WO2023130949A1 - 切换用夹管阀阀头及夹管阀阀组 - Google Patents

切换用夹管阀阀头及夹管阀阀组 Download PDF

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Publication number
WO2023130949A1
WO2023130949A1 PCT/CN2022/140183 CN2022140183W WO2023130949A1 WO 2023130949 A1 WO2023130949 A1 WO 2023130949A1 CN 2022140183 W CN2022140183 W CN 2022140183W WO 2023130949 A1 WO2023130949 A1 WO 2023130949A1
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WIPO (PCT)
Prior art keywords
valve
valve head
pipe groove
pinch
head
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PCT/CN2022/140183
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English (en)
French (fr)
Inventor
祝家彦
王杰武
王昊原
徐江运
徐龙渤
徐茏林
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浙江金仪盛世生物工程有限公司
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Publication of WO2023130949A1 publication Critical patent/WO2023130949A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
    • F16K11/20—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members
    • F16K11/22—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members with an actuating member for each valve, e.g. interconnected to form multiple-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K7/00—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves
    • F16K7/02—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with tubular diaphragm
    • F16K7/04—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with tubular diaphragm constrictable by external radial force
    • F16K7/045—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with tubular diaphragm constrictable by external radial force by electric or magnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K7/00—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves
    • F16K7/02—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with tubular diaphragm
    • F16K7/04—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with tubular diaphragm constrictable by external radial force
    • F16K7/07—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with tubular diaphragm constrictable by external radial force by means of fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L41/00—Branching pipes; Joining pipes to walls
    • F16L41/02—Branch units, e.g. made in one piece, welded, riveted
    • F16L41/03—Branch units, e.g. made in one piece, welded, riveted comprising junction pieces for four or more pipe members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L41/00—Branching pipes; Joining pipes to walls
    • F16L41/08—Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of the wall or to the axis of another pipe
    • F16L41/16—Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of the wall or to the axis of another pipe the branch pipe comprising fluid cut-off means

Definitions

  • the present application relates to the relevant technical field of pinch valves, in particular to a valve head of a pinch valve for switching and a valve group of a pinch valve.
  • valve head needs to have a support portion with a certain area. To avoid the reduction of the strength of the valve head due to too many pipe grooves in the valve body, that is, too much hollow area; Cost, thereby increasing the overall manufacturing cost of the valve group.
  • a pinch valve valve head and a pinch valve valve group for switching are provided.
  • the present application firstly provides a pinch valve valve head for switching, including the valve head; the valve head is provided with at least two pipe grooves, and the two through-holes of each pipe groove are respectively located at two ends of the valve head.
  • two adjacent sides, and a pair of adjacent sides of the valve head has at most one pipe groove, and the pipe groove opens toward the ridge line formed by the two adjacent sides;
  • the distance between the center line of the pipe groove and the corresponding ridge line is 6.7 mm to 19.3 mm;
  • the first end surface of the valve head is also provided with at least two valve plate through holes, and the pipe groove and the The through holes of the valve plates correspond to each other and communicate with each other.
  • the included angle formed by the centerline of the tube groove and the corresponding two adjacent side surfaces is the same.
  • valve head is a cuboid, and the included angle between the centerline of the pipe groove and the corresponding side is 45°.
  • the first end surface of the valve head is square and four pipe grooves are opened on the valve head.
  • the first intersection line formed by the inner walls along the direction of approaching each other is located on the side surface.
  • the pipe groove has a diameter ranging from 12.7 mm to 25.4 mm.
  • a pinch valve valve group comprising a base plate, a plurality of pinch valves, and a pinch valve valve head for switching in any of the above embodiments; the first end surface is fixedly connected to one side of the base plate, and the pinch tube The valve is fixed on the other side of the base plate and corresponds to the through hole of the valve plate one by one, and one end of the pinch valve passes through the base plate and the through hole of the valve plate into the pipe groove.
  • the pinch valve includes a driver and a valve plate, the driver is fixed on the base plate, and the valve plate passes through the base plate and the through hole of the valve plate to the pipe groove Inside.
  • Fig. 1 is a schematic perspective view of a pinch valve valve group according to one or more embodiments.
  • FIG. 5 is a schematic diagram of an enlarged structure at point A in FIG. 1 .
  • FIG. 6 is a schematic perspective view of the three-dimensional structure of the pinch valve in FIG. 4 after being cut away.
  • valve head of the pinch valve for switching 1, the side; 2, the ridge line; 3, the first end surface; 4, the center line; 100, the hose; 110, the branch hose; 10, the valve head; 11. Pipe groove; 12. Valve plate through hole; 131. Notch; 132. Groove; 14.
  • a component when a component is said to be “mounted on” another component, it can be directly on the other component or there can also be an intervening component.
  • a component When a component is said to be “set on” another component, it may be set directly on the other component or there may be an intervening component at the same time.
  • a component When a component is said to be “fixed” to another component, it may be directly fixed to the other component or there may be an intervening component at the same time.
  • This application first provides a pinch valve valve head 1000 for switching, please refer to Fig. 1, Fig. 2 and Fig. 3, including the valve head 10; the valve head 10 is provided with at least two pipe grooves 11, and each pipe groove The two through openings of 11 are respectively located on two adjacent side surfaces 1 of the valve head 10, and a pair of adjacent side surfaces 1 of the valve head 10 have at most one pipe groove 11, and the pipe groove 11 faces the two adjacent side surfaces
  • the ridgeline 2 formed by 1 opens in the direction; the distance between the centerline 4 of the pipe groove 11 and the corresponding ridgeline 2 is 6.7mm-19.3mm; the first end surface 3 of the valve head 10 is also provided with at least two valve plates
  • the through holes 12, the tube grooves 11 correspond to and communicate with the through holes 12 of the valve plate one by one.
  • the area of the pipe groove 11 refers to the cross-sectional area of the pipe groove 11 along the direction perpendicular to its path length.
  • the cross-sectional area of the valve head 10 refers to the cross-sectional area of the valve head 10 along the direction perpendicular to the reciprocating movement of the pinch valve 30 .
  • the area of the pipe groove 11 in the valve head 10 is too large, that is, the area of the hollow part in the valve head 10 is too large, the strength of the valve head 10 will decrease. In order to ensure the strength of the valve head 10 and increase its reliability, it is necessary to increase the The volume of the valve head 10 is to increase the area of the solid part.
  • the area of the pipe groove 11 in the valve head 10 is the hollow area.
  • the ratio of the area ratio is defined as a stable value, so in order to ensure the strength of the valve head 10, the proportion of the pipe groove 11 needs to be smaller than the stable value. Since the above-mentioned stable value is a fixed value, by reducing the area of the pipe groove 11 in the valve head 10, the area of the valve head 10 required when the ratio of the area of the pipe groove 11 to the area of the valve head 10 is a stable value can be reduced, i.e.
  • valve head 10 Only a small valve head 10 is needed to make the strength of the valve head 10 meet the requirements of production and use; thus, while ensuring the high strength of the valve head 10, the volume of the valve head 10 is reduced as much as possible, and the material of the valve head 10 is reduced. cost effect.
  • the pipe groove 11 is a cylindrical groove.
  • the path length of the pipe groove 11 inside the valve head 10 can also be reduced, thereby reducing the valve head 10.
  • the area of the inner pipe groove 11 achieves the effect of reducing the volume of the valve head 10 .
  • the distance between the centerline 4 of the pipe groove 11 and the corresponding ridgeline 2 is 6.7 mm to 19.3 mm, so as to reduce the distance between the centerline 4 of the pipe groove 11 and the corresponding ridgeline 2 to reduce valve
  • the first 10 volume effects are 6.7 mm to 19.3 mm, so as to reduce the distance between the centerline 4 of the pipe groove 11 and the corresponding ridgeline 2 to reduce valve
  • the first 10 volume effects are 6.7 mm to 19.3 mm.
  • the distance between the center line of the pipe groove 11 and the corresponding ridge line 2 is greater than or equal to the radius of the pipe groove 11, which can ensure that after the hose 100 is installed in the pipe groove 11, the part corresponding to the ridge line 2 is completely located on the In the pipe groove 11, the normal operation of the equipment is guaranteed.
  • the spacing of 6.7mm ⁇ 19.3mm the distance between the center line 4 of the pipe groove 11 and the corresponding ridge line 2 is reduced as much as possible, so as to achieve the effect of reducing the volume of the valve head 10.
  • the valve head 10 is a cuboid, and the angle between the center line 4 of the pipe groove 11 and the corresponding side 1 is 45°; in the embodiments shown in FIGS. 2 and 3 , the first end surface 3 of the valve head 10 is square and the valve head 10 is provided with four pipe grooves 11 , that is, each corner of the valve head 10 corresponds to a pipe groove 11 .
  • the movement freedom of the branch hoses 110 is limited by the abutment effect between the branch hoses 110 and the inner walls of the pipe grooves 11, so that the branch hoses 110
  • the road hose 110 only has a degree of freedom of movement along the length direction of the pipe groove 11 and toward the direction corresponding to the ridge line 2 .
  • the hose 100 is fixed and formed by a plurality of branch hoses 110, among which the four branch hoses 110 in the four pipe grooves 11 are connected first in turn, so the corresponding branch hoses in the four pipe grooves 11 are Under the limit action of 110, the hose 100 is completely limited, so as to prevent the hose 100 from translational shaking in the valve head 10 and ensure that the hose 100 is installed stably.
  • the first intersection line 14 formed by the inner walls of any two adjacent pipe grooves 11 along the direction of approaching each other is located on the side surface 1 of the valve head 10 .
  • Two adjacent pipe grooves 11 or their extended intersection parts correspond to the bending connection part of the branch hose 110 in the two pipe grooves 11; if the intersection position of adjacent pipe grooves 11 is located in the valve head 10, it will increase The area of the hollow part in the valve head 10 is large. In order to ensure the overall strength of the valve head 10 , it is necessary to increase the area of the solid part in the valve head 10 , resulting in an increase in the overall volume of the valve head 10 .
  • the first intersection line 14 formed by their inner walls along the direction of approaching each other is located on the side 1 of the valve head 10, that is, the intersection position of adjacent pipe grooves 11 is located outside the valve head 10 ;
  • the four pipe grooves 11 have been able to realize the complete limit of the flexible pipe 100 through the four pipe grooves 11 to the limit of the branch hose 110, so it is not necessary to arrange the bending part of the branch hose 110 on the outside of the valve head 10 It will affect the installation stability of the hose 100 .
  • the pipe groove 11 has a diameter ranging from 12.7 mm to 25.4 mm for accommodating hoses 100 of different diameters.
  • the diameter of the pipe groove 11 can be selected according to the diameter of the hose 100, usually the diameter of the pipe groove 11 is equal to or slightly larger than the diameter of the hose 100, that is, the hose 100 will not be deformed after being installed in the pipe groove 11, and can be connected with the pipe The inner wall of the groove 11 is bonded. On the one hand, it prevents the hose 100 from being in a deformed state for a long time, resulting in shortened service life or even damage;
  • the diameter of the pipe groove 11 is 25.4mm, the radius is 12.7mm, and the distance between the center line 4 of the pipe groove 11 and the corresponding ridge line 2 is 19.3mm, that is, the distance between the pipe groove 11
  • the distance between the centerline 4 and the corresponding ridgeline 2 is greater than or equal to the radius of the pipe groove 11, so that the corresponding part of the hose 100 and the ridgeline 2 can be completely accommodated in the pipe groove 11 to ensure the normal operation of the equipment.
  • the diameter of the pipe groove 11 and the distance between the center line 4 and the corresponding ridge line 2 can also be selected from other values, as long as the diameter of the pipe groove 11 can match the diameter of the hose 100, and the center line 4 of the pipe groove 11 corresponds to The distance between the ridgelines 2 is greater than or equal to the radius of the pipe groove 11.
  • the pinch valve 30 can be installed to the valve head 10 through the valve plate through hole 12, and at least two valve plate through holes 12 are opened on the valve head 10, so that multiple clamps can be installed on the same valve head 10 in this application. Therefore, when installing the valve group, as long as a single valve head 10 is installed on the base plate 20, and then each pinch valve 30 is installed to the corresponding through hole 12 of the valve plate, the installation of the valve group can be completed. The installation workload when installing the valve head 10 to the base plate 20 is reduced, and the overall installation efficiency of the valve group is improved.
  • the driver 31 can drive the valve plate 32 to reciprocate along the axial direction of the valve plate through hole 12, so that the valve plate 32 can squeeze or loosen the branch hose 110 located in the pipe groove 11, so as to realize the closure and flow of the branch hose 110. flow through.
  • a notch 131 corresponding to the through hole 12 of the valve plate is provided in the valve head 10 , and the notch 131 communicates with the pipe groove 11 along the central axis of the through hole 12 of the valve plate.
  • the notch 131 is also communicated with the through hole 12 of the valve plate;
  • a groove 132 corresponding to the notch 131 is also provided in the valve head 10, and the groove 132 is set on the side of the pipe groove 11 away from the notch 131, and is connected with The pipe groove 11 communicates.
  • the valve plate 32 has a limiting block 321 that can be slidably connected with the notch 131 and the groove 132, and the sliding connection between the limiting block 321 and the corresponding notch 131 and the groove 132 prevents the valve plate 32 from moving along the through hole of the valve plate. Radial shaking occurs when the axial direction of 12 reciprocates, so as to increase the operation stability of the pinch valve 30 .
  • the valve plate 32 will abut against the inner wall of the pipe groove 11 , so that the pipe groove 11 cannot be completely blocked.
  • the groove 132 is set so that the valve plate 32 can move to the bottom wall of the groove 132 when it moves along the axis direction of the valve plate through hole 12. At this time, the valve plate 32 completely blocks the tube.
  • the groove 11 is used to ensure that the valve plate 32 can completely shut off the branch hose 110 by squeezing, so as to increase the reliability of the pinch valve 30 .
  • the driving member 31 may be a power assembly such as a motor or a cylinder.
  • the driver 31 is a cylinder
  • the cylinder includes a tension spring 311, a housing 312 and a bottom support 313, wherein the housing 312 is fixed on the bottom support 313, and one end of the tension spring 311 is It is fixed with the bottom support 313, and the other end is fixed with the valve plate 32.
  • the part of the valve plate 32 located inside the housing 312 is completely in contact with the inner wall of the housing 312 and is slidably connected.
  • the surface of the housing 312 is provided with an interface for connecting with the The air pump is connected.
  • the air pump starts to fill the cylinder with gas, and the gas pushes the valve plate 32 to overcome the tension of the tension spring 311 and move away from the driving member 31 until the hose 100 is clamped.
  • the air pump stops the air intake, and the valve plate 32 moves to the direction close to the driver 31 to reset under the pulling force of the tension spring 311, and the hose 100 flows through at this time.
  • the interface surfaces 314 of the cylinders are all away from the center of the valve head 10, and the interface surfaces 314 of any two adjacent cylinders are perpendicular to each other; by opening the cylinder connection ports away from the center of the valve head 10, even if the distance between the cylinders In smaller cases, since the air ports are facing outward, the air pipes inserted into the air ports of each cylinder will not interfere with each other, so that it is no longer necessary to reserve space for air pipes and other components between the cylinders, reducing the need for air pipes between the cylinders. Requirements for gaps between.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Housings (AREA)
  • Lift Valve (AREA)

Abstract

一种切换用夹管阀阀头(1000)及夹管阀阀组(2000)。该切换用夹管阀阀头(1000)，包括阀头(10)；阀头(10)贯穿开设有至少两个管槽(11)，每一管槽(11)的两个贯穿口分别位于阀头(10)的两个相邻侧面(1)，且阀头(10)的一对相邻侧面(1)至多开设一个管槽(11)，管槽(11)还朝向阀头(10)对应的两个相邻侧面(1)所形成的棱线(2)方向开口；管槽(11)的中心线(4)与对应的阀头(10)的棱线(2)之间的间距为6.7mm～19.3mm。

Description

切换用夹管阀阀头及夹管阀阀组
相关申请
本申请要求2022年1月4日申请的，申请号为202210000755.6，发明名称为“切换用夹管阀阀头及夹管阀阀组”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及夹管阀相关技术领域，特别是涉及一种切换用夹管阀阀头及夹管阀阀组。
背景技术
在生物制药生产设备或其他需要对多路液体进行切换的设备中，通常采取多个夹管阀以实现对多路液体的切换；
但是，多个独立设置的夹管阀在安装时，需要将每个夹管阀安装至对应的阀头，再将各个夹管阀与阀头安装至基板，导致安装过程较为繁琐；
而若将多个夹管阀安装至同一阀头，则需要在阀头内开设供软管穿设的管槽，且为保证阀头自身的牢固性，阀头需要具有一定面积的支撑部，以避免因阀体内管槽部分过多，即中空面积过多而导致阀头强度下降；因此，为同时保证管槽面积以及支撑部面积，会使得阀头体积较大，从而增加阀头的材料成本，进而增加阀组整体的制造成本。
发明内容
根据本申请的各种实施例，提供一种切换用夹管阀阀头及夹管阀阀组。
本申请首先提供一种切换用夹管阀阀头，包括阀头；所述阀头贯穿开设有至少两个管槽，每一所述管槽的两个贯穿口分别位于所述阀头的两个相邻的侧面，且所述阀头的一对相邻的所述侧面至多开设一个所述管槽，所述管槽朝向该两个相邻的所述侧面所形成的棱线方向开口；所述管槽的中心线与对应的所述棱线之间的间距为6.7mm～19.3mm；所述阀头的第一端面还开设有至少两个阀片通孔，所述管槽与所述阀片通孔一一对应且连通。
在其中一个实施例中，所述管槽的所述中心线与对应的两个相邻所述侧面所成的夹角角度相同。
在其中一个实施例中，所述阀头为长方体，所述管槽的所述中心线与对应的所述侧面之间的夹角为45°。
在其中一个实施例中，所述阀头的所述第一端面呈正方形且所述阀头开设有四个管槽。
在其中一个实施例中，任意两个相邻的所述管槽，其内壁沿相互靠近方向形成的第一条交汇线位于所述侧面。
在其中一个实施例中，所述管槽的直径范围为12.7mm～25.4mm。
在其中一个实施例中，所述管槽的直径为25.4mm，所述中心线与对应的所述棱线之间的间距为19.3mm。
一种夹管阀阀组，包括基板、多个夹管阀以及上述任一实施例的切换用夹管阀阀头；所述第一端面与所述基板的一侧固定连接，所述夹管阀固设于所述基板的另一侧且与所述阀片通孔一一对应，所述夹管阀的一端贯穿所述基板与所述阀片通孔至所述管槽内。
在其中一个实施例中，所述夹管阀包括驱动件以及阀片，所述驱动件固设于所述基板，所述阀片贯穿所述基板与所述阀片通孔至所述管槽内。
在其中一个实施例中，所述驱动件为气缸，所述气缸的接口面均背离所述阀头的中心，且任意相邻两个所述气缸的接口面互相垂直。
本申请的一个或多个实施例的细节在下面的附图和描述中提出。本申请的其它特征、目的和优点将从说明书、附图以及权利要求书变得明显。
附图说明
为了更好地描述和说明这里公开的那些发明的实施例和/或示例，可以参考一幅或多幅附图。用于描述附图的附加细节或示例不应当被认为是对所公开的发明、目前描述的实施例和/或示例以及目前理解的这些发明的最佳模式中的任何一者的范围的限制。
图1为根据一个或多个实施例的夹管阀阀组的立体结构示意图。
图2为图1中阀头剖开后的立体结构示意图。
图3为图1中的阀头后视方向的立体结构示意图。
图4为图1中夹管阀的立体结构示意图。
图5为图1中A处的放大结构示意图。
图6为图4的夹管阀剖开后的立体结构示意图。
图中，1000、切换用夹管阀阀头；1、侧面；2、棱线；3、第一端面；4、中心线；100、软管；110、支路软管；10、阀头；11、管槽；12、阀片通孔；131、槽口；132、槽沟；14、第一条交汇线；20、基板；30、夹管阀；31、驱动件；311、拉伸弹簧；312、壳体；313、底部支撑件；314、接口面；32、阀片；321、限位块；2000、夹管阀阀组。
以上主要元件符号说明结合附图及具体实施方式对本申请作进一步详细的说明。
具体实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明的是，当组件被称为“安装于”另一个组件，它可以直接在另一个组件上或者也可以存在居中的组件。当一个组件被认为是“设置于”另一个组件，它可以是直接设置在另一个组件上或者可能同时存在居中组件。当一个组件被认为是“固定于”另一个组件，它可以是直接固定在另一个组件上或者可能同时存在居中组件。
除非另有定义，本文所使用的所有的技术和科学术语与属于本申请的技术领域的技术人员通常理解的含义相同。本文中在本申请的说明书中所使用的术语只是为了描述具体的实施例的目的，不是旨在于限制本申请。本文所使用的术语“或/及”包括一个或多个相关的所列项目的任意的和所有的组合。
本申请首先提供一种切换用夹管阀阀头1000，请结合图1、图2以及图3所示，包括阀头10；阀头10贯穿开设有至少两个管槽11，每一管槽11的两个贯穿口分别位于阀头10的两个相邻的侧面1，且阀头10的一对相邻的侧面1至多开设一个管槽11，管槽11朝向该两个相邻的侧面1所形成的棱线2方向开口；管槽11的中心线4与对应的棱线2之间的间距为6.7mm～19.3mm；阀头10的第一端面3还开设有至少两个阀片通孔12，管槽11与阀片通孔12一一对应且连通。
为便于下文描述，将面积定义为按照图2将阀头10剖开后，所涉及的各 部件剖面的横截面积；此外，将占比定义为按照图2将阀头10剖开后，所涉及的各部件剖面的横截面积与阀头10的横截面积之比。
需要说明的是，当所涉及部件为管槽11时，管槽11的面积是指管槽11沿垂直于其路径长度方向的横截面积。阀头10的横截面积是指阀头10沿垂直于夹管阀30往复运动方向的横截面积。
若阀头10内管槽11的面积过大，即阀头10内中空部分的面积过大，会导致阀头10的强度下降，为保证阀头10的强度，增加其牢靠性，需要增大阀头10的体积以增大实体部分的面积。
本申请中，管槽11沿直线开设时，与阀头10相同且管槽11具有一定弧度的情况相比，能够减少管槽11位于阀头10内的路径长度，进而减小阀头10内管槽11的面积。
而每一管槽11的两个贯通口分别开设于阀头10的两个相邻的侧面1时，与管槽11的两个贯通口开设于阀头10的一组相对的侧面1的开设方式、或其他开设方式相比，同样能够减少管槽11位于阀头10内的路径长度，进而减小阀头10内管槽11的面积。由于阀头内管槽的面积即为阀头内的中空部分，因此，中空部分的减少使得阀头仅需要更小的实体部分即可保证阀头的强度，进而在保证阀头轻度的同时，达到了减少阀头的体积，减少阀头材料成本的效果。
阀头10内管槽11部分的面积即为中空面积，中空面积越大，阀头10的强度越低；若将阀头10强度要求恰好符合生产使用需求时，管槽11面积与阀头10面积之比的比值定义为稳定值，则为保证阀头10的强度，管槽11的占比需要小于稳定值。由于上述稳定值为定值，因此通过减小阀头10内管槽11的面积，能够减小管槽11面积与阀头10面积之比为稳定值时所需的阀头 10的面积，即仅需要较小的阀头10即可使得阀头10的强度符合生产使用需求；从而在保证阀头10具有较高强度的同时，尽可能减少了阀头10的体积，达到减少阀头10材料成本的效果。
此外，管槽11为圆柱槽，通过减少管槽11的中心线4与对应的棱线2之间的距离，同样能够减少管槽11位于阀头10内的路径长度，进而减小阀头10内管槽11的面积，达到减少阀头10体积的效果。
本申请中，管槽11的中心线4与对应棱线2之间的间距为6.7mm～19.3mm，以减小管槽11的中心线4与对应棱线2之间的间距，达到减少阀头10体积的效果。
在一些实施例中，管槽11的中心线4与对应棱线2之间的间距大于等于管槽11的半径。可以理解，管槽11的半径是指管槽11沿垂直于其路径长度方向的截面的半径。
若管槽11的中心线4与对应的棱线2之间的间距过小，可能由于管槽11过小，导致软管100与棱线2对应的部分沿软管100的径向突出于阀头10。
此情况下，一方面会导致软管100的限位不牢靠，软管100容易在生产工作过程中发生晃动，甚至脱离管槽11，影响设备正常运行。另一方面，由于夹管阀30需要与阀头10配合实现对软管100的夹紧截流，若软管100与棱线2对应的部分沿软管100的径向突出于阀头10，则会导致该部分突出于阀头10的软管100无法被夹管阀30完全夹紧，从而影响夹管阀30的截流效果。
而本申请中，管槽11的中心线与对应棱线2之间的间距大于等于管槽11的半径，能够保证软管100安装至管槽11后，其与棱线2对应的部分完全位于管槽11内，保证设备的正常运行。配合6.7mm～19.3mm的间距，尽可能减 小了管槽11的中心线4与对应的棱线2之间的距离，达到减少阀头10体积的效果。
在图2所示实施例中，管槽11的中心线4与对应的两个相邻侧面1所成的夹角角度相同。
在管槽11的中心线4与对应的棱线2之间的间距为定值的情况下，管槽11的中心线4与对应的两个相邻侧面1所成夹角角度相同时，相较于两个夹角角度不同的情况，前者的管槽11位于阀头10内的路径长度较短，从而能够达到进一步减少阀头10体积的效果。
在图2所示的实施例中，阀头10为长方体，管槽11的中心线4与对应的侧面1之间的夹角为45°；在图2和图3所示的实施例中，阀头10的第一端面3呈正方形且阀头10开设有四个管槽11，即阀头10的每一个棱角均对应一个管槽11。
因此当四个支路软管110分别安装至四个管槽11内后，通过支路软管110与管槽11内壁的抵接作用，从而限制支路软管110的移动自由度，使得支路软管110仅具有沿管槽11长度方向，以及朝向对应棱线2方向的移动自由度。
又由于软管100通过多根支路软管110固定形成，其中四个管槽11内的四个支路软管110依次首位相连，因此在四个管槽11对各自对应的支路软管110的限位作用下，使得软管100被完全限位，从而防止软管100在阀头10内发生平移晃动，保证软管100安装稳定。
在图2所示的实施例中，任意两个相邻的管槽11，其内壁沿相互靠近方向形成的第一条交汇线14位于阀头10的侧面1。
两个相邻管槽11或其延长后的交汇部分对应两个管槽11内支路软管110的弯折连接部分；若相邻管槽11的交汇位置位于阀头10内，则会增大阀头 10内的中空部分面积，为保证阀头10的整体强度，需要增加阀头10内实体部分面积，从而导致阀头10的整体体积增加。
本申请中，任意两个相邻的管槽11，其内壁沿相互靠近方向形成的第一条交汇线14位于阀头10的侧面1，即相邻管槽11的交汇位置位于阀头10外部；一方面通过四个管槽11对支路软管110的限位作用，已经能够实现对软管100的完全限位，因此将支路软管110的弯折部分设置于阀头10外部不会影响软管100的安装稳定性。
另一方面，由于支路软管110的弯折部分设置于阀头10外部，因此减小了阀头10内管槽11的面积，即减小了阀头10的中空面积，进而达到了减小阀头10体积的效果。
在一些实施例中，管槽11的直径范围为12.7mm～25.4mm，以用于容置不同直径的软管100。
管槽11的直径可根据软管100的直径进行选择，通常管槽11的直径等于或稍大于软管100的直径，即软管100安装至管槽11后不会发生变形，且能够与管槽11的内壁贴合。一方面避免软管100长时间处于变形状态导致寿命缩短甚至损坏，另一方面保证管槽11的内壁能够通过与软管100的抵接，为软管100提供可靠的限位。
在图2所示的实施例中，管槽11的直径为25.4mm，半径为12.7mm，管槽11的中心线4与对应的棱线2之间的间距为19.3mm，即管槽11的中心线4与对应的棱线2之间的间距大于等于管槽11的半径，从而使得软管100与棱线2对应部分能够完全容置于管槽11内，以保证设备正常运行。
当然，管槽11的直径以及中心线4与对应的棱线2之间的间距也可选择其他数值，只要管槽11直径能够与软管100直径匹配，且管槽11的中心线4 与对应的棱线2之间的间距大于等于管槽11的半径即可。
本申请第二方面提供一种夹管阀阀组2000，包括基板20、多个夹管阀30以及上述的切换用夹管阀阀头1000。第一端面3与基板20的一侧固定连接，夹管阀30固设于基板20的另一侧且与阀片通孔12一一对应，夹管阀30的一端贯穿基板20与阀片通孔12至管槽11内。
相关技术中在进行阀组安装时，需要先将各个传统阀头安装至基板20，再将各夹管阀30安装至对应的传统阀头，安装过程较为繁琐。
本申请中，夹管阀30能够通过阀片通孔12安装至阀头10，通过阀头10上开设至少两个阀片通孔12，使得本申请中同一阀头10上能够安装多个夹管阀30，因此在进行阀组安装时，只要将单个阀头10安装至基板20，再将各夹管阀30安装至对应的阀片通孔12，即可完成阀组的安装。减少了将阀头10安装至基板20时的安装工作量，提高了阀组整体的安装效率。
在图4和图5所示的实施例中，夹管阀30包括驱动件31以及阀片32，驱动件31固设于基板20，阀片32贯穿基板20与阀片通孔12至管槽11内。
驱动件31能够驱动阀片32沿阀片通孔12的轴线方向往复运动，从而通过阀片32挤压或放松位于管槽11内的支路软管110，实现支路软管110的截流与通流。
在图5所示的实施例中，阀头10内还开设有与阀片通孔12一一对应的槽口131，槽口131沿阀片通孔12的中轴线的方向与管槽11连通，槽口131还与阀片通孔12连通；阀头10内还开设有与槽口131一一对应的槽沟132，槽沟132开设于管槽11远离槽口131的一侧，且与管槽11连通。
阀片32具有能够与槽口131以及槽沟132滑动连接的限位块321，通过限位块321与对应槽口131以及槽沟132的滑动连接，以避免阀片32在沿阀 片通孔12的轴线方向往复运动时发生径向晃动，以增加夹管阀30的运行稳定性。
此外，相较于未开设槽沟132的情况下，阀片32会与管槽11的内壁抵接而导致无法将管槽11完全阻挡。本申请中通过开设槽沟132，使得阀片32在沿阀片通孔12的轴线方向运动过程时，能够运动至与槽沟132的底壁贴合抵接，此时阀片32完全阻挡管槽11，以保证阀片32能够通过挤压将支路软管110完全截流，以增加夹管阀30的可靠性。
驱动件31可以为电机或气缸等动力组件。在图6所示的实施例中，驱动件31为气缸，气缸包括拉伸弹簧311、壳体312以及底部支撑件313，其中，壳体312固设于底部支撑件313，拉伸弹簧311一端与底部支撑件313固设，另一端与阀片32固设，阀片32位于壳体312内部分与壳体312的内壁完全抵接并滑动连接，壳体312表面开设有接口，用于与气泵连通。
当需要阻断软管100流通时，气泵开始向气缸内充入气体，气体推动阀片32克服拉伸弹簧311的拉力向远离驱动件31的方向运动，直至夹紧软管100。
反之当需要软管100通流时，气泵停止进气，阀片32在拉伸弹簧311的拉力作用下向靠近驱动件31方向运动至复位，此时软管100通流。
此外，气缸的接口面314均背离阀头10的中心，且任意相邻两个气缸的接口面314互相垂直；通过将气缸接气口背离阀头10的中心开设，以使得即使各气缸之间间距较小的情况下，由于接气口朝向外侧，各气缸的接气口插接的气管也不会相互干涉，从而使得各气缸之间不再需要为气管等部件预留空间，降低了对各气缸之间预留间隙的要求。
而通过将任意相邻两个气缸的接口面314互相垂直，以使得任意两个相 邻的气缸的靠近侧端面互相平行，即相邻两个气缸之间能够紧密排布，从而减小了各气缸之间的间距，达到了减小夹管阀阀组2000整体体积的效果。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对发明专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。

Claims (10)

  1. 一种切换用夹管阀阀头，其特征在于，包括阀头；
    所述阀头贯穿开设有至少两个管槽，每一所述管槽的两个贯穿口分别位于所述阀头的两个相邻的侧面，且所述阀头的一对相邻的所述侧面至多开设一个所述管槽，所述管槽朝向该两个相邻的所述侧面所形成的棱线方向开口；
    所述管槽的中心线与对应的所述棱线之间的间距为6.7mm～19.3mm；
    所述阀头的第一端面还开设有至少两个阀片通孔，所述管槽与所述阀片通孔一一对应且连通。
  2. 根据权利要求1所述的切换用夹管阀阀头，其中，所述管槽的所述中心线与对应的两个相邻所述侧面所成的夹角角度相同。
  3. 根据权利要求2所述的切换用夹管阀阀头，其中，所述阀头为长方体，所述管槽的所述中心线与对应的所述侧面之间的夹角为45°。
  4. 根据权利要求3所述的切换用夹管阀阀头，其中，所述阀头的所述第一端面呈正方形且所述阀头开设有四个管槽。
  5. 根据权利要求4所述的切换用夹管阀阀头，其中，任意两个相邻的所述管槽，其内壁沿相互靠近方向形成的第一条交汇线位于所述侧面。
  6. 根据权利要求1所述的切换用夹管阀阀头，其中，所述管槽的直径范围为12.7mm～25.4mm。
  7. 根据权利要求6所述的切换用夹管阀阀头，其中，所述管槽的直径为25.4mm，所述中心线与对应的所述棱线之间的间距为19.3mm。
  8. 一种夹管阀阀组，其特征在于，包括基板、多个夹管阀以及如权利要求1～7中任意一项所述的切换用夹管阀阀头；
    所述第一端面与所述基板的一侧固定连接，所述夹管阀固设于所述基板的另一侧且与所述阀片通孔一一对应，所述夹管阀的一端贯穿所述基板与所述阀片通孔至所述管槽内。
  9. 根据权利要求8所述的夹管阀阀组，其中，所述夹管阀包括驱动件以及阀片，所述驱动件固设于所述基板，所述阀片贯穿所述基板与所述阀片通孔至所述管槽内。
  10. 根据权利要求9所述的夹管阀阀组，其中，所述驱动件为气缸，所述气缸的接口面均背离所述阀头的中心，且任意相邻两个所述气缸的接口面互相垂直。
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