High differential pressure and micro flow regulating valve for hydrogen supply system

Abstract

The present invention belongs to the technical field of control valves, and particularly relates to a high-pressure differential and micro-flow control valve for a hydrogen supply system. The present invention includes more than two groups of rotary valve components with flow channels connected in series. Each group of rotary valve components includes a valve core and a valve seat located outside the valve core that are coaxially matched with each other. A flow channel hole is provided at the valve seat, and a longitudinal flow channel is coaxially provided at the valve core. Moreover, a grooved window communicating the flow channel hole with the longitudinal flow channel is provided on the outer wall of the valve core. The medium generates a flow regulation action through the regulation flow channel formed by the grooved window and the flow channel hole. The grooved window at the valve core is a water droplet-shaped hole formed by cutting a closed triangle surrounded by a first curve, a second curve, and the valve core bus along the extension direction of a third curve. The present invention has an efficient regulation ability to cope with large pressure differential working conditions, and can effectively improve the flow control accuracy of the valve.

Description

Technical Field

[0001] The present invention belongs to the technical field of control valves, and particularly relates to a high-pressure differential and micro-flow control valve for a hydrogen supply system. Background Art

[0002] In modern industrial production, control valves are important control components in the process of transporting media, and are key devices to ensure the normal operation of various process equipment. They are widely used in fields such as electric power and chemical industry. With the development of industrial technology, there are more and more high-pressure differential medium process devices, and at the same time, the requirement for the ability to accurately regulate the flow rate is getting higher and higher; under the conditions of high-pressure differential media in a wide operating range, problems such as insufficient regulation ratio, valve core oscillation, and vibration noise are likely to occur, resulting in the inability to meet the regulation requirements.

[0003] Currently, there are mainly three structural forms of high-pressure differential medium and micro-flow control valves, namely needle valves, V-ball valves, and plug valves. The orifice diameters of needle valves are generally small, and their valve core structures are needle-shaped. The regulation ability of the valve is increased by changing the shape of the valve core head; V-ball valves and plug valves control the rotation opening of the valve core by rotating the control shaft connected to the valve core, so that the V-shaped opening on the valve core forms different flow areas with the flow path of the medium, thereby changing the flow rate of the medium. The above-mentioned traditional micro-flow control valves can all meet the flow regulation within a certain range, but there are also the following problems: for the former needle valve, its orifice diameter is generally small. If an ultra-large adjustable ratio is to be achieved, the valve core head needs to be processed to an ultra-small diameter, and at this time, the valve core is easily damaged; therefore, needle valves can only be applied to ultra-clean media. For the latter V-ball valves and plug valves, the existing application orifice diameters are usually large, but under the condition of a small orifice diameter, the regulation window of the traditional valve core through-hole structure is small, and the regulation angle is even not greater than 90°, which makes it difficult for V-ball valves and plug valves to meet the requirements of accurate flow regulation. Whether it is possible to develop a valve that not only has an ultra-large adjustable ratio but also has an accurate flow regulation function, so as to greatly improve the regulation ability of the original structure to cope with large pressure difference working conditions, and at the same time, can further improve the flow control accuracy of the valve, is a technical problem that has been urgently needed to be solved in this field in recent years. Summary of the Invention

[0004] The purpose of the present invention is to overcome the above-mentioned deficiencies of the prior art, and provide a high-pressure differential and micro-flow control valve for a hydrogen supply system that is compact in structure and convenient, reliable in operation. The present invention has an efficient regulation ability to cope with large pressure difference working conditions, and can effectively improve the flow control accuracy of the valve.

[0005] To achieve the above purpose, the present invention adopts the following technical solutions:

[0006] A high-pressure differential and micro-flow regulating valve for a hydrogen supply system, characterized in that: it includes more than two groups of rotary valve components with their flow channels connected in series. Each group of rotary valve components includes a valve core and a valve seat located outside the valve core, which are coaxially matched with each other. A flow channel hole is provided at the valve seat, and a longitudinal flow channel is coaxially provided at the valve core. A grooved window communicating the flow channel hole with the longitudinal flow channel is provided on the outer wall of the valve core. The medium generates a flow regulation action through the regulation flow channel formed by the grooved window and the flow channel hole. Among them:

[0007] Make an axial section coinciding with the axis of the valve core, and take the axis of the valve core as the Y-axis and the horizontal line perpendicular to the axis of the valve core on this axial section as the X-axis to form a rectangular coordinate system with the origin of coordinates located at half the height of the valve core. At this time, the expressions of the first curve and the second curve passing through the origin of coordinates are:

[0008]

[0009]

[0010] Among them:

[0011] R1 and R2 are the distances from the intersection points of the corresponding curves and the generatrix of the valve core to the X-axis;

[0012] r1 is the radius of the small end of the valve core;

[0013] r2 is the radius of the large end of the valve core;

[0014] h is the height of the valve core;

[0015] At the same time, make a cross-section perpendicular to the axis of the valve core at half the height of the valve core, and establish a polar coordinate system with the point where the axis of the valve core is located as the origin on this cross-section. At this time, the expression of the third curve obtained is:

[0016]

[0017] Among them:

[0018] R is the diameter of the valve flow channel;

[0019] r = (r1 + r2) / 2.

[0020] The grooved window at the valve core is a water droplet-shaped channel formed by cutting the closed triangle surrounded by the first curve, the second curve and the generatrix of the valve core along the extension direction of the third curve.

[0021] Preferably, along the direction of the medium flow, the maximum flow rates of each rotary valve component decrease step by step.

[0022] Preferably, the rotary valve assembly is placed inside the valve housing. A through hole is vertically provided through the valve housing, and both ends of the through hole are sealed by sealing parts, thereby forming a sealed valve cavity inside the through hole. The valve stem penetrates through one of the sealing parts and extends into the valve cavity, and the extended end of the valve stem is non-rotatably fitted with the valve core. The outer wall of the valve core is frustum-shaped, so as to be fitted and fixed to the frustum-shaped valve seat fixed on the valve cavity.

[0023] Preferably, a first flow channel cavity is provided through one side of the valve housing, and a second flow channel cavity is provided through the other sealing part. The first flow channel cavity, the flow channel hole at the valve seat, the grooved window at the valve core, the longitudinal flow channel at the valve core, and the second flow channel cavity communicate with each other. One set of rotary valve assembly and valve stem form a set of valve body. Along the medium flow direction, or between the first flow channel cavities of two adjacent sets of valve bodies, or between the first flow channel cavity of one set of valve body and the second flow channel cavity of another set of valve body, or between the second flow channel cavities of two adjacent sets of valve bodies are communicated with each other through an intermediate pipeline, so that the flow channels of each rotary valve assembly are connected in series with each other.

[0024] Preferably, the valve stem is non-rotatably fitted coaxially with the small end of the valve core through a spline. The sealing part includes an upper sealing part located at the top end of the through hole and a lower sealing part located at the bottom end of the through hole. The upper sealing part includes packing for filling the gap between the valve stem and the through hole and a gland screwed to the top end of the through hole for pressing the packing. The lower sealing part includes a pipe joint screwed to the bottom end of the through hole. An axial compression spring is arranged between the pipe joint and the large end of the valve core, and the pipe cavity of the pipe joint constitutes the second flow channel cavity.

[0025] Preferably, there are two sets of rotary valve assemblies and they are arranged coaxially with each other. The small ends of the valve cores of the two sets of rotary valve assemblies are arranged in series in the same valve cavity either in the same direction or in the opposite direction. The valve stems of the two sets of rotary valve assemblies are coaxial with each other and respectively penetrate through one of the sealing parts. A medium inlet communicating with the flow channel hole at the valve seat of the first set of rotary valve assembly is provided through the side wall of the valve housing where the first set of rotary valve assembly is located, and a medium outlet communicating with the flow channel hole at the valve seat of the second set of rotary valve assembly is provided through the side wall of the valve housing where the second set of rotary valve assembly is located, and the longitudinal flow channels at the valve cores of the two sets of rotary valve assemblies communicate with each other.

[0026] Preferably, the valve stems of the two sets of rotary valve assemblies are both non-rotatably fitted coaxially with the large ends of the valve cores through splines, and the small ends of the valve cores are opposite to each other and have a gap. The sealing part includes an upper sealing part located at the top end of the through hole and a lower sealing part located at the bottom end of the through hole. Both the upper sealing part and the lower sealing part include packing for filling the gap between the corresponding valve stem and the through hole and a gland screwed to the corresponding end of the through hole for pressing the packing.

[0027] Preferably, an axial compression spring for axially pressing the valve core against the valve seat is sleeved on the spline.

[0028] Preferably, there are two sets of rotary valve assemblies which are coaxially arranged with each other. The longitudinal flow channels between the two adjacent valve cores of the two sets of rotary valve assemblies are connected to each other through an intermediate force transmission pipe, so that the small ends of the valve cores of the two sets of rotary valve assemblies are arranged in series in the same valve cavity either in the same direction or in the opposite direction. At this time, the two valve cores are synchronously driven by a valve rod. A medium inlet communicating with the flow channel hole at the valve seat of this set of rotary valve assemblies is penetrated and arranged at the side wall of the valve housing where the first set of rotary valve assemblies is located, and a medium outlet communicating with the flow channel hole at the valve seat of this set of rotary valve assemblies is penetrated and arranged at the side wall of the valve housing where the second set of rotary valve assemblies is located.

[0029] Preferably, the valve rod is in anti-rotation fit coaxially with the large end of the upper valve core through a spline. The small ends of the two valve cores face each other and have a gap, and are connected to each other through the intermediate force transmission pipe with a spline-structured outer wall having a communication cavity. The sealing part includes an upper sealing part located at the top of the through hole and a lower sealing part located at the bottom of the through hole. The upper sealing part includes a packing for filling the gap between the valve rod and the through hole and a gland threadedly fitted at the top of the through hole for pressing the packing. The lower sealing part is a threaded cover threadedly fitted at the bottom of the through hole, and an axial compression spring is arranged between the threaded cover and the large end of the lower valve core.

[0030] The beneficial effects of the present invention are as follows:

[0031] 1) Through the above scheme, through the multi-stage rotary valve assemblies arranged in series with each other, the step-by-step series adjustment function is realized, so as to ensure the high-efficiency adjustment ability under the large pressure difference working condition. More importantly, considering that the rotary valve can ensure the adjustment effect and sealing ability under the large pressure difference working condition as much as possible, but the improvement of the flow control accuracy of the conventional rotary valve structure has always been a difficult problem. Especially under the large pressure difference working condition, how to ensure that the change of the flow coefficient caused by the rotation of the valve core by a unit angle is as low as possible to improve its flow control accuracy as much as possible is the key point to be solved in this invention. Through the fitting of the above three curves, a specific groove window adapted to the current valve core size can be formed, so as to further make up for the flow adjustment range of the above multi-stage series rotary valve, minimize the change of the flow coefficient caused by the rotation of the valve core by a unit angle, and finally improve the ability to adjust the micro flow under high pressure difference and ensure its adjustment accuracy at the same time.

[0032] Practice has proved that the change of the flow coefficient caused by the rotation of the valve core of the present invention by a unit angle is extremely obvious compared with that of the traditional regulating valve, and the actual flow control accuracy can be greatly improved.

[0033] So far, the present invention has the high-efficiency adjustment ability to cope with the large pressure difference working condition, can effectively improve the flow control accuracy of the valve, and the multi-stage series connection mode also makes its structure compact and the operation very convenient and reliable. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 , Figure 2 and Figure 3 are the structural sectional views of three different embodiments of the present invention;

[0035] Figure 4 is the three-dimensional structure diagram of the valve core;

[0036] Figure 5 is Figure 4 's top view;

[0037] Figure 6 is the rectangular coordinate system diagram when establishing the first curve and the second curve;

[0038] Figure 7 is the polar coordinate diagram when establishing the third curve;

[0039] Figure 8 is the regulation curve diagram of the traditional DN5 caliber regulating valve;

[0040] Figure 9 is the regulation curve diagram of the DN5 caliber regulating valve of the present invention.

[0041] The actual corresponding relationship between each label of the present invention and the component name is as follows:

[0042] I - the first curve; II - the second curve; III - the third curve;

[0043] a - the first flow channel cavity; b - the second flow channel cavity; c - the medium inlet; d - the medium outlet;

[0044] 10 - the rotary valve assembly; 11 - the valve core; 11a - the grooved window; 11b - the longitudinal flow channel;

[0045] 12 - the valve seat; 20 - the valve housing; 21 - the through hole; 30 - the valve stem; 40 - the intermediate pipeline;

[0046] 51 - the upper sealing part; 52 - the lower sealing part; 60 - the axial compression spring; 70 - the intermediate force transmission pipe. Detailed implementation mode

[0047] For easy understanding, here in combination with Figures 1-9 , the specific structure and working mode of the present invention are further described as follows:

[0048] The specific structure of the present invention is as shown in Figures 1-7 . Its main structure includes an integral valve housing 20, and two groups of rotary valve assemblies 10 are arranged in the valve housing 20, thus forming the valve bodies of two sets of plug valves that are either juxtaposed or coaxial with each other. These two sets of valve bodies can be driven respectively by different valve stems 30 as shown in Figure 1 and Figure 2 , or directly as shown in Figure 3As shown, the valves are driven synchronously by the same valve stem 30, and only the functions of series connection and gradual adjustment can be realized.

[0049] When the above series structure is formed, under normal circumstances, that is, Figure 1 In the illustrated case, the upright frustum-shaped valve core 11 is used as a positive reference. The valve cores 11 of the two sets of rotary valve assemblies 10 can be connected in series in a positive direction or in a reverse direction, or even in a reverse direction. Figures 2-3 The forward and reverse series connection shown only needs to be able to achieve its step-by-step adjustment effect.

[0050] On the basis of the above structure, in order to further compensate for the flow regulation defects of this type of plug valve or rotary valve, and to reduce the flow coefficient change caused by the unit angle of rotation of the valve core 11 as much as possible, so as to improve the ability to regulate the flow under high pressure difference, and simultaneously ensure its regulation accuracy, the present invention introduces three curves to combine and obtain the most preferred groove window 11a structure. In other words, the special tadpole-shaped or water drop-shaped groove window 11a of the present invention has an appearance contour composed of three curves, and the first curve I and the second curve II form an acute angle and finally form an intersection, and rely on the change of the third curve to expand the groove window 11a, so as to achieve multi-stage pressure reduction and throttling, and improve the regulation ability. Specifically:

[0051] Make an axial section that coincides with the axis of the valve core 11, and take the axis of the valve core 11 as the Y axis and the horizontal line perpendicular to the axis of the valve core 11 on the axial section as the X axis to form a rectangular coordinate system with the origin at half the height of the valve core 11. Figure 6 As shown, the expressions of the first curve I and the second curve II passing through the coordinate origin are:

[0052]

[0053]

[0054] in:

[0055] R1 and R2 are the distances from the intersection of the corresponding curve and the generatrix of the valve core 11 to the X axis;

[0056] r1 is the radius of the small end of the valve core 11;

[0057] r2 is the radius of the large end of the valve core 11;

[0058] h is the height of the valve core 11;

[0059] At the same time, a cross section perpendicular to the axis of the valve core 11 is made at half the height of the valve core 11, and a polar coordinate system is established on the cross section with the point where the axis of the valve core 11 is located as the origin, referring to Figure 7 As shown, the expression of the third curve III is obtained as follows:

[0060]

[0061] Wherein:

[0062] R is the through diameter of the valve flow channel;

[0063] r = (r1 + r2) / 2.

[0064] The grooved window 11a at the valve core 11 is a tadpole-shaped or water droplet-shaped channel formed by cutting the closed triangle surrounded by the first curve I, the second curve II and the generatrix of the valve core 11 along the extension direction of the third curve III. For the specific shape of the grooved window 11a, refer to Figures 4-5 as shown.

[0065] For the valve core 11 and the valve seat 12, they are both nested frustum-shaped and conical sleeve-shaped. For the valve core 11, when the medium enters the valve cavity through the longitudinal flow channel 11b of the valve core 11, pressure balance will be achieved at both ends of the valve core 11, reducing the rotational torque; however, since the valve core 11 is frustum-shaped and the areas of the large end and the small end are different, an upward medium unbalance force will be generated under the action of pressure, which can help the valve achieve sealing, and as the medium pressure increases, the improvement degree is higher.

[0066] As the key point of the present invention, the arrangement position of the grooved window 11a is at half the height of the valve core 11 and presents a distribution state as Figures 4-5 shown. Of course, for the convenience of observing details, Figures 1-3 all the valve cores 11 in

[0067] have the same size; during actual operation, since the maximum flow rate of each rotary valve assembly 10 gradually decreases along the medium flow direction, the size of the valve core 11 should gradually decrease, so that the grooved windows 11a based on the size of the valve core 11 gradually shrink, thereby forming a design effect of gradually decreasing flow rate along the medium flow direction. For the valve seat 12, the arrangement of its flow channel holes is relatively conventional, and conventional hole types such as round holes can be used, and the corresponding basic design can be carried out in adaptation to the grooved window 11a, which will not be elaborated here.

[0067] Under the external shape structure of the specific grooved window 11a at the valve core 11 described above, the present invention also provides three different implementation structures to specifically protect the valve structures that may be extended.

[0068] Embodiment 1:

[0069] The specific implementation structure of this embodiment can be referred to Figure 1 as shown. Its main structure includes a valve body, and the valve body takes the integral valve housing 20 as the main body. Two through holes 21 are vertically penetrated through the valve housing 20, and each through hole 21 is sealed by an upper sealing portion 51 and a lower sealing portion 52 to form two juxtaposed valve cavities.

[0070] The valve stem 30 vertically penetrates through the upper sealing part 51 and extends into the valve cavity, so as to non-rotatably fit with the small end of the tapered valve core 11 in a spline manner. The large end of the valve core 11 is elastically fitted on the lower sealing part 52 through an axial compression spring 60. Under the action of the axial compression spring 60, the valve core 11 can always be reliably sealed and pressed on the valve seat 12 due to the conical surface fit with the valve seat 12, so as to ensure the sealing performance and working reliability during adjustment.

[0071] For the upper sealing part 51, it is composed of a packing and a gland; for the lower sealing part 52, it is formed by the threaded fitting of a pipe joint at the bottom end of the through hole 21. Due to the threaded fitting structure of the pipe joint, the pipe joint can be axially adjusted relative to the through hole 21, so as to appropriately adjust the pressing force of the axial compression spring 60, and further achieve the purpose of adjusting the sealing effect of the rotary valve assembly 10.

[0072] In Figure 1 it is obvious that both of the first flow channel cavities a are located on the side wall of the valve housing 20 and correspondingly communicate with the flow channel holes at the valve seats 12 in the two valve cavities. Taking the structure shown in Figure 1 as an example, when the medium flows in from the first flow channel cavity a on the left side, it can sequentially pass through the left valve housing 20, the flow channel hole at the valve seat 12, the grooved window 11a at the valve core 11, the second flow channel cavity b formed by the pipe cavity of the pipe joint, the intermediate pipeline 40 and the same structure on the right side, and finally flow out from the first flow channel cavity a on the right side. Of course, if the series connection mode of the two flow channel cavities with the above structure is positive-positive series connection, then the two flow channel cavities can also be connected in positive-negative series or negative-negative series, and the action effect can also be achieved.

[0073] Embodiment 2:

[0074] The specific implementation structure of the present invention can also be referred to as shown in Figure 2 The main structure is basically the same, and the difference is that the two valve bodies formed by the two sets of rotary valve assemblies 10 are coaxial and symmetrically arranged face to face, so as to form the double-valve-stem single-valve-cavity drive structure shown in Figure 2 Compared with Embodiment 1, there is no intermediate pipeline 40 in Embodiment 2, and the communication between the two valve cores 11 is completely realized by relying on the gap between them. The existence of the gap, on the one hand, ensures the non-interference of the actions of the two valve cores 11, and on the other hand, can also form an intermediate transition channel for temporarily storing the medium, so as to realize the medium circulation function.

[0075] During actual operation, taking Figure 2The left cavity is the medium inlet c. The medium can enter through the medium inlet c and flow out through the medium outlet d after passing through the upper valve seat 12, the upper valve core 11, the lower valve core 11, and the lower valve seat 12 in sequence. Of course, vice versa. Whether the two rotary components are arranged in the same direction or in the opposite direction does not affect their actual working state, but attention should be paid to the adaptive adjustment of the axial compression spring 60, etc.

[0076] In this embodiment, the upper sealing part 51 and the lower sealing part 52 have the same structure, both consisting of packing and gland; the axial pressure is realized by the axial compression spring 60 sleeved on the spline of the valve stem 30.

[0077] In Embodiment 2, as the two valve stems 30 drive the corresponding valve cores 11 to rotate different angles respectively, the grooved windows 11a at the valve cores 11 cooperate with the flow channel holes at the valve seats 12 to form throttling areas of different sizes, so as to achieve the purpose of regulating the flow rate.

[0078] Compared with Embodiment 1, Embodiment 2 is more suitable for occasions where the lateral layout space is limited.

[0079] Embodiment 3:

[0080] The specific implementation structure of Embodiment 3 can be referred to Figure 3 As shown, its main structure is similar to that of Embodiment 2. The difference is that on the one hand, a single valve stem 30 is used for driving, forming a single-valve-stem single-valve-cavity drive structure; on the other hand, since there is no valve stem 30 in the lower sealing part 52, a solid threaded cover can be used in combination with the axial compression spring 60 to improve the sealing performance of the two series-connected rotary valve assemblies 10.

[0081] In addition, compared with Embodiment 2, the lower valve core 11 in this embodiment needs to be connected to each other through an intermediate force-transmitting pipe 70 with a splined appearance and a communication cavity. On the one hand, the intermediate force-transmitting pipe 70 plays a role in transmitting the medium through the communication cavity, that is, relying on the communication cavity to form a medium channel; on the other hand, the spline fit of the intermediate force-transmitting pipe 70 is used to achieve the torque transmission effect. In addition, due to the spline fit, there are still fitting gaps, which do not affect the penetration of the medium to both ends of the valve core 11, so as to achieve the effect of pressure balance.

[0082] Compared with Embodiment 2, in this embodiment, the lower valve core 11 and the upper valve core 11 are directly connected through the intermediate force-transmitting pipe 70, and the two share a single valve stem 30 for driving. Therefore, as the valve stem 30 drives the two valve cores 11 to rotate the same angle, the purpose of regulating the flow rate can be achieved.

[0083] Similarly, whether the two rotary valve assemblies 10 are connected in series in the same direction or in the opposite direction does not affect their working state; the adaptive position changes of the various accessories such as the axial compression spring 60 generated hereby will not be elaborated here.

[0084] Comparative example:

[0085] For better understanding of the present invention, considering the particularity of the grooved window 11a, here the regulating valve applied in the present invention is compared with a traditional regulating valve with a DN5 caliber, and the regulation curve graph as shown in Figures 8-9 is obtained.

[0086] Figures 8-9 In Figure 8 is the regulation curve graph of the regulating valve with a DN5 caliber formed by a conventional valve core, Figure 9 is the regulation curve graph of the regulating valve with a DN5 caliber formed by the valve core 11 with a grooved window 11a adopted in the present invention.

[0087] It can be seen from the comparison between the two that the rated flow coefficient values of the two regulating valves are similar. However, from the actual test data, the change in the flow coefficient caused by the rotation of the valve core 11 of the present invention per unit angle is on average reduced by 219.96% compared with the traditional regulating valve, and the reduction amplitude is very large. Especially when the rotary valve assembly 10 is in a multi-stage series layout, when the two are combined, the flow control accuracy can be further improved, and the effect is very remarkable.

[0088] Certainly, for those skilled in the art, the present invention is not limited to the details of the above exemplary embodiments, but also includes the same or similar structures that can be implemented in other specific forms without departing from the spirit or basic characteristics of the present invention. Therefore, from any point of view, the embodiments should be regarded as exemplary and non-limiting. The scope of the present invention is defined by the appended claims rather than the above description. Therefore, all changes falling within the meaning and scope of the equivalent elements of the claims are intended to be included in the present invention. Any reference signs in the claims should not be regarded as limiting the claims involved.

[0089] In addition, it should be understood that although this specification is described according to embodiments, not every embodiment only contains an independent technical solution. This narrative way of the specification is only for clarity. Those skilled in the art should regard the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0090] The technologies, shapes, and structures not described in detail in the present invention are all well-known technologies.

Claims

1. A high differential pressure and micro flow regulating valve for a hydrogen supply system, characterized in that: A rotary valve assembly (10) including more than two groups of flow channels connected in series with each other. Each group of rotary valve assemblies (10) includes a valve core (11) and a valve seat (12) located outside the valve core (11) that are coaxially fitted with each other. A flow channel hole is provided at the valve seat (12), a longitudinal flow channel (11b) is coaxially provided at the valve core (11), and a grooved window (11a) communicating the flow channel hole with the longitudinal flow channel (11b) is provided on the outer wall of the valve core (11). The medium generates a flow rate adjustment action through the adjustment flow channel formed by the grooved window (11a) and the flow channel hole. Among them: Make an axial section coinciding with the axis of the valve core (11), and take the axis of the valve core (11) as the Y-axis, and the horizontal line perpendicular to the axis of the valve core (11) on this axial section as the X-axis to form a rectangular coordinate system with the origin of coordinates located at half the height of the valve core (11). At this time, the expressions of the first curve (I) and the second curve (II) passing through the origin of coordinates are: Among them: R1 and R2 are the distances from the intersection points of the corresponding curves and the generatrix of the valve core (11) to the X-axis; r1 is the radius of the small end of the valve core (11); r2 is the radius of the large end of the valve core (11); h is the height of the valve core (11); At the same time, make a cross-section perpendicular to the axis of the valve core (11) at half the height of the valve core (11). Establish a polar coordinate system with the point where the axis of the valve core (11) is located as the origin on this cross-section. At this time, the expression of the third curve (III) is obtained as: Among them: R is the diameter of the valve flow channel; r＝(r1+r2) / 2； The grooved window (11a) at the valve core (11) is a water droplet-shaped channel formed by cutting the closed triangle surrounded by the first curve (I), the second curve (II) and the generatrix of the valve core (11) along the extension direction of the third curve (III).

2. The high-pressure differential and micro-flow regulating valve for a hydrogen supply system according to claim 1, wherein: Along the flow direction of the medium, the maximum flow rate of each rotary valve assembly (10) decreases step by step.

3. The high-pressure differential and micro-flow regulating valve for a hydrogen supply system according to claim 1 or 2, characterized in that: The rotary valve assembly (10) is placed in a valve housing (20). A through hole (21) is vertically penetrated through the valve housing (20). Both ends of the through hole (21) are sealed by a sealing part, so as to form a sealed valve cavity in the through hole (21). The valve stem (30) penetrates through one of the sealing parts and extends into the valve cavity, and the extending end of the valve stem (30) is non-rotatably fitted with the valve core (11). The outer wall of the valve core (11) is frustum-shaped, so as to be fitted and fixed to the frustum-shaped valve seat (12) fixed on the valve cavity.

4. The high-pressure differential and micro-flow regulating valve for a hydrogen supply system according to claim 3, characterized in that: A first flow channel cavity (a) is penetrated through one side of the valve housing (20), and a second flow channel cavity (b) is penetrated through the other sealing part. The first flow channel cavity (a), the flow channel hole at the valve seat (12), the grooved window (11a) at the valve core (11), the longitudinal flow channel (11b) at the valve core (11), and the second flow channel cavity (b) are communicated with each other. One set of valve bodies is formed by one group of rotary valve assemblies (10) and the valve stem (30). Along the flow direction of the medium, or between the first flow channel cavities (a) of two adjacent sets of valve bodies, or between the first flow channel cavity (a) of one set of valve bodies and the second flow channel cavity (b) of another set of valve bodies, or between the second flow channel cavities (b) of two adjacent sets of valve bodies are communicated with each other through an intermediate pipeline (40), so that the flow channels of each rotary valve assembly (10) are connected in series with each other.

5. The high-pressure differential and micro-flow regulating valve for a hydrogen supply system according to claim 4, characterized in that: The valve stem (30) is in a non-rotating coaxial fit with the small end of the valve core (11) through splines; the sealing part includes an upper sealing part (51) at the top of the through hole (21) and a lower sealing part (52) at the bottom of the through hole (21). The upper sealing part (51) includes packing for filling the gap between the valve stem (30) and the through hole (21) and a gland that is in threaded fit at the top of the through hole (21) to compress the packing; the lower sealing part (52) includes a pipe joint that is in threaded fit at the bottom of the through hole (21). An axial compression spring (60) is arranged between the pipe joint and the large end of the valve core (11), and the lumen of the pipe joint forms the second flow channel cavity (b).

6. The high-pressure differential and micro-flow regulating valve for a hydrogen supply system according to claim 3, wherein: There are two sets of rotary valve assemblies (10) which are coaxially arranged with each other. The small ends of the valve cores (11) of the two sets of rotary valve assemblies (10) are arranged in series in the same valve cavity either in the same direction or in the opposite direction; the valve stems (30) of the two sets of rotary valve assemblies (10) are coaxial with each other and respectively penetrate through one of the sealing parts; a medium inlet (c) communicating with the flow channel hole at the valve seat (12) of the first set of rotary valve assemblies (10) is penetrated and arranged on the side wall of the valve housing (20) where the first set of rotary valve assemblies (10) is located, and a medium outlet (d) communicating with the flow channel hole at the valve seat (12) of the second set of rotary valve assemblies (10) is penetrated and arranged on the side wall of the valve housing (20) where the second set of rotary valve assemblies (10) is located, and the longitudinal flow channels (11b) at the valve cores (11) of the two sets of rotary valve assemblies (10) communicate with each other.

7. A high differential pressure and micro flow regulating valve for a hydrogen supply system according to claim 6, characterized in that: The valve stems (30) of the two sets of rotary valve assemblies (10) are both in a non-rotating coaxial fit with the large ends of the valve cores (11) through splines, and the small ends of the valve cores (11) face each other and have a gap; the sealing part includes an upper sealing part (51) at the top of the through hole (21) and a lower sealing part (52) at the bottom of the through hole (21). Both the upper sealing part (51) and the lower sealing part (52) include packing for filling the gap between the corresponding valve stem (30) and the through hole (21) and a gland that is in threaded fit at the corresponding end of the through hole (21) to compress the packing.

8. The high differential pressure and micro flow regulating valve for a hydrogen supply system according to claim 7, characterized in that: An axial compression spring (60) for axially pressing the valve core (11) against the valve seat (12) is sleeved on the splines.

9. The high-pressure differential and micro-flow regulating valve for a hydrogen supply system according to claim 3, wherein: There are two sets of rotary valve assemblies (10) which are coaxially arranged with each other. The longitudinal flow channels (11b) between the two adjacent valve cores (11) of the two sets of rotary valve assemblies (10) are communicated with each other through an intermediate force transmission pipe (70), so that the small ends of the valve cores (11) of the two sets of rotary valve assemblies (10) are arranged in series in the same valve cavity either in the same direction or in the opposite direction. At this time, the two valve cores (11) are synchronously driven by a single valve stem (30); a medium inlet (c) communicating with the flow channel hole at the valve seat (12) of this set of rotary valve assemblies (10) is penetrated and arranged on the side wall of the valve housing (20) where the first set of rotary valve assemblies (10) is located, and a medium outlet (d) communicating with the flow channel hole at the valve seat (12) of this set of rotary valve assemblies (10) is penetrated and arranged on the side wall of the valve housing (20) where the second set of rotary valve assemblies (10) is located.

10. A high-pressure differential and micro-flow regulating valve for a hydrogen supply system according to claim 9, characterized in that: The valve stem (30) is in a non-rotating coaxial fit with the large end of the valve core (11) above through splines. The small ends of the two valve cores (11) face each other and there is a gap between them, and they are connected to each other through the intermediate force transmission pipe (70) with a spline-structured outer wall having a communicating cavity. The sealing part includes an upper sealing part (51) located at the top of the through hole (21) and a lower sealing part (52) located at the bottom of the through hole (21). The upper sealing part (51) includes a packing for filling the gap between the valve stem (30) and the through hole (21) and a gland that is in a threaded fit at the top of the through hole (21) to compress the packing. The lower sealing part (52) is a threaded cover that is in a threaded fit at the bottom of the through hole (21), and an axial compression spring (60) is arranged between the threaded cover and the large end of the valve core (11) below.

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