US20150285400A1 - Vibration Damping Device for a Valve - Google Patents
Vibration Damping Device for a Valve Download PDFInfo
- Publication number
- US20150285400A1 US20150285400A1 US14/743,798 US201514743798A US2015285400A1 US 20150285400 A1 US20150285400 A1 US 20150285400A1 US 201514743798 A US201514743798 A US 201514743798A US 2015285400 A1 US2015285400 A1 US 2015285400A1
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- United States
- Prior art keywords
- valve
- valve member
- closed position
- inerter
- housing
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
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Images
Classifications
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
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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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/12—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with streamlined valve member around which the fluid flows when the valve is opened
- F16K1/126—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with streamlined valve member around which the fluid flows when the valve is opened actuated by fluid
-
- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
-
- 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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0433—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with vibration preventing means
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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
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/44—Mechanical actuating means
- F16K31/52—Mechanical actuating means with crank, eccentric, or cam
- F16K31/524—Mechanical actuating means with crank, eccentric, or cam with a cam
- F16K31/52408—Mechanical actuating means with crank, eccentric, or cam with a cam comprising a lift valve
- F16K31/52433—Mechanical actuating means with crank, eccentric, or cam with a cam comprising a lift valve with a streamlined or helically shaped valve member, e.g. for reducing flow losses or guiding the fluid flow
-
- 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
- F16K47/00—Means in valves for absorbing fluid energy
-
- 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
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7781—With separate connected fluid reactor surface
- Y10T137/7793—With opening bias [e.g., pressure regulator]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7904—Reciprocating valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
- Y10T74/1876—Reciprocating or oscillating to or from alternating rotary including inertia device
Definitions
- the invention relates generally to devices for controlling linear vibration by converting linear motion to rotary motion.
- the invention relates to devices for controlling vibrations in valves (e.g., pressure relief valves).
- embodiments provide a valve that includes a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet, a valve member arranged at least partially within the housing and movable between an open position where flow is provided from the inlet through the valve seat to the outlet, and a closed position where flow is inhibited through the valve seat, and an inerter element arranged to convert linear motion of the valve member into rotary movement beginning at the closed position, thereby damping the valve.
- the valve further includes a biasing element that biases the valve member toward the closed position, or the valve member moves linearly between the open position and the closed position, the linear motion of the valve member converted by the inerter element into rotary movement of the valve member, the mass and rotational movement of the valve member providing inertial damping, or the inerter element is fixed to the housing, or the valve member moves linearly between the open position and the closed position, or the inerter element rotates in response to the linear movement of the valve member, the mass and rotational movement of the inerter element providing inertial damping, or the inerter element defines a cam profile, the valve member engaging the cam profile, or the cam profile is helical, or the valve member is biased toward the open position by a pressure, or the valve member actuates in response to a non-mechanical force.
- a biasing element that biases the valve member toward the closed position, or the valve member moves linearly between the open position and the closed position, the linear motion of the valve member converted by the inerter element into
- embodiments provide a valve that includes a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet, a valve member arranged at least partially within the housing and movable between an open position where flow is provided from the inlet through the valve seat to the outlet, and a closed position where flow is inhibited through the valve seat, the valve member coupled to the housing for linear and rotary movement relative to the housing about an axis, and an inerter element substantially fixed to the housing and defining a cam profile, a portion of the valve member engaging the cam profile such that in response to a non-mechanical force the valve member moves between the open position and the closed position and linear motion of the valve member is converted to rotary motion of the valve member, thereby damping the valve when the valve member leaves the closed position.
- the cam profile is helical, or the valve member includes a pin that engages the cam profile, or the valve member is biased toward the closed position, or the valve member is coupled to the inerter element such that the inerter element supports the valve member for linear motion along the axis and rotation about the axis.
- embodiments provide a method for damping a valve, the valve including a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet, a valve member arranged at least partially within the housing and moveable between an open position where flow is provided from the inlet through the valve seat to the outlet and a closed position where flow is inhibited through the valve seat, and an inerter element.
- the method includes engaging a cam profile defined in the inerter element with the valve member and damping the valve by continuously rotating the valve member along the cam profile as the valve member moves from the closed position to the open position in response to a non-mechanical force and as the valve member moves from the open position to the closed position in response to a non-mechanical force.
- the method further includes engaging a pin with the cam profile, or continuously rotating the valve member includes helically rotating the valve member along a helical cam profile, or the method further includes linearly moving the valve member between the open position and the closed position, converting the linear motion of the valve member into rotary motion of the valve member with the inerter element, and inertially damping the valve member with the mass and rotary motion of the valve member
- FIG. 1 is a top view of a pressure relief valve.
- FIG. 2 is a section view of the pressure relief valve of FIG. 1 taken along the line 2 - 2 of FIG. 1 .
- FIG. 3 is a section view of the pressure relief valve of FIG. 1 taken along the line 3 - 3 of FIG. 1 .
- FIG. 4 is a top left perspective view of an inerter system of the pressure relief valve of FIG. 1 .
- FIG. 5 is a top view of the inerter system of FIG. 4 .
- FIG. 6 is a top right perspective view of the inerter system of FIG. 4 .
- FIG. 7 is a left side view of the inerter system of FIG. 4 taken from the perspective of line 7 - 7 of FIG. 5 .
- FIG. 8 is a section view of the inerter system taken along line 8 - 8 of FIG. 5 .
- FIG. 9 is a section view of the inerter system taken along line 9 - 9 of FIG. 5 .
- FIG. 10 is a right side view of the inerter system of FIG. 4 taken from the perspective of line 10 - 10 of FIG. 5 .
- FIG. 11 is a top left perspective view of another inerter system.
- FIG. 12 is a top view of the inerter system of FIG. 11 .
- FIG. 13 is a top right perspective view of the inerter system of FIG. 11 .
- FIG. 14 is a sectional view of the inerter system of FIG. 11 taken along line 14 - 14 of FIG. 12 .
- FIG. 15 is a front view of the inerter system of FIG. 11 .
- FIG. 16 is a section view of the inverter system of FIG. 11 taken along line 16 - 16 of FIG. 12 .
- FIG. 17 is a top view of another pressure relief valve.
- FIG. 18 is a section view of the pressure relief valve of FIG. 18 taken along line 18 - 18 of FIG. 17 .
- FIG. 19 is a section view of the pressure relief valve of FIG. 18 taken along line 19 - 19 of FIG. 17 .
- FIG. 20 is a section view of the pressure relief valve of FIG. 18 taken along line 20 - 20 of FIG. 17 .
- FIG. 21 is a bottom right perspective view of another inerter system.
- FIG. 22 is a top view of the inerter system of FIG. 21 .
- FIG. 23 is a bottom left perspective view of the inerter system of FIG. 21 .
- FIG. 24 is a sectional view of the inerter system of FIG. 21 taken along line 24 - 24 of FIG. 22 .
- FIG. 25 is a front view of the inerter system of FIG. 21 .
- FIG. 26 is a right side view of the inerter system of FIG. 21 taken from the perspective of line 26 - 26 of FIG. 22 .
- Section I describes a pressure relief valve that includes a first construction of the invention with respect to FIGS. 1-10 .
- Section II describes a pressure relief valve including a second construction of the invention with respect to FIGS. 11-16 .
- Section III describes a pressure relief valve including a third construction of the invention with respect to FIGS. 17-26 .
- Section IV includes a discussion of the invention in a broader sense as it relates to other valves types and other modes in which the invention can be used to attenuate and dampen vibrations.
- FIGS. 1-3 show a pressure relief valve (hereinafter “PRV”) 10 according to one embodiment of the invention.
- the PRV 10 serves to relieve pressure formed in a piping system, pressure vessel or associated component (hereinafter “pressure vessel system”).
- pressure vessel system As shown in FIG. 2 , the PRV 10 includes a housing 14 , a bonnet 18 , and an inerter system 22 .
- the housing 14 defines an inlet flange 26 for coupling to the pressure vessel system, a flanged outlet port 30 , an interior surface or chamber 34 between the inlet flange 26 and the outlet port 30 , and bonnet flange 36 defining a shoulder 38 rimming an opening 40 adjacent an upper portion (as shown in FIG. 2 ) of the chamber 34 .
- a nozzle 42 is received within the inlet flange 26 and defines a shaped nozzle profile 46 between a nozzle inlet 50 and a valve seat in the form of a nozzle outlet 54 .
- the bonnet 18 includes a bonnet housing 58 that defines a housing flange 62 arranged for coupling to the bonnet flange 36 of the housing 14 and defining a shoulder 66 .
- the bonnet housing 58 also defines an adjustment screw aperture 70 sized to threadingly receive an adjustment screw 74 .
- a spindle 78 is slidingly received within the adjustment screw 74 and extends along a central axis 82 .
- An upper spring washer 86 is positioned adjacent the adjustable screw 74 and slidingly receives the spindle 78 .
- a lower spring washer 90 is positioned distally from the upper spring washer 86 with a spring 94 arranged therebetween.
- a spindle bracket 98 is pinned to a lower end (as shown in FIG. 2 ) of the spindle 78 .
- the lower spring bracket 90 abuts the spindle bracket 98 .
- the spring 94 acts between the upper spring washer 86 and the lower spring washer 90 to bias the spindle bracket 98 downward (as shown in FIG. 2 ).
- the adjustable screw 74 can be threaded into and out of the bonnet housing 58 to increase and decrease the biasing force applied by the spring 94 .
- the inerter system 22 includes an inerter hub 102 and a valve member in the form of a disk holder 106 .
- the inerter hub 102 defines a hub flange 110 and a hub body 114 .
- a vent 118 is defined in the hub flange 110 and a central hub bore 122 extends through the inerter hub 102 along the central axis 82 .
- a bearing in the form of a bushing 126 is received within the central hub bore 122 .
- the hub body 114 defines a first slot 130 and a second slot 134 .
- the first slot 130 and second slot 134 together define a cam profile.
- the slots 130 , 134 provide a generally helical cam profile.
- the disk holder 106 includes a central shaft 138 that holds at a first end a bearing in the form of a spherical crystal bearing 142 and defines a pin aperture 146 .
- a substantially cylindrical pin 148 is fixedly received within the pin aperture 146 .
- the disk holder 106 also includes a disk recess 150 arranged to receive a disk 154 .
- the inerter system 22 is inserted into the bonnet flange 36 of the housing 14 such that the hub flange 110 is received on the shoulder 38 .
- the bonnet 18 is installed onto the housing 14 and the inerter system 22 with the shoulder 66 of the housing flange 62 engaging the hub flange 110 .
- the bonnet flange 36 is then fastened to the housing flange 62 with the hub flange 110 fixed therebetween such that the joint is substantially hermetically sealed and the inerter hub 102 is rotationally fixed relative to the housing 14 .
- the vent 118 provides fluid communication between the chamber 34 and the bonnet 18 such that no substantial pressure differential exists therebetween.
- the spindle bracket 98 engages the spherical bearing 142 and the spring 94 biases the disk holder 106 downward (as shown in FIG. 2 ) toward a closed position.
- the bias force is adjusted by manipulation of the adjustable screw 74 according to the predetermined specifications of the greater system in which the PRV 10 is installed (e.g., the pressure vessel system).
- the disk holder 106 is arranged such that the pin 148 is received in the first slot 130 and the second slot 134 and the central shaft 138 is guided vertically by the bushing 126 for linear movement along the central axis 82 .
- the disk 154 is arranged such that in the closed position (as shown in FIG. 2 ), the disk 154 engages the nozzle outlet 54 to inhibit fluid flow therethrough.
- the resultant force on the disk holder 106 will overcome the bias force exerted by the spring 94 such that the disk holder 106 will move toward an open position wherein the disk 154 does not engage the nozzle outlet 54 and fluid is permitted to flow from the nozzle inlet 50 and out the outlet port 30 .
- the pin 148 rides along the cam profile of the first slot 130 and the second slot 134 during movement between the open position and the closed position.
- the slots 130 , 134 guide the pin 148 along the cam profile.
- the configuration of the slots 130 , 134 determines the ratio of conversion of linear motion to rotational motion.
- the conversion ratio for helically shaped slots having a long lead angle (i.e., more travel distance per one revolution) and a small helix angle is relatively small.
- the conversion ratio for slots having a short lead angle (i.e., less travel distance per one revolution) and a large helix angle is greater.
- the conversion ratio is approximately 9 - 10 inches of linear motion per one revolution of the disc holder 106 .
- Other cam profiles are contemplated and would be used, as determined by one skilled in the art.
- the inerter system 22 also converts translational kinetic energy, which is defined by:
- the disc holder 106 rotates in response to linear motion caused by vibration, and thus, is sensitive to acceleration and more effective in reducing or controlling vibration than passive damping techniques.
- the mass of the disk holder 106 itself acts as the flywheel in the inerter system 22 .
- FIGS. 11-16 show an inerter system 200 that can be used with the housing 14 and bonnet 18 shown in FIGS. 1-3 in place of the inerter system 22 .
- the bonnet housing 58 also defines a cap shoulder 204 .
- the inerter system 200 includes an inerter hub 208 , a disk holder 212 , a bellows 216 , a flywheel 220 , and a cap 224 .
- the inerter hub 208 defines a hub flange 228 and a hub body 232 .
- a bearing raceway 236 is defined in the hub flange 228 .
- the bearing raceway 236 is a substantially semi-circular and annular raceway. Alternate arrangements are conceivable, such as a raceway arranged for pin bearings, etc.
- a first motion constraining slot 240 and a second motion constraining slot 244 are formed in the hub body 232 .
- the motion constraining slots 240 , 244 are parallel and substantially vertically oriented (as shown in FIG. 14 ).
- a central hub bore 248 is defined and extends through the inerter hub 208 along the central axis 82 .
- a bearing in the form of a bushing 252 is received within the central hub bore 248 .
- the disk holder 212 includes a central shaft 256 that holds at a first end a bearing in the form of a spherical crystal bearing 260 and defines a motion constraining pin aperture 264 and a flywheel pin aperture 268 .
- a substantially cylindrical motion constraining pin 272 is fixedly received within the motion constraining pin aperture 264 and a substantially cylindrical flywheel pin 276 is fixedly received within the flywheel pin aperture 268 .
- the disk holder 212 also defines a bellows mating feature in the form of threads 280 and a disk recess 284 sized to receive a disk 288 .
- the bellows 216 includes a mating feature in the form of threads 292 arranged to sealingly mate with the threads 280 of the disk holder 212 .
- the bellows 216 further include a expandable body portion 296 arranged to accommodate vertical motion (as shown in FIG. 14 ) of the disk holder 212 and a gasket portion 300 arranged to mate with a bottom surface of the hub flange 228 .
- the flywheel 220 defines an annular ring that includes a bottom surface 304 , an upper aperture 308 , an upper bearing raceway 312 , a first cam slot 316 , and a second cam slot 320 .
- the bottom surface 304 defines a bearing raceway and can define a different shape intended to function optimally with different bearing types than are illustrated herein.
- the first cam slot 316 and second cam slot 320 together define a cam profile. In the illustrated embodiment, the slots 316 , 320 provide a generally helical and linear cam profile.
- the cap 224 defines an upper surface 324 , an inner aperture 328 , and a bearing raceway 332 .
- the illustrated bearing raceway 332 is a shoulder recess. In other arrangements, the bearing raceway 332 can be arranged differently.
- the raceway 332 can be arranged to receive pin bearings, or can include a contoured surface (e.g., semi-circular depression, rectangular recess, etc.).
- the inerter system 200 is assembled by installing the bellows 216 onto the disk holder 212 by threading the bellows threads 292 onto the disk holder threads 280 such that a seal is formed therebetween.
- the disk holder 212 and bellows 216 are then installed on the inerter hub 208 by sliding the central shaft 256 into the bushing 252 and positioning the disk holder 212 such that the motion constraining pin 272 is received within the motion constraining slots 240 , 244 .
- the motion of the disk holder 212 is then constrained by the slots 240 , 244 to substantially only vertical movement (as shown in FIG. 14 ) and substantial rotation is inhibited.
- a bearing element in the form of a plurality of ball bearings 336 is arranged in the bearing raceway 236 of the inerter hub 208 , and the flywheel 220 installed onto the inerter system 200 by engaging the first cam slot 316 and the second cam slot 320 with the flywheel pin 276 , and engaging the bottom surface 304 with the ball bearings 336 .
- the bearing raceway 236 of the inerter hub 208 does not extend around the full annulus of the central hub bore 248 , but rather inhibits the ball bearings 336 from interfering with the flywheel pin 276 when the disk holder 212 is in the closed position (as shown in FIG. 15 ).
- the bearing raceway 236 can extend fully about the central hub bore 248 and the pin 276 can be arranged differently so no interference exists.
- Another bearing element (in the form of ball bearings 336 ) is arranged between the upper bearing raceway 312 of the flywheel 220 and the bearing raceway 332 of the cap 224 .
- the ball bearings 336 provide smooth rotation of the flywheel 220 under load.
- other bearing elements can be used.
- the ball bearings 336 can be retained within separate raceways, the bearing elements can be pin or needle bearings, conical bearings, or another shape of bearing, as desired.
- the bearing elements can include bushings, or other arrangements designed to provide adequate rotation of the flywheel 220 .
- the assembled inerter system 200 is then installed between the housing 14 and the bonnet 18 (see FIGS. 2 and 14 ).
- the inerter system 200 is inserted into the housing 14 such that the gasket portion 300 of the bellows 216 engages and seals against the shoulder 38 of the housing 14 .
- the shoulder 66 of the bonnet 18 engages the inerter hub 208
- the cap shoulder 204 of the bonnet 18 engages the upper surface 324 of the cap 224 .
- the hub flange 228 and the gasket portion 300 are compressed between the shoulder 66 of the bonnet 18 and the shoulder 38 of the housing 14 such that rotation of both components is inhibited.
- the cap 224 is compressed relative to the inerter hub 208 to constrain the flywheel 220 .
- the ball bearings 336 provide for rotational movement of the flywheel 220 .
- the disk holder 212 is movable between a closed position in which the disk 288 seals against the nozzle outlet 54 to inhibit fluid flow therethrough, and an open position in which the disk disengages from the nozzle outlet 54 to permit fluid flow through the nozzle 42 and out the outlet port 30 . Movement of the disk holder 212 is constrained by the central shaft 256 and the motion constraining pin 272 such that the disk holder 212 moves only in the vertical direction (as shown in FIG. 14 ) between the open position and the closed position with substantially no rotational movement.
- the bellows 216 is arranged to compress and expand along with the motion of the disk holder 212 between the open position and the closed position.
- the bellows 216 provides a barrier between the fluid and the other components of the inerter system 200 as can be advantageous in corrosive fluid control or other implementations.
- the flywheel pin 276 engages and moves along the first cam slot 316 and the second cam slot 320 such that the flywheel 220 is forced into rotation by the cam profile defined by the first cam slot 316 and the second cam slot 320 .
- the rotation of the flywheel 220 causes inertial damping of the disk holder 212 similarly to the inerter system 22 discussed above in Section I.
- FIGS. 17-26 show a PRV 400 according to one embodiment of the invention that includes a housing 414 , a bonnet 418 , and an inerter system 422 .
- the housing 414 defines an inlet flange 426 for coupling to a pressure vessel system, a flanged outlet port 430 , an interior surface or chamber 434 between the inlet flange 426 and the outlet port 430 , and a bonnet flange 436 defining a housing shoulder 438 rimming an opening adjacent an upper portion 440 (as shown in FIG. 18 ) of the chamber 434 .
- a nozzle 442 is received within the inlet flange 426 and defines a shaped nozzle profile 446 between a nozzle inlet 450 and a nozzle outlet 454 .
- the bonnet 418 includes a bonnet housing 458 that defines a housing flange 462 arranged for coupling to the bonnet flange 436 of the housing 414 and defining a bonnet shoulder 466 .
- the bonnet housing 458 also defines an adjustment screw aperture 470 sized to threadingly receive an adjustment screw 474 .
- a spindle 478 is slidingly received within the adjustment screw 474 and extends along a central axis 482 .
- An upper spring washer 486 is positioned adjacent the adjustable screw 474 and slidingly receives the spindle 478 .
- a lower spring washer 490 is positioned distally from the upper spring washer 486 with a spring 494 arranged therebetween.
- a spindle bracket 498 is pinned to a lower end (as shown in FIG.
- the adjustable screw 474 can be threaded into and out of the bonnet housing 458 to increase and decrease the biasing force applied by the spring 494 , as desired.
- the inerter system 422 includes an inerter hub 502 , a cam element 506 , a jerk absorber 510 , a cam follower element 514 , and a disk holder 518 .
- the inerter hub 502 defines a hub flange 522 , a hub body 526 extending downward (as shown in FIG. 24 ) from the hub flange 522 , and a jerk aperture 530 defined through the hub flange 522 .
- the hub body 526 defines hub body threads 532 substantially adjacent the hub flange 522 .
- a central aperture 534 is defined through the inerter hub 502 along the central axis 482 .
- the central aperture 534 is manufactured such that an inner surface of the central aperture 534 forms a bearing surface.
- the bearing surface can be machined and polished, reamed, or formed in another way to provide a suitable bearing surface.
- a bearing or bushing can be inserted within the central aperture 534 .
- the jerk aperture 530 is sized to press fittingly receive the jerk absorber 510 .
- the jerk aperture 530 can be threaded, or can be filleted in preparation of a welding procedure.
- Other arrangements are conceivable (e.g., soldering, fastening, gluing, etc.).
- the cam element 506 defines a cam element flange 538 , a central aperture 542 that is sized to receive the hub body 526 , a first cam 546 , and a second cam 550 .
- the cam element flange 538 defines a jerk aperture 554 .
- the central aperture 542 defines cam element threads 558 sized to loosely engage the hub body threads 532 .
- the first cam 546 and the second cam 550 together define a cam profile. In the illustrated embodiment, the cams 546 , 550 provide a generally helical cam profile.
- the jerk absorber 510 includes a jerk pin 562 that defines a vent 566 (as shown in FIG. 24 ) and is sized to be press fit into the jerk aperture 530 of the inerter hub 502 .
- the jerk absorber 510 also includes a bushing 570 engaged on the jerk pin 562 and received within the jerk aperture 554 of the cam element 506 .
- the illustrated bushing 570 is constructed of a shock dissipating material such as rubber, includes a bushing flange 574 arranged to be sandwiched between the hub flange 522 and the cam flange 538 , and is snugly received within the jerk aperture 554 of the cam element 506 .
- the cam follower element 514 defines a follower flange 578 that includes two flat portions 582 , a central aperture 586 sized to receive the cam element 506 , and a follower threaded portion 590 .
- Each flat portion 582 includes a cam pin aperture 594 sized to receive a cam pin 598 .
- the cam pin apertures 594 (and therefore the pins 598 ) are positioned off-center with respect to the center axis 482 (as shown in FIG. 26 ).
- the cam pins 598 are arranged to engage the first cam 546 and the second cam 550 .
- the follower threaded portion 590 includes a threaded aperture 602 sized to receive a set screw 606 .
- the disk holder 518 defines a central shaft 610 that holds at a first end a bearing in the form of a spherical crystal bearing 614 (as shown in FIG. 18 ) and defines a disk recess 618 arranged to receive a disk 622 .
- the disk holder 518 further includes a holder threaded portion 626 arranged to threadingly receive the follower threaded portion 590 , and a set screw aperture 630 arranged to receive the set screw 606 .
- the jerk bushing 570 is inserted into the jerk aperture 554 of the cam element 506 .
- the cam element 506 is then coupled to the inerter hub 502 by threading the cam element threads 558 onto the hub body threads 532 .
- the threads 558 , 532 engage loosely such that the cam element 506 spins easily.
- the jerk aperture 530 of the inerter hub 502 is then aligned with the jerk aperture 554 of the cam element 506 .
- the jerk pin 562 is press fit into the jerk aperture 530 of the inerter hub 502 , and the jerk bushing 570 that is positioned in the jerk aperture 554 of the cam element 506 .
- the threaded portion 590 of the cam follower element 514 is then threaded onto the threaded portion 626 of the disk holder 518 , and the set screw 606 is tightened such that the cam follower element 514 is substantially rigidly coupled to the disk holder 518 .
- the disk holder 518 and the cam follower element 514 are then slid onto the cam element 506 such that the pins 598 are engaged with the first cam 546 and the second cam 550 .
- the hub flange 522 is engaged with the shoulder 438 of the housing 414 such that the disk 622 engages the nozzle outlet 454 .
- the bonnet 418 is then installed with the shoulder 466 of the bonnet flange 462 engaging the hub flange 522 and the spindle bracket 498 engaging the spherical bearing 614 .
- the bonnet 418 is then fastened to the housing 414 such that the inerter hub 502 is fixed in place and inhibited from rotational and linear movement.
- the disk holder 518 is moveable between an open position where fluid is permitted to flow from the nozzle inlet 450 through the nozzle outlet 454 , and out of the outlet port 430 , and a closed position where the disk 622 engages the nozzle outlet 454 and inhibits fluid flow therethrough.
- the PRV 400 is typically in the closed position, and when pressure acting on the disk holder 518 overcomes the bias force of the spring 494 , the disk holder 518 moves toward the open position. Moving toward the open position, the pins 598 engage the first cam 546 and the second cam 550 and move the disk holder 518 along the cam profile. This results in a translation of linear motion to rotational work and has an inertial damping effect on the system, as discussed above.
- the jerk absorber 510 functions to absorb the initial shock and impact that the inerter system 422 undergoes upon the pressure in the pressure vessel or any downstream vibration overcoming the bias force of the spring 494 .
- the jerk bushing 570 absorbs the impact and the threaded portions 532 , 558 interact to allow a slight rotation of the cam element 506 relative to the inerter hub 502 .
- PRVs form an undamped linear spring mass mechanism and are configured to enable pressure control over narrow pressure ranges.
- Resonant acoustic frequencies due to inlet pipe and/or other periodic inlet pipe dynamics cause an undesirable rapid cycling motion or vibration in the PRVs, sometimes known as “chatter,” wherein the disc rapidly cycles between the open and closed positions.
- Such vibration reduces the capacity of the PRV and can cause damage to internal components such as the disc and valve seat (i.e., nozzle outlet).
- Attempts have been made to reduce the effects of such vibration by modifying disc face, seat, and nozzle geometries in order to enhance the stability of PRVs. This method is effective at enhancing stability at relatively low pressures but has limited effectiveness in enhancing stability at relatively high pressures.
- Embodiments of the invention provide, among other things, an inerter system wherein linear motion along a center axis is converted to rotational motion about the center axis. This conversion has the effect of adding inertial damping to the PRV.
- the inerter system reacts to acceleration of the system, as opposed to the more traditional passive systems that react to velocity. In other words, the invention has a much faster reaction and provides better damping with significantly less movement of the disc holder away form the nozzle outlet.
- the magnitude of the inertial damping effect provided by the inerter system is at least in part controlled by a cam profile defined by the structure of the inerter system (e.g., slots 130 , 134 , 316 , 320 and cams 546 , 550 ).
- the cam profile can have a constant or variable lead, a curved shape, a variable shape, a straight shape that is angled relative to the center axis, a shape in accordance with a square or cube root function or a combination of such shapes, and other suitable shapes.
- the cam profile is helically shaped.
- the cam profile can include at least one stepped portion that is located between first and second curved portions, for example.
- the disc holder initially rotates in a first portion of the cam profile, dwells, then resumes rotation in a second portion of the cam profile.
- the cam profile has a right hand lead, resulting in a corresponding rotation direction.
- the cam profile can be positioned in an angled orientation relative to the center axis that is opposite than that depicted in the figures.
- the cam profile can have a left hand lead.
- Embodiments of the invention control vibration in a PRV without adding significant mass to the disc holder when compared with a typical disk holder.
- existing PRVs can be retrofitted in the field with the invention without extensive modification.
- the invention can be used in conjunction with other types of valves.
- the invention can also be used in any suitable valve configuration having a component or components, such as a valve stem that includes a disc or other components, which move in a linear motion and which are susceptible to an undesirable rapid cycling motion due to dynamic instability or vibration.
- the invention can be applied to various types of line valves, check valves, relief valves, or other valves that are subject to vibrations and pressure fluctuations.
- 15-20% of the energy produced by vertical movement is converted to rotary energy in the damping process. In other embodiments, more or less energy can be converted, depending on the desired characteristics of the damping system. For example, 10-50% or more of the vertical energy can be converted to rotary energy by the inerter system. As discussed above, the cam profile can be manipulated to produce the desired damping characteristics.
- Another advantage offered by embodiments of the invention is the ability to produce damped valves that are functional as single fluid valves. That is to say, a single valve design can be used for both a gas product and a liquid product.
- Current passively damped valves are not suitable for single fluid arrangement, because they are not capable of damping the systems to stability in the presence of the variety of conditions that are posed by a liquid product versus a gas product, or vice versa.
- the present invention recognizes the problem of damping and chatter issues as a lack of non-active systems that dampen in response to acceleration of a vibration and provide a wide ranging mode for dealing with such vibrations.
- the concept of a floating input e.g., disk holder, etc. is one that reacts to non-mechanical force such as pressure. That is to say, the floating input is not coupled between two fixed mechanical points for damping vibrations formed therebetween.
- a floating input is not connected to a linkage (e.g., automobile suspension), not directly moved by a contact force (e.g., physical impact by an object), or rigidly coupled at its extremities.
- valves are direct spring operated
- the invention is capable with working with suitable actuation systems, including but not limited to, pilot operation, solenoid operation, and other control mechanisms.
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Abstract
Embodiments provide a valve including a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet. The valve further includes a valve member arranged at least partially within the housing and moveable between an open position where flow is provided from the inlet through the valve seat to the outlet and a closed position where flow is inhibited through the valve seat The valve further includes an inerter element arranged to convert linear motion of the valve member into rotary movement beginning at the closed position, thereby damping the valve.
Description
- This application is a continuation of U.S. patent application Ser. No. 14/198,401 filed on Mar. 5, 2014 which claims the benefit of U.S. Provisional Patent Application No. 61/773,458 filed on Mar. 6, 2013, the entire disclosures of which are hereby incorporated herein by reference.
- The invention relates generally to devices for controlling linear vibration by converting linear motion to rotary motion. In more particular embodiments, the invention relates to devices for controlling vibrations in valves (e.g., pressure relief valves).
- In one aspect, embodiments provide a valve that includes a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet, a valve member arranged at least partially within the housing and movable between an open position where flow is provided from the inlet through the valve seat to the outlet, and a closed position where flow is inhibited through the valve seat, and an inerter element arranged to convert linear motion of the valve member into rotary movement beginning at the closed position, thereby damping the valve.
- In some embodiments, the valve further includes a biasing element that biases the valve member toward the closed position, or the valve member moves linearly between the open position and the closed position, the linear motion of the valve member converted by the inerter element into rotary movement of the valve member, the mass and rotational movement of the valve member providing inertial damping, or the inerter element is fixed to the housing, or the valve member moves linearly between the open position and the closed position, or the inerter element rotates in response to the linear movement of the valve member, the mass and rotational movement of the inerter element providing inertial damping, or the inerter element defines a cam profile, the valve member engaging the cam profile, or the cam profile is helical, or the valve member is biased toward the open position by a pressure, or the valve member actuates in response to a non-mechanical force.
- In another aspect, embodiments provide a valve that includes a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet, a valve member arranged at least partially within the housing and movable between an open position where flow is provided from the inlet through the valve seat to the outlet, and a closed position where flow is inhibited through the valve seat, the valve member coupled to the housing for linear and rotary movement relative to the housing about an axis, and an inerter element substantially fixed to the housing and defining a cam profile, a portion of the valve member engaging the cam profile such that in response to a non-mechanical force the valve member moves between the open position and the closed position and linear motion of the valve member is converted to rotary motion of the valve member, thereby damping the valve when the valve member leaves the closed position.
- In some embodiments, the cam profile is helical, or the valve member includes a pin that engages the cam profile, or the valve member is biased toward the closed position, or the valve member is coupled to the inerter element such that the inerter element supports the valve member for linear motion along the axis and rotation about the axis.
- In yet another aspect, embodiment provide a method for damping a valve, the valve including a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet, a valve member arranged at least partially within the housing and moveable between an open position where flow is provided from the inlet through the valve seat to the outlet and a closed position where flow is inhibited through the valve seat, and an inerter element. The method includes engaging a cam profile defined in the inerter element with the valve member and damping the valve by continuously rotating the valve member along the cam profile as the valve member moves from the closed position to the open position in response to a non-mechanical force and as the valve member moves from the open position to the closed position in response to a non-mechanical force.
- In some embodiments, the method further includes engaging a pin with the cam profile, or continuously rotating the valve member includes helically rotating the valve member along a helical cam profile, or the method further includes linearly moving the valve member between the open position and the closed position, converting the linear motion of the valve member into rotary motion of the valve member with the inerter element, and inertially damping the valve member with the mass and rotary motion of the valve member
- The foregoing and other aspects and advantages of the invention will appear from the following description. In the description, reference is made to the accompanying drawings which form a part hereof, and in which there is shown by way of illustration a preferred embodiment of the invention. Such embodiment does not necessarily represent the full scope of the invention, however, and reference is made therefore to the claims and herein for interpreting the scope of the invention.
- The invention will be better understood and features, aspects and advantages other than those set forth above will become apparent when consideration is given to the following detailed description thereof. Such detailed description makes reference to the following drawings.
-
FIG. 1 is a top view of a pressure relief valve. -
FIG. 2 is a section view of the pressure relief valve ofFIG. 1 taken along the line 2-2 ofFIG. 1 . -
FIG. 3 is a section view of the pressure relief valve ofFIG. 1 taken along the line 3-3 ofFIG. 1 . -
FIG. 4 is a top left perspective view of an inerter system of the pressure relief valve ofFIG. 1 . -
FIG. 5 is a top view of the inerter system ofFIG. 4 . -
FIG. 6 is a top right perspective view of the inerter system ofFIG. 4 . -
FIG. 7 is a left side view of the inerter system ofFIG. 4 taken from the perspective of line 7-7 ofFIG. 5 . -
FIG. 8 is a section view of the inerter system taken along line 8-8 ofFIG. 5 . -
FIG. 9 is a section view of the inerter system taken along line 9-9 ofFIG. 5 . -
FIG. 10 is a right side view of the inerter system ofFIG. 4 taken from the perspective of line 10-10 ofFIG. 5 . -
FIG. 11 is a top left perspective view of another inerter system. -
FIG. 12 is a top view of the inerter system ofFIG. 11 . -
FIG. 13 is a top right perspective view of the inerter system ofFIG. 11 . -
FIG. 14 is a sectional view of the inerter system ofFIG. 11 taken along line 14-14 ofFIG. 12 . -
FIG. 15 is a front view of the inerter system ofFIG. 11 . -
FIG. 16 is a section view of the inverter system ofFIG. 11 taken along line 16-16 ofFIG. 12 . -
FIG. 17 is a top view of another pressure relief valve. -
FIG. 18 is a section view of the pressure relief valve ofFIG. 18 taken along line 18-18 ofFIG. 17 . -
FIG. 19 is a section view of the pressure relief valve ofFIG. 18 taken along line 19-19 ofFIG. 17 . -
FIG. 20 is a section view of the pressure relief valve ofFIG. 18 taken along line 20-20 ofFIG. 17 . -
FIG. 21 is a bottom right perspective view of another inerter system. -
FIG. 22 is a top view of the inerter system ofFIG. 21 . -
FIG. 23 is a bottom left perspective view of the inerter system ofFIG. 21 . -
FIG. 24 is a sectional view of the inerter system ofFIG. 21 taken along line 24-24 ofFIG. 22 . -
FIG. 25 is a front view of the inerter system ofFIG. 21 . -
FIG. 26 is a right side view of the inerter system ofFIG. 21 taken from the perspective of line 26-26 ofFIG. 22 . - Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting. The use of “including,” “comprising,” or “having” and variations thereof herein is meant to encompass the items listed thereafter and equivalents thereof as well as additional items. Unless specified or limited otherwise, the terms “mounted,” “connected,” “supported,” and “coupled” and variations thereof are used broadly and encompass both direct and indirect mountings, connections, supports, and couplings. Further, “connected” and “coupled” are not restricted to physical or mechanical connections or couplings.
- The following discussion is presented to enable a person skilled in the art to make and use embodiments of the invention. Various modifications to the illustrated embodiments will be readily apparent to those skilled in the art, and the generic principles herein can be applied to other embodiments and applications without departing from embodiments of the invention. Thus, embodiments of the invention are not intended to be limited to embodiments shown, but are to be accorded the widest scope consistent with the principles and features disclosed herein.
- The following detailed description is to be read with reference to the figures, in which like elements in different figures have like reference numerals. The figures, which are not necessarily to scale, depict selected embodiments and are not intended to limit the scope of embodiments of the invention. Skilled artisans will recognize the examples provided herein have many useful alternatives and fall within the scope of embodiments of the invention.
- The following description includes four sections. Section I describes a pressure relief valve that includes a first construction of the invention with respect to
FIGS. 1-10 . Section II describes a pressure relief valve including a second construction of the invention with respect toFIGS. 11-16 . Section III describes a pressure relief valve including a third construction of the invention with respect toFIGS. 17-26 . Section IV includes a discussion of the invention in a broader sense as it relates to other valves types and other modes in which the invention can be used to attenuate and dampen vibrations. - Section I
-
FIGS. 1-3 show a pressure relief valve (hereinafter “PRV”) 10 according to one embodiment of the invention. ThePRV 10 serves to relieve pressure formed in a piping system, pressure vessel or associated component (hereinafter “pressure vessel system”). As shown inFIG. 2 , thePRV 10 includes ahousing 14, abonnet 18, and aninerter system 22. Thehousing 14 defines aninlet flange 26 for coupling to the pressure vessel system, aflanged outlet port 30, an interior surface orchamber 34 between theinlet flange 26 and theoutlet port 30, andbonnet flange 36 defining ashoulder 38 rimming anopening 40 adjacent an upper portion (as shown inFIG. 2 ) of thechamber 34. Anozzle 42 is received within theinlet flange 26 and defines a shapednozzle profile 46 between anozzle inlet 50 and a valve seat in the form of anozzle outlet 54. - With continued reference to
FIG. 2 , thebonnet 18 includes abonnet housing 58 that defines ahousing flange 62 arranged for coupling to thebonnet flange 36 of thehousing 14 and defining ashoulder 66. Thebonnet housing 58 also defines anadjustment screw aperture 70 sized to threadingly receive anadjustment screw 74. Aspindle 78 is slidingly received within theadjustment screw 74 and extends along acentral axis 82. Anupper spring washer 86 is positioned adjacent theadjustable screw 74 and slidingly receives thespindle 78. Alower spring washer 90 is positioned distally from theupper spring washer 86 with aspring 94 arranged therebetween. Aspindle bracket 98 is pinned to a lower end (as shown inFIG. 2 ) of thespindle 78. Thelower spring bracket 90 abuts thespindle bracket 98. Thespring 94 acts between theupper spring washer 86 and thelower spring washer 90 to bias thespindle bracket 98 downward (as shown inFIG. 2 ). Theadjustable screw 74 can be threaded into and out of thebonnet housing 58 to increase and decrease the biasing force applied by thespring 94. - As shown in
FIGS. 4-10 , theinerter system 22 includes aninerter hub 102 and a valve member in the form of adisk holder 106. As shown inFIG. 8 , theinerter hub 102 defines ahub flange 110 and ahub body 114. Avent 118 is defined in thehub flange 110 and a central hub bore 122 extends through theinerter hub 102 along thecentral axis 82. A bearing in the form of abushing 126 is received within the central hub bore 122. Thehub body 114 defines afirst slot 130 and asecond slot 134. Thefirst slot 130 andsecond slot 134 together define a cam profile. In the illustrated embodiment, theslots - With continued reference to
FIG. 8 , thedisk holder 106 includes acentral shaft 138 that holds at a first end a bearing in the form of aspherical crystal bearing 142 and defines apin aperture 146. A substantiallycylindrical pin 148 is fixedly received within thepin aperture 146. Thedisk holder 106 also includes adisk recess 150 arranged to receive adisk 154. - Assembly of the
PRV 10 will be described with reference toFIG. 2 . Theinerter system 22 is inserted into thebonnet flange 36 of thehousing 14 such that thehub flange 110 is received on theshoulder 38. Thebonnet 18 is installed onto thehousing 14 and theinerter system 22 with theshoulder 66 of thehousing flange 62 engaging thehub flange 110. Thebonnet flange 36 is then fastened to thehousing flange 62 with thehub flange 110 fixed therebetween such that the joint is substantially hermetically sealed and theinerter hub 102 is rotationally fixed relative to thehousing 14. Thevent 118 provides fluid communication between thechamber 34 and thebonnet 18 such that no substantial pressure differential exists therebetween. - With the
housing 14,bonnet 18, andinerter system 22 assembled, thespindle bracket 98 engages thespherical bearing 142 and thespring 94 biases thedisk holder 106 downward (as shown inFIG. 2 ) toward a closed position. The bias force is adjusted by manipulation of theadjustable screw 74 according to the predetermined specifications of the greater system in which thePRV 10 is installed (e.g., the pressure vessel system). - The
disk holder 106 is arranged such that thepin 148 is received in thefirst slot 130 and thesecond slot 134 and thecentral shaft 138 is guided vertically by thebushing 126 for linear movement along thecentral axis 82. Thedisk 154 is arranged such that in the closed position (as shown inFIG. 2 ), thedisk 154 engages thenozzle outlet 54 to inhibit fluid flow therethrough. - With continued reference to
FIG. 2 , when sufficient pressure builds in thenozzle inlet 50, the resultant force on thedisk holder 106 will overcome the bias force exerted by thespring 94 such that thedisk holder 106 will move toward an open position wherein thedisk 154 does not engage thenozzle outlet 54 and fluid is permitted to flow from thenozzle inlet 50 and out theoutlet port 30. Thepin 148 rides along the cam profile of thefirst slot 130 and thesecond slot 134 during movement between the open position and the closed position. - When the
disk holder 106 moves from the closed position toward the open position, theslots pin 148 along the cam profile. The result is that the linear motion of thedisk holder 106 is, at least in part, converted to rotational motion about thecentral axis 82. The configuration of theslots disc holder 106. Other cam profiles are contemplated and would be used, as determined by one skilled in the art. - The
inerter system 22 also converts translational kinetic energy, which is defined by: -
E translation=½ m V 2; -
- where m=mass and
- V=linear velocity
along thecenter axis 82 to rotational kinetic energy, which is defined by: - Erotational=½ J ω2;
- where J=polar moment of inertia and
- ω=angular velocity about the
center axis 82.
Therefore, thedisc holder 106 serves as a flywheel to which energy from linear motion in the form of vibration is transferred.
- In the embodiment shown in
FIGS. 1-10 , thedisc holder 106 rotates in response to linear motion caused by vibration, and thus, is sensitive to acceleration and more effective in reducing or controlling vibration than passive damping techniques. The mass of thedisk holder 106 itself acts as the flywheel in theinerter system 22. - Section II
-
FIGS. 11-16 show aninerter system 200 that can be used with thehousing 14 andbonnet 18 shown inFIGS. 1-3 in place of theinerter system 22. When theinerter system 200 is used with thebonnet 18, thebonnet housing 58 also defines acap shoulder 204. - As shown in
FIG. 14 , theinerter system 200 includes aninerter hub 208, adisk holder 212, abellows 216, aflywheel 220, and acap 224. Theinerter hub 208 defines ahub flange 228 and ahub body 232. As shown inFIGS. 14 and 16 , a bearingraceway 236 is defined in thehub flange 228. The bearingraceway 236 is a substantially semi-circular and annular raceway. Alternate arrangements are conceivable, such as a raceway arranged for pin bearings, etc. A firstmotion constraining slot 240 and a secondmotion constraining slot 244 are formed in thehub body 232. Themotion constraining slots FIG. 14 ). A central hub bore 248 is defined and extends through theinerter hub 208 along thecentral axis 82. A bearing in the form of abushing 252 is received within the central hub bore 248. - With continued reference to
FIG. 14 , thedisk holder 212 includes acentral shaft 256 that holds at a first end a bearing in the form of aspherical crystal bearing 260 and defines a motion constrainingpin aperture 264 and aflywheel pin aperture 268. A substantially cylindricalmotion constraining pin 272 is fixedly received within the motion constrainingpin aperture 264 and a substantiallycylindrical flywheel pin 276 is fixedly received within theflywheel pin aperture 268. Thedisk holder 212 also defines a bellows mating feature in the form ofthreads 280 and adisk recess 284 sized to receive adisk 288. - The bellows 216 includes a mating feature in the form of
threads 292 arranged to sealingly mate with thethreads 280 of thedisk holder 212. Thebellows 216 further include aexpandable body portion 296 arranged to accommodate vertical motion (as shown inFIG. 14 ) of thedisk holder 212 and agasket portion 300 arranged to mate with a bottom surface of thehub flange 228. - The
flywheel 220 defines an annular ring that includes abottom surface 304, anupper aperture 308, anupper bearing raceway 312, afirst cam slot 316, and asecond cam slot 320. Thebottom surface 304 defines a bearing raceway and can define a different shape intended to function optimally with different bearing types than are illustrated herein. Thefirst cam slot 316 andsecond cam slot 320 together define a cam profile. In the illustrated embodiment, theslots - The
cap 224 defines anupper surface 324, aninner aperture 328, and abearing raceway 332. The illustratedbearing raceway 332 is a shoulder recess. In other arrangements, the bearingraceway 332 can be arranged differently. For example, theraceway 332 can be arranged to receive pin bearings, or can include a contoured surface (e.g., semi-circular depression, rectangular recess, etc.). - With continued reference to
FIG. 14 , theinerter system 200 is assembled by installing thebellows 216 onto thedisk holder 212 by threading thebellows threads 292 onto thedisk holder threads 280 such that a seal is formed therebetween. Thedisk holder 212 and bellows 216 are then installed on theinerter hub 208 by sliding thecentral shaft 256 into thebushing 252 and positioning thedisk holder 212 such that themotion constraining pin 272 is received within themotion constraining slots disk holder 212 is then constrained by theslots FIG. 14 ) and substantial rotation is inhibited. - A bearing element in the form of a plurality of
ball bearings 336 is arranged in thebearing raceway 236 of theinerter hub 208, and theflywheel 220 installed onto theinerter system 200 by engaging thefirst cam slot 316 and thesecond cam slot 320 with theflywheel pin 276, and engaging thebottom surface 304 with theball bearings 336. As shown inFIGS. 15 and 16 , the bearingraceway 236 of theinerter hub 208 does not extend around the full annulus of the central hub bore 248, but rather inhibits theball bearings 336 from interfering with theflywheel pin 276 when thedisk holder 212 is in the closed position (as shown inFIG. 15 ). In other constructions, the bearingraceway 236 can extend fully about the central hub bore 248 and thepin 276 can be arranged differently so no interference exists. - Another bearing element (in the form of ball bearings 336) is arranged between the
upper bearing raceway 312 of theflywheel 220 and the bearingraceway 332 of thecap 224. Theball bearings 336 provide smooth rotation of theflywheel 220 under load. As noted above, other bearing elements can be used. For example, theball bearings 336 can be retained within separate raceways, the bearing elements can be pin or needle bearings, conical bearings, or another shape of bearing, as desired. The bearing elements can include bushings, or other arrangements designed to provide adequate rotation of theflywheel 220. - The assembled
inerter system 200 is then installed between thehousing 14 and the bonnet 18 (seeFIGS. 2 and 14 ). Theinerter system 200 is inserted into thehousing 14 such that thegasket portion 300 of thebellows 216 engages and seals against theshoulder 38 of thehousing 14. Theshoulder 66 of thebonnet 18 engages theinerter hub 208, and thecap shoulder 204 of thebonnet 18 engages theupper surface 324 of thecap 224. When thebonnet 18 is fastened to thehousing 14, thehub flange 228 and thegasket portion 300 are compressed between theshoulder 66 of thebonnet 18 and theshoulder 38 of thehousing 14 such that rotation of both components is inhibited. Thecap 224 is compressed relative to theinerter hub 208 to constrain theflywheel 220. Theball bearings 336 provide for rotational movement of theflywheel 220. - In operation, and referring to portions of
FIGS. 2 , 14, and 16, thedisk holder 212 is movable between a closed position in which thedisk 288 seals against thenozzle outlet 54 to inhibit fluid flow therethrough, and an open position in which the disk disengages from thenozzle outlet 54 to permit fluid flow through thenozzle 42 and out theoutlet port 30. Movement of thedisk holder 212 is constrained by thecentral shaft 256 and themotion constraining pin 272 such that thedisk holder 212 moves only in the vertical direction (as shown inFIG. 14 ) between the open position and the closed position with substantially no rotational movement. - The bellows 216 is arranged to compress and expand along with the motion of the
disk holder 212 between the open position and the closed position. The bellows 216 provides a barrier between the fluid and the other components of theinerter system 200 as can be advantageous in corrosive fluid control or other implementations. - As the
disk holder 212 moves between the open position and the closed position, theflywheel pin 276 engages and moves along thefirst cam slot 316 and thesecond cam slot 320 such that theflywheel 220 is forced into rotation by the cam profile defined by thefirst cam slot 316 and thesecond cam slot 320. The rotation of theflywheel 220 causes inertial damping of thedisk holder 212 similarly to theinerter system 22 discussed above in Section I. - Section III
-
FIGS. 17-26 show aPRV 400 according to one embodiment of the invention that includes ahousing 414, abonnet 418, and aninerter system 422. As shown inFIG. 18 , thehousing 414 defines aninlet flange 426 for coupling to a pressure vessel system, aflanged outlet port 430, an interior surface orchamber 434 between theinlet flange 426 and theoutlet port 430, and abonnet flange 436 defining ahousing shoulder 438 rimming an opening adjacent an upper portion 440 (as shown inFIG. 18 ) of thechamber 434. Anozzle 442 is received within theinlet flange 426 and defines a shapednozzle profile 446 between anozzle inlet 450 and anozzle outlet 454. - The
bonnet 418 includes abonnet housing 458 that defines ahousing flange 462 arranged for coupling to thebonnet flange 436 of thehousing 414 and defining abonnet shoulder 466. Thebonnet housing 458 also defines anadjustment screw aperture 470 sized to threadingly receive anadjustment screw 474. Aspindle 478 is slidingly received within theadjustment screw 474 and extends along acentral axis 482. Anupper spring washer 486 is positioned adjacent theadjustable screw 474 and slidingly receives thespindle 478. Alower spring washer 490 is positioned distally from theupper spring washer 486 with aspring 494 arranged therebetween. Aspindle bracket 498 is pinned to a lower end (as shown inFIG. 18 ) of thespindle 478. Thelower spring washer 490 abuts thespindle bracket 498. Thespring 494 acts between theupper spring washer 486 and thelower spring washer 490 to bias thespindle bracket 498 downward (as shown inFIG. 18 ). Theadjustable screw 474 can be threaded into and out of thebonnet housing 458 to increase and decrease the biasing force applied by thespring 494, as desired. - As shown in
FIG. 24 , theinerter system 422 includes aninerter hub 502, acam element 506, ajerk absorber 510, acam follower element 514, and adisk holder 518. Theinerter hub 502 defines ahub flange 522, ahub body 526 extending downward (as shown inFIG. 24 ) from thehub flange 522, and ajerk aperture 530 defined through thehub flange 522. Thehub body 526 defineshub body threads 532 substantially adjacent thehub flange 522. Acentral aperture 534 is defined through theinerter hub 502 along thecentral axis 482. In the illustrated embodiment, thecentral aperture 534 is manufactured such that an inner surface of thecentral aperture 534 forms a bearing surface. The bearing surface can be machined and polished, reamed, or formed in another way to provide a suitable bearing surface. In other constructions, a bearing or bushing can be inserted within thecentral aperture 534. - With continued reference to
FIG. 24 , thejerk aperture 530 is sized to press fittingly receive thejerk absorber 510. Alternatively, thejerk aperture 530 can be threaded, or can be filleted in preparation of a welding procedure. Other arrangements are conceivable (e.g., soldering, fastening, gluing, etc.). - The
cam element 506 defines acam element flange 538, acentral aperture 542 that is sized to receive thehub body 526, afirst cam 546, and asecond cam 550. Thecam element flange 538 defines ajerk aperture 554. Thecentral aperture 542 definescam element threads 558 sized to loosely engage thehub body threads 532. Thefirst cam 546 and thesecond cam 550 together define a cam profile. In the illustrated embodiment, thecams - As shown in
FIGS. 22 and 24 , thejerk absorber 510 includes ajerk pin 562 that defines a vent 566 (as shown inFIG. 24 ) and is sized to be press fit into thejerk aperture 530 of theinerter hub 502. Thejerk absorber 510 also includes abushing 570 engaged on thejerk pin 562 and received within thejerk aperture 554 of thecam element 506. The illustratedbushing 570 is constructed of a shock dissipating material such as rubber, includes abushing flange 574 arranged to be sandwiched between thehub flange 522 and thecam flange 538, and is snugly received within thejerk aperture 554 of thecam element 506. - The
cam follower element 514 defines afollower flange 578 that includes twoflat portions 582, acentral aperture 586 sized to receive thecam element 506, and a follower threadedportion 590. Eachflat portion 582 includes acam pin aperture 594 sized to receive acam pin 598. The cam pin apertures 594 (and therefore the pins 598) are positioned off-center with respect to the center axis 482 (as shown inFIG. 26 ). The cam pins 598 are arranged to engage thefirst cam 546 and thesecond cam 550. The follower threadedportion 590 includes a threadedaperture 602 sized to receive aset screw 606. - The
disk holder 518 defines acentral shaft 610 that holds at a first end a bearing in the form of a spherical crystal bearing 614 (as shown inFIG. 18 ) and defines adisk recess 618 arranged to receive adisk 622. Thedisk holder 518 further includes a holder threadedportion 626 arranged to threadingly receive the follower threadedportion 590, and aset screw aperture 630 arranged to receive theset screw 606. - Assembly of the
inerter system 422 will be described with reference toFIG. 24 . Thejerk bushing 570 is inserted into thejerk aperture 554 of thecam element 506. Thecam element 506 is then coupled to theinerter hub 502 by threading thecam element threads 558 onto thehub body threads 532. Thethreads cam element 506 spins easily. Thejerk aperture 530 of theinerter hub 502 is then aligned with thejerk aperture 554 of thecam element 506. Thejerk pin 562 is press fit into thejerk aperture 530 of theinerter hub 502, and thejerk bushing 570 that is positioned in thejerk aperture 554 of thecam element 506. - The threaded
portion 590 of thecam follower element 514 is then threaded onto the threadedportion 626 of thedisk holder 518, and theset screw 606 is tightened such that thecam follower element 514 is substantially rigidly coupled to thedisk holder 518. - The
disk holder 518 and thecam follower element 514 are then slid onto thecam element 506 such that thepins 598 are engaged with thefirst cam 546 and thesecond cam 550. - As shown in
FIG. 18 , with theinerter system 422 assembled, thehub flange 522 is engaged with theshoulder 438 of thehousing 414 such that thedisk 622 engages thenozzle outlet 454. Thebonnet 418 is then installed with theshoulder 466 of thebonnet flange 462 engaging thehub flange 522 and thespindle bracket 498 engaging thespherical bearing 614. Thebonnet 418 is then fastened to thehousing 414 such that theinerter hub 502 is fixed in place and inhibited from rotational and linear movement. - In operation, and as shown in
FIG. 18 , thedisk holder 518 is moveable between an open position where fluid is permitted to flow from thenozzle inlet 450 through thenozzle outlet 454, and out of theoutlet port 430, and a closed position where thedisk 622 engages thenozzle outlet 454 and inhibits fluid flow therethrough. - The
PRV 400 is typically in the closed position, and when pressure acting on thedisk holder 518 overcomes the bias force of thespring 494, thedisk holder 518 moves toward the open position. Moving toward the open position, thepins 598 engage thefirst cam 546 and thesecond cam 550 and move thedisk holder 518 along the cam profile. This results in a translation of linear motion to rotational work and has an inertial damping effect on the system, as discussed above. - The
jerk absorber 510 functions to absorb the initial shock and impact that theinerter system 422 undergoes upon the pressure in the pressure vessel or any downstream vibration overcoming the bias force of thespring 494. Thejerk bushing 570 absorbs the impact and the threadedportions cam element 506 relative to theinerter hub 502. - Section IV
- Many current PRVs form an undamped linear spring mass mechanism and are configured to enable pressure control over narrow pressure ranges. Resonant acoustic frequencies due to inlet pipe and/or other periodic inlet pipe dynamics cause an undesirable rapid cycling motion or vibration in the PRVs, sometimes known as “chatter,” wherein the disc rapidly cycles between the open and closed positions. Such vibration reduces the capacity of the PRV and can cause damage to internal components such as the disc and valve seat (i.e., nozzle outlet). Attempts have been made to reduce the effects of such vibration by modifying disc face, seat, and nozzle geometries in order to enhance the stability of PRVs. This method is effective at enhancing stability at relatively low pressures but has limited effectiveness in enhancing stability at relatively high pressures. Further, the use of passive damping techniques such as viscous type dampers (i.e., velocity sensitive dampers) or drag type dampers (i.e., position sensitive dampers) have been marginally successful in addressing undesirable vibration. In particular, such techniques are effective only after the vibration has already started.
- Embodiments of the invention provide, among other things, an inerter system wherein linear motion along a center axis is converted to rotational motion about the center axis. This conversion has the effect of adding inertial damping to the PRV. The inerter system reacts to acceleration of the system, as opposed to the more traditional passive systems that react to velocity. In other words, the invention has a much faster reaction and provides better damping with significantly less movement of the disc holder away form the nozzle outlet.
- The magnitude of the inertial damping effect provided by the inerter system is at least in part controlled by a cam profile defined by the structure of the inerter system (e.g.,
slots cams 546, 550). The cam profile can have a constant or variable lead, a curved shape, a variable shape, a straight shape that is angled relative to the center axis, a shape in accordance with a square or cube root function or a combination of such shapes, and other suitable shapes. In one construction, the cam profile is helically shaped. In another construction, the cam profile can include at least one stepped portion that is located between first and second curved portions, for example. In such a configuration, the disc holder initially rotates in a first portion of the cam profile, dwells, then resumes rotation in a second portion of the cam profile. In one construction, the cam profile has a right hand lead, resulting in a corresponding rotation direction. Alternatively, the cam profile can be positioned in an angled orientation relative to the center axis that is opposite than that depicted in the figures. For example, the cam profile can have a left hand lead. - Embodiments of the invention control vibration in a PRV without adding significant mass to the disc holder when compared with a typical disk holder. As a result, existing PRVs can be retrofitted in the field with the invention without extensive modification. In addition, the invention can be used in conjunction with other types of valves. The invention can also be used in any suitable valve configuration having a component or components, such as a valve stem that includes a disc or other components, which move in a linear motion and which are susceptible to an undesirable rapid cycling motion due to dynamic instability or vibration. For example, the invention can be applied to various types of line valves, check valves, relief valves, or other valves that are subject to vibrations and pressure fluctuations.
- In some embodiments of the invention, 15-20% of the energy produced by vertical movement is converted to rotary energy in the damping process. In other embodiments, more or less energy can be converted, depending on the desired characteristics of the damping system. For example, 10-50% or more of the vertical energy can be converted to rotary energy by the inerter system. As discussed above, the cam profile can be manipulated to produce the desired damping characteristics.
- Another advantage offered by embodiments of the invention is the ability to produce damped valves that are functional as single fluid valves. That is to say, a single valve design can be used for both a gas product and a liquid product. Current passively damped valves are not suitable for single fluid arrangement, because they are not capable of damping the systems to stability in the presence of the variety of conditions that are posed by a liquid product versus a gas product, or vice versa.
- The present invention recognizes the problem of damping and chatter issues as a lack of non-active systems that dampen in response to acceleration of a vibration and provide a wide ranging mode for dealing with such vibrations. The concept of a floating input (e.g., disk holder, etc.) is one that reacts to non-mechanical force such as pressure. That is to say, the floating input is not coupled between two fixed mechanical points for damping vibrations formed therebetween. For example, a floating input is not connected to a linkage (e.g., automobile suspension), not directly moved by a contact force (e.g., physical impact by an object), or rigidly coupled at its extremities.
- Although the above described valves are direct spring operated, the invention is capable with working with suitable actuation systems, including but not limited to, pilot operation, solenoid operation, and other control mechanisms.
- It will be appreciated by those skilled in the art that while the invention has been described above in connection with particular embodiments and examples, the invention is not necessarily so limited, and that numerous other embodiments, examples, uses, modifications and departures from the embodiments, examples and uses are intended to be encompassed by the claims attached hereto. The entire disclosure of each patent and publication cited herein is incorporated by reference, as if each such patent or publication were individually incorporated by reference herein.
- Various features and advantages of the invention are set forth in the following claims.
Claims (20)
1. A valve comprising:
a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet;
a valve member arranged at least partially within the housing and movable between an open position where flow is provided from the inlet through the valve seat to the outlet, and a closed position where flow is inhibited through the valve seat; and
an inerter element arranged to convert linear motion of the valve member into rotary movement beginning at the closed position, thereby damping the valve.
2. The valve of claim 1 , further comprising a biasing element biasing the valve member toward the closed position.
3. The valve of claim 1 , wherein the valve member moves linearly between the open position and the closed position, the linear motion of the valve member converted by the inerter element into rotary movement of the valve member, the mass and rotational movement of the valve member providing inertial damping.
4. The valve of claim 1 , wherein the inerter element is fixed to the housing.
5. The valve of claim 1 , wherein the valve member moves linearly between the open position and the closed position,
wherein the inerter element rotates in response to the linear movement of the valve member, the mass and rotational movement of the inerter element providing inertial damping.
6. The valve of claim 1 , wherein the inerter element defines a cam profile, the valve member engaging the cam profile.
7. The valve of claim 6 , wherein the cam profile is helical.
8. The valve of claim 1 , wherein the valve member is biased toward the open position by a pressure.
9. The valve of claim 1 , wherein the valve member actuates in response to a non-mechanical force.
10. A valve comprising:
a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet;
a valve member arranged at least partially within the housing and movable between an open position where flow is provided from the inlet through the valve seat to the outlet, and a closed position where flow is inhibited through the valve seat, the valve member coupled to the housing for linear and rotary movement relative to the housing about an axis; and
an inerter element substantially fixed to the housing and defining a cam profile, a portion of the valve member engaging the cam profile such that in response to a non-mechanical force the valve member moves between the open position and the closed position and linear motion of the valve member is converted to rotary motion of the valve member, thereby damping the valve when the valve member first leaves the closed position.
11. The valve of claim 10 , wherein the cam profile is helical.
12. The valve of claim 10 , wherein the valve member includes a pin that engages the cam profile.
13. The valve of claim 10 , wherein the valve member is biased toward the closed position.
14. The valve of claim 10 , wherein the valve member is coupled to the inerter element such that the inerter element supports the valve member for linear motion along the axis and rotation about the axis.
15. A method for damping a valve, the valve including a housing defining an inlet, an outlet, and a valve seat between the inlet and the outlet, a valve member arranged at least partially within the housing and moveable between an open position where flow is provided from the inlet through the valve seat to the outlet and a closed position where flow is inhibited through the valve seat, and an inerter element, the method comprising:
engaging a cam profile defined in the inerter element with the valve member; and
damping the valve by continuously rotating the valve member along the cam profile as the valve member moves from the closed position to the open position in response to a non-mechanical force and as the valve member moves from the open position to the closed position in response to a non-mechanical force.
16. The method of claim 15 , further comprising engaging a pin with the cam profile.
17. The method of claim 15 , wherein continuously rotating the valve member includes helically rotating the valve member along a helical cam profile.
18. The method of claim 15 , further comprising linearly moving the valve member between the open position and the closed position.
19. The method of claim 18 , further comprising converting the linear motion of the valve member into rotary motion of the valve member with the inerter element.
20. The method of claim 19 , further comprising inertially damping the valve member with the mass and rotational motion of the valve member.
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US14/743,798 US20150285400A1 (en) | 2013-03-06 | 2015-06-18 | Vibration Damping Device for a Valve |
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US14/198,401 US9103467B2 (en) | 2013-03-06 | 2014-03-05 | Vibration damping device for a valve |
US14/743,798 US20150285400A1 (en) | 2013-03-06 | 2015-06-18 | Vibration Damping Device for a Valve |
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US14/198,373 Active US9103466B2 (en) | 2013-03-06 | 2014-03-05 | Vibration damping device |
US14/743,798 Abandoned US20150285400A1 (en) | 2013-03-06 | 2015-06-18 | Vibration Damping Device for a Valve |
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EP2187084A1 (en) | 2008-11-14 | 2010-05-19 | Joseph Talpe | Hydraulic rotation damper |
JP5424751B2 (en) | 2009-07-10 | 2014-02-26 | カヤバ工業株式会社 | Suspension device |
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-
2014
- 2014-03-05 US US14/198,345 patent/US9200726B2/en active Active
- 2014-03-05 US US14/198,401 patent/US9103467B2/en active Active
- 2014-03-05 US US14/198,373 patent/US9103466B2/en active Active
- 2014-03-06 AU AU2014225650A patent/AU2014225650B2/en active Active
- 2014-03-06 EP EP14760064.7A patent/EP2964971B8/en active Active
- 2014-03-06 KR KR1020157027819A patent/KR102013562B1/en active IP Right Grant
- 2014-03-06 CA CA2904050A patent/CA2904050C/en active Active
- 2014-03-06 WO PCT/US2014/021316 patent/WO2014138438A1/en active Application Filing
- 2014-03-06 BR BR112015021943A patent/BR112015021943A2/en not_active IP Right Cessation
-
2015
- 2015-06-18 US US14/743,798 patent/US20150285400A1/en not_active Abandoned
- 2015-06-18 US US14/743,785 patent/US20150285331A1/en not_active Abandoned
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Publication number | Priority date | Publication date | Assignee | Title |
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WO2020135396A1 (en) * | 2018-12-28 | 2020-07-02 | 浙江三花制冷集团有限公司 | Flow control valve |
US11313475B2 (en) | 2018-12-28 | 2022-04-26 | Zhejiang Sanhua Climate and Appliance Controls Group Co., Ltd. | Flow control valve |
Also Published As
Publication number | Publication date |
---|---|
US9103466B2 (en) | 2015-08-11 |
EP2964971B1 (en) | 2018-06-06 |
KR20150122250A (en) | 2015-10-30 |
EP2964971A1 (en) | 2016-01-13 |
AU2014225650B2 (en) | 2017-06-15 |
US20150285331A1 (en) | 2015-10-08 |
US9103467B2 (en) | 2015-08-11 |
EP2964971A4 (en) | 2016-11-09 |
BR112015021943A2 (en) | 2017-07-18 |
US9200726B2 (en) | 2015-12-01 |
AU2014225650A1 (en) | 2015-10-29 |
EP2964971B8 (en) | 2018-07-18 |
CA2904050C (en) | 2019-06-18 |
WO2014138438A1 (en) | 2014-09-12 |
US20140251462A1 (en) | 2014-09-11 |
US20140251457A1 (en) | 2014-09-11 |
US20140251458A1 (en) | 2014-09-11 |
KR102013562B1 (en) | 2019-10-21 |
CA2904050A1 (en) | 2014-09-12 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |
|
AS | Assignment |
Owner name: PENTAIR FLOW CONTROL AG, SWITZERLAND Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:PENTAIR FLOW SERVICES AG;REEL/FRAME:040523/0653 Effective date: 20160810 |