WO1996006316A1 - Self-adjusting superheat valve - Google Patents
Self-adjusting superheat valve Download PDFInfo
- Publication number
- WO1996006316A1 WO1996006316A1 PCT/US1994/010255 US9410255W WO9606316A1 WO 1996006316 A1 WO1996006316 A1 WO 1996006316A1 US 9410255 W US9410255 W US 9410255W WO 9606316 A1 WO9606316 A1 WO 9606316A1
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- WO
- WIPO (PCT)
- Prior art keywords
- die
- valve
- evaporator
- temperature
- force
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
- F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/062—Capillary expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/068—Expansion valves combined with a sensor
- F25B2341/0681—Expansion valves combined with a sensor the sensor is heated
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
Definitions
- the present invention relates to techniques for configuring valves to control the flow of fluid therethrough in response to selected parameters, and particularly to methods and apparatus for automatically controlling fluid flow with an automatic, self-adjusting valve which responds to system changes.
- the present invention finds particular application to closed loop vapor cycle refrigeration systems, and more particularly to apparatus and methods for automatically adjusting the refrigerant flow in such a refrigeration system for variations in the refrigeration system design and changes in the operating and ambient conditions.
- refrigeration system refers to any such system to lower temperature, and includes air conditioning systems as well as systems to cool relatively confined spaces, such as systems typically called refrigerators and freezers, for example.
- a type of mechanical expansion valve commonly used contains a body having an inlet port and an outlet port and a movable valve, or closure, element placed within the body for opening and closing the valve orifice.
- a compression spring is placed at one end of the valve element to apply a force to it in a first direction.
- a second force generator such as a fluid-filled bellows or diaphragm, is placed against the other end of the closure element to provide a force against it representative of a system parameter, such as the outlet temperature of the evaporator coil, in a second direction that is opposite to the direction of the force provided by the compressed spring.
- the second force generator is coupled in fluid communication with a thermal probe, with the second force generator, the probe and the communication conduit therebetween being filled with an appropriate fluid.
- the probe typically is attached thermally to the evaporator coil outlet.
- the pressure in the probe, and thus in the second force generator changes, causing the bellows or diaphragm, for example, to expand or to contract, thereby providing a force at the closure device that is representative of the temperature of the region where the probe is located, such as at the evaporator coil outlet.
- Examples of various valves may be found in U.S. Patent Nos. 5.026,022, 5,065,595, and 5,148,684.
- the present invention provides a method and apparatus for controlling the flow of refrigerant fluid in a refrigeration system, which is responsive to parameters of the system. More particularly, the present invention provides method and apparatus for controlling the flow of refrigerant in a refrigeration system by providing an automatic continuously self-adjusting thermally powered expansion valve.
- a probe senses the temperature of the air flowing past the evaporator and applies a quantity of fluid pressure that is representative of the temperature of the air to configure the valve to control the flow of refrigerant to the evaporator.
- the configuring of the valve controls the flow of refrigerant to maintain the temperature at the outlet end of the evaporator lower than the temperature of the air external to the evaporator and higher than the temperature within the evaporator decreases; the flow of refrigerant decreases when the difference between the temperature at the outlet end of the evaporator and the temperature within the evaporator decreases, or the difference between the temperature of the air external to the evaporator and the temperature within the evaporator increases.
- Two temperature sensing probes may be used, with one probe sensing the temperature at the outlet end of the evaporator and the other probe sensing the temperature of the air external to the evaporator. Forces that are representative of the sensed temperatures and of the pressure in the evaporator are generated to control the configuration of the valve. T e flow of refrigerant to the evaporator is thus increased when the temperature of the air external to the evaporator decreases, or the temperature at the outlet end of the evaporator increases, or the pressure in the evaporator decreases. Likewise, the flow of refrigerant is decreased when the temperature of the air external to the evaporator increases, or the temperature at the outlet end of the evaporator decreases, or the pressure in the evaporator increases.
- Two force generators operable by application of fluid pressure thereto, are provided to operate in generally opposite directions to configure the valve.
- Each of the two probes is in fluid pressure communication with one of the force generators so that one force generator generates force representative of the temperature sensed by one of the probes and the other force generator generates force representative of the temperature sensed by the o ⁇ er probe.
- the force generators apply force in generally opposite directions to a valve element whose position in a valve body determines the flow passage area for flow of refrigerant through the valve. Fluid pressure is communicated to the valve element from within the evaporator as well so that forces representative of the two sensed temperatures and of the pressure within the evaporator configure the valve.
- a spring provides a force to tend to close the valve to provide a response of the valve to change in the difference between the temperature at the outlet end of the evaporator and the temperature within the evaporator that is at least partially proportional.
- One of the force generators may generate force greater than the force generated by the other force generator in response to the same quantity of fluid pressure applied to each of the force generators.
- the two force generators may comprise bellows such that the operable area of one bellows for generating force for configuring the valve is larger than the operable area of the other bellows.
- a self-adjusting thermally powered valve according to the present invention may comprise a sliding valve element within a chamber in a valve body, intermediate in inlet port and an outlet port, with the position of the valve element determining the fluid flow through the valve, and multiple force generators applying ratiometric forces representative of system parameters to move the valve element accordingly.
- the present invention provides method and apparatus for controlling the flow of refrigerant in a refrigeration system by the generation of forces representative of parameters of the refrigeration system, including the temperature of the air flow by the evaporator of the system, for example, wherein the forces are so produced ratiometrically, that is, proportional to the difference in the operative areas of the two force generators of the valve of the invention for producing force to configure the valve.
- the valve of the present invention features balanced inlet and outlet ports so that he movement of the valve element is not hindered by flow of fluid through the valve. Further, the valve is not responsive to liquid line pressure upstream of the valve.
- a compression spring operates to provide a proportional response of the valve element to changes in the temperature of the superheat of the refrigeration system.
- a valve according to the present invention is self-adjusting, that is, the valve adjusts automatically in response to changes in the parameters of the system employing the valve such as the air being cooled by a refrigeration system; the valve is thermally powered, that is, the configuration of the valve is determined and changed by forces that are generated by heat changes and according to differences in temperatures; and the valve is mechanically self-adjusted, that is. the thermal powering of the valve configuration changes is effected utilizing fluid pressure applied to the valve components.
- Fig. 1 is a schematic illustration of a closed loop vapor cycle refrigeration system utilizing a self-adjusting thermally powered expansion valve according to the present invention
- Fig. 2 is an enlarged, schematic, cross-sectional view of an expansion valve according to the present invention utilized in the system illustrated in Fig. 1
- Fig. 3 is a graph of a response curve of the expansion valve shown in Fig. 2.
- a closed loop vapor cycle refrigeration system 10 is shown generally in Fig. 1.
- the refrigeration system 10 preferably includes a compressor 12 for compressing a low pressure gas refrigerant, a condenser 14 for condensing the compressed gas refrigerant to a liquid, a receiver 16 for receiving and storing the liquid refrigerant, and an evaporator system 18 including an evaporator coil 20 for evaporating the liquid refrigerant to the low pressure gas.
- the evaporator system 18 further includes a self-adjusting thermally powered mechanical expansion valve 22 coupled to the evaporator coil 20 for controlling the flow of refrigerant to the evaporator coil.
- the refrigeration system 10 also features a microcontroller circuit 24 for controlling the operation of the system in response to various system parameters in accordance with programmed instructions.
- Various sensors provide information about selected system parameters of the refrigeration system 10 to the control circuit 24.
- the compressor 12 preferably receives the low pressure gas refrigerant from the evaporator coil 20 by way of a suction line 26 and compresses the low pressure gas to a high pressure and high temperature gas refrigerant.
- the high pressure gas refrigerant is conducted by way of a line
- a fan 30 at the condenser 14 causes air to flow across the condenser 14. as indicated by the arrow 32, thereby condensing the compressed gas refrigerant to a liquid.
- the fan 30 may be of any appropriate type, including a fixed or variable speed type.
- the air 32 flowing across the condenser 14 removes thermal energy of condensation from the refrigerant in the condenser and causes the refrigerant to condense to liquid.
- the liquid refrigerant from the condenser 14 discharges by way of a liquid return line 34 to the receiver or reservoir 16 where the liquid is stored as indicated at 36.
- a conduit 38 conveys the liquid refrigerant from the reservoir 16 to the inlet side of the expansion valve 22.
- the valve 22 is located between the reservoir 16 and the inlet end 40 of the evaporator coil 20 for controlling the flow of refrigerant from the reservoir to the evaporator coil.
- the refrigerant fluid absorbs thermal energy of evaporation from air in contact with the coil, and evaporates to the gaseous state for egress through the outlet end 42 of the coil and return to the compressor 12 along the refrigerant tube 26.
- the flow path of refrigerant around the refrigeration system 10 is thus a closed loop, or circuit. Ambient air flows into the evaporator system 18 and over the evaporator coil 20 as indicated by the arrows 44.
- the ambient air that is cooled by removal of thermal energy to evaporate the refrigerant in the evaporator coil 20 is discharged from the area of the coil 20 as indicated by the arrows 46.
- the cooling of the ambient air flow 44 and 46 establishes the useful refrigeration effect.
- the ambient air may be circulated so that the flow 44 into the evaporator system is return air that is to be cooled again after absorbing thermal energy in cooling a load at some other location.
- appropriate sensors are positioned throughout the refrigeration system 10 to generate electrical signals representative of the temperature or fluid pressure at respective locations.
- the electrical signals are conveyed to the control circuit 24 for processing and utilization by the control circuit in the operation of the system 10.
- a temperature sensor 48 is placed in the liquid flow conduit 28 to obtain a signal that is representative of the temperature of the liquid entering the condenser 14.
- a temperature sensor 50 and a pressure sensor are placed in the liquid flow conduit 28 to obtain a signal that is representative of the temperature of the liquid entering the condenser 14.
- the 52 may be positioned along the liquid return line 34 to the reservoir 16 to provide electrical signals representative of the temperature and pressure, respectively, of the refrigerant in that return line.
- a temperature sensor 54 is placed in the evaporator system 18 in the path of the return air flow 44 to provide an electrical signal representative of the of the temperature of the return air.
- a temperature sensor 56 is positioned in the path of the discharge air flow 46 from the evaporator system 18 to provide a signal representative of the temperature of the air leaving the evaporator coil 20.
- Temperature sensors 58 and 60 are positioned at the inlet end 40 of the evaporator coil 20 and at the outlet end 42 of the coil to provide signals representative of the temperature of the refrigerant entering and leaving the evaporator coil, respectively. Additionally, pressure sensors
- 62 and 64 are connected to the inlet end 40 and the outlet end 42 of the evaporator coil 20 to provide signals that are representative of the pressure of the refrigerant at the coil inlet and outlet ends, respectively.
- Additional temperature sensors such as 66 and 68, may be located in the compressor 12 to determine the temperature of the compressor crankcase and the temperature of the oil in the compressor, respectively.
- the microcontroller circuit 24 includes a microprocessor, appropriate analog-to-digital converters and comparators, for example, and switching circuitry.
- the control circuit 24 is operatively coupled to the temperature sensors 48, 50, 54, 56, 58, 60, 66 and 68, the pressure sensors 52, 62 and 64, the compressor 12 and the fan 30 by appropriate conductors (not shown).
- Outgoing arrows as parts of the sensor symbols and inward arrows 70 at the controller circuit 24 indicate that the sensors are operatively coupled to and provide relevant information signals to the controller.
- the control circuit 24 continually receives information from the various sensors of the system and, in response thereto, controls the operation of various system components, such as the compressor 12 and the fan 30, in accordance with instructions provided to or stored in the circuit 24.
- the configuration of the expansion valve 22 is automatically and continuously adjusted directly with the use of two thermal sensing probes operatively connected to the valve itself.
- a first probe 74 is connected to a first end of the expansion valve 22 by a conduit 76, and a second probe 78 is connected to the opposite, second end of the valve by a conduit 80.
- the first probe 74 is thermally connected to the outlet end 42 of the evaporator coil 20, which is connected to the suction line 26 to the compressor 12.
- the second probe 78 is place in a suitable location in the refrigeration system 10 such as in the path of the return air 44 to the evaporator system 18 as illustrated, or in the refrigeration area (not shown) being cooled by the cooled air flow 46 discharged from the evaporator system 18, or in the path of the discharge air flow 46, for example.
- the construction and operation of the valve 22 and the operation of the probes 74 and 78 will now be discussed with reference to Fig. 2.
- the expansion valve 22 preferably includes a generally elongate body 82 having a generally cylindrical inner chamber 84, a first (or upper) end 86, a second (or lower) end 88, an inlet port 90 to the chamber transverse to the cylindrical axis of the body 82, and an outlet port 92 leading from the chamber substantially on the opposite side of the body 82 from the inlet port 90 and at least approximately longitudinally aligned with the inlet port.
- a tubular inlet coupling 94 extends transversely from the cylindrical axis of the body 82 at the inlet port 90, and a tubular outlet coupling 96 extends transversely from the body at the outlet port 92.
- valve outlet coupling 96 is joined to the inlet end 40 of the evaporator coil 20 so that refrigerant allowed to pass through the valve 22 to its outlet port 92 may flow into the evaporator coil.
- a structured valve element or closure device 98 such as a piston, preferably is located in the valve chamber 84 for longitudinal movement along the cylindrical axis of the chamber.
- the valve element 98 is generally cylindrical, and fits within the chamber 84 with the outer surface of the valve element in sliding, sealing engagement with the interior surface of the body 82 defining, in part, the chamber 84.
- the valve element 98 divides the chamber 84 into two regions on opposite sides of the valve element.
- the cylindrical surface of the valve element 98 is broken by one or more (three are shown) grooves or circular passages 100.
- the longitudinal position of the valve element 98 relative to the valve body 82 determines the position of each groove 100 relative to the inlet port 90 and the outlet port 92.
- Each groove 100 provides a fluid flow passage around the interior of the chamber 84 between the inner surface of the body 82 and the valve element 98 so that a groove aligned with both the inlet port 90 and the outlet port 92 establishes a flow path for fluid through the valve 22.
- the valve element 98 provides a seal across the inlet port 90, and the valve is closed.
- the grooves may be of different cross-sectional areas, or two or more such grooves may have the same cross-sectional area.
- Multiple grooves 100 in the valve element 98 may also be positioned at various spacings along the valve element, or the grooves may be evenly spaced.
- the valve inlet port 90 preferably is smaller than the outlet port 92.
- some or all of the grooves may be aligned with the outlet port 92, while at the same time a smaller number, or even none, of the grooves are aligned with the inlet port 90.
- Any groove 100, or any portion of a groove cross section, that is aligned with the inlet port 90 will also be aligned with the outlet port 92 in the port configuration illustrated.
- a groove 100 aligned only with the outlet port 92 and not the inlet port 90 does not break the seal between the valve element 98 and the inner surface of the body 82, and does not provide a passage for fluid through the valve 22.
- the inlet port 90 may be considered the orifice of the valve 22, whose opening is controlled by the position of the valve element 98 relative to the valve body 82.
- the flow rate of refrigerant through the valve 22 to the evaporator coil 20 thus is determined by the position of the valve element 98 within the valve body 82, so that moving die valve element along the chamber 84 causes the flow rate through the valve to vary.
- the number, size and spacing of the grooves 100 may be selected to achieve different degrees of sensitivity of the valve control as well as different amounts of flow rate change for given valve configuration changes.
- the movement of d e sliding valve element is not opposed by die flow of fluid against die valve element such as would be die case for a plunger-type valve element, for example; also, die valve configuration using die sliding element is not responsive to d e fluid line pressure upstream of die valve inlet port.
- the operation of the valve 22, diat is, die positioning of die valve element 98 widiin die valve chamber 84, is controlled by a combination of forces acting at die opposite, longitudinal ends 86, 88 of die valve element 98.
- a large diameter bellows 102 preferably is located widiin die valve chamber 84 between die first end 86 of die valve 22 and die near end of die valve element 98.
- the conduit 76 is sealed to die valve body 82 and is in fluid communication with die interior of die large bellows 102.
- the opposite end 104 of die large bellows 102 contacts die near end of die valve element 98.
- the bellows 102, die conduit 76 and die diermal probe 74 are fluid-filled so that an increase in pressure of die fluid due to its heating with a temperature rise at die probe 74 is communicated to die bellows 102, which then tends to expand against die valve element 98.
- the force applied to die valve element 98 by the bellows 102 is given by die product of die pressure of die fluid in die bellows and die cross-sectional area A, of die bellows end 104 contacting the end of die valve element 98.
- a small diameter bellows 106, diat is, a bellows having an end 108 with a cross-sectional contact area A 2 diat is smaller than die area A, preferably is placed widiin die valve chamber 84 between die second end 88 of die valve body 82 and die opposite end of die valve element 98 from diat which is in contact widi die large bellows 102.
- the fluid conduit 80 is sealed to die valve body
- die small bellows 106 is in fluid communication with die interior of die small bellows 106.
- the small bellows 106, die conduit 80 and die diermal probe 78 are fluid-filled so diat an increase in pressure of die fluid due its heating with a temperature rise at die probe 78 is communicated to die interior of die bellows, which then tends to expand against die valve element 98.
- the force exerted by die small bellows 106 on die valve element 98 is given by die product of die pressure in die bellows and die area A 2 of die bellows end 108 contacting d e valve element.
- the probes 74, 78 may comprise, for example, diermal bulbs.
- the fluid in die probes 74 and 78, die conduits 76 and 78, and the two bellows 102 and 106 preferably comprises an appropriate fluid, such as a refrigerant, to respond to temperature changes in the temperature ranges to which die probes are exposed to effect corresponding pressure changes at die respective bellows to contribute to control of die valve 22.
- a compression spring 110 preferably circumscribes die small bellows 106 widiin die valve chamber 84 and is generally compressed between die second end 88 of die valve body 82 and die near end of die valve element 98.
- the spring 110 dius exerts a force on die valve element 98 diat is determined by die amount of compression of die spring and die spring constant. It will be appreciated d at die spring 110 and die small bellows 106 may both apply forces on die valve element 98 in die upward direction as viewed in Fig. 2, and die large bellows may apply a force on die valve element in die opposite, or downward, direction, widi each force tending to move the valve element in die direction of die applied force.
- the valve element 98 is broken by a longitudinal passage 112 extending die entire length of die element and providing a fluid pressure communication conduit across die valve element.
- the two bellows 102 and 106 are not sealed to die ends of the valve element 98.
- the region widiin die valve body chamber 84 above die valve element 98, as viewed in Fig. 2, and outside die large bellows 102 is in fluid pressure communication, along d e passage 112, with the region widiin die chamber 84 below die valve element 98 and outside die small bellows 106.
- Longitudinal movement of die valve element 98 widiin die chamber 84, dierefore, is not hindered or opposed by a fluid pressure differential in die chamber, across die valve element and outside the two bellows.
- a conduit 114 connects the interior of the valve outlet coupling 96 widi die valve body chamber 84 above die valve element 98.
- Widi die valve 22 incorporated in a refrigeration system such as at 10 in Fig. 1, die fluid pressure downstream of die valve element 98, particularly downstream of die inlet port 90, and widiin die evaporator coil 20 is thus communicated along die outlet coupling 96 and die conduit 114 to die upper region of die valve chamber 84 above die valve element 98 and, by way of die valve element passage 112, to die valve chamber region below d e valve element 98.
- the evaporator coil pressure is dius equalized across die valve element 98.
- die forces applied to die two bellows 102 and 106 due to die evaporator coil pressure are dependent on die surface area of die respective bellows, as discussed below.
- the fluid pressure widiin die evaporator coil 20 may be communicated across the valve element 98 and to die two bellows 102 and 106 by odier structures.
- a second conduit (not shown) may be provided between die oudet coupling 96 and die valve body chamber 84 below die valve element 98 radier dian utilizing a passage 112 dirough the valve element. Then, fluid pressure from die evaporator coil 20 is communicated directly to bodi sides of die valve element 98.
- die passage 112 may be positioned away from die central axis of the valve element 98 so as to communicate widi each of die grooves 100, and no external conduits such as 114, for example, are utilized to connect die outlet coupling 96 widi die valve chamber 84 on eidier side of die valve element 98.
- fluid pressure from die evaporator coil 20 is communicated dirough die outlet port 92 to any of die grooves 100 aligned widi die outlet port and along the longitudinal passage dirough die valve element 98 to both sides of die valve element.
- the liquid refrigerant 36 is conveyed to d e valve 22 by die tube 38. and passes dirough die valve inlet port 90 into die body chamber 84, along one or more groove passages 100 of die valve element 98, and out dirough die oudet port 92 to die evaporator coil 20.
- the refrigerant begins to change state upon traversing die oudet port 92 and die outlet tubular connector 96, and enters the evaporator coil 20 as a liquid and vapor mixture.
- the pressure of die refrigerant itself exerts force diat affects die tendency of die valve element 98 to be moved along die valve body 82 to alter die flow rate dirough die valve 22.
- the pressure of die fluid in die first probe 74 which preferably is representative of die coil outlet temperature, diat is, die temperature of die refrigerant exiting die evaporator coil 20, generates a downward (as viewed in Fig. 2) force F co dirough die large bellows 102 acting on die upper end of die valve element 98.
- the force F co increases as die coil outlet temperature increases to expand die fluid in die probe 74, and such force decreases as die coil outlet temperature decreases.
- F cu P C (A,) (2) where P c is die fluid pressure in die coil.
- diat die net force applied by die fluid pressure P c of die refrigerant in the valve 22, tending to affect die valve element 98, is given by die product P C (A, - A 2 ) and acts on die large bellows 102, tending to allow die valve element 98 to be moved upwardly (as viewed in Fig. 2) against die large bellows 102.
- the fluid pressure in die second probe 78 which preferably is representative of die temperature of die return air flow 44 as illustrated, and which increases or decreases as diat temperature rises or falls, respectively, generates an upward force on die small bellows 106 contacting die valve element 98, as viewed in Fig.
- die equilibrium equation In die equilibrium state, die sum of all die forces tending to move die valve element 98 upwardly equals die sum of all die forces tending to move die valve element downwardly.
- A,(P co - P c ) A 2 (P r - P e ) + F t . (8) If die ratio A 2 /A- of the surface area of die small bellows end 108 to die large bellows end 104 is set equal to R, then
- dien F is zero, and if die same fluid is used in the two diermal probes 74 and 78 diat is used as die refrigerant, die temperature and pressure of the fluid for all remaining terms are proportional, and die temperatures may be substituted for the corresponding pressure values to yield
- Equation (10) provides a single set point for die expansion valve 22 which is independent of fluctuations in odier system parameters, including die suction pressure in die suction line 26.
- die valve 22 is configured so diat downward movement of die valve element 98 is required to increase fluid flow dirough die valve.
- die valve element 98 is in die off, or closed, configuration when it is positioned in die chamber 84 toward die large bellows 102.
- die grooves 100 are all displaced toward die first end 86 of die valve body 82, and none of die grooves are aligned widi die inlet port 90. It will be appreciated d at die coil fluid pressure acting on die two bellows 102 and 106 is die same for both bellows; however, since die bellows end areas
- the valve 22 is, dierefore, responsive, in part, to the fluid pressure in die evaporator coil 20.
- die return air temperature T r will be higher dian die coil temperature T c as will die coil outlet temperature T co . Also, die coil outlet temperature T co will be lower dian die return air temperature
- T r so diat T is smaller dian T 2 .
- die valve 22 adjusts according to Equation (10) so that die valve element 98 is moved to increase die cross-sectional area of die grooves intersecting die inlet port 90, and refrigerant flow dirough die valve increases when (a) die return air temperature decreases, (b) die coil outlet temperature increases, or (c) die pressure in die coil 20 decreases.
- die valve 22 adjusts so diat die valve element 98 is moved to decrease d e cross-sectional area of die grooves 100 intersecting die inlet port 90, and refrigerant flow dirough die valve decreases when (a) die return air temperature increases, (b) the coil outlet temperature decreases, or (c) die pressure in die coil 20 increases.
- die return air temperature T r decreases
- F r decreases
- T r - T c decreases
- die force imbalance on die valve element 22 moves die valve element downwardly toward die second end 88 of die valve body 82 to align more groove flow passage cross-sectional area widi die inlet port 90, diereby allowing a greater flow rate of refrigerant into die evaporator coil 20.
- Equation 10 makes clear diat die valve element 98 is moved to increase die flow passage area for fluid dirough die valve 22 if die difference between die coil outlet temperature and die temperature of refrigerant in die coil 20 increases or die difference between die return air temperature and die temperature widiin die coil decreases, and die valve element moves to decrease die flow passage area dirough die valve if die difference between die coil outlet temperature and die temperature widiin die coil decreases or die difference between die return air temperature and die temperature widiin die coil increases.
- valve element 98 diat are of different size areas results in die production of ratiometric forces controlling, at least in part, die configuration of die valve 22. and enables die valve to have a single, self-adjusting set point for control of die flow of refrigerant dirough die valve to die evaporator coil 20.
- forces due to selected temperatures and to the evaporator coil pressure are generated to configure die valve in die same ratio as die ratio of die bellows' ends, as may be appreciated by reference to Equations (7) and (10), for example.
- Fig. 3 shows die response curve of die self-adjusting expansion valve 22 of Fig. 2.
- the opening of die valve orifice, diat is, die total cross-sectional area of die grooves 100 aligned with die inlet port 90, taken as a percentage of die maximum possible opening, or 100%, diat is, die alignment of die maximum cross-sectional area of die grooves widi die inlet port diat is possible, is plotted along die ordinate as a function of die temperature difference T, between the coil outlet temperature T co and die coil temperature T c , plotted along die abscissa.
- T- dirough which die valve 22 will self-adjust to different percentages of die maximum opening of die valve orifice is between die values A and B of T- as indicated in Fig. 3.
- die force F, of die spring 110 acting on die valve element 98 is large enough compared to the force acting in opposition to die spring force diat die valve orifice is maintained closed and no refrigerant flows dirough die valve.
- the inlet port 90 begins to open at die point A where T, is equal to RC ⁇ ), and continues to open in linear relation to T, as indicated by the line C.
- equal to the value B die valve element is positioned so mat die valve orifice is open 100%, and for all values of T- greater dian die value B die valve orifice stays completely open for maximum refrigerant flow rate to die evaporator coil.
- the value of T, equal to B is less dian die value of T r as die graph of Fig. 3 illustrates.
- the slope of die line C depends on die spring constant.
- the values of A and B at which die valve orifice is fully closed and fully open, respectively, may be altered by changing die geometry of die valve.
- the length of die valve element 98, for example, and die position of die groove passages 100 along die length of die valve element determine how far die valve element must move to open or close die orifice. Varying die pattern of die groove passages, by changing die number of grooves, dieir positions along die valve element, and dieir cross-sectional areas, for example, can vary die shape of die line C from a straight line as shown to a selected curve.
- a significant advantage of die valve according to die present invention is diat die range of operation of die valve in which die valve orifice opening is variable, such as die range of values of Ti from A to B as illustrated in Fig. 3, is selectable by selection of die relative sizes of the bellows surface areas. A) and A 2 .
- die coil outlet temperature T co is always higher dian die coil temperature T c and lower than die return air temperature T r .
- die valve orifice opening adjusts according to Equation 10 in response to changes in T r , T co and die pressure in die coil, which is related to T c .
- diat T c is a measure of die temperature of die refrigerant entering die evaporator coil 20
- T r is a measure of die amount of cooling of die load being provided by die refrigeration system 10.
- a further advantage of die above-described expansion valve is diat die valve is integral, or self-contained, and self-adjusts without external electrical control signals, for example. Additionally, existing refrigeration systems can easily be modified to incorporate die present invention.
- die invention is illustrative and explanatory thereof, and various changes in die mediod steps as well as die details of die apparatus may be made widiin die scope of die appended claims widiout departing from die spirit of die invention.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US1994/010255 WO1996006316A1 (en) | 1994-08-25 | 1994-08-25 | Self-adjusting superheat valve |
AU79549/94A AU7954994A (en) | 1994-08-25 | 1994-08-25 | Self-adjusting superheat valve |
EP94932173A EP0777843A4 (en) | 1994-08-25 | 1994-08-25 | Self-adjusting superheat valve |
CA002197572A CA2197572A1 (en) | 1994-08-25 | 1994-08-25 | Self-adjusting superheat valve |
US08/818,704 US6105379A (en) | 1994-08-25 | 1997-03-14 | Self-adjusting valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US1994/010255 WO1996006316A1 (en) | 1994-08-25 | 1994-08-25 | Self-adjusting superheat valve |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US08/818,704 Continuation-In-Part US6105379A (en) | 1994-08-25 | 1997-03-14 | Self-adjusting valve |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996006316A1 true WO1996006316A1 (en) | 1996-02-29 |
Family
ID=22242962
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1994/010255 WO1996006316A1 (en) | 1994-08-25 | 1994-08-25 | Self-adjusting superheat valve |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0777843A4 (en) |
AU (1) | AU7954994A (en) |
CA (1) | CA2197572A1 (en) |
WO (1) | WO1996006316A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1152195A1 (en) * | 2000-05-04 | 2001-11-07 | Linde Aktiengesellschaft | Method for operating a (compound) refrigeration system |
KR100553965B1 (en) * | 1996-12-11 | 2006-05-16 | 하.크란츠-테케테 게엠베하 | Drive unit |
WO2008080436A1 (en) * | 2007-01-04 | 2008-07-10 | Carrier Corporation | Superheat control for refrigeration circuit |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2363010A (en) * | 1941-04-29 | 1944-11-21 | Gen Controls Co | Refrigerant control system |
US2579034A (en) * | 1945-06-08 | 1951-12-18 | Alco Valve Co | Multiple response override for thermal valves |
US2856759A (en) * | 1955-09-26 | 1958-10-21 | Gen Motors Corp | Refrigerating evaporative apparatus |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2242334A (en) * | 1938-03-30 | 1941-05-20 | Detroit Lubricator Co | Refrigerating system |
US2538861A (en) * | 1947-10-01 | 1951-01-23 | Detroit Lubricator Co | Refrigeration expansion valve |
GB687011A (en) * | 1950-06-08 | 1953-02-04 | Gustav Sperling | Thermostatically-operated fluid flow control devices |
US3803864A (en) * | 1972-07-07 | 1974-04-16 | Borg Warner | Air conditioning control system |
-
1994
- 1994-08-25 WO PCT/US1994/010255 patent/WO1996006316A1/en not_active Application Discontinuation
- 1994-08-25 CA CA002197572A patent/CA2197572A1/en not_active Abandoned
- 1994-08-25 AU AU79549/94A patent/AU7954994A/en not_active Abandoned
- 1994-08-25 EP EP94932173A patent/EP0777843A4/en not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2363010A (en) * | 1941-04-29 | 1944-11-21 | Gen Controls Co | Refrigerant control system |
US2579034A (en) * | 1945-06-08 | 1951-12-18 | Alco Valve Co | Multiple response override for thermal valves |
US2856759A (en) * | 1955-09-26 | 1958-10-21 | Gen Motors Corp | Refrigerating evaporative apparatus |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100553965B1 (en) * | 1996-12-11 | 2006-05-16 | 하.크란츠-테케테 게엠베하 | Drive unit |
EP1152195A1 (en) * | 2000-05-04 | 2001-11-07 | Linde Aktiengesellschaft | Method for operating a (compound) refrigeration system |
WO2008080436A1 (en) * | 2007-01-04 | 2008-07-10 | Carrier Corporation | Superheat control for refrigeration circuit |
Also Published As
Publication number | Publication date |
---|---|
EP0777843A1 (en) | 1997-06-11 |
EP0777843A4 (en) | 1999-03-31 |
CA2197572A1 (en) | 1996-02-29 |
AU7954994A (en) | 1996-03-14 |
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