WO2020065348A1 - Soupape - Google Patents

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Publication number
WO2020065348A1
WO2020065348A1 PCT/GB2019/052746 GB2019052746W WO2020065348A1 WO 2020065348 A1 WO2020065348 A1 WO 2020065348A1 GB 2019052746 W GB2019052746 W GB 2019052746W WO 2020065348 A1 WO2020065348 A1 WO 2020065348A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve housing
gap
compressible member
housing
Prior art date
Application number
PCT/GB2019/052746
Other languages
English (en)
Inventor
Pietro Valdastri
Simone CALÒ
James Henry CHANDLER
Original Assignee
University Of Leeds
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by University Of Leeds filed Critical University Of Leeds
Publication of WO2020065348A1 publication Critical patent/WO2020065348A1/fr

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Classifications

    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61M—DEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M39/00—Tubes, tube connectors, tube couplings, valves, access sites or the like, specially adapted for medical use
    • A61M39/22—Valves or arrangement of valves
    • A61M39/28—Clamping means for squeezing flexible tubes, e.g. roller clamps
    • A61M39/285—Cam clamps, e.g. roller clamps with eccentric axis
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61M—DEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M39/00—Tubes, tube connectors, tube couplings, valves, access sites or the like, specially adapted for medical use
    • A61M39/22—Valves or arrangement of valves
    • A61M39/28—Clamping means for squeezing flexible tubes, e.g. roller clamps
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61M—DEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M5/00—Devices for bringing media into the body in a subcutaneous, intra-vascular or intramuscular way; Accessories therefor, e.g. filling or cleaning devices, arm-rests
    • A61M5/14—Infusion devices, e.g. infusing by gravity; Blood infusion; Accessories therefor
    • A61M5/168—Means for controlling media flow to the body or for metering media to the body, e.g. drip meters, counters ; Monitoring media flow to the body
    • A61M5/16804—Flow controllers
    • A61M5/16813—Flow controllers by controlling the degree of opening of the flow line

Definitions

  • the present invention relates to a valve, a method of manufacturing the valve, a valve assembly, a method of controlling a flow rate of fluid through the valve assembly, and a device incorporating the valve assembly.
  • Flow regulatory devices such as valves, are widely used in a variety of different applications which require the rate of flow of a fluid to be controlled.
  • MIS minimally invasive surgery
  • Fluid flow can be controlled using in-line valves.
  • in-line valves involve direct interaction between the valve diaphragm and the fluid flowing through the valve, which increases the risk of contamination of both the valve diaphragm and the fluid.
  • valve diaphragm In medical applications of soft robotics where the fluid concerned is typically a saline solution, interaction between the valve diaphragm and the saline solution can lead to metallic elements from the valve diaphragm contaminating the saline before it is injected into the body of a patient. Furthermore, any contaminated saline back-flowing from the patient through the valve can cause contamination of the valve diaphragm which will require sterilisation before reuse.
  • the HydroJet is an endoscope which helps to enable ultra-low-cost gastric cancer screening procedures to be performed in low and middle-income countries.
  • the Hydrojet comprises a disposable capsule which is attached at the end of a multi-lumen catheter, and is able to move inside a person's stomach cavity via three water jets located around the capsule body and spaced 120° from each other.
  • the catheter and the capsule are single use components which can be disposed of after each procedure, avoiding costly re-processing, which helps to reduce the cost of an examination, and thereby makes screenings more accessible.
  • the flow of water from the jets is controlled by valves.
  • the valves are intended to be reusable, to help further reduce costs, and, for this reason, the valves must remain sterile and avoid contact with contaminants, such as the water used for propulsion.
  • valve diaphragm in applications where the fluid is a corrosive substance, interaction between the valve diaphragm and the fluid can lead to deterioration of the valve diaphragm, and can also lead to contamination of the fluid with by-products of the corrosion. This subsequently leads to high maintenance costs as well as reduced purity of the fluid being transmitted through the valve.
  • valve diaphragm is physically separated from the fluid generally offer a more appropriate solution for many applications, such as medical applications.
  • One type of physically separated valve that is commonly used for such applications is a pinch-valve, like the one described in US 2016/0161004 Al.
  • An example of a pinch valve is shown in Figure 1, described below.
  • pinch valves introduce large stresses at a single point of a compressible pipe which forms the fluid flow path through the pinch valve. This often results in plastic deformation, thereby altering the flow characteristics through the pinch valve over time. Aside from the increased risk of failure at the pinch-point of the compressible pipe, varying flow characteristics caused by plastic deformation adversely affect the accuracy with which the rate of fluid flow can be controlled. Therefore, in order to integrate pinch valves into systems for use in applications which require accurate control, closed-loop control is typically required in order to address the change in flow characteristics over time caused by plastic deformation and provide the pinch valve with the necessary levels of accuracy and repeatability. However, closed-loop control requires expensive sensors which increases system complexity and cost significantly.
  • closed loop control is particular undesirable in medical applications, where the pinch valve and associated sensor are often part of an assembly that must be sterile before use. After use, the assembly is either discarded or sterilised for reuse. In either case the presence of the sensor is undesirable, since discarding the sensor increases per-unit costs and manufacturing a sterilisable sensor may not be possible or is at least likely to be expensive.
  • the aim of the present invention is to alleviate at least some of the aforementioned issues.
  • a rotary valve having a valve housing and a valve member positioned relative to the valve housing so as to define a gap between the valve member and the valve housing.
  • a compressible member is located within the gap between the valve housing and the valve member.
  • the compressible member defines a fluid flow path through the valve.
  • the compressible member is configured to compress so as to control a rate of fluid flow through the valve.
  • a portion of the valve member is configured to rotate relative to the valve housing and, in doing so, move the portion of the valve member along a length of the compressible member.
  • the portion of the valve member is configured to move in such a way as to vary a width of the gap between the valve member and the valve housing, that is, the width of the gap varies as the portion of the valve member moves relative to the valve housing along the length of the compressible member.
  • the portion of the valve member is configured to compress the compressible member within the gap between valve member and the valve housing so as to control the rate of fluid flow through the valve.
  • the fluid flow rate through the valve varies depending on the width of the gap. Since the width of the gap varies depending on the position of the portion of the valve member relative to the valve housing (along the length of the compressible member), the fluid flow rate through the valve varies depending on the position of the portion of the valve member relative to the valve housing (along the length of the compressible member). In this way, the fluid flow rate from the valve may be controlled by rotating the portion of the valve member relative to the valve housing, along the length of the compressible member.
  • valve member being configured to move along the length of the compressible member in this way, the point at which the compressible member is compressed varies during operation, rather than the compressible member being constantly compressed at a single point (as in a pinch valve).
  • This provides the advantage of minimising the levels of plastic deformation at a single point of the compressible member, and hence reduces the chance of failure of the compressible member and helps to minimise plastic deformation which may lead to a change in flow characteristics over time.
  • the width of the gap between the valve member and the valve housing may vary along a length of the valve housing.
  • the width of the gap between the valve member and the valve housing as a function of the length of the valve housing is referred to herein as a gap profile.
  • the width of the gap (gap profile) may vary either continuously or discontinuously (for example, in a step or saw tooth profile) along the length of the valve housing. This allows any desired flow profile to be generated in a highly repeatable fashion by a simple rotation of the valve member relative to the valve housing.
  • the width of the gap between the valve member and the valve housing may vary so as to obtain a desired flow profile. For example, either a linear or a non-linear flow profile.
  • the valve may further comprise a feeder.
  • the feeder may be configured to constrain the compressible member within the valve housing.
  • the feeder may be configured to substantially constrain any movement of the compressible member relative to the valve housing. This helps to prevent any movement of the compressible member within the valve housing, and therefore helps to achieve better alignment between the compressible member and the valve member, which in turn helps to provide a more accurate and repeatable flow.
  • the compressible member may be fixed within a portion of the valve housing. This helps to prevent any movement of the compressible member within the valve housing, and therefore helps to achieve better alignment between the compressible member and the valve member, which in turn helps to provide a more accurate and repeatable flow.
  • the width of the gap between the valve member and the valve housing may be substantially no smaller than twice the wall thickness of the compressible member. This intrinsically limits the maximum stress that can be applied to the compressible member and therefore helps to further minimise damage to the compressible member.
  • the width of the gap between the valve member and the valve housing may not be substantially larger than the outer diameter of the compressible member when the compressible member is in an un-compressed state. This minimises the size of the valve housing and also allows for a more responsive valve as each movement of the valve member will act to adjust the flow rate.
  • the valve may be configured to rotate relative to the valve housing via rotation of the valve member and/or via rotation of the valve housing.
  • a rotary valve is compact and straightforward to manufacture since rotary actuators are simple and cheap.
  • the valve member may be an eccentric valve member.
  • An eccentric valve member may allow the compression to be spread over a larger area thereby further minimising plastic deformation and associated damage to the compressible member.
  • the valve housing may comprise at least one casing and an insert releasably mounted to the casing. This enables the valve to be easily adapted to different compressible members (for example, different sizes, shapes or material properties), or to be adapted for different desired flow rate profiles for different applications (for example, swapping from a linear to a non-linear flow profile) since the insert can be easily removed and replaced with an insert shaped to achieve the desired flow profile.
  • the valve member may comprise a bearing configured to rotate relative to the compressible member.
  • a bearing reduces the amount of shear stress placed on the compressible member and thereby helps to reduce associated damage to the compressible member.
  • the compressible member may comprise a compressible pipe. This ensures that there is no direct contact between the valve member and the fluid flowing therethrough. This helps to prevent the material of valve member from contaminating the fluid flowing through the valve and also helps to prevent the fluid flowing through the valve from causing corrosion, or other deterioration, through contact with the valve member.
  • the valve may be for controlling the flow rate of a pre-pressurised fluid.
  • the valve housing may comprise an opening configured to permit passage of the compressible member into and out of the valve housing.
  • the opening may be sized such that there is substantially no compression of the compressible member between the valve member and the valve housing about the opening. This helps to avoid any unwanted pinching of the compressible member between the valve member and the valve housing at the opening, thereby further improving valve accuracy and responsiveness.
  • valve assembly comprising the valve according to the first aspect.
  • the valve assembly has a valve actuator and a drive means configured to move a portion of the valve member relative to the valve housing, along the length of the compressible member.
  • the valve assembly may further comprise a controller configured to command the valve actuator to actuate the portion of the valve member and/or the valve housing to a desired position based upon a desired flow rate set-point.
  • the controller may be an open loop controller.
  • An open loop controller is advantageous because it reduces system complexity and associated costs. Since the valve of the claimed invention provides the advantage of minimising the levels of plastic deformation at a single point of the compressible member, and hence helps minimise the change in flow characteristics over time, the repeatability of the valve is improved. The valve can therefore be controlled via open-loop control. This provides the important benefit of reducing costs since the requirement for expensive sensors is avoided. This is particularly advantageous when the valve is used within a disposable medical device where it is desirable to keep per-unit costs to a minimum.
  • a device comprising the valve assembly according to the second aspect.
  • the device may comprises at least one of: a medical device, an unmanned aquatic vehicle (UUV), a robotic device and/or a dispensing device.
  • UUV unmanned aquatic vehicle
  • a method of controlling a flow rate of fluid through a valve assembly comprises providing a valve housing and a valve member positioned relative to the valve housing so as to define a gap therebetween.
  • a compressible member is located within the gap between the valve housing and the valve member.
  • the compressible member defines a fluid flow path through the valve.
  • the compressible member is configured to compress so as to control the rate of fluid flow through the valve.
  • a desired flow rate of fluid through the valve is determined.
  • a portion of the valve member is rotated relative to the valve housing along a length of the compressible member to a desired position so as to vary a width of the gap between the valve member and the valve housing, and so as to compress the compressible member within the gap between valve member and the valve housing, wherein the width of the gap, and therefore the level of compression of the compressible member, at the desired position corresponds to the desired flow rate of fluid through the valve.
  • the method may further comprise providing a valve actuator and a drive means and providing a controller configured to command the valve actuator to actuate the portion of the valve member and/or the valve housing to a desired position.
  • the desired flow rate is input into the controller.
  • the portion of the valve member is moved to a desired position relative to the valve housing, along the length of the compressible member, based upon a command sent to the valve actuator by the controller corresponding to the inputted desired flow rate.
  • a method of manufacturing a valve according to the first aspect comprises determining a desired flow profile of the valve and determining a gap profile based on the desired flow profile, a movement path of a valve member relative to a valve housing, and a property of a compressible member.
  • the gap profile is the width of the gap between the portion of the valve member and the valve housing as a function of position of the portion of the valve member relative to the valve housing.
  • the size of the gap at a given position leads to a particular flow profile, with the actual flow profile achieved being influenced by the response of the compressible member to compressing forces at each position.
  • the property of the compressible member may be one or more of: a width of the compressible member, a wall thickness of the compressible member, and a material property (such as elasticity) of the compressible member.
  • the gap profile may be calculated analytically, or determined through an iterative process of adjusting the gap profile to reduce an error between the flow profile achieved by the valve and the desired flow profile.
  • Determining the flow profile achieved by the valve may comprise manufacturing a valve having the gap profile and determining the flow profile of the manufactured valve based on measurements of the flow rate from the manufactured valve.
  • the flow profile may be determined based on a mathematical model of a valve having the gap profile and having a compressible member modelled according to dimensional and material characteristics of the compressible member. This enables the performance of the valve to be determined more efficiently and economically as expensive prototyping can be avoided.
  • Figure 1A illustrates a side view of a pinch-valve according to an example known from the prior art, where the pinch valve is in a first position in which the rate of fluid flow through the valve is substantially unrestricted
  • Figure IB illustrates a side view of the pinch-valve according to the example illustrated in Figure 1A, where the pinch valve is in a second position in which the rate of fluid flow through the valve is restricted;
  • Figure 2 illustrates a schematic plan view of a valve according to an embodiment of the present invention
  • Figure 3 illustrates a schematic plan view of a valve housing according to the embodiment illustrated in Figure 2;
  • Figure 4 is a schematic flow diagram illustrating a method of determining a gap profile to achieved a desired flow rate from the valve shown in Figures 2 and 3;
  • Figure 4A is a line graph illustrating the differences between a desired flow profile and an actual flow profile for a valve having a gap profile determined using the method illustrated in Figure 4;
  • Figure 4B is a line graph comparing an actual flow profile for a valve having a gap profile determined using the method illustrated in Figure 4, an actual flow profile for a linearly-varying ECV, an actual flow profile for a solenoid valve and an actual flow profile for a pinch valve;
  • Figure 4C is a series of line graphs illustrating the differences between a desired bending angle and an actual, obtained bending angle of the Hydrojet when employing a solenoid valve, a pinch valve and a valve having a gap profile determined using the method illustrated in Figure 4, measured over a variety of different frequencies;
  • Figure 4D is a bar chart illustrating the orientation error between the desired bending angle and the actual, obtained bending angle of the valves compared in Figure 4C;
  • FIG. 5 illustrates a perspective view of the valve according to the embodiment illustrated in Figures 2 and 3 in which the feeder is visible;
  • Figure 5A illustrates a perspective view of the feeder illustrated in Figure 5 in isolation
  • Figure 5B is a photograph showing a comparison of the plastic deformation in the compressible member of a pinch valve (such as the pinch valve shown in Figures 1A and IB) compared with a valve according to the present invention
  • Figure 6 illustrates an exploded perspective view of a valve assembly incorporating the valve according to the embodiment illustrated in Figures 2 and 3;
  • Figure 7 illustrates a schematic block diagram illustrating a method of controlling a flow rate of fluid through the valve assembly according to the embodiment illustrated in Figure 6.
  • FIGS 1A and IB illustrate an example of a pinch valve 1 which is known from the prior art.
  • the pinch valve 1 comprises a housing 2 and a compressible pipe 4 configured to convey a fluid through the pinch valve 1.
  • a plunger 6 and a pinching support 8 are located within the housing 2 and are located directly opposite to one another so as to define a gap 9 therebetween.
  • the gap 9 is sized to receive the compressible pipe 4 such that the plunger 6 and pinching support 8 abut opposing sides of the compressible pipe 4, as shown in Figure 1A.
  • the plunger 6 is configured to reciprocate within the housing 2 relative to the pinching support 8.
  • the plunger 6 may be mounted on runners within the housing 2 to allow translation of the plunger 6 in an axial direction along the housing 2 between a number of different positions relative to the pinching support 8.
  • the pinch valve 1 further comprises an actuator (not shown) configured to actuate the plunger 6 from a first position, as shown in Figure 1A, in which there is substantially no compression of the compressible pipe 4 within the gap 9 between the plunger 6 and the pinching support 8, to a second position, as shown in Figure IB, in which the width of the gap 9 between the plunger 6 and the pinching support 8 is reduced when compared with the width of the gap 9 when the plunger 6 is in the first position.
  • the compressible pipe 4 is typically made from a resilient material and is therefore compressed upon the application of a load. Therefore, as the plunger 6 is actuated from the first position to the second position, as shown in Figure IB, the compressible pipe 4 becomes compressed between the plunger 6 and the pinching support 8 as the width of the gap 9 is reduced.
  • Compressing the compressible pipe 4 has the effect of reducing the cross-sectional area of the compressible pipe 4 and subsequently the rate of fluid flow through the pinch valve 1.
  • the position of the plunger 6 relative to the pinching support 8 can therefore be varied so as to control the width of the gap 9 between the plunger 6 and the pinching support 8, and subsequently the level of compression of the compressible pipe 4. In this way, the rate of fluid flow through the pinch valve 1 can be controlled based upon the position of the plunger 6 relative to the pinching support 8.
  • Figure 2 shows a valve 10 according to an embodiment of the present invention aimed at addressing the aforementioned issues with pinch valves, such as the pinch valve 1 illustrated in Figure 1.
  • the valve 10 comprises a valve housing 20, a valve member 30 and a compressible member 40 which defines a fluid flow path through the valve 10.
  • the valve housing 20 comprises a base 22 and a generally cylindrical sidewall 24 extending substantially upwardly therefrom.
  • the inner surface 24a of the sidewall 24 defines an internal recess 26 within the valve housing 20 having a generally circular cross-section, the internal recess 26 being sized to receive the valve member 30 within the valve housing 20.
  • the valve member 30 in the illustrated embodiment is an eccentric valve member and is rotatably mounted within the internal recess 26 of the valve housing 20.
  • the valve member 30 comprises an aperture 31 offset from its centre-point about which the valve member 30 is configured to rotate.
  • the aperture 31 is configured to receive a drive shaft (not shown) which shall be described in greater detail in Figure 6.
  • a portion of the eccentric valve member 30 defines a cam 32.
  • the valve member 30 is positioned relative to the inner surface 24a of the valve housing 20 such that a gap 28 is defined between the cam 32 and the inner surface 24a of the valve housing 20.
  • the cam 32 is configured to move relative to the inner surface 24a of the valve housing 20.
  • Figure 3 shows the sidewall 24 of the valve housing 20.
  • a reference curve R ref is provided in Figure 3 depicting the circumference of a fixed radius curve. It should be noted that the reference curve is provided for illustrative purposes only and does not form part of the illustrated embodiment.
  • the sidewall 24 is shaped such that the radius of the internal recess 26 varies along the length of the sidewall 24 from a minimum radius point 24b to a maximum radius point 24c. Due to the varying radius of the internal recess 26 of the valve housing 20, as the cam 32 is rotated relative to the sidewall 24 of the valve housing 20, the width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20 also subsequently varies based upon the position of the cam 32 relative to the sidewall 24. Referring back to Figure 2, the compressible member 40 is disposed within the internal recess 26 of the valve housing 20 along the length of the sidewall 24, and within the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20.
  • the compressible member 40 comprises a fluid inlet 42 and a fluid outlet 44 which allow for fluid to enter and exit the valve 10.
  • the fluid inlet may be provided at 44 and the fluid outlet may be provided at 42.
  • the compressible member 40 is provided in the form of a compressible pipe.
  • any other suitable compressible fluid conveying means may be used.
  • the compressible member 40 is made up of a resilient material (such as Silicone Rubber, Latex Rubber, Tygon ® or PVC) which compresses upon the application of a load and returns substantially to its original shape when the load is removed.
  • the resilient material is selected to suit the pressure and application requirements of the valve 10.
  • the application requirements may include biocompatibility.
  • the application requirements may include different parameters.
  • the compressible member 40 Upon application of a load sufficient to compress the compressible member 40, the compressible member 40 is deformed, reducing the cross-sectional area of the compressible member 40 and consequently the rate of fluid flow through the valve 10.
  • the compressible member 40 becomes compressed within the gap 28 between the cam 32 and the sidewall 24.
  • the width of the gap 28, and therefore the amount of compression of the compressible member 40 varies based upon the position of the cam 32 as the cam 32 is rotated relative to the sidewall 24 of the valve housing 20.
  • the valve 10 is thereby able to control the rate of fluid flow based on the position of the valve member 30 relative to the valve housing 20.
  • the gap profile (the width of the gap between the cam 32 and the sidewall 24 as a function of the position of the cam 32 relative to the sidewall 24) controls the flow profile (the flow rate achieved from the fluid outlet 44 as a function of the position of the cam 32 relative to the sidewall 24) of the valve 10.
  • the rate of flow of fluid passing through the valve 10 is dependent on the minimum width of the gap between the valve member 30 and the sidewall 24 of the valve housing 20 since this gap corresponds to the minimum cross-sectional area of the compressible member 40, which determines the rate of fluid flow through the valve 10.
  • the valve member 30 is therefore located within the internal recess 26 relative to the sidewall 24 of the valve housing 20 such that the minimum width of the gap between the valve member 30 and the sidewall 24 of the valve housing 20 is located at the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20.
  • the shape of the sidewall 24 of the valve housing 20 is determined such that the minimum radius, Rmin, of the internal recess 26, located at minimum radius point 24b, is sized to obtain a minimum width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20 that is substantially no smaller than twice the width of a wall thickness of the compressible member 40 at any given position of the cam 32 along the sidewall 24 of the valve housing 20.
  • This helps to prevent the walls of the compressible member 40 from becoming plastically deformed during operation of the valve 10 and thereby helps to intrinsically limit the amount of stress that can be applied to the compressible member 40 during use. This feature therefore helps to minimise any plastic deformation and damage to the compressible member during operation.
  • the shape of the sidewall 24 of the valve housing 20 is determined such that the maximum radius, Rmax, of the internal recess 26, located at the maximum radius point 24c, is sized to obtain a maximum width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20 that is not substantially larger than an outer diameter of the compressible member 40 when the compressible member 40 is in an uncompressed state. This has the benefit of minimising the size of the valve housing 20 and therefore enables the valve 10 to be made more compact.
  • the flow rate obtained by the valve 10 at each position of the cam 32 relative to the sidewall 24 of the valve housing 20 defines a flow profile for the valve 10, which can be plotted on a graph, as shall be described in greater detail with reference to Figure 4a.
  • the sidewall 24 is shaped such that the radius of the internal recess 26 varies continuously along the length of the sidewall 24 about an angular distance, a, from the minimum radius point 24b, which in the illustrated embodiment corresponds to a point at an angular position of 0 degrees along the length of the sidewall 24, to the maximum radius point 24c, which corresponds to a point at an angular position of 300 degrees along the length of the sidewall 24.
  • the sidewall 24 of the valve housing 20 may be shaped to obtain any desired flow profile.
  • the sidewall 24 of the valve housing 20 may be shaped such that the flow rate obtained by the valve 10 varies linearly as the cam 32 is moved between each respective position.
  • the sidewall 24 of the valve housing 20 may be shaped such that the radius of the internal recess varies discontinuously and/or in a non-linear fashion.
  • the sidewall of the valve housing may be shaped to obtain a desired flow profile based upon a quadratic function, a trigonometric (e.g. sinusoidal) function, a step function or in any other suitable function, depending on the desired flow profile.
  • a method for determining the shape of the sidewall 24 necessary to achieve a desired flow profile is described in greater detail with reference to Figures 4 and 4A below.
  • the valve housing 20 further comprises an opening 25 which extends along an angular distance, b.
  • the opening 25 is configured to permit passage of the compressible member 40 into and out of the internal recess 26 of the valve housing 20.
  • the opening 25 is sized such that there is substantially no compression of the compressible member 40 between the valve member 30 and the valve housing 20 about the opening 25 of the valve 10. Therefore, the angular distance, b, of the opening 25 is chosen based upon the dimensional and material properties of the compressible member 40 in order to avoid any unwanted "pinching" of the compressible member 40, about the opening 25. "Pinching” can cause the "actual" flow rate obtained by the valve 10 to be different to that which is desired, particularly when the cam 32 is positioned at a location corresponding to a large gap width, and hence a high rate of flow. Tailoring the angular distance of the opening to avoid “pinching” therefore helps to improve the accuracy of the valve and also ensures that the valve remains responsive to the movement of the cam 32.
  • the opening is sized to have a large angular distance, b, the corresponding angular distance, a, between the minimum 24b and maximum 24c radius points is subsequently reduced.
  • a large angular distance, a, between the minimum 24b and maximum radius 24c points is typically desirable as this provides a greater distance across which the flow rate obtained by the valve 10 can be adjusted and therefore greater angular distances, a, provide improved valve resolution.
  • a balance is struck between an angular distance, b, of the opening which is large enough to avoid any "pinching" of the compressible member 40 while the angular distance, a, is still large enough to provide sufficient valve resolution.
  • an angular distance, a, of 300 degrees between the minimum 24b and maximum 24c radius points, and an angular distance, b, of 60 degrees for the opening are chosen as they have been found to achieve this balance.
  • a and b may be preferred.
  • Figure 4 shows an example of a method of determining the gap profile of the valve 10.
  • the gap profile is the width of the gap between the cam 32 and the sidewall 24 as a function of the position of the cam 32 relative to the sidewall 24.
  • the gap profile is used to inform the geometry of the components of the valve 10, such as the shape of the sidewall 24, needed to achieve the desired flow profile from the valve 10.
  • a desired flow profile is determined.
  • the desired flow profile is a linearly varying flow profile.
  • the desired flow profile may instead be based upon a quadratic function, a trigonometric (e.g. sinusoidal) function, a step function or on any other suitable function, depending on the application.
  • the gap profile is then determined at step 52, taking into account the geometry of the valve components and the way they move relative to one another (for example, based on the movement path of the valve member relative to the sidewall 24) and based on the dimensions of the compressible member 40 (such as the width and wall thickness).
  • the gap profile is determined such that the minimum radius, Rmin, of the internal recess 26 corresponds to a minimum width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20 which is sized such that the width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20 at the minimum radius point 24b is substantially no smaller than twice the width of a wall thickness of the compressible member 40.
  • Rmin minimum radius
  • any other suitable minimum radius may be used.
  • the gap profile is determined such that the maximum radius, R ma x, of the internal recess 26 corresponds to a maximum width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing which is sized such that the width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20 at the maximum radius point 24c is not substantially larger than an outer diameter of the compressible member 40 when the compressible member 40 is in an uncompressed state.
  • R ma x the maximum radius of the internal recess 26 corresponds to a maximum width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing which is sized such that the width of the gap 28 between the cam 32 and the sidewall 24 of the valve housing 20 at the maximum radius point 24c is not substantially larger than an outer diameter of the compressible member 40 when the compressible member 40 is in an uncompressed state.
  • any other suitable maximum radius may be used.
  • the valve housing 20 illustrated in Figures 2 and 3 has a gap profile where the minimum 24b and maximum 24c radius points are spaced apart by an angular distance, a, of 300 degrees and the sidewall 24 is initially shaped such that the radius of the internal recess 26, and hence the width of the gap between the cam 32 and the sidewall 24 of the valve housing 20, varies continuously and linearly along an angular distance of 300 degrees along the length of the sidewall 24.
  • the minimum and maximum radius points may be spaced apart by any other suitable angular distance, a, and hence the shape of the valve housing may be determined such that the radius of the internal recess may vary across any other suitable angular distance.
  • the gap profile necessary to achieve the desired flow profile could be calculated analytically based on the geometry of the valve, and the dimensions and material properties of the compressible member 40.
  • the gap profile may be determined through an iterative process whereby a trial gap profile is generated (such as a linear change in gap width between the minimum 24b and maximum 24c radius points) and the flow profile of a valve having that trial gap profile determined (step 54).
  • the flow profile of the valve having the trial gap profile may be determined by constructing a valve having the trial gap profile and measuring the actual flow profile of the valve by using a flow-meter (or other suitable sensor) to determine an actual flow rate achieved when the cam 32 is positioned adjacent to the sidewall 24 at a number of positions.
  • the outputted flow profile may be predicted using a computer model based on the dimensions and material characteristics of the compressible member 40.
  • the actual or predicted flow profile outputted by the valve 10 can then be compared to the desired flow profile as illustrated in Figure 4a.
  • the dashed line 210 illustrates the linearly varying flow profile that it is desired for the valve 10 to obtain.
  • the sidewall 24 of the valve housing 20 is initially shaped according to the trial gap profile, where the width of the gap varies linearly along the length of the sidewall 24, in an attempt to achieve the desired linearly varying flow profile 210.
  • the actual or predicted flow profile 212 achieved by the valve 10 it is found that whilst the radius of internal recess 26 varies linearly between the respective radius points, this does not correspond to a linearly varying flow profile. This may be due, for example, to the dimensions or material properties of the compressible member 40.
  • the error between the actual flow profile 212 and the desired flow profile 210 can be calculated at various positions of the cam 32 relative to the sidewall 24 of the valve housing 20 which can then be fed back to a design programme to allow the shape of the sidewall 24 to be adjusted at step 56 to account for any errors between the actual flow profile 212 obtained by the valve housing 20 and the desired flow profile 210.
  • the shape of the sidewall 24 may be adjusted by altering a CAD model of the valve, to account for any error between the actual 212 and desired flow profiles 210.
  • the shape of the sidewall 24 can be updated to achieve a desired flow profile 210 which varies linearly between each position of the cam 32 relative to the sidewall 24 of the valve housing 20.
  • this process can also be iteratively repeated so as to iteratively reduce the margin of error between the outputted flow profile and the desired flow profile until an optimised sidewall shape is achieved, at step 58, in which the desired flow rate is obtained at each position of the cam 32 for a particular size and/or material of compressible member.
  • valve housing 20 can then be manufactured incorporating the optimised sidewall shape, for example via uploading the CAD model to a CAM system.
  • Figure 4b illustrates how the optimised, updated valve housing 20 can significantly improve flow-rate linearity when compared to known solenoid or pinch valves.
  • the line 214 in Figure 4b illustrates the flow profile provided by the optimised, updated valve housing 20 and the line 212 illustrates the actual flow profile obtained by a linearly varying valve housing.
  • line 216 illustrates the flow- profile provided by a solenoid valve and line 218 illustrates the flow-profile provided by a pinch valve.
  • valve 10 of the present invention enables the valve 10 of the present invention to minimize undesirable abrupt flow-rate changes. This is particularly important for open-loop control applications.
  • a medical device such as the Hydrojet
  • providing a linear and steadily varying flow rate over a substantial portion of the valve opening range enables the device to follow a desired motion trajectory, whilst avoiding oscillations. In the Hydrojet, this allows for a stable visualization of the target area.
  • Figure 4c illustrates the error between the actual bending angle (a), which is the angle between the end of the Hydrojet capsule and a central axis of the Hydrojet, obtained by a variety of different valve types compared to a desired bending angle to be obtained.
  • Line 220 illustrates the desired bending angle
  • line 222 illustrates the actual bending angle obtained by a solenoid valve
  • line 224 illustrates the actual bending angle obtained by a pinch valve
  • line 226 illustrates the actual bending angle obtained by the valve 10 of the present invention.
  • the valve 10 of the present invention exhibits a significantly reduced error between the actual and desired bending angle values when compared with the bending angles obtained via solenoid and pinch valves.
  • Figure 4d further illustrates the orientation error, which is the difference between the desired bending angle and the actual, obtained bending angle, for the valves of Figure 4c.
  • the valve 10 of the present invention exhibits a significantly lower margin of error when compared with the solenoid or pinch valve.
  • Figure 5 shows a perspective, cut-away view of a fully assembled valve 10 in which the drive shaft 110 is visible.
  • the drive shaft 110 is coupled to the valve member 30 for rotating the cam 32 relative the sidewall 24 of the valve housing 20.
  • the compressible member 40 is constrained within the internal recess 26 of the valve housing 20 via a feeder 60.
  • the feeder 60 may be omitted.
  • the compressible member 40 may be constrained within the valve housing 20 using any other suitable means.
  • the compressible member may be fixed to the valve housing using an adhesive or a bracket.
  • the compressible member may be left unfixed to the valve housing.
  • the feeder 60 of the illustrated embodiment is typically made up of a plastics material, however it shall be appreciated that any other suitable material may be used.
  • the feeder is shown in greater detail in Figure 5A.
  • the feeder 60 is provided in the form of a cylinder having an upper face 62 featuring a generally circular cross section, and a flange 64 extending downwardly about an edge of the upper face 62.
  • the feeder 60 is sized to fit within the internal recess 26 of the valve housing 20.
  • An internal surface 64a of the flange 64 defines a hollow cavity 66 sized to receive the valve member 30 when the feeder 60 is located within the internal recess 26 of the valve housing 20, as shown in Figure 5.
  • the feeder 60 further comprises an opening 67 located along the flange 64, the position of the opening 67 corresponding to the position of the cam 32 of the valve member 30 when the valve member 30 is received within the hollow cavity 66 of the feeder 60 to allow contact between the cam 32 and the compressible member 40.
  • An external surface 64b of the flange 64 further comprises a circumferential groove 68 configured to receive the compressible member 40 when the feeder 60 is located within the internal recess 26 of the valve housing 20.
  • the circumferential groove 68 is configured to substantially constrain any movement of the compressible member 40 relative to the valve housing 20 and to align the compressible member 40 with the valve member 30 along the length of the sidewall 24. This helps to ensure that the compressible member 40 undergoes the desired amounts of compression as it is contacted by the cam 32, and therefore helps to ensure that the valve 10 delivers accurate and repeatable flow rates.
  • the feeder 60 is coupled to the drive shaft 110 via a coupling 69. Therefore, as the drive shaft 110 is rotated to move the cam 32 relative the sidewall 24 of the valve housing 20, the opening of the feeder 60 also subsequently rotates with the cam 32 thereby enabling compression of the compressible member 40 between the cam 32 and the sidewall 24 of the valve housing 20.
  • the cam 32 Since the compressible member 40 is constrained within the valve housing 20, as the cam 32 is moved relative to the sidewall 24 of the valve housing 20 via rotation of the valve member 30, the cam 32 also moves along a length of the compressible member 40. Therefore, unlike in the pinch valve 1 described in Figure 1, in the valve 10 of the present invention, the point at which the compressible member 40 is compressed varies during operation, based upon the position of the cam 32, and the compression of the compressible member 40 is therefore not constrained to a single point. This provides the advantage of minimising the levels of plastic deformation at a single point of the compressible member, and hence enables the valve according to present invention to minimise the change in flow characteristics over time, which enables the valve to achieve more accurate and repeatable control of the flow rate.
  • Figure 5b shows the levels of damage found in the compressible pipe 4 of the pinch valve 1, illustrated in Figure 1, and the compressible member 40 of the valve 10 of the illustrated embodiment.
  • the region of the compressible pipe 4 located about the gap 9 between the plunger 6 and the pinching support 8 exhibits significant amounts of plastic deformation following use, whereas the compressible member 40 of the illustrated embodiment is substantially unaffected by plastic deformation following use.
  • valve member 30 of the illustrated embodiment is provided in the form of a bearing, and therefore, as the valve member 30 moves along the length of the compressible member 40, rotation of the valve member 30 relative to the compressible member 40 is permitted.
  • the movement of the bearing relative to the compressible member 40 has the further advantage of reducing the amounts of shear stress placed on the compressible member 40 during movement of the cam 32 along the length of the compressible member 40 and therefore helps to further reduce the amount of damage caused to the compressible member 40 during use.
  • a valve assembly 100 comprising the valve 10 of the illustrated embodiment shall now be described in relation to Figure 6.
  • the valve assembly 100 comprises a drive means in the form of a drive shaft 110 having a first end 112 for coupling with the valve member 30 and a second end 114 for coupling with an actuator 120.
  • the first end 112 of the drive shaft 110 extends through aperture 31 of the valve member 30 and aperture 69 of the feeder 60 and is received within an upper shaft support bearing 115.
  • the second end 114 of the drive shaft 110 extends through respective apertures in the valve housing 10 and is received within a lower shaft support bearing 116.
  • the first 112 and second 114 ends of the drive shaft 110 are secured within the respective upper 115 and lower 116 shaft support bearings by respective aligning nuts 117, 118.
  • the valve assembly further comprises a shaft coupling 130 configured to couple the actuator 120 with the drive shaft 110.
  • the shaft coupling 130 has a first end 132 configured to receive and couple with a driver 122 of the actuator 120 and a second end 134 configured to couple with the aligning nut 118.
  • the actuator is a rotary actuator in the form of a stepper actuator configured to rotate the valve member 30 in incremental steps of 0.9 degrees.
  • the actuator motor (not shown) enacts a rotation of the driver 122, the rotation is transferred from the driver 122, to the shaft coupling 130 and onto the second end 114 of the drive shaft 110 via the aligning nut 118. The rotation of the drive shaft 110 is then subsequently transferred onto the valve member 30 so as to cause a rotation of the cam 32 to a desired position within the valve housing 20.
  • the aligning nuts 117, 118 are configured to ensure optimal alignment between the drive shaft 110 and the valve member 30. This helps to ensure that the rotation of the driver 122 is accurately transferred onto the valve member 30 and therefore helps to improve the levels of accuracy provided by the valve 10.
  • alternative alignment means may be used.
  • the valve assembly 100 also typically comprises a controller 140 configured to command the actuator 120 to actuate the cam 32 of the valve member 30 to a desired position based upon a desired flow rate which is inputted into the controller 140.
  • the controller 140 is provided in the form of a computer processor. However, in other embodiments, it shall be appreciated that any other suitable form of controller may be used, or in a further alternative, the controller may be omitted.
  • the controller is an open-loop controller. As has been discussed previously, open-loop control of the valve assembly is possible since the valve of the present invention is able to achieve more accurate and repeatable control of flow rate due to the lack of plastic deformation at the compressible member.
  • Open loop control provides the advantage of reducing system complexity and associated costs since the requirement for expensive sensors is avoided. This is particularly advantageous for applications in disposable products, such as disposable medical devices, where per-unit costs must be kept to a minimum. However, it shall be appreciated that in other embodiments for certain applications, closed loop control may be used.
  • the valve housing 20 of the valve assembly 100 illustrated in Figure 6 is made up of plurality of sections including a lower casing 102, an upper casing 108 and an insert 104 sandwiched therebetween.
  • the insert 104 is releasably mounted within the upper 108 and lower 102 casings and comprises the base 22, sidewall 24 and internal recess 26 of the valve housing 20.
  • the insert 104 is therefore easily replaceable which allows the valve assembly 100 to be easily adapted to different compressible member types and different desired flow rate profiles via replacement of the insert 104. Therefore, the adaptability of the valve 10 and valve assembly 100 is improved.
  • the valve housing may be formed as a unitary structure, or in other alternatives, the valve housing may comprise a single casing component.
  • the valve housing 20 further comprises a tube guide component 160 comprising a pair of hollow tubular arms 162, 164 for receiving respective portions of the compressible member 40 proximal to the fluid inlet 42 and fluid outlet 44 respectively.
  • the tubular arm 162 is configured to receive the portion of the compressible member 40 proximal to the fluid inlet 42 and the tubular arm 164 is configured to receive the portion of the compressible member 40 proximal to the fluid outlet 44, or vice-versa.
  • the tube guide component 160 is configured to sit within the opening 25 of the sidewall 24 of the valve housing 20 and is shaped such that the sidewall 24 and tube guide component 160 together form a substantially complete ring about the internal recess 26 of the valve housing 20.
  • the tube guide component 160 further comprises a plurality of downwardly extending projections 166 which are configured to interconnect with corresponding apertures 106 located at the base 22 of the valve housing 20 about the opening 25 so as to secure the tube guide component 160 to the valve housing 20.
  • the provision of the tube guide 160 helps to prevent any unwanted movement of the compressible member, and therefore helps to prevent misalignment between the compressible member and the valve member which can lead to a reduction in the accuracy of the valve.
  • the tube guide component may be omitted.
  • the valve assembly further comprises a mount 150 and a plurality of support structures 152, 154, 156, 158 configured to support the valve housing 20.
  • the mount 150 is configured to sit atop an upper surface 124 of the actuator 120 and comprises a plurality of apertures 151, 153, 155, 157 configured to receive respective projections 152a, 154a, 156a, 158a extending from the lower surface of each of the respective support structures 152, 154, 156, 158, thereby securing the support structures 152, 154, 156, 158 to the mount 150.
  • the upper surfaces of the support structures 152, 154, 156, 158 further comprise respective apertures 152b, 154b, 156b, 158b.
  • the apertures 152b, 154b, 156b, 158b are configured to align with respective apertures located on the upper 108 and lower 102 casings of the valve housing 20 and are each sized to receive a fastener (not shown).
  • the fasteners pass through the respective apertures of the upper 108 and lower 102 casings and are received within the respective apertures 152b, 154b, 156b, 158b of the support structures 152, 154, 156, 158 thereby securing the insert 104 within the upper 108 and lower 102 casings and securing the valve housing 20 to the mount 150 via the support structures 152, 154, 156, 158.
  • a desired flow rate is determined by a user and inputted into the controller 140 as a desired flow rate set-point 200.
  • the desired flow rate set-point 200 is then processed via a suitable algorithm programmed into the controller 140, which is configured to convert the inputted flow rate set-point 200 into a position command 201 based upon previous measurements.
  • the algorithm may be provided in the form of a look-up table.
  • the algorithm may be further configured to interpolate between values provided in the look-up table.
  • any other suitable algorithm may be used.
  • the position command 201 is passed to the actuator 120 which causes the actuator to output a rotation movement 202.
  • the rotation movement 202 is transferred from the actuator driver 122 to the drive shaft 110 which is subsequently rotated.
  • the movement 203 of the drive shaft 110 is then transferred onto the valve member 30 to cause a rotation of the cam 32 to a desired position relative to the valve housing 20 based upon the desired flow rate set-point 200.
  • the width of the gap 28 between the cam 32 and the valve housing 20 is varied which subsequently causes a compression of the compressible member 40 within the gap 28 between the cam 32 and the valve housing 20.
  • the level of compression of the compressible member 40 at the desired position corresponds to the desired flow rate of fluid through the valve 10. This leads to a change in the rate of fluid flow such that the flow rate 204 outputted by the valve 10 corresponds to the desired flow rate set-point 200.
  • valve assembly described in the illustrated embodiment is suited for controlling the flow rate of a pre-pressurised fluid to facilitate movement control of an unmanned robotic medical device.
  • the valve assembly may alternatively be used for an unpressurised system, and may be for use in applications in other kinds of medical device, such a fluid delivery systems, may be used for other kinds of unmanned aquatic vehicle (UUV), may be used in dispensing devices, such as beverage dispensing devices or in a further alternative, may be used in substantially any suitable application.
  • UUV unmanned aquatic vehicle
  • valve member may be configured to move relative to the inner surface of the valve housing via rotation of the valve housing, or by a combination of rotation of the valve member and the valve housing.
  • valve member of the illustrated embodiment is described in relation to an eccentric valve member having a cam, in other embodiments it shall be appreciated that any other suitable valve member may be used. Furthermore, the portion of the valve member may alternatively be any other suitable portion.
  • the illustrated embodiment is described as having a drive means in the form of a drive shaft, it shall be appreciated that any other suitable drive means may be used.
  • the drive means may be a drive chain made up of a plurality of linkages and mechanical connections.

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  • Health & Medical Sciences (AREA)
  • Heart & Thoracic Surgery (AREA)
  • Hematology (AREA)
  • Engineering & Computer Science (AREA)
  • Anesthesiology (AREA)
  • Biomedical Technology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Animal Behavior & Ethology (AREA)
  • General Health & Medical Sciences (AREA)
  • Public Health (AREA)
  • Veterinary Medicine (AREA)
  • Pulmonology (AREA)
  • Vascular Medicine (AREA)
  • Lift Valve (AREA)

Abstract

Une soupape rotative comprend un boîtier de soupape, un élément de soupape positionné par rapport au boîtier de soupape de manière à définir un espace, et un élément compressible situé à l'intérieur de l'espace. Une partie de l'élément de soupape est conçue pour tourner par rapport au boîtier de soupape de façon à faire varier la largeur de l'espace entre l'élément de soupape et le boîtier de soupape. Lorsque la largeur d'espace est modifiée, l'élément compressible est comprimé, ce qui modifie ensuite la vitesse d'écoulement de fluide à travers la soupape. Ainsi, la vitesse d'écoulement de fluide à travers la soupape est contrôlée sur la base de la position de la partie de l'élément de soupape par rapport au boîtier de soupape. A la différence des soupapes à pincement connues, l'élément de soupape est conçu pour se déplacer le long d'une longueur de l'élément compressible lorsque la partie de l'élément de soupape tourne par rapport au boîtier de soupape.
PCT/GB2019/052746 2018-09-28 2019-09-27 Soupape WO2020065348A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1815959.0 2018-09-28
GB201815959 2018-09-28

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Publication Number Publication Date
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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3865134A (en) * 1973-04-23 1975-02-11 Cornelius Co Sanitary valve
US3915167A (en) * 1974-05-23 1975-10-28 Atlantic Design & Dev Corp Intravenous clamp
US4660802A (en) * 1985-11-08 1987-04-28 Rao Medical Devices, Inc. Liquid flow control device
US4821996A (en) * 1987-01-28 1989-04-18 Baxter Travenol Laboratories, Inc. Fluid flow control valve and transfer set
US5113906A (en) * 1989-09-07 1992-05-19 Hoegner Marcelo A Multiple rotary control valve for use with a sterilizing apparatus
US7074212B1 (en) * 2002-12-11 2006-07-11 Florea Erica J Flow regulator device and method of using
US20120053556A1 (en) * 2010-08-26 2012-03-01 Freddie Eng Hwee Lee Infusion control device
WO2014062013A1 (fr) * 2012-10-18 2014-04-24 주식회사 우영메디칼 Appareil de régulation d'écoulement de liquide chimique
US20160161004A1 (en) 2014-12-04 2016-06-09 Bradley Richard Thompson Pinch valve systems and methods
CN108506519A (zh) * 2018-03-30 2018-09-07 中国科学院力学研究所 一种微型可程控的旋压式夹管阀

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3865134A (en) * 1973-04-23 1975-02-11 Cornelius Co Sanitary valve
US3915167A (en) * 1974-05-23 1975-10-28 Atlantic Design & Dev Corp Intravenous clamp
US4660802A (en) * 1985-11-08 1987-04-28 Rao Medical Devices, Inc. Liquid flow control device
US4821996A (en) * 1987-01-28 1989-04-18 Baxter Travenol Laboratories, Inc. Fluid flow control valve and transfer set
US5113906A (en) * 1989-09-07 1992-05-19 Hoegner Marcelo A Multiple rotary control valve for use with a sterilizing apparatus
US7074212B1 (en) * 2002-12-11 2006-07-11 Florea Erica J Flow regulator device and method of using
US20120053556A1 (en) * 2010-08-26 2012-03-01 Freddie Eng Hwee Lee Infusion control device
WO2014062013A1 (fr) * 2012-10-18 2014-04-24 주식회사 우영메디칼 Appareil de régulation d'écoulement de liquide chimique
US20160161004A1 (en) 2014-12-04 2016-06-09 Bradley Richard Thompson Pinch valve systems and methods
CN108506519A (zh) * 2018-03-30 2018-09-07 中国科学院力学研究所 一种微型可程控的旋压式夹管阀

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