding to the current coolant temperature in a pre-calibrated temperature mapping table. This temperature mapping table is obtained by measuring the outlet gas temperature when fully vaporized at each coolant temperature calibration point on the test bench.

[0108] S6: In response to the above determination, the control unit actively reduces the opening of the adjustable valve 9, for example, by reducing it in steps of 10% to 20% of the current opening, in order to reduce the gas flow rate and prolong the heat exchange residence time of the gas in the flow channel, so that it can fully absorb heat and vaporize; if the liquid entrainment state continues for 30 seconds and is not eliminated, the control unit sends a warning signal to the cab, prompting the driver to reduce the engine load; when the gas temperature at the gas outlet 7 returns to above the reference value and remains stable for 30 seconds, the control unit exits the protection mode and resumes the normal adjustment mode.

[0109] The switching between modes is as follows: the cold start flow limiting mode, the gradual unlimiting mode, and the normal adjustment mode switch sequentially in one direction as the coolant temperature rises; a hysteresis of 2°C is set when the coolant temperature crosses the first threshold and the second threshold to prevent frequent mode switching caused by temperature fluctuations near the threshold.

[0110] In embodiments without a control unit and drive mechanism, the operating end 6 extends to the cab via a flexible shaft or cable, and the driver manually presses or rotates the operating end 6 to adjust the opening degree according to the vehicle's operating status. In embodiments with both manual and electronic control, when the electronic control fails, the drive mechanism disengages from the transmission connection with the operating end 6, and the driver directly controls the valve core through the operating end 6. When the electronic control is normal, the driver sets the upper limit of the opening degree, and the control unit automatically fine-tunes within this upper limit.

[0111] Performance comparison test:

[0112] To verify the technical effectiveness of the aforementioned device and control method, a comparative test was conducted on a test bench. The test conditions were: liquefied petroleum gas supply pressure of 1.6 MPa, gas demand flow rate of 10 kg / h, and the comparative example was an existing single-chamber hydrothermal gasification pressure regulating device.

[0113] Under steady-state conditions with a coolant temperature of 60°C, liquid droplets were detectable in the outlet gas of the comparative example, with an outlet pressure fluctuation range of ±15 kPa. In this embodiment, the outlet gas exhibited no liquid entrainment, and the outlet pressure fluctuation range was narrowed to ±5 kPa. Under cold-start conditions with an initial coolant temperature of 5°C, the comparative example continuously output liquid-containing gas for 180 seconds after startup. In this embodiment, no liquid gas penetration occurred in the cold-start flow-limiting mode, and all flow restrictions were lifted 90 seconds after startup when the coolant temperature reached 60°C, entering normal regulation mode.

[0114] The above test data are exemplary test results; the specific values ​​will vary depending on the product's structural dimensions and test conditions.

[0115] This invention is not limited to the optional embodiments described above, and anyone can derive other various forms of products based on the teachings of this invention. The specific embodiments described above should not be construed as limiting the scope of protection of this invention; the scope of protection of this invention should be determined by the claims, and the specification can be used to interpret the claims.

Claims

1. A gasification pressure regulating device, characterized in that, The device includes a housing, within which a first vaporization chamber, a liquid-cooled chamber, and a second vaporization chamber are arranged sequentially along the height direction. The liquid-cooled chamber is located between the first vaporization chamber and the second vaporization chamber. Both the first vaporization chamber and the second vaporization chamber are fluidly isolated from the liquid-cooled chamber but thermally connected. The housing is provided with a liquefied gas inlet (8) and a gas outlet (7), the liquefied gas inlet (8) is connected to the first vaporization chamber, and the gas outlet (7) is connected to the second vaporization chamber; the housing is provided with a communication channel connecting the first vaporization chamber and the second vaporization chamber; An adjustable valve (9) is also provided on the housing, which is used to adjust the flow rate of the gas flowing into the second vaporization chamber from the connecting channel.

2. The gasification pressure regulating device according to claim 1, characterized in that, A lower flow channel (16) is formed in the first vaporization chamber. The lower flow channel (16) is a meandering flow channel. The liquefied gas inlet (8) is connected to the starting end of the lower flow channel (16), and the connecting channel is connected to the end of the lower flow channel (16).

3. The gasification pressure regulating device according to claim 2, characterized in that, The connecting channels include a first channel (12) and a second channel (13) that are interconnected. Both the first channel (12) and the second channel (13) are arranged adjacent to the liquid cooling cavity and are fluidly isolated from the liquid cooling cavity. One end of the second channel (13) is connected to the end of the lower flow channel (16), and the other end of the second channel (13) is connected to one end of the first channel (12). The other end of the first channel (12) forms an opening leading to the second vaporization cavity. The adjustable valve (9) is used to adjust the cross-sectional area of ​​the opening.

4. The gasification pressure regulating device according to claim 3, characterized in that, The second vaporization chamber has an inner vaporization channel (10) and an outer vaporization channel (11). The opening of the first channel (12) leads to the inner vaporization channel (10). The inner vaporization channel (10) is connected to the outer vaporization channel (11). The gas outlet (7) is connected to the outer vaporization channel (11).

5. The gasification pressure regulating device according to claim 4, characterized in that, The housing includes a top cover (1), a vaporization section (2), a liquid cooling section (3), and a bottom cover (4); the vaporization section (2) is superimposed on one side of the liquid cooling section (3), the inner vaporization channel (10) and the outer vaporization channel (11) are opened on the surface of the vaporization section (2) facing the liquid cooling section (3), and the top cover (1) covers the side of the vaporization section (2) facing away from the liquid cooling section (3); the surface of the liquid cooling section (3) facing the vaporization section (2) is provided with a liquid cooling groove (14), and the liquid cooling groove (14) constitutes the liquid cooling cavity; the surface of the liquid cooling section (3) facing away from the vaporization section (2) is provided with a downflow channel (16), and the bottom cover (4) seals the surface of the liquid cooling section (3); the surfaces of the vaporization section (2) and the liquid cooling section (3) that are in contact with each other constitute a heat-conducting partition.

6. The gasification pressure regulating device according to claim 5, characterized in that, An annular sealing ring is provided on the outer ring of the surface of the vaporization section (2) that is in contact with the liquid cooling section (3).

7. The gasification pressure regulating device according to claim 5, characterized in that, The liquid cooling tank (14) is provided with a partition, which divides the liquid cooling tank (14) into a series of interconnected flow channel areas; the liquid cooling part (3) is provided with an inlet (15) and a coolant pipe (5) communicating with the liquid cooling tank (14) on the same side wall. The coolant enters the liquid cooling tank (14) from the inlet (15), flows through the entire flow channel area and then flows out from the coolant pipe (5).

8. The gasification pressure regulating device according to claim 1, characterized in that, The housing is an integral structure, and the first vaporization chamber, the liquid cooling chamber, the second vaporization chamber, and the connecting channel are all integrally formed inside the housing.

9. The gasification pressure regulating device according to claim 3, characterized in that, The adjustable valve (9) includes a valve core and an operating end (6) that is throttle-connected to the valve core; the valve core is provided corresponding to the opening, and the operating end (6) passes through the housing and extends outside the housing. The operating end (6) is used to receive external pressing or turning force to drive the valve core to change the communication cross-sectional area of ​​the opening.

10. A gasification pressure regulation control method, characterized in that, The method, applied to the gasification pressure regulating apparatus as described in any one of claims 1 to 9, comprises: Obtain the temperature of the coolant inside the liquid cooling chamber; When the temperature of the coolant is lower than the first threshold, the maximum opening of the adjustable valve (9) is limited to the first opening value; When the temperature of the coolant is not lower than the first threshold and is lower than the second threshold, the maximum opening limit of the adjustable valve (9) is gradually increased as the temperature of the coolant increases, according to the preset temperature-opening mapping curve. When the temperature of the coolant is not lower than the second threshold, the maximum opening limit of the adjustable valve (9) is released, and the opening of the adjustable valve (9) is adjusted according to the engine speed, throttle opening or intake manifold pressure. The gas temperature at the gas outlet (7) is obtained. When the gas temperature is lower than the reference value corresponding to the current temperature of the coolant and the duration exceeds the preset duration, the opening of the adjustable valve (9) is reduced until the gas temperature recovers to above the reference value. The reference value is the gas temperature value corresponding to the current temperature of the coolant in a temperature mapping table calibrated in advance through experiments.

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