|Publication number||US3691783 A|
|Publication date||Sep 19, 1972|
|Filing date||Sep 25, 1970|
|Priority date||Sep 25, 1970|
|Publication number||US 3691783 A, US 3691783A, US-A-3691783, US3691783 A, US3691783A|
|Inventors||Robert H Proctor|
|Original Assignee||American Standard Inc|
|Export Citation||BiBTeX, EndNote, RefMan|
|Referenced by (13), Classifications (14)|
|External Links: USPTO, USPTO Assignment, Espacenet|
United States Patent Proctor  REFRIGERANT EVAPORATOR TEMPERATURE CONTROL  Inventor: Robert H. Proctor, Dearbom, Mich.
 Assignee: American Standard Inc., New York,
 Filed: Sept. 25, 1970  Appl. No.: 75,713
Related U.S. Application Data  Continuation of Ser. No. 795,828, Feb. 3,
 U.S. Cl. ..62/212, 62/217, 62/225  Int. Cl ..F25b 41/00  Field of Search ..62/204212,'217, 62/225  4 References Cited UNITED STATES PATENTS 2,116,801 5/1938 Shivers .....62/217 3,316,731 5/1967 Quick ..62/217 3,314,248 4/1967 Baker ..62/217 3,365,905 1/1968 Barbier ..62/217 COP/PRESS 0R ca/vomsER l4 RECEIVER [4 1 Sept. 19, 1972 1,990,663 2/1935 Muffly ..62/217 3,296,816 l/l967 Weibel ..62/217 3,314,248 4/1967 Baker ..62/217 3,388,864 6/1968 Noakes ..62/225 Primary Examiner-Meyer Perlin Attorney-John E. McRae, Tennes I. Erstad and Robert G. Crooks [5 7] ABSTRACT An automotive air conditioner system having a temperature-responsive power means in the refrigerant suction line for throttling refrigerant flow from the evaporator when the evaporator temperature drops toward a value low enough to cause ice formations on the evaporator fin surfaces; the power means is preferably located upstream from the actuator means of a thermostatic expansion valve so that the throttling action reduces the pressure at the actuator means and causes the actuator means to respond to relatively high superheat, thereby requiring the expansion valve to flood the evaporator in a manner to temporarily raise the pressure and temperature within the evaporator for de-icer action.
10 Claims, 3 Drawing Figures fV/PPORA ran REFRIGERANT EVAPORATOR TEMPERATURE CONTROL This application is a continuation of U.S. Application Ser. No. 795,828, Refrigerant Evaporator Temperature Control, filed Feb. 3, 1969 and now abandoned.
THE DRAWINGS FIG. 1, partly schematic, shows one form in which the invention can be practiced.
FIG. 2 is a chart showing temperature-pressure conditions in a system using the FIG. 1 apparatus.
FIG. 3 is a temperature-motion diagram for a thermostatic power means usable in the FIG. 1 apparatus.
THE DRAWINGS IN DETAIL There is shown an automotive air conditioner system comprising a refrigerant compressor driven from the engine by a clutch (not shown), a refrigerant condenser 12, receiver 14, expansion valve. 18-and evaporator 16. Valve 18 comprises aported body 20 permanently assembled into the refrigerant system, and a removable valve cartridge 22 having a thermostatic actuator means 24.
Actuator means 24 includes a sleeve 26 permanently affixed to the cartridge, as by the staking at 28, a lower cap 29, a metallic diaphragm 30, and an upper cap 32, the various members being welded together by a continuous peripheral weld 34. The space between diaphragm 30 and cap 32 is occupied by a thermally expansible material 36, for example the same material used in the refrigerant system. Thermal insulation is provided at 37 to insulate the charge from the ambient temperature.
SUPERHEAT CONTROL During operation of the system the refrigerant issues from the evaporator outlet in gaseous form at a superheat determined by the adjustment of a spring 38 within the expansion valve. The superheat control occurs as a result of the opposing forces produced by thermal expansion of the charge 36 and spring 38, plus the pressure in chamber 42 acting on the diaphragm 30. Relatively high temperature gas in suction line 40 flows through chamber 42 in valve 18 and heats or cools the pad 44 carried by diaphragm 30, thereby causing thermal charge 36 to produce a proportionate downward force on the valve stem 46. Spring 38 develops an opposing upward force on the nut 47 and the stem 46, so that any movement of the metering valve element 48 is a function of the suction line temperature, all as conventional in the art. Variation in superheat setting can be achieved by turning nut 47 on the stem.
SUCTION LINE THROTTLING AT 74 The present invention most particularly concerns a throttling mechanism 50 located in the suction line upstream from chamber 42. As shown, the mechanism includes a housing 52 screwed into valve body 20, and operatively mounting a valve seat 54. Located on the downstream side of seat 54 is a temperature-responsive power means 56 comprising a container 58, piston 60, and a pellet-like mass of temperature-sensitive material 62. Container 58 includes a cup-like element 64 and sleeve-like cover 66 suitably connected together for retention of an elastomeric diaphragm 68 and plug 70 in sealing relation to the pellet material 62. In operation, temperature increase of the vapor surrounding cup 64 causes the pellet 62 to transform from the solid state to the liquid state, thereby expanding to produce pressures on the diaphragm 68 sufficient to move plug 70 bodily outwardlyrelative to sleeve 66. Sleeve 66 is arranged as a slide fit on a piston 60 which is suitably anchored on a spider 72 carried by housing 52. Therefore the net effect of pellet 62 expansion is to produce a leftward movement of container 58 and the poppet valve element 74 carried thereby. Temperature decrease in the vapor surrounding cup 64 produces pellet 62 contraction, which allows the compression spring 75 to return the container 58 and poppet element 74 toward its illustrated position.
' PELLET EXPANSION Pellet 62 preferably includes a mass of wax which undergoes solid-liquid transition in a temperature range near or spanning 32 F, as for example completely solid at 28 F and completely liquid at 39 F. Suitable waxes are commercially available for solid-liquid expansion in the desired range; such waxes are mixtures of different hydrocarbons which produce the effective transition in wider or narrower temperature ranges according to composition of the pellet as determined by the initial fractionating and compounding, all according to known practice in the art. FIG. 3 illustrates the temperature-motion curve of a thermostatic power means useful in practice of the invention. 1
Pressures produced by pellet 62 expansion can be comparatively high, as for example over 2,000 p.s.i., if the expansion process is resisted, as by holding the piston and container in their start positions. In the actual installation the pellet pressures may reach fairly high values since the piston and container are restrained by the spring 75 and the radial friction loads between plug 70 and sleeve 66, plus the pressure difference across the valve due to the throttling action at 74. The capability of the pellet for producing relatively high forces is important in that it allows the temperature-responsive power means to move only as a function of the suction line temperature without in any way being influenced by variations in suction line pressure. Suction line pressures are usually relatively low, on the order of 50 psi. or less.
SYSTEM OPERATION During operation of the illustrated system the throttling element 74 will exert no throttling effect as long as the suction line temperature is above 39 F; element 74 is then spaced leftwardly away from seat 54. Should the temperature drop below 39 F element 74 will exert a progressively greater throttling effect according to how much the temperature drops; at 28 F the element will close against seat 54, thereby completely interrupting refrigerant flow from the evaporator to the compressor.
Compressor 10 is usually running on a continuous basis as long as the vehicle engine is running and the occupant has turned the air conditioner switch to the on position. On a continuous run basis for the compressor, the actual temperature in the passenger space will be controlled by dampers and/or variable speed fans operating on the airstream flowing across the evaporator. Assuming sufficient demand for air cooling, the evaporator will be at a high enough temperature to prevent any icing on its fin surfaces. However during low demand periods less refrigerant will be evaporated in the evaporator, and the continuously-running compressor will tend to reduce the pressure and temperature in the suction line and evaporator, all in accordance with curve 76 of FIG. 2.
If mechanism 50 were not in the system the evaporator temperature could well drop below 32 F; ice might then form on the tin surfaces. However in actual practice ice at 32 F is rather slushy or only temporarily on the fin surfaces due to air heating effects or air'movement efiects. Usually the fin temperature must get down to about 28 F before permanent ice formations occur; 28 F is therefore chosen as the temperature at which throttling mechanism 50 fully interrupts flow of refrigerant from the evaporator to the compressor.-
In operation of the system with. mechanism 50 installed therein, the system functions in the normal manner at evaporator temperatures above 39 F. However should the air-cooling demand be soreduced as to permit the compressor to lower the evaporator pressure below about 27 p.'s.i.g. thecorresponding drop in suction line temperature will cause material 62 to partially solidify so as to produce a throttling movement of poppet element 74 toward seat 54. The throttling action will cause two things to happen, as follows: (I) the pressure in the evaporator will be higher than if no throttling had taken place, and (2) the superheat in chamber 42 will be somewhat higher than otherwise.
LOCATION OF THROTTLING DEVICE It is preferred that throttling mechanism 50 be located on the upstream side of chamber 42 to wholly or'partially isolate the thermal charge 36 from the evaporator temperatures during the throttling periods. This isolation effect is advantageous in that charge 36 assumes an artificially high superheat for more fully opening the metering element 48. The action tends to produce a flooding action in the evaporator, both because element 48 is feeding the evaporator with liquid and because element 74 is restricting the escape of vapor from the evaporator. Such flooding tendency raises the evaporator pressure and evaporator temperature, thus producing a de-icing and/or icer-prevent action on the evaporator surfaces, the temperature-pressure relationship following generally along line 78 in FIG. 2.
It will be understood that the operation is a modulating action wherein throttling and pressure-temperature changes may be gradual without full throttling or full opening of element 74. Also, the described temperatures of 28 F full-closed and 39 F full-open are somewhat arbitrary; useful results may be achieved using different temperature'ranges. In general however it is preferred to choose temperatures which are just above the evaporator fin icing level; this lets the evaporator have more cooling capacity with a given surface area, thereby permitting a smaller evaporator for a given duty.
FORCE REQUIREMENT It is of some importance that power means 56 be insensitive to pressure variations in the suction line, and
. throttling on expansion of the charge.
that power means 56 have sufficient force capability to open and close the throttling element 74 independent of the pressure drop across seat 54. if a low force power means such as a bimetal or liquid-charged bellows were used in lieu of power means 56 the pressure drop across the valve seat would tend to increase the throttling effect to an undesirable extent, sufiicient to prevent normal operation of the system. Therefore the thermostatic power means must be pressure-insensitive for proper results.
The drawings show power means 56 as a waxcharged element wherein temperature decrease produces contraction of pellet 62. It is contemplated that the charge could be water instead of wax, in which case a temperature decrease to a value below approximately 32 F would produce a change of state from liquid (water) to solid (ice) with an accompanying expansion of the charge. The relationship between the valve element and seat would be such as to produce I claim:
1. In a refrigerant system which includes a continuously running refrigerant compressor, condenser, evaporator, refrigerant metering means between the condenser and evaporator, and a suction line between the evaporator and compressor: the improvement comprising a'throttling means in the suction line, and temperature-responsive power means having a movable output member for operating said throttling means in accordance with variations in suction line temperature; said power means being constructed so that its output member moves solely as a function of the suction line temperature without being influenced by section line pressure; said power means comprising a contained mass of temperature-sensitive material which undergoes transformation between the solid and liquid states in a temperature range in the vicinity of 32 F, whereby the output member enjoys movement in such a temperature range; said power means and throttling means being connected so that the throttling means increases its throttling action as the temperature drops within said range, and so that the throttling means reduces its throttling action as the temperature rises within said range.
2. The system of claim 1 wherein the power means comprises a movable container for the mass of temperature-sensitive material, and a fixed piston slidably projecting into the container, whereby expansion of the material causes movement of the container; the aforementioned throttling means comprising a flow-throttling element carried by the container.
3. The system of claim 2 wherein the flow-throttling element is carried by a portion of the container located upstream from the temperature-sensitive material, whereby the suction line fluid washes the sensitive material after movement past the throttling element.
4. The system of claim 1 wherein the refrigerant metering means comprises a thermostatic expansion valve having a temperature-responsive actuator means controlled by suction line temperature; the aforementioned temperature-responsive power means being located upstream from the actuator means, whereby movement of the throttling means toward a no-flow respond to asyntheti c superheat.
5. The system of claim 4 wherein the thermostatic expansion valve comprises a valve body having a chamber therein which constitutes part of the suction line, said actuator means being located in thermal engagement with said chamber; the aforementioned power means-throttling means assembly being constructed as an insert device attached directly to the expansion valve body immediately upstream from the aforementioned chamber.
6. A closed refrigerant system wherein a thermostatic expansion valve controls the flow rate of liquid refrigerant entering the evaporator in response to the superheat of the refrigerant gas leaving the evaporator, including a throttling valve which is responsively controlled by a decrease in the temperature alone of the refrigerant in the suction line to throttle the flow of refrigerant leaving said evaporator so that the refrigerant in said evaporator is prevented from falling below a predetermined temperature which could allow the formation of ice in said evaporator.
7. A closed refrigerant system wherein a thermostatic expansion valve controls the flow rate of liquid refrigerant entering the evaporator in response to the superheat of the refrigerant gas leaving the evaporator, including a throttling valve having a temperature responsive power means and a mechanical valve means disposed internally of the suction line leading from the evaporator, which is responsively controlled by a decrease in temperature alone of the refrigerant in the suction line to throttle the flow of refrigerant leaving said evaporator so that the refrigerant in said evaporator is prevented from falling below a predetermined temperature which could allow the formation of ice in said evaporator.
8. The closed refrigerant system as defined in claim 7, wherein said temperature responsive power means includes a thermal sensitive material and at least one relatively movable element.
9. The closed refrigerant system as defined in claim 8, wherein said thermal sensitive material is a mass of substance which undergoes a transition when the-suction line temperature decreases thereby causing movement of said movable element.
10. A closed refrigerant system wherein a thermostatic expansion valve controls the flow rate of liquid refrigerant entering the evaporator in response to the superheat of the refrigerant gas leaving the evaporator, including a throttling valve which is responsively controlled by a decrease in temperature alone of the refrigerant in the suction line to throttle the flow of refrigerant leaving said evaporator so that the refrigerant in said evaporator is prevented from falling below a predetermined temperature which could allow the formation of ice in said evaporator, said thermostatic expansion valve and said throttling valve being formed as a single unit.
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|US3810366 *||Jul 31, 1972||May 14, 1974||Controls Co Of America||Refrigeration valve|
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|US3822563 *||Apr 25, 1973||Jul 9, 1974||Controls Co Of America||Refrigeration system incorporating temperature responsive wax element valve controlling evaporator outlet temperature|
|US3886761 *||Mar 3, 1971||Jun 3, 1975||Chrysler Corp||Thermostatically operated suction throttling valve|
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|US20040129008 *||Oct 17, 2003||Jul 8, 2004||Dianetti Eugene A.||Refrigeration expansion valve with thermal mass power element|
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|U.S. Classification||62/212, 62/217, 62/225|
|International Classification||F16K17/38, F25B41/04, F25B41/06|
|Cooperative Classification||F16K17/38, F25B2341/0683, F25B41/043, F25B41/062, F25B2600/21|
|European Classification||F25B41/06B, F25B41/04B, F16K17/38|