CN110259977B

CN110259977B - High-pressure-difference multistage pressure-reducing adjusting ball valve

Info

Publication number: CN110259977B
Application number: CN201910390378.XA
Authority: CN
Inventors: 陈凤官; 王渭; 明友; 耿圣陶; 余宏兵; 叶晓节; 王勤; 杨玲玲; 靳卫华
Original assignee: Hefei General Machinery Research Institute Co Ltd
Current assignee: Hefei General Machinery Research Institute Co Ltd
Priority date: 2019-05-10
Filing date: 2019-05-10
Publication date: 2021-02-09
Anticipated expiration: 2039-05-10
Also published as: CN110259977A; CN112664671A; CN112664671B

Abstract

The high-pressure-difference multistage pressure-reducing regulating ball valve comprises a valve body, a ball body and a valve rod, wherein the ball body is arranged in the valve body, an inlet valve seat and an outlet valve seat are respectively arranged on the left side and the right side of the valve body, a cavity is formed in one side edge of the ball body, an interchangeable throttling component is arranged in the cavity, and a plurality of groups of through holes penetrating through the ball body are formed in the inner wall of the cavity in the. The throttling assembly comprises a plurality of independent channels, each independent channel and each group of through holes form an independent fluid channel, the fluid channels are divided into a plurality of sections, and the minimum sectional area in the fluid channels of the adjacent sections is gradually increased or unchanged along the fluid flowing direction. According to the invention, through the throttling component arranged in the cavity, multi-stage pressure reduction and noise reduction can be realized, the throttling component can be replaced, the throttling component is suitable for different working conditions, the maintenance difficulty is reduced, and the accurate regulation of flow/pressure can be realized under the condition of adapting to the working condition of high pressure difference due to the arrangement of the independent fluid channel.

Description

High-pressure-difference multistage pressure-reducing adjusting ball valve

Technical Field

The invention relates to the technical field of regulating valves, in particular to a high-pressure-difference multi-stage pressure-reducing regulating ball valve.

Background

The ball valve is widely applied to industries such as long-distance transmission pipelines, electric power, water conservancy and the like, and plays a significant role in national economy. The ball valve is mainly used for cutting off, distributing and changing the flow direction of a medium in a pipeline, and can be closed tightly only by rotating 90 degrees and a small rotating moment. The ball valve is most suitable for being used as a switch and a stop valve, but more and more ball valves are applied to adjustment in recent years.

There are limitations to the use of ball valves of conventional construction directly as regulating valves, for example: use at small openings should be avoided; and the method can not be applied to high-pressure-difference working conditions and the like. Even if the V-shaped adjusting ball valve has a high adjustable ratio and can adapt to media containing fibers, tiny solid particles, slurry and the like, the problem of adaptability of a high-pressure-difference working condition still cannot be solved.

In order to solve the problem of adaptability of the adjusting ball valve under the working condition of high pressure difference, technical personnel in the industry provide various technical schemes, but the multi-stage pressure reducing/noise reducing adjusting ball valve in the prior art still generally has the problems of large processing difficulty, difficult maintenance, poor working condition adaptability and the like.

Disclosure of Invention

In order to overcome the defects of the prior art, the invention provides a high-pressure-difference multi-stage pressure reducing regulating ball valve.

In order to achieve the purpose, the invention adopts the following technical scheme:

the high-pressure-difference multistage pressure-reducing adjusting ball valve comprises a valve body, a ball body and a valve rod, wherein the ball body is arranged in the valve body, the upper part of the ball body is connected with the valve rod, the valve rod rotates to drive the ball body to rotate, an inlet valve seat and an outlet valve seat are respectively arranged on the left side and the right side of the valve body, a cavity is formed in one side edge of the ball body, the central axis of the cavity in the length direction is perpendicular to the central axis of the valve rod, a replaceable throttling assembly is arranged in the cavity, a plurality of groups of through holes penetrating through the ball body are formed in the inner wall of the cavity in the length direction, and when the;

the throttling assembly comprises a plurality of independent channels, each independent channel and each group of through holes form an independent fluid channel, the fluid channels are divided into a plurality of sections, and the minimum sectional area in the fluid channels of the adjacent sections is gradually increased or unchanged along the fluid flowing direction.

Optimized, the orifice assembly includes hugs closely the polylith orifice plate of array on along cavity length direction, be provided with the discharge orifice on the adjacent orifice plate, the discharge orifice falls into the multiunit, the discharge orifice group one-to-one that overflows on every group discharge orifice and the left and right sides orifice plate forms the fluid passage section, be close to the discharge orifice group and multiunit through-hole one-to-one on the import disk seat, the setting angle that staggers between discharge orifice and the relative through-hole on the orifice plate of cavity innermost, and the setting angle that staggers of discharge orifice that adjacent orifice plate is relative, along the fluid flow direction, the angle that staggers of adjacent orifice plate is unchangeable or diminishes, corresponding cross area that makes adjacent orifice plate is unchangeable.

Preferably, the side of the inner surface of the pore plate facing the through hole is provided with a groove, the groove is internally provided with a plurality of overflowing holes, and the hole in each groove forms an overflowing hole group.

Preferably, the grooves are a plurality of annular grooves which are arranged outwards from the center by taking the center of the pore plate as a circle center, and a plurality of overflowing holes are formed in each annular groove along the central annular array of the pore plate.

Preferably, waist-shaped grooves which use the center of the pore plate as a central annular array are arranged on one side edge of the pore plate, and an overflowing hole is arranged in each waist-shaped groove.

Optimized, the side close to the through hole in the two adjacent pore plates is a first pore plate, the other pore plate is a second pore plate, the horizontal projection of the overflowing hole in the first pore plate on the second pore plate is located in the groove of the second pore plate, and the overflowing hole in the groove is staggered with the horizontal projection.

Preferably, the throttling assembly comprises a plurality of sleeves which are sleeved, and a fluid passage is formed in a gap between each adjacent outer sleeve and each adjacent inner sleeve.

Preferably, the cross section of the fluid channel is in a tooth-shaped gradually-expanding shape in the flow direction, and a left end support plate and a right end support plate for fixing all sleeves are arranged at two ends of each sleeve.

Optimally, a spiral groove formed by a convex block or a groove is arranged on the contact surface of the sleeve close to the outer side and the sleeve close to the inner side, and the spiral groove is of a unidirectional spiral structure or a bidirectional hedging spiral structure; the spiral groove is single-stranded or multi-stranded.

Preferably, the inlet valve seat is of a V-shaped structure, and a throttling lip edge is arranged on the inner side wall of the inlet valve seat.

The invention has the advantages that:

(1) according to the invention, the cavity is arranged in the ball body, and the throttling component is arranged in the cavity, so that multistage pressure reduction and noise reduction can be realized, the throttling component can be replaced, the maintenance difficulty is reduced, and impurities can be conveniently cleaned. The arrangement of the independent fluid channel can realize the accurate adjustment of flow/pressure under the condition of adapting to the working condition of high pressure difference.

(2) According to the invention, a plurality of pore plates are tightly attached to the array along the length direction of the cavity, so that a plurality of independent fluid channels are ensured. The flow channel is bent and bent by the staggered set angle of each group of through holes and the corresponding flow through hole group and the adjacent flow through hole groups, so that the energy of the fluid is dissipated, the flow speed is reduced, the minimum sectional area of the fluid channel in the adjacent section is gradually increased or unchanged along the flow direction of the fluid, and the effects of high pressure difference and multistage pressure reduction and noise reduction are finally realized.

(3) According to the invention, the annular groove or the waist-shaped groove is arranged on the side plate, and then the overflowing hole is arranged on the groove, so that a more tortuous fluid passage structure can be formed, and the effects of pressure reduction and noise reduction are further improved.

(4) The sleeve is sleeved, the cross section of the fluid channel is in a tooth-shaped gradually-expanding type, namely the cross section of the fluid channel at the tooth crest is gradually increased in the flowing direction of fluid, so that the processing is convenient, and specifically, the tooth shape in the tooth-shaped gradually-expanding type can be a triangle, a sawtooth, a trapezoid or an arc, and can also be processed into different ring grooves.

(5) Through leaning on outside sleeve and leaning on the coaxial intussusception of inboard sleeve contact to be fixed in the sleeve scheme of the second kind, closely laminate with spheroid one side in the spheroid to need not support, independent fluid passage is realized to the helicla flute about the stranded, and uses one-way helical structure or two-way offset helical structure, and when the fluid flows, its decompression effect is better showing. The arrangement of the multi-strand spiral groove can also improve the flow capacity.

(6) The orifice plate type throttling assembly or the sleeve type throttling assembly can realize multi-stage pressure reduction and noise reduction under the working condition of high pressure difference. Set up telescopic throttling assembly of multilayer axial, the positive and negative spiral of the stranded positive and negative rotation that has on it, when the fluid flows in the spiral groove, can strike the energy dissipation each other, the flow is longer, can realize the decompression noise reduction effect that is showing.

(7) The high-pressure-difference adjusting ball valve has a compact structure, one side of the ball body is provided with the cavity, the other side of the ball body keeps the spherical surface, the spherical surface is provided with a plurality of groups of through holes, the adjusting ball valve can be opened/closed when the valve rod is rotated, and the flow channel and the pressure reducing channel thereof are changed step by step in the opening/closing process.

(8) The throttling part is formed on the throttling lip edge by the throttling lip edge of the valve seat, so that the main sealing surface and the auxiliary sealing surface are protected, and the service life of the valve is prolonged.

Drawings

Fig. 1-2 are schematic structural diagrams of a multi-stage throttling assembly regulating ball valve with a multi-layer flat laminated orifice plate.

Fig. 3-4 are schematic structural diagrams of a multi-stage throttling assembly adjusting ball valve with a multi-layer axial sleeve.

Fig. 5 is a schematic structural diagram of a sphere.

FIG. 6 is a schematic view of a first configuration of an inlet valve seat.

FIG. 7 is a second schematic view of the inlet valve seat.

FIG. 8 is a schematic view of a structure of a hole plate in example 1.

FIG. 9 is a schematic view of a structure of a hole plate in example 2.

FIG. 10 is a schematic view of a third orifice plate configuration.

Fig. 11 is a schematic structural view of a sleeve type throttle unit (stepwise expansion) in embodiment 3.

FIG. 12 is a schematic view of the structure of a sleeve-type throttling element (multi-strand forward and reverse spiral grooves) in example 4.

FIG. 13 is a flow path with orifice plates of a first of the group A versions of the throttling assembly offset by different angles.

FIG. 14 is a schematic flow path diagram of a second version of the group A version of the throttling assembly.

FIG. 15 is a flow path with orifice plates of a third of the group A versions of the throttling assembly offset by different angles.

The notations in the figures have the following meanings:

1-left valve body 2-right valve body 3-sphere 31-through hole 32-cavity 33-notch

4-outlet valve seat 5-inlet valve seat 41-flow passage orifice 42-leading-in angle

43-primary seal face 44-secondary seal face 45-throttling lip

61-orifice plate 610-overflowing hole 611-annular groove 612-kidney-shaped groove

62-sleeve 620-projection 621-first sleeve 622-second sleeve 623-third sleeve

624-bidirectional hedging spiral structure 625-unidirectional spiral structure

7-elastic retainer ring 81-left end support plate 82-right end support plate

101-valve rod 102-gland 103-packing 104-central bolt nut

Detailed Description

1-12, the high pressure difference multi-stage pressure reducing regulating ball valve comprises a valve body, a ball body 3 and a valve rod 101, wherein the valve body can be of a top-mounted type or a two-piece type or a three-piece type, and the ball body 3 can be a fixed ball or a floating ball. In the embodiment, the valve body is of two pieces and respectively consists of a left valve body 1 and a right valve body 2. The ball 3 is arranged in the valve body. The upper portion of the ball body 3 is connected with the valve rod 101, the ball body 3 is driven to rotate after the valve rod 101 rotates, and the left side and the right side of the valve body are respectively provided with an inlet valve seat 5 and an outlet valve seat 4. The ball 3 is also provided with a notch 33 which is connected with the valve rod 101, and the notch 33 can be a square groove or a flat groove or a spline groove. The valve rod 101 seal can be a graphite packing 103 seal or a PTFE packing 103 seal or an O-ring seal, and a gland 102 is arranged above the valve body seal. The driving means for driving the valve rod 101 in rotation may be pneumatic or electric or hydraulic or manual.

The working principle of the adjusting ball valve is as follows: the driving device drives the valve rod 101 to rotate, and the valve rod 101 is connected with the sphere 3, so that the valve rod 101 drives the sphere 3 to rotate. Since the ball 3 is free to rotate between the seats, the ball 3 is driven by the valve stem 101 to rotate about the axis of the valve stem 101 between the seats.

In order to realize the fluid passage in the ball 3, a cavity 32 is formed in the ball 3, and a central axis of the cavity 32 in the length direction is perpendicular to a central axis of the valve rod 101. The cavity 32 is internally provided with a replaceable throttling component, the inner wall of the cavity 32 in the length direction is provided with a plurality of groups of through holes 31 penetrating through the ball body 3, and the through holes 31 are arranged in an array. When the through hole 31 has an intersection area with the inlet valve seat 5 during the rotation of the ball 3, the throttle assembly has an intersection area with the outlet valve seat 4. In this embodiment, the orifice assembly faces the outlet valve seat 4 when the through bore 31 faces the inlet valve seat 5. The cavity 32 may be prismatic or cylindrical. The outer edge of the throttling assembly is in close abutment with the inner wall of the chamber 32. If the throttling component is a prism, the corresponding throttling component is a prism, so that the relative position between the throttling components does not need to be fixed by an additional structure, and if the throttling component is a cylinder, the corresponding throttling component is also a cylinder, so that the throttling component can rotate in the cavity 32. In the following embodiments, a cylindrical shape is taken as an example, and the axis of the cylindrical shape coincides with the center line of the cavity 32 in the length direction.

The throttling assembly comprises a plurality of independent channels, each independent channel and each group of through holes 31 form an independent fluid channel, and the flow channel orifices on the outlet valve seat 4 and the inlet valve seat 5 are matched with the fluid channels to complete the opening and closing adjustment work of the valve. Each fluid passage has a constant sectional area and/or an enlarged sectional area in a direction from the inside to the outside of the longitudinal direction of the chamber 32, i.e., a fluid flow direction.

The throttling assembly comprises a plurality of schemes, and different throttling assembly schemes are described below respectively.

Group A scheme of throttling assembly

The orifice component comprises a plurality of orifice plates 61 tightly attached to the array along the length direction of the cavity 32, flow holes 610 are formed in the adjacent orifice plates 61, the flow holes 610 are divided into a plurality of groups, the flow hole groups on the flow holes 610 in each group and the orifice plates 61 on the two adjacent sides form fluid channel sections in a one-to-one correspondence mode, the flow hole groups close to the inlet valve seat 5 are in one-to-one correspondence with the through holes 31 in the plurality of groups, the flow holes on the orifice plate 61 on the innermost side of the cavity 32 and the through holes 31 opposite to each other are staggered to set angles, the flow holes opposite to the adjacent orifice plates 61 are staggered to set angles, the staggered angles of the adjacent orifice plates 61 are not changed or changed along the fluid flowing direction, when the staggered angles of the adjacent orifice plates 61 are.

The orifice plate 61 is provided with a plurality of schemes, as shown in fig. 8, the first scheme is that the orifice plate 61 is a circular cylindrical plate, the overflowing holes 610 are directly formed in the thickness direction of the orifice plate 61, and the adjacent orifice plates 61 are staggered by a set angle, so that the cross area of the corresponding overflowing holes 610 on the adjacent orifice plates 61 is smaller than the aperture of the overflowing holes 610, in the scheme, the orifice plates 61 can be sequentially staggered by a uniform angle in the fluid flowing direction, or the staggered angles are sequentially decreased gradually. The fluid channels formed in the way are independent channels, and the throttle area of the fluid channels can be adjusted according to the requirements of working conditions, so that the remarkable pressure reduction and noise reduction effects can be obtained.

In this solution, different shapes of flow channels can be obtained depending on the angle of staggering, as shown in fig. 13. The orifice plates 61 arranged in sequence from the position close to the through hole 31 along the length direction of the cavity are respectively marked as an orifice plate A1, an orifice plate B1, an orifice plate A2, an orifice plate B2, an orifice plate A3 and an orifice plate B3, the axes of the overflowing holes 610 in the orifice plate A1, the orifice plate A2 and the orifice plate A3 are coincident, and the axes of the overflowing holes 610 in the orifice plate B1, the orifice plate B2 and the orifice plate B3 are coincident. The orifice plate A1 and the orifice plate B1 are staggered at a certain angle along one direction, the orifice plate B1 and the orifice plate A2 are staggered at a certain angle along the other direction, and the orifice plate B2, the orifice plate A3 and the orifice plate B3 are arranged repeatedly to form the scheme of the left figure in the figure 13.

The orifice plates 61 which are sequentially arranged from the position close to the through hole 31 along the length direction of the cavity are respectively marked as an orifice plate A1, an orifice plate B1, an orifice plate A2, an orifice plate B2, an orifice plate A3 and an orifice plate B3, and the orifice plate A1, the orifice plate B1, the orifice plate A2, the orifice plate B2, the orifice plate A3 and the orifice plate B3 are sequentially staggered by a set angle along a certain direction, so that the scheme in the middle diagram of FIG. 13 is formed.

The orifice plates 61 which are sequentially arranged from the position close to the through hole 31 along the length direction of the cavity are respectively marked as an orifice plate A1, an orifice plate B1, an orifice plate A2, an orifice plate B2, an orifice plate A3 and an orifice plate B3, the orifice plate A1, the orifice plate B1 and the orifice plate A2 are sequentially staggered by a set angle along a certain direction, and the orifice plate B2, the orifice plate A3 and the orifice plate B3 are sequentially staggered by a set angle towards the other direction, so that the scheme of the right figure in fig. 13 is formed.

In addition, a groove is formed in one side edge in the pore plate 61, a plurality of overflowing holes 610 are formed in the groove, and an overflowing hole group is formed in each groove. The grooves may be irregular or regular. For ease of machining, regular grooves are used here.

Specifically, as shown in fig. 1-2,5-7, and 9, the second scheme of the orifice plate 61 is: a plurality of annular grooves 611 which are arranged outwards from the center by taking the center of the orifice plate 61 as a circle center are arranged on one side edge of the orifice plate 61, and a plurality of overflowing holes 610 are arranged in each annular groove 611 in an annular array along the center of the orifice plate 61.

In this embodiment, the orifice plates 61 are sequentially provided from the position near the through hole 31 along the length direction of the chamber, and are respectively designated as orifice plate a1, orifice plate B1, orifice plate a2, orifice plate B2, and orifice plate A3. Any overflow hole on the orifice plate A1 is positioned in the corresponding annular groove of the orifice plate B1 in horizontal projection on the orifice plate B1 and is positioned between two overflow holes on the orifice plate B1, and other orifice plates are arranged in the manner described above, so that the scheme of figure 14 is formed.

As shown in fig. 1-2,5-7,10, a third version of the orifice plate 61: one side of the orifice plate 61 is provided with waist-shaped grooves 612 which are annularly arrayed by taking the center of the orifice plate 61 as the center, and each waist-shaped groove 612 is internally provided with an overflowing hole 610. Specifically, the side of two adjacent pore plates 61 close to the through hole 31 is a first pore plate, the other pore plate is a second pore plate, the horizontal projection of the overflowing hole 610 on the first pore plate on the second pore plate is located in the groove of the second pore plate, and the overflowing hole 610 in the groove is arranged in a staggered manner with the horizontal projection. Along the fluid flow direction, the sphere 3 is tightly attached to the pore plate 61, and the pore plate 61 is tightly attached to the pore plate 61, and the pore plates 61 are staggered by uniform angles in sequence. Compared with the first scheme of the orifice plate 61, the second scheme and the third scheme can form a more zigzag throttling flow passage structure, and further improve the decompression and noise reduction effects.

In this scheme, the orifice plates 61, which are provided in this order from the vicinity of the through hole 31 along the length direction of the chamber, are designated as an orifice plate a1, an orifice plate a2, an orifice plate A3, an orifice plate a4, and an orifice plate a5, respectively. The projection of any flow aperture of orifice plate a1 is located at one end of a corresponding kidney slot 612 in orifice plate a2, the other end of the kidney slot 612 being provided with a flow aperture. In the left scheme of fig. 15, the through-flow holes of the waist-shaped grooves 612 of the orifice plate a1, the orifice plate A3 and the orifice plate a5 are coaxially arranged, and the through-flow holes of the waist-shaped grooves 612 of the orifice plate a2 and the orifice plate a4 are coaxially arranged. In the right sub-scheme in fig. 15, the waist-shaped grooves of the orifice plate a1, the orifice plate a2, the orifice plate A3, the orifice plate a4 and the orifice plate a5 are all arranged on the same side of the waist-shaped groove.

Relative position can be guaranteed through the locating pin between above three kinds of orifice plate 61 structures, then fix through central bolt nut 104 or circlip 7, the orifice plate 61 that central bolt nut 104 axial fixity set gradually.

Group B scheme of throttling component

The throttling assembly includes a plurality of sleeves 62 that are nested, with the space between each adjacent outer sleeve 62 and inner sleeve 62 forming an independent fluid passage. The group B of schemes includes a plurality of schemes, each of which is described below.

First solution formed by a plurality of sleeves 62: as shown in fig. 3 and fig. 11, in this embodiment, there are 3 sleeves 62, which are respectively a first sleeve 621, a second sleeve 622, and a third sleeve 623 that are coaxially sleeved, two ends of the first sleeve 621, the second sleeve 622, and the third sleeve 623 are provided with a left end support plate 81 and a right end support plate 82, thereby ensuring that the first sleeve 621, the second sleeve 622 and the third sleeve 623 are coaxially arranged, specifically, the left end support plate 81 and the right end support plate 82 are both provided with ring grooves or pin holes for fixing the first sleeve 621, the second sleeve 622 and the third sleeve 623, and are also provided with liquid passing holes through which fluid can pass, an independent fluid passage is formed between the first sleeve 621 and the second sleeve 622, another independent fluid passage is formed between the second sleeve 622 and the third sleeve 623, the horizontal section of the fluid channel is in a tooth-shaped gradually-expanding shape in the flow direction, so that the decompression and noise reduction effects of the fluid channel can be improved. A plurality of second sleeves 622 can be sleeved, and the plurality of second sleeves 622 form a throttling channel, and the channels are independent along the radial direction; the structure can be used for conveniently processing different groove-shaped structures, such as triangles, sawteeth, trapezoids, circular arcs and the like, and can also be used for processing different ring grooves so that the throttling area of the ring grooves is gradually increased along the flow direction.

Second solution formed by a plurality of sleeves 62: as shown in fig. 4 and 12, in this embodiment, there are 3 sleeves 62. The contact surfaces of the sleeve close to the outer side and the sleeve close to the inner side are provided with spiral grooves formed by a convex block 620 or a groove, wherein the spiral grooves can be formed by protruding or grooves arranged on one of the sleeve 62 close to the outer side or the sleeve 62 close to the inner side, the other sleeve 62 is a smooth surface arrangement mode, or grooves or protrusions are arranged on opposite surfaces of the two sleeves, the spiral grooves are of a one-way spiral structure 625 or a two-way hedging spiral structure 624, can be single-stranded or multi-stranded, the number of the spiral grooves in two directions is equal, the spiral grooves are uniformly crossed, and single-stranded spiral grooves with different rotation directions are arranged on the contact surfaces of the two adjacent sleeves. In this embodiment, the adjacent sleeves 62 have projections or recesses on both their inner and outer surfaces forming helical grooves, or projections or recesses on the outer surface of the inner sleeve only in the adjacent sleeve 62 for ease of machining. When fluid flows through the throttling channel formed by the multi-strand bidirectional hedging spiral structure 624, the pressure reducing effect is more remarkable, and meanwhile, the circulation capacity can be improved.

The outlet valve seat 4 and the inlet valve seat 5 are both circular and have a leading-in angle 42, a main sealing surface 43, an auxiliary sealing surface 44 and a flow passage orifice 41, and one of the two schemes is that as shown in fig. 6, the flow passage orifice 41 is arranged in the center of the inlet valve seat 5 and the outlet valve seat 4, and the flow passage orifice 41 is circular. Alternatively, as shown in fig. 7, the flow passage opening 41 is V-shaped or otherwise shaped, and if it is a non-circular opening, it is provided with a throttling lip 45, in this embodiment the flow passage opening 41 of the inlet valve seat 5 is V-shaped.

The invention is not to be considered as limited to the specific embodiments shown and described, but is to be understood to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the invention as defined by the appended claims.

Claims

1. The high-pressure-difference multistage pressure-reducing regulating ball valve comprises a valve body, a ball body (3) and a valve rod (101), the ball body (3) is arranged in the valve body, the upper part of the ball body (3) is connected with the valve rod (101), the valve rod (101) rotates to drive the ball body (3) to rotate, the left side and the right side of the valve body are respectively provided with an inlet valve seat (5) and an outlet valve seat (4), it is characterized in that a cavity (32) is arranged on one side of the sphere (3), the central axis of the cavity (32) in the length direction is vertical to the central axis of the valve rod (101), a replaceable throttling component is arranged in the cavity (32), a plurality of groups of through holes (31) penetrating through the ball body (3) are arranged on the inner wall of the cavity (32) in the length direction, in the rotating process of the ball body (3), when the through hole (31) and the inlet valve seat (5) have a cross area, the throttling component and the outlet valve seat (4) have a cross area;

the throttling assembly comprises a plurality of independent channels, each independent channel and each group of through holes (31) form an independent fluid channel, the fluid channels are divided into a plurality of sections, and the minimum sectional area in the fluid channels of the adjacent sections is gradually increased or unchanged along the fluid flowing direction;

the orifice assembly includes along polylith orifice plate (61) of cavity (32) length direction facial make-up array, be provided with overflow hole (610) on adjacent orifice plate (61), overflow hole (610) divide into the multiunit, overflow hole group one-to-one on every group overflow hole (610) and the left and right sides orifice plate (61) forms the fluid passage section, be close to overflow hole group and multiunit through-hole (31) one-to-one on the import disk seat (5), stagger between the overflow hole and relative through-hole (31) on the orifice plate (61) of cavity (32) innermost side and set for the angle, and the relative overflow hole of adjacent orifice plate (61) staggers and sets for the angle, along the fluid flow direction, the angle that adjacent orifice plate (61) staggers is unchangeable or diminishes, the corresponding cross area that makes adjacent orifice plate (61) is unchangeable or grow.

2. The high differential pressure multistage pressure reducing and regulating ball valve according to claim 1, wherein the side of the orifice plate (61) facing the through hole (31) is provided with a groove, a plurality of overflowing holes (610) are arranged in the groove, and the hole in each groove forms an overflowing hole group.

3. The high pressure difference multi-stage pressure reducing regulating ball valve as claimed in claim 2, wherein the groove is a plurality of annular grooves (611) arranged outward from the center with the center of the orifice plate (61) as a center, and a plurality of overflowing holes (610) are arranged in each annular groove (611) along the central annular array of the orifice plate (61).

4. The high-pressure-difference multistage pressure-reducing regulating ball valve as claimed in claim 2, wherein an annular array of kidney-shaped grooves (612) is arranged on one side of the orifice plate (61) and centered on the center of the orifice plate (61), and each kidney-shaped groove (612) is internally provided with one overflowing hole (610).

5. The high-pressure-difference multi-stage pressure-reducing regulating ball valve according to claim 2, wherein one of the two adjacent orifice plates (61) close to the through hole (31) is a first orifice plate, the other orifice plate is a second orifice plate, a horizontal projection of the overflowing hole (610) in the first orifice plate on the second orifice plate is positioned in the groove of the second orifice plate, and the overflowing hole (610) in the groove of the second orifice plate is arranged in a staggered manner from the horizontal projection.

6. A high differential pressure multistage pressure reducing regulating ball valve according to claim 1, characterized in that the inlet valve seat (5) is of V-shaped structure and is provided with a throttling lip (45) on its inner side wall.