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WO2025160135A1 - Commutateurs de fin de course destinés à des compresseurs - Google Patents

Commutateurs de fin de course destinés à des compresseurs

Info

Publication number
WO2025160135A1
WO2025160135A1 PCT/US2025/012540 US2025012540W WO2025160135A1 WO 2025160135 A1 WO2025160135 A1 WO 2025160135A1 US 2025012540 W US2025012540 W US 2025012540W WO 2025160135 A1 WO2025160135 A1 WO 2025160135A1
Authority
WO
WIPO (PCT)
Prior art keywords
pin
central channel
chamber
compressor
annular groove
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.)
Pending
Application number
PCT/US2025/012540
Other languages
English (en)
Inventor
Merced Gabriel JOHNSON JR.
Douglas A. Sahm
James B. MACON
Hunter MCWHIRT
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TPE Midstream LLC
Original Assignee
TPE Midstream LLC
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 TPE Midstream LLC filed Critical TPE Midstream LLC
Publication of WO2025160135A1 publication Critical patent/WO2025160135A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/008—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being a fluid transmission link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves

Definitions

  • This disclosure relates generally to compressors and, more particularly, to end-of- stroke switches for compressors.
  • Some compressors or pumps utilize a drive piston that moves in a reciprocating motion in a drive chamber.
  • a switching valve alternates between applying high pressure gas on either side of the drive piston, which causes the drive piston to move back-and-forth in the drive chamber.
  • the drive piston can be connected to one or more secondary pistons used to pump and/or otherwise transfer fluid from one location to another location.
  • FIG. 1 is a schematic diagram of an example compressor constructed in accordance with the teachings of this disclosure.
  • FIG. 2 is a perspective cross-sectional view of a physical implementation of the example compressor of FIG. 1 and showing two example end-of-stroke switches.
  • FIG. 3A is a cross-sectional view of one of the example end-of-stroke switches of FIG. 2.
  • the end-of-stroke switch is in a closed state.
  • FIG. 3B shows the example end-of-stroke switch of FIG. 3A engaged by an example drive piston and moved to an open state.
  • FIG. 4 is a wireframe model of the example end-of-stroke switch of FIGS. 3A and 3B.
  • FIG. 5 is a perspective view of the example end-of-stroke switch of FIGS. 3 A and 3B.
  • FIG. 6 shows an example of the end-of-stroke switch of FIGS. 3 A and 3B with an example fluid line to pressure balance the example switch.
  • FIG. 7 shows an example of the end-of-stroke switch of FIGS. 3A and 3B in which an example pin has an example central channel to pressure balance the example switch.
  • FIG. 8 shows an alternative tip portion of an example pin of the example end-of- stroke switch of FIGS. 3A and 3B.
  • FIG. 9 shows an example of the end-of-stroke switch of FIGS. 3A and 3B having an example seal.
  • FIG. 10 is a schematic diagram of the example compressor of FIG. 1 having an alternative placement of the example end-of-stroke switches.
  • Some types of compressors or pumps utilize a drive piston that moves in a reciprocating motion in a drive chamber.
  • the drive piston is coupled to a rod, which extends into one or more cylinders for pumping and/or otherwise moving fluid from one location to another location.
  • the compressor includes a switching valve that receives high pressure gas (e.g., pressurized air) from a high pressure gas source.
  • the switching valve alternates between directing high pressure gas into the drive chamber on either side of the drive piston, which causes the drive piston to move back-and-forth in the drive chamber.
  • the switching valve may direct the high pressure gas into a first side of the drive chamber while venting the second side of the drive chamber, which causes the piston to move in a first direction.
  • the switching valve switches states and directs high pressure gas into the second side of the drive chamber while venting gas from the first side of the drive chamber, which causes the piston to move in a second or opposite direction.
  • the switching valve alternates between these two states to cause the piston to move back-and-forth in the drive cylinder.
  • Some known compressors utilize pressure sensors to measure pressure spikes in the drive chamber in attempts to determine when the piston has reached the end of its stroke and trigger the switching valve to switch states.
  • very high pressure gas e.g., 1,000 pounds-per-square-inch (PSI) or higher
  • PSI pounds-per-square-inch
  • these types of sensors often trigger the switching valve pre-maturely or at a delayed time after the piston has already reached the end of its stroke.
  • high pressure gas sources often experience variations or spikes in pressure, which can be relatively large. These variations or spikes can also pre-maturely trigger the switching valve.
  • Disclosed herein are example end-of-stroke switches for use in an example compressor.
  • the end-of-stroke switches are physical switches that are activated when physically contacted or engaged by a drive piston of the compressor, and therefore accurately sense when the piston has reached the end of its stroke.
  • two end-of-stroke switches can be disposed in the drive chamber and coupled to coupling blocks on the opposite ends of the drive chamber.
  • the drive piston physically contacts or engages one of the end-of-stroke switches.
  • the switch then generates and/or otherwise transmits a pneumatic signal (e.g., a pressurized air signal) to the switching valve, which causes the switching valve to switch states and drive the drive piston in the opposite direction.
  • a pneumatic signal e.g., a pressurized air signal
  • the end-of-stroke position may be defined as the position when the piston can longer accept additional high pressure gas to press the piston toward the opposing coupling block, and the switch is fully depressed.
  • the compressor can be configured such that the piston does not contact the coupling block at its end-of-stroke position, and instead moves in the opposite direction before making contact.
  • the example end-of-stroke switches disclosed herein are advantageous for use with compressors driven by high pressure gases.
  • the high pressure gas used to drive the drive piston may be 1,000 PSI or higher. With such high pressures, it is important to ensure the switches are not pre-maturely triggered.
  • the example switches disclosed herein are configured to operate in relatively high pressure environments and only switch between closed and open states when physically engaged by the piston.
  • the pneumatic signal provided by the end-of-stroke switch may be a relatively low pressure gas signal.
  • the switch may be fluidly connected to a low pressure gas source by a fluid line.
  • the switch is also fluidly connected to the switching valve by another fluid line.
  • the switch includes a pin that is moveable betw een a closed position and an open position. When the piston is not at the end of its stroke, the pin remains in the closed position. In the closed position, the pin blocks or prevents the flow of the lower pressure gas to the switching valve. When the piston reaches the end of its stroke, the piston contacts the pin and moves the pin to its open position. In the open position, the pin allow s the flow of gas from the low pressure gas source to the switching valve.
  • This flow of gas acts as a pneumatic signal, which indicates the piston is at the end of its stroke.
  • the low pressure gas is much lower than the high pressure gas used to drive the piston.
  • the pressures may differ by an order of magnitude.
  • the low pressure gas for generating the pneumatic signal may be 100 PSI, while the high pressure gas for driving the drive piston may be 1,000 PSI or higher.
  • the example end-of-stroke switches disclosed herein are configured to isolate the high pressure gas environment from the low pressure signal environment. This is advantageous because high pressure gas sources often have variations or spikes in pressure.
  • the examples disclosed herein ensure the switch is only activated by direct contact with the piston and not prematurely or incorrectly activated by some pressure fluctuation in the high pressure environment. Therefore, the example switches can operate or be exposed to a relatively high pressure environment and still accurately control a relatively low pressure signal.
  • FIG. 1 is a schematic diagram of an example compressor 100 constructed in accordance with the teachings herein.
  • the example compressor 100 can be used to compress, pump and/or otherwise transport or move fluid from one location to another location.
  • FIG. 1 shows an example inlet manifold 102 that can be connected to a fluid source.
  • FIG. 1 also shows an example outlet manifold 104 that can be connected to a downstream location where the fluid is to be transferred.
  • the compressor 100 When the compressor 100 is activated, the compressor 100 transfers fluid from the inlet manifold 102 to the outlet manifold 104, as disclosed in further detail herein.
  • the fluid being transferred can be any type of fluid, such as water, oil, natural gas, methane, etc.
  • the compressor 100 includes a drive cylinder 106 and first and second coupling blocks 108a, 108b coupled to opposite ends of the drive cylinder 106.
  • the compressor 100 includes a first gas cylinder 110a coupled to and extending from the first coupling block 108a, and a second gas cylinder 110b coupled to an extending from the second coupling block 108b.
  • the compressor 100 includes a first gas block 112a coupled to the distal end of the first gas cylinder 110a, and a second gas block 112b coupled to the distal end of the second gas cylinder 110b.
  • the drive cylinder 106 and the coupling blocks 108a, 108b define a drive chamber 114.
  • the compressor 100 includes a drive piston 116 in the drive chamber 114.
  • the drive piston 116 divides the drive chamber 114 into a first chamber 118a (between the drive piston 116 and the first coupling block 108a) and a second chamber 118b (between the drive piston 11 and the second coupling block 108b).
  • high pressure gas e.g., pressurized air
  • the compressor 100 includes a rod 120 coupled to and extending from the drive piston 116 in both directions.
  • the rod 120 extends through the first coupling block 108a and into the first gas cylinder 110a.
  • the compressor 100 includes a first piston 122a disposed in the first gas cylinder 110a and coupled to the rod 120.
  • the first piston 122a divides the first gas cylinder 110a into first and second chambers 124a, 124b, which may be referred to as a double acting cylinder chamber.
  • first and second chambers 124a, 124b which may be referred to as a double acting cylinder chamber.
  • the first gas block 112a includes (e.g., forms or defines) a first fluid passageway 126a with a first inlet check valve 128a that fluidly couples the inlet manifold 102 and the first chamber 124a, and a second fluid passageway 126b with a first outlet check valve 130a that fluidly couples the outlet manifold 104 and the first chamber 124a.
  • the first coupling block 108a includes (e.g., forms or defines) a first fluid passageway 132a with a second inlet check valve 128b that fluidly couples the inlet manifold 102 and the second chamber 124b, and a second fluid passageway 132b with a second outlet check valve 130b that fluidly couples the outlet manifold 104 and the second chamber 124b.
  • any of the check valves can be arranged outside of the blocks.
  • the compressor 100 includes a second piston 122b that is disposed in the second gas cylinder 110b and coupled to the rod 120, and which divides the divides the second gas cylinder 110b into first and second chambers 134a, 134b. which may be referred to as a double acting cylinder chamber.
  • the second gas block 112b includes (e.g., forms or defines) a first fluid passageway 136a with a first inlet check valve 138a that fluidly couples the inlet manifold 102 and the first chamber 134a, and a second fluid passageway 136b with a first outlet check 140a valve that fluidly couples the outlet manifold 104 and the first chamber 134a.
  • the second coupling block 108b includes (e.g., forms or defines) a first fluid passageway 142a with a second inlet check valve 138b that fluidly couples the inlet manifold 102 and the second chamber 134b, and a second fluid passageway 142b with a second outlet check valve 140b that fluidly couples the outlet manifold 104 and the second chamber 134b.
  • the second gas cylinder 110b operates the same as the first gas cylinder 110 to transfer gas from the inlet manifold 102 to the outlet manifold 104.
  • the compressor 100 is pneumatically driven.
  • the compressor 100 is powered or driven by high pressure/compressed gas from a high pressure gas source 144.
  • the high pressure gas source 144 can be air or another gas (e.g., carbon-dioxide, nitrogen, natural gas, etc.).
  • the high pressure gas source 144 is relatively high pressure, such as 1,000 PSI or higher.
  • the high pressure gas source 144 can be at a lower pressure.
  • the compressor 100 includes a switching valve 146.
  • the switching valve 146 is fluidly coupled to the high pressure gas source 144.
  • the switching valve 146 is fluidly coupled to the first chamber 118a by a first fluid line 148a and fluidly coupled to the second chamber 118b by a second fluid line 148b.
  • the switching valve 146 alternates between a first state and a second state. In the first state, the switching valve 146 fluidly connects the high pressure gas source 144 and the first fluid line 148a, which supplies high pressure gas into the first chamber 118a, and fluidly connects the second fluid line 148b to a vent 149b, which vents the gas in the second chamber 118b.
  • the switching valve 146 fluidly connects the high pressure gas source 144 and the second fluid line 148b, which supplies high pressure gas into the second chamber 118b. and fluidly connects the first fluid line 148a to a vent 149a, which vents the gas in the first chamber 118a.
  • the switching valve 146 alternatives rapidly between these first and second states. This operation causes the drive piston 116 to move back-and-forth in a reciprocating motion.
  • the example compressor 100 includes a first example end-of- stroke switch 150a and a second example end-of-stroke switch 150b, referred to herein as first and second switches 150a, 150b, respectively.
  • first switch 150a is coupled to the first coupling block 108a.
  • second example switch 150b is coupled to the second coupling block 110b.
  • the switching valve 146 is in the second state in which high pressure gas is supplied into the second chamber 118b while the first chamber 118a is vented. This causes the drive piston 116 to move to the left in FIG. 1.
  • the drive piston 116 When the drive piston 116 reaches the left end of the drive chamber 114 (e.g., the end-of-stroke), the drive piston 116 physically contacts or engages the first switch 150a. This triggers the first switch 150a to transmit a pneumatic signal (e.g., a pressurized air signal) to the switching valve 146. In response to receiving the pneumatic signal, the switching valve 146 switches to the first state in which high pressure gas is supplied to the first chamber 118a and while gas from second chamber 118b is vented to the atmosphere, which causes the drive piston 116 to move to the right in FIG. 1.
  • a pneumatic signal e.g., a pressurized air signal
  • the drive piston 116 When the drive piston 116 reaches the right end of the drive chamber 114 (e.g., the end-of-stroke), the drive piston 116 physically contacts or engages the second switch 150b.
  • the second switch 150b transmits a pneumatic signal to the switching valve 146.
  • the switching valve 146 switches back to the second state, and the example process continues.
  • This switching causes the drive piston 116 to move back-and-forth in a reciprocating motion.
  • the first and second pistons 122a, 122b are also driven back-and-forth in their respective cylinders, which causes the pumping action to transfer fluid from the inlet manifold 102 to the outlet manifold 104.
  • the compressor 100 While in this example the compressor 100 includes two gas cylinders 1 10a, 110b, in other examples, the compressor 100 may include only one gas cylinder.
  • the drive piston 116 is driven by high pressure gas
  • the drive piston 116 can be driven by hydraulic pressure.
  • the switching valve 146 contains no electronic devices. Instead, the switching valve 146 is operated entirely by pneumatic or hydraulic power.
  • the compressor 100 may be used to pump or transfer combustible fluids, such as natural gas or methane. Therefore, it is advantageous from a safety' perspective to avoid use of any electronic devices that could otherwise cause a spark.
  • FIG. 2 is a cross-sectional view of an example physical implementation of the example compressor 100.
  • FIG. 2 shows the drive cylinder 106 and portions of the first and second gas cylinders 110a, 110b.
  • the first switch 150a is coupled to the first coupling block 108a
  • the second switch 150b is coupled to the second coupling block 108b.
  • any example structure and/or functions disclosed in connection with the first example switch 150a likewise apply to the second example switch 150b.
  • the first coupling block 108a has a first side 200 facing the drive chamber 114 and a second side 202 opposite the first side 200.
  • the first coupling block 108a has a bore 204 extending into the first side 200.
  • the bore 204 extends in an axial direction in the first coupling block 108a.
  • the first switch 150a is at least partially disposed in the bore 204.
  • the first coupling block 108a has a supply passage 206 and an exhaust passage 208.
  • the supply and exhaust passages 206. 208 extend in a radial direction between the bore 204 and an outer peripheral surface 210 of the first coupling block 108.
  • the supply passage 206 is to be fluidly connected to a supply of pressurized air 212.
  • a fluid line can be threaded into a port of the supply passage 206 on the outer peripheral surface 210, and the fluid line can be fluidly coupled to the supply of pressurized air 212.
  • This supply of pressurized air 212 is used to generate a pneumatic signal, as disclosed in further detail herein.
  • the exhaust passage 208 is fluidly coupled to the switching valve 146.
  • a fluid line can be threaded into a port of the exhaust passage 208 on the outer peripheral surface 210.
  • the fluid line can be fluidly coupled to the switching valve 146.
  • the pressurized air 212 may be at a relatively lower pressure than the high pressure gas source 144 (FIG. 1).
  • the pressurized air 212 may be at 80-100 PSI.
  • the first switch 150a includes a body 214 and a pin 216 that is moveable in the body 214.
  • the pin 216 may also be referred to as an actuator, dis/engagement trigger, valve stem, button, shuttle, or flow control member.
  • the pin 216 is moveable between a first position, referred to herein as a closed position, when the pin 216 is not engaged by the drive piston 116, and a second position, referred to herein as an open position, when the drive piston 116 engages the pin 216.
  • the first switch 150a blocks air flow from the supply passage 206 to the exhaust passage 208.
  • the pin 216 When the pin 216 is contacted by the drive piston 116, the pin 216 is moved to the open position, in which the first switch 150a allows air flow from the supply passage 206 to the exhaust passage 208. This air flow forms an air signal that is sensed by the switching valve 146. In response to the air signal, the switching valve 146 switches states to drive the drive piston 1 16 in the opposite direction. When the drive piston 116 disengages the first switch 150a, the pin 216 moves back into the closed position (e.g., via a spring, via a pressure bias, etc.) and therefore stops the air signal to the switching valve 146.
  • the closed position e.g., via a spring, via a pressure bias, etc.
  • first switch 150a is configured to control the flow of air to generate a pneumatic signal
  • first switch 150a can be configured to generate another type of signal, such as a hydraulic signal (e.g., using hydraulic oil) or an electrical signal.
  • FIGS. 3A and 3B are enlarged cross-sectional views of the first coupling block 108a with the first switch 150a.
  • FIG. 3A shows the pin 216 in the closed position
  • FIG. 3B shows the pm 216 moved to the open position by the drive piston 116.
  • the bore 204 extends into the first side 200 of the first coupling block 108a.
  • the bore 204 is defined by an inner side surface 300 and an inner end surface 302.
  • the first switch 150a is disposed in the bore 204.
  • the body 214 of the first switch 150a is cylindrical or disc-shaped.
  • the body 214 has a first end 304, a second end 306 opposite the first end 304, and an outer side surface 308 between the first and second ends 304, 306.
  • the body 214 has a central channel 310 extending through the body 214 between the first end 304 and the second end 306.
  • the central channel 310 is defined or formed by an inner surface 312.
  • the body 214 is disposed in the bore 204 such that the second end 306 is engaged with the inner end surface 302 of the bore 204.
  • the compressor 100 includes a retainer 314 (e.g., a circ-clip) that is disposed in a groove 316 in the inner side surface 300 of the bore 204, and which is engaged with and/or otherwise blocks the first end 304 of the body 214.
  • the retainer 314 prevents the body 214 from moving out of the bore 204.
  • the first switch 150a can be coupled to the first coupling block 108a via other mechanical and/or chemical coupling techniques (e.g. friction fit, welding, one or more threaded fasteners, an adhesive, etc.).
  • mechanical and/or chemical coupling techniques e.g. friction fit, welding, one or more threaded fasteners, an adhesive, etc.
  • the switch 150a includes four seals 318a, 318b, 318c, 318d (e.g., o-rings) that form a pressure tight seal between the outer side surface 308 of the body 214 and the inner side surface 300 of the bore.
  • the seals 318a-318d are spaced axially from each other and disposed in respective glands or grooves in the outer side surface 308 of the body 214.
  • the first switch 150a can include more or fewer seals to seal between the body 214 and the first coupling block 108a.
  • the pin 216 is disposed in the central channel 310 of the body 214.
  • the pin 216 is slidable in the central channel 310, as disclosed in further detail herein.
  • the pin 216 is coaxial with the body 214.
  • a portion of the pin 216 extends outward from the central channel 310 and beyond the first end 304 of the body 214.
  • the pin 216 has a tip end 320 and a back end 322 opposite the tip end 320.
  • the tip end 320 extends beyond the first side 200 of the first coupling block 108a and into the first chamber 1 18a.
  • the pin 216 is depicted as three parts or components that are coupled together. In some examples, this facilities assembly of the pin 216 in the body 214. However, in other examples, the pin 216 can be constructed by more or fewer parts (e.g., the pin 216 can be constructed as a monolithic structure).
  • the first switch 150a includes a seal 324 disposed in a seal gland 326 formed in the inner surface 312 of the central channel 310.
  • the seal 324 forms a pressure tight seal between the body 214 and the pin 216.
  • the seal 324 prevents fluid leakage passed the seal 324 and, thus, prevents fluid leakage between the first chamber 118a, on the right side of the seal 324 in FIG. 3A, and the portion of the central channel 310 to the left side of the seal 324 in FIG. 3A. Therefore, the seal 324 isolates the high pressure gas in the first chamber 118a and the low pressure gas in the middle portion 334 of the central channel 310 that is used as the pressure signal.
  • the central channel 310 has an enlarged portion that forms a cavity 328.
  • the pin 216 has a sealing surface 330
  • the inner surface 312 of the channel 310 has a corresponding sealing surface 332, referred to herein as a seat 332.
  • the sealing surface 330 and the seat 332 are tapered (e.g., angled).
  • the sealing surface 330 is sealed against (e.g., sealingly engaged with) the seat 332 to block fluid flow through the central channel 310. In particular, this blocks or prevents fluid from the cavity 328 from flowing into the central channel 310 to the right of the seat 332 in FIG.
  • the body 214 and the pin 216 are constructed of metal (e.g., aluminum, stainless steel, etc.). This metal-to- metal contact forms a tight seal.
  • the sealing surface 330 and/or the seat 332 may be highly polished to form smooth surfaces. In some examples, the sealing surface 330 and/or the seat 332 are constructed of ceramic.
  • the central channel 310 has a middle portion 334 that is defined between the seat 332 and the seal gland 326.
  • the middle portion 334 of the central channel 310 has a larger diameter than the portion of the pin 216 in the middle portion 334, such that fluid can flow between the pin 216 and the inner surface 312 in the middle portion 334 of the central channel 310.
  • the cavity 238 is on a first side (e.g., the left side in FIG. 3 A) of the seat 332, while the middle portion 334 is on a second side (e.g., the right side in FIG. 3A) of the seat 332.
  • the pin 216 controls the flow of fluid through the seat 332 between the cavity 328 and the middle portion 334 of the central channel 310.
  • the first switch 150a includes a spring 338 to bias the pin 216 to the closed position.
  • the spring 338 is disposed in a rear cavity 340 formed in the inner end surface 302 of the bore 204 of the first coupling block 108a.
  • the spring 338 is engaged with the back end 322 end of the pin 216.
  • the spring 338 biases the pin 216 into or tow ard the seat 332 (e.g., to the right in FIG. 3 A).
  • the back end 322 of the pin 216 is exposed to fluid in the rear cavity 340.
  • the spring 338 biases the pin 216 to the right in FIG. 3A, which maintains the pin 216 in the closed position.
  • the first coupling block 118a has a passage 342 that extends in a radial direction between the bore 204 and the outer peripheral surface 210 of the first coupling block 108.
  • the passage 243 may be used during assembly/disassembly of the first switch 150a.
  • the passage 342 is closed from atmosphere by a plug 341.
  • the cavity 328, the rear cavity 340, and the passage 342 can be filled with pressurized air 212 from the supply passage 206.
  • the rear cavity 340 may be open.
  • a diaphragm 345 may be coupled to the pin 216 and the body 214 to separate the cavity 328 into a signal side (e.g., on the right side of the diaphragm 345) and atmospheric pressure (e.g., on the left side of the diaphragm 345).
  • the diaphragm 345 is coupled to the pin 216 between a spring retaining portion 343a and a central body portion 342b of the pin 216.
  • the passage 342 can be coupled to a pressurized air source to provide pressurized air (e.g., at a higher pressure than atmospheric pressure) into the rear cavity' 340.
  • pressurized air e.g., at a higher pressure than atmospheric pressure
  • This pressure helps to bias the pin 216 to the closed position against the force acting on the right side of the pin 216 from the high pressure gas in the first chamber 118. Therefore, in some examples, this enables the use of a smaller spring.
  • the tip end 320 has a smaller area than the back end 322. In some examples, this results in a higher force on the back end 322 to help bias the pin 216 to the closed position.
  • the outer side surface 308 of the body 214 has a first annular groove 344 (e.g., an annular, a recess, etc.) that is radially aligned with the supply passage 206.
  • the first annular groove 344 is filled with pressurized air from the supply passage 206.
  • the first annular groove 344 is fluidly coupled to the cavity 328.
  • FIG. 4 is perspective cross-sectional view of the switch 150a in the first coupling block 108a shown in wireframe.
  • the body 214 of the first switch 150a has a first set of radial passages 400 extending through the body 214 between the first annular groove 344 and the cavity 328.
  • the cavity 328 is filled with pressurized air from the supply passage 206.
  • the first set of radial passages 400 may extend in the radial direction and be spaced apart from each other (e.g., space equidistant from each other around a circumference of the cavity' 328).
  • the body 214 can include any number of the radial passages 400 (e.g., one, tw o, three, four, etc.).
  • the outer side surface 308 of the body 214 has a second annular groove 346 that is radially aligned with the exhaust passage 208.
  • the second annular groove 346 is fluidly coupled to the middle portion 334 of the central channel 310.
  • the body 214 includes a second set of radial passages 402 extending through the body 214 between the second annular groove 346 and the inner surface 312 of the central channel 310 along the middle portion 334 of the central channel 310.
  • the pin 216 remains in the closed position, even while the pressure in the first chamber 118a may increase significantly.
  • the pressure in the first chamber 118a creates on a force on the nght side of the pin 216.
  • the force provided by the spring 338 exceeds this force and, therefore, maintains the pin 216 in the closed position.
  • the position of the pin 216 in the closed position prevents the switch 150a from prematurely opening from the relatively high pressure buildup in the first chamber 118a. Instead, the pin 216 remains in the closed position until the drive piston 116 physically engages (e.g., touches, contacts) and moves the pin 216 to the left, i.e., to the open position.
  • FIG. 3B shows the pin 216 after being engaged by the drive piston 116 and moved to the open position.
  • the pin 216 has been engaged by the drive piston 116 and moved (e.g., slid) to the left.
  • the sealing surface 330 of the pin 216 is separated or spaced from the seat 332, which enables fluid flow through the central channel 310.
  • the pressurized air from the supply passage 206 flows through the first annular groove 344, through the passages 400 (FIG. 4). through the cavity 328. through the seat 332, through the middle portion 334 of the central channel 310, through the passages 402 (FIG.
  • the exhaust passage 208 is fluidly connected (e.g., via one or more fluid lines or hoses) to the switching valve 146 (FIGS. 1 and 2).
  • the pressurized air provided by the exhaust passage 208 acts as a pneumatic signal or air signal, which indicates the drive piston 116 is at the end of its stroke.
  • the switching valve 146 senses the air signal and, in response, switches to a state in which high pressure air is directed into the first chamber 118a and vent from the second chamber 118b to cause the drive piston 116 to move in the opposite direction.
  • the spring 338 (and/or any force from pressure in the rear cavity 340) moves the pin 216 to the right to the closed position, where the sealing surface 330 is sealed against the seat 332.
  • FIG. 5 is a perspective view of the first switch 150a, which includes the body
  • the pin 216 is disposed in the central channel 310 of the body 214.
  • the pin 216 extends outward from the first end 304 of the body 214.
  • the outer side surface 308 of the body 214 has the first annular groove 344 with the passages 400 (one of which is referenced in FIG. 5) and the second annular groove 346 with the passages 402 (one of which is referenced in FIG. 5).
  • the pin 216 controls the flow of air between the first annular groove 344 and the second annular groove 346. As disclosed above, in the closed position, the pin 216 blocks air flow' from the first annular groove 344 to the second annular groove 346.
  • the rear cavity 340 may be fluidly coupled to the first chamber 1 18a (FIG. 3 A).
  • the pin 216 is substantially pressure balanced (e.g., ⁇ 10% pressure difference), since the pressure from the first chamber 118a is acting on both ends of the pin 216.
  • FIG. 6 show's an example in which the compressor 100 includes a fluid line 600 that fluidly couples the passage 342 and the first chamber 118a.
  • the rear cavity 340 is at the same pressure as the first chamber 118a.
  • the pin 216 is substantially pressure balanced.
  • the pressure on the left and right sides of the pin 216 are the same or substantially the same (e.g., ⁇ 10%). This reduces the likelihood of the pin 216 moving prematurely by the increased pressure in the first chamber 118a.
  • the spring 338 can be sized significantly smaller (e.g., less than half of the spring force), because the spring 338 is primarily used to return the pin 216 to the closed position. In other examples, the spring 338 can be omitted. Instead, the area of the back end 322 of the pin 216 is greater than the area of the tip end 320, which results in a net force on the back end 322, so the pin 216 is naturally biased to the closed position.
  • FIG. 7 shows an example in which the pin 216 has a central channel 700 (e.g., an orifice) extending between the tip end 320 and the back end 322 (FIG. 3 A) of the pin 216.
  • the central channel 700 enables fluid communication between the first chamber 118a and the rear cavity 340.
  • the rear cavity 340 is at the same pressure as the first chamber 118a and, thus, the pin 216 is substantially pressure balanced (e.g., ⁇ 10% pressure difference).
  • Pressure balancing the pin 216 reduces the likelihood of the pin 216 moving pre-maturely by the increased pressure in the first chamber 118a. Pressure balancing also enables the use of a smaller spring 338 to maintain the pin 216 in the closed position.
  • the passage 342 is plugged or sealed.
  • the central channel 700 is relatively small, such as l/8inch. In other examples the central channel 700 may be larger or smaller.
  • the spring 338 can be omitted.
  • the tip portion of the pin 216 can be shaped differently. For example. FIG. 8 shows an example in which the pin 216 has an enlarged bulb 800 near the tip end 320. The first end 304 of the body 214 has an enlarged bore 802 to receive the bulb 800. Fluid from the first chamber 118a can flow to an area 804 behind the bulb 800. When the pin 216 is pushed to the left by the drive piston 116 (FIG.
  • the fluid in the area 804 provides a cushion, which creates a dampening effect as the gas in the area 804 stalls momentarily to evacuate to the bore 802 around the bulb 800.
  • the bulb 800 helps to block debris and other particulate in the first chamber 118a from venting the central channel 310 of the body 214.
  • some pneumatic or hydraulic fluids may be relatively dirty 7 and carry particles and other debris. The bulb 800 helps to prevent this dirt or debris in the first chamber 118a from flowing into the central channel 310 where the dirt and debris could negatively impact the sliding motion of the pin 216.
  • FIGS. 3 A and 3B the sealing surface 330 of the pin 216 is pressed into and sealed against the seat 332 of the channel 310.
  • a seal such as an o-ring, can be used to form at least a portion of the sealing interface between the two surfaces.
  • FIG. 9 shows an example of the first switch 150a including a seal 900 (e.g., an o-ring) that is disposed in a seal gland 902 formed on the seat 332 of the inner surface 312 of the central channel 310.
  • the sealing surface 330 of the pin 216 is pressed into and sealed against the seal 900, which blocks or prevents fluid from the cavity 328 from flowing into the central channel 310 to the right of the seal 900.
  • the seal 900 may be constructed of an elastic or compliant material such as PTFE, Nitrile (Buna), Neoprene, EPDM Rubber, and/or Fluorocarbon (Viton).
  • multiple seals e.g., a stack of o-rings
  • one or more seals can be carried on the sealing surface 330 of the pin 216.
  • the angle or taper of the sealing surfaces 330, 332 is shallower than in the example in FIGS. 3A and 3B. This shallower angle allows for great contact patch and, thus, sealing between the two parts.
  • the first and second switches 150a, 150b are on the inner surfaces of the coupling blocks 108a, 108b.
  • the switches 150a, 150b can be disposed in other locations.
  • FIG. 10 shows an example of the compressor 100 in which the first sw itch 150a is on the outer surface of the first coupling block 108a, and the second switch 150b is on the outer surface of the second coupling block 108b.
  • the first switch 150a is triggered when engaged by the first piston 122a in the first gas cylinder 1 10a, and the second switch 150b is triggered by the second piston 122b in the second gas cylinder 110b.
  • the first and second switches 150a, 150b operate in substantially the same manner as disclosed above and provide air signals to the switching valve 146.
  • the first and second switches 150a, 150b can be located on the inner surfaces of the gas blocks 112a, 112b.
  • the first switch 150a can be disposed on the outer surface (e.g., the second side 202) of the first coupling block 108a, and the second switch 150b can be disposed on the inner surface of the first gas block 112a. Therefore, both switches are in the first gas cylinder 110a and triggered by the first piston 122a. Additionally or alternatively, two switches can be provided in the second gas cylinder 110b.
  • A, B, and/or C refers to any combination or subset of A, B, C such as (1) A alone, (2) B alone, (3) C alone, (4) A with B, (5) A with C, (6) B with C, or (7) A with B and with C.
  • the phrase “at least one of A and B” is intended to refer to implementations including any of (1) at least one A, (2) at least one B, or (3) at least one A and at least one B.
  • the phrase “at least one of A or B” is intended to refer to implementations including any of (1) at least one A, (2) at least one B, or (3) at least one A and at least one B.
  • the phrase “at least one of A and B” is intended to refer to implementations including any of (1) at least one A, (2) at least one B, or (3) at least one A and at least one B.
  • the phrase “at least one of A or B” is intended to refer to implementations including any of (1) at least one A, (2) at least one B, or (3) at least one A and at least one B.
  • any part e.g., a layer, fdm, area, region, or plate
  • any part e.g., a layer, fdm, area, region, or plate
  • the referenced part is either in contact with the other part, or that the referenced part is above the other part with one or more intermediate part(s) located therebetween.
  • connection references may include intermediate members between the elements referenced by the connection reference and/or relative movement between those elements unless otherwise indicated. As such, connection references do not necessarily infer that two elements are directly connected and/or in fixed relation to each other. As used herein, stating that any part is in “contact”’ with another part is defined to mean that there is no intermediate part between the two parts.
  • descriptors such as “‘first,” “‘second,” “third,” etc., are used herein without imputing or otherwise indicating any meaning of priority, physical order, arrangement in a list, and/or ordering in any way, but are merely used as labels and/or arbitrary names to distinguish elements for ease of understanding the disclosed examples.
  • the descriptor “first” may be used to refer to an element in the detailed description, while the same element may be referred to in a claim with a different descriptor such as “second” or “third.” In such instances, it should be understood that such descriptors are used merely for identifying those elements distinctly within the context of the discussion (e.g., within a claim) in which the elements might, for example, otherwise share a same name.
  • “approximately” and “about” modify their subjects/values to recognize the potential presence of variations that occur in real world applications. For example, “approximately” and “about”’ may modify dimensions that may not be exact due to manufacturing tolerances and/or other real world imperfections as will be understood by persons of ordinary skill in the art. For example, “approximately” and “about” may indicate such dimensions may be within a tolerance range of +/- 10% unless otherwise specified herein.
  • the phrase “in communication,” including variations thereof, encompasses direct communication and/or indirect communication through one or more intermediary components, and does not require direct physical (e.g., wired) communication and/or constant communication, but rather additionally includes selective communication at periodic intervals, scheduled intervals, aperiodic intervals, and/or one-time events.
  • example systems, apparatus, methods, and articles of manufacture have been disclosed that enable a compressor or pump to determine when a drive piston has reached its end-of-stroke position.
  • the examples disclosed herein provide a more accurate and reliable approach to determining the end-of-stroke.
  • the example switches disclosed herein can operate in a high pressure environment while still accurately controlling a lower pressure air signal.
  • Example 1 is a compressor comprising: a drive chamber defined by a drive cylinder and first and second coupling blocks coupled to opposite ends of the drive cylinder; a drive piston in the drive chamber, the drive piston dividing the drive chamber into a first chamber and a second chamber; a switching valve to be fluidly coupled to a high pressure gas source, the switching valve to direct high pressure gas into the first chamber and the second chamber in an alternating sequence to drive the drive piston in a reciprocating motion; and a switch coupled to the first coupling block, the switch including: a body having a central channel; and a pin in the central channel, the pin having a tip end extending into the first chamber, wherein the pin is moveable from a closed position to an open position when the drive piston contacts the tip end of the pin, and wherein, when the pin is moved to the open position, the switch is to transmit a signal to the switching valve.
  • Example 2 includes the compressor of Example 1, w herein an inner surface of the central channel has a seat, wherein the pin has a sealing surface, and wherein: when the pin is in the closed position, the sealing surface is sealed against the seat to block fluid flow through the central channel, and when the pin is in the open position, the sealing surface is spaced from the seat to enable fluid flow through the central channel.
  • Example 3 includes the compressor of Example 2, w herein an outer side surface of the body has a first annular groove and a second annular groove, the first annular groove fluidly coupled to a cavity in the central channel on a first side of the seat, the second annular groove fluidly coupled to a middle portion of the central channel on a second side of the seat.
  • Example 4 includes the compressor of Example 3, w herein the body has a first set of radial passages extending through the body between the first annular groove and the cavity and a second set of radial passages extending through the body between the second annular groove and an inner surface of the central channel.
  • Example 5 includes the compressor of Examples 3 or 4, further including a seal disposed in a seal gland formed in the central channel of the body, the seal forming a pressure tight seal between the body and the pin to isolate the high pressure gas in the first chamber and the middle portion of the central channel.
  • Example 6 includes the compressor of any of Examples 3-5, wherein the first coupling block has a first side facing the drive chamber and a second side opposite the first side, the first coupling block having a bore extending into the first side, the switch disposed in the bore.
  • Example 7 includes the compressor of Example 6, wherein the first coupling block has a supply passage and an exhaust passage that extend in a radial direction between the bore and an outer peripheral surface of the first coupling block, wherein the supply passage is to be fluidly connected to a supply of pressurized air, and wherein the exhaust passage is to be fluidly coupled to the switching valve.
  • Example 8 includes the compressor of Example 7, wherein the first annular groove is radially aligned with the supply passage and the second annular groove is radially aligned with the exhaust passage.
  • Example 9 includes the compressor of any of Examples 1-8, wherein the pin has a tip end and a back end opposite the back end, wherein the tip end is to be exposed to the high pressure gas in the first chamber, and wherein the back end is to be exposed to fluid in a rear cavity.
  • Example 10 includes the compressor of Example 9, wherein the rear cavity is formed in the first coupling block.
  • Example 11 includes the compressor of Examples 9 or 10, wherein the tip end has a smaller area than the back end.
  • Example 12 includes the compressor of any of Examples 9-11, further including a spring in the rear cavity and engaged with the back end of the pin, the spring to bias the pin to the closed position.
  • Example 13 includes the compressor of any of Examples 9-12, further including a fluid line to fluidly connect the rear cavity and the first chamber such that the pin is substantially pressure balanced.
  • Example 14 includes the compressor of any of Examples 9-12, wherein the pin has a central channel between the tip end and the back end to enable fluid communication between the first chamber and the rear cavity such that the pin is substantially pressure balanced.
  • Example 15 includes the compressor of any of Examples 1-14, wherein the signal is a pneumatic signal.
  • Example 16 is an end-of-stroke switch for a compressor, the end-of-stroke switch comprising: a body having a first end, a second end opposite the first end, and an outer side surface between the first and second ends, the body having a central channel extending through the body between the first end and the second end, an inner surface of the central channel forming a seat, the outer side surface having a first annular groove and a second annular groove, the first annular groove to receive a supply of pressurized air, the second annular groove to be fluidly coupled to a switching valve of the compressor, the first annular groove fluidly coupled to a cavity in the central channel on a first side of the seat, the second annular groove fluidly coupled to a middle portion of the central channel on a second side of the seat; and a pin in the central channel, the pin having a sealing surface, the pin moveable between a closed position in which the sealing surface is sealed against the seat to block fluid flow between the cavity 7 and the middle portion of the central channel and open position in which
  • Example 17 includes the end-of-stroke switch of Example 16, wherein the body has a first set of radial passages extending through the body between the first annular groove and the cavity 7 and a second set of radial passages extending through the body between the second annular groove and the inner surface of the central channel.
  • Example 18 includes the end-of-stroke switch of Examples 16 or 17, further including a seal disposed in a seal gland formed in the central channel of the body, the seal forming a pressure tight seal between the body and the pin to isolate high pressure gas in a chamber of the compressor and the middle portion of the central channel.
  • Example 19 includes the end-of-stroke switch of any of Examples 16-18, wherein the sealing surface and the seat are tapered.
  • Example 20 includes the end-of-stroke switch of any of Examples 16-19, further including a spring to bias the pin to the closed position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

Sont divulgués des commutateurs de fin de course destinés à des compresseurs. Un compresseur donné à titre d'exemple comprend un piston d'entraînement dans une chambre d'entraînement. Le compresseur comprend une soupape de commutation destinée à être accouplée de manière fluidique à une source de gaz haute pression. La soupape de commutation est destinée à diriger un gaz haute pression dans une première chambre et une seconde chambre dans une séquence alternée afin d'entraîner le piston d'entraînement dans un déplacement en va-et-vient. Le compresseur comprend un commutateur accouplé au premier bloc d'accouplement. Le commutateur comprend un corps comportant un canal central et une broche dans le canal central. La broche comporte une extrémité de pointe s'étendant dans la première chambre. La broche est mobile d'une position fermée à une position ouverte lorsque le piston d'entraînement entre en contact avec l'extrémité de pointe de la broche. Lorsque la broche est déplacée vers la position ouverte, le commutateur doit transmettre un signal à la soupape de commutation.
PCT/US2025/012540 2024-01-23 2025-01-22 Commutateurs de fin de course destinés à des compresseurs Pending WO2025160135A1 (fr)

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Application Number Priority Date Filing Date Title
US202463624092P 2024-01-23 2024-01-23
US63/624,092 2024-01-23

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06280501A (ja) * 1993-03-18 1994-10-04 Graco Inc エアーモータ
KR200233299Y1 (ko) * 2001-03-13 2001-10-08 전영근 에어 구동식 유압펌프
WO2016136667A1 (fr) * 2015-02-23 2016-09-01 アネスト岩田株式会社 Pompe à piston à mouvement de va-et-vient
KR102247489B1 (ko) * 2017-08-30 2021-05-03 에스엠시 가부시키가이샤 증압장치
US20210355924A1 (en) * 2018-05-13 2021-11-18 Tpe Midstream Llc Fluid Transfer and Depressurization System

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06280501A (ja) * 1993-03-18 1994-10-04 Graco Inc エアーモータ
KR200233299Y1 (ko) * 2001-03-13 2001-10-08 전영근 에어 구동식 유압펌프
WO2016136667A1 (fr) * 2015-02-23 2016-09-01 アネスト岩田株式会社 Pompe à piston à mouvement de va-et-vient
KR102247489B1 (ko) * 2017-08-30 2021-05-03 에스엠시 가부시키가이샤 증압장치
US20210355924A1 (en) * 2018-05-13 2021-11-18 Tpe Midstream Llc Fluid Transfer and Depressurization System

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