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Publication numberUS2337862 A
Publication typeGrant
Publication dateDec 28, 1943
Filing dateJan 9, 1942
Priority dateJan 9, 1942
Publication numberUS 2337862 A, US 2337862A, US-A-2337862, US2337862 A, US2337862A
InventorsAlvin H Baer
Original AssigneeAlvin H Baer
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Liquid pressure reducing means
US 2337862 A
Abstract  available in
Previous page
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Claims  available in
Description  (OCR text may contain errors)

Dec. 28, 1943. A, H, BAER 2,337,862

. LIQUID PRESSURE REDUGING MEANS v Filed Jan. 9. 1942 limited to such use.

Painid Dasr 2s, 1943 UNITED STATES PATENT OFFICEl I 2,337,862 LIQUID PRESSURE REDUCING MEANS l Alvin 11pm, sonni orange, N. J.l Application January 9, 1942, serial No. 426,211

' 15 claims. (cm2-s) My invention relates to liquid pressure reducing means particularly intended for use in refrigerating apparatus of the compressor-condenser-evaporator type, i. e.; in refrigerating' apparatus wherein pressure is reduced for the purpose of decreasing the temperature of a volatile refrigerating uid, though not necessarily One of the known expedientsfor that purpose consists of a so-called capillary tube, which is a tube of small diameter through which refrigerant flows under pressure and wherein the pressure is reduced due to the resistance offered by the small tube, so that the pressure is much less at the outlet than at the inlet, the amount of pressure reduction varying with the length of the tube and the entering pressure, while the quantity of fluid passing through the-tube is dependent on the diameter of the tube and the ratio of the inlet and outlet pressures. A device of this kind is illustrated in Patent No.' 1,919,500 lto Carpenter.

It is now well known that a restricted tube alone, such as the capillary tube illustrated in this patent, will be limited in its application to the particular refrigerating machine and the particular condensing pressure and evaporator pressure for which it is designed. If applied tc a machine or system workingwith other pressures, its capacity will not suit that machine and system. Obviously, such a tube will pass a greater amount of liquid refrigerant when the ratio of the condenser pressure to the evaporator pressure is greater and a lesser amount when pressure ratios are less. v

Now,the cooling capacity of a refrigerating machine becomes less as the ratio of the condenser pressure to the evaporator pressure becomes greater. Therefore, in practice, the capacity of a plain capilllary tube will increase during a period when the operating pressures causes a decrease in the capacity of the refrigerating machine. There is, therefore, direct opposition, with respect to capacity changes, between the capillary tube and the refrigerating machine for which it is designed when that ma- -chine and system happens to be applied to cooling at a difference in pressures other than that for which the tube is made. What is more important, this same opposing situation exists when seasonal and weather changes create changing condensing pressures for the refrigeratng machine.

Thus it becomesapparent that any refrigerating machine and system for which liquid refrigerant is supplied and controlled by means of the so-called capillary tube, will require a different design of tube for every combination' of pressures in the condenser and evaporatorthe length of the tube would have to be greater for each increase in condenser pressure or each decrease in evaporator pressure and vice versa the tube would have to be shorter when the pressures change in the oppositedirections.` Thus a multitude of tube designs `are required for 'each size of refrigerating machine if that/machine .is to operate according to the efficiency conditions for which it was designed.

In addition, if a multitude of interchangeable tube units are to be used in order that the machine may operate at its full eiioiency for each set of pressures, it will, of course, be necessary for one tube unit to be removed, and another substituted for it, 'each time the pressure ratios change a substantial amount.A This, of course, is expensive and troublesome andpit is also so inconvenient, in many cases, as to be almost impossible. Therefore the refrigerating machine,

working with'such capillary tube units, will in very many cases operateunder a greater or less degree of impaired eliciency and capacity.

My invention provides a device that is able to utilize the advantages of the plain capillary tube-including the equalizing of pressures when the refrigerating compressor is idle-with a compensating means and adjusting means that controls the ow of liquid in such manner as to promote a substantially uniform pressure and temperature in the evaporator, regardless of the variations of weather and condensing pressures, and the resulting change of pressure ratios from hour to hour, or day to day. ff l I also provide a device that may automatically regulate the flow of liquid refrigerant between relatively wide maximum and minimum capacity limits in the refrigerating plant and system, regardless of weather changes and varying condenser pressures. Thus a give refrigerating machine and system may accommodate itself automatically to capacity changes as they occur.

Again, it is Well known that the same refriger,

ating machine andv system will in one case include an evaporator that is to function under lower pressures and temperatures, while in another case, or numerous other cases, the evaporator is, to function under other pressures and temperatures. In either case the evaporator must operate at substantially uniform pressures and temperatures. My invention provides a means for accomplishing this.

Also, it is well known that many refrigerating Vmachinesare constructed with means designed controls.

and builtinto their structures for changing capacity automatically from hour to'hour. or day to day. VSuch variations of capacity frequently change one hundred per cent, that is, a given refrigerating compressormay at one moment operate at a rate of five tons capacity and at anvothermoment ata rate of ten tons capacity.

In such case the liquid refrigerant feed must also automatically adjust itself to the change. An example of this kind is found in many air conditioning plants. 1 ,I y

My invention, together with the capillary tube,

may operate to suit such changes in capacity bymaintaining a given pressure and temperature within the evaporator and varying itself automatically to changes in Ythe refrigerating machine, whether they be up or down. Itis alsoI adaptable ,for refrigerating systems of different characters, particularly systems of a commercial character and those that are of larger size than the standardized units, cabinets, etc., such as household refrigerators, ice cream cabinets, wa. f

yter coolers, and so on.

It is also very desirable thatliquid feed devices of Athis class be capable of additional manual ad- Y justment in` order that they may be changed to operate with entirely different refrigerating machines and systems, or with` different classes of refrigerant liquids, so that they may be used with one refrigerating system for a time, and then may 4be removed and applied to another system., Thus,

' the reconditioning of equipment andinstallationl of new machines, orchanges to the system, need not result in therejection of perfectly goodfeed v AMy invention includes fixed adjustment that v Vfor attaching tube I1 to the controlunit, and 23 enables the self-acting elements used withit to be changed to suit different operating pressure ratios, that isgtheir-maximuxn and minimum limits are changed, and the scope of capacity changes that may be accomplishedwith it is thus enlarged.

Itis also very desirable for devices of this class to be of such type that the customary refrigerating plant sizes with which they may be used can be served with the fewest possible unit sizes. Thus the manufacture of the units can be ac`- cornplished in quantity order's with resulting lower manufacturing costs that accompany such.

ing control devices: and a further tubeor tubes may also have non-self-acting control, or a simi lar self-acting control with the other tube.

Referring to the drawing which is made a part of this application and-in which similar reference' characters indicate similar parts:

Fig. 1 is an elevation, partly diagrammatic, illustrating the method of embodying my invention in a refrigerating system,

Fig. `2, a longitudinal vertical section of one .form of my invention, and

Fig. 3, a similar view of a modified form of the invention.

In the drawing, Figure 1 'illustrates in diagrammatic form a compressor-condenser-evap- `oratortype of refrigerating system in which I0 is the refrigerant gas compressor, is a motor for driving the compressor, I2 is the refrigerant condenser, |3 is aliquid receiver sometimes used, I4 is my control unit, and I5 is a commonly used form of evaporator for cooling. .All of these units, excepting i4, may be of any wel1known `type and they are connected by suitable pipes I3,

the evaporator being shown as located in a refrigerator, though my invention may be used in connection with various types of cooling machinery.

In Figure 2, I1 is the common liquid inlet pipe which may be 'a part of the uppermost pipe I6, and |8.and I9 are each parallel tubes of restricted size, often referred to as capillary tubes, by means of which the pressure of the liquid flow is very' much reduced'. Numeral 20 indicates acommon outlet pipe leading to the evaporator. Parts 2| and 22 constitute ahead and clamping fitting is a sleeve for enclosing a. liquid screen 24 that is held in place bya flange clamped between parts 2| and 23, said sleeve 23 also having threaded thereon a casing head 25. Any of the wellknown liquid screens'may be used and this screen does not constitute a partof my invention.

A-casing 26 connects the head 25 to another 'casing' head 21 at the outlet end of tubes I8 and I9. Said casing encloses the tubes |8 and I3 and it may be used as theouter part of aheat exchanger if it is provided with an inlet and outlet at opposite ends for'passing return gas from the evaporator to the compressor, but I prefer to production. In'addition/such a feature reducesv f may be in any other convenientr form. I do, however, use two or more tubesworking inparallel, with at least one tube freeof any separate control or restraint, and another tube or tubes provided withadditional control devices, so that there may be one or more lsimple capillary tubes feeding liquid uniformly, and one or moreother tubes that are under restraint, and therefore feed irregularly.

I do not require more than two tubes for the average control unit, but there may be more than ltwo tubes required for some units. In such cases .one or more vtubes will be free of restraint; one or more other tubes may have adjustable self-act- -use it as a protective enclosure for the tube. It

may have flexible insulating filling around the tubes, or it may also be perforated when placed in a refrigerated space.

Theoutlet casing head 21 at the outlet end of casing 26 comprises'a clamping nut 28 and a gland23 for attaching the outlet pipe 20 tothe head 21. A valve sleeve 30 is threaded at its' upper y,end in a recess in the head 21 and a valve I 33 serving to vary.the

3| is normallyl seatedin'the lower end ofY said sleeve. A conduit 32 leads from tube I8 through orifices in the sleeve 30 and past the reduced stem of valve 3| and so to outlet pipe 20. A plug 33 is threaded in the upper end of the valve sleeve 3| said plug serving to close the sleevf and also serving as a stop for a spring 34 bearing on the head of valve 3|, adjustment of plug pressure of the spring on the valve. IA cap 35 is screwed into the top of the valve recess in the head 21 and must be removed before the plug,r` can be adjusted. Gas- 4kets 36, 31, and 38 of any suitable type are provided between opposed faces of the head, the sleeve, and the ca'p.

A conduit 33 leads from pipe I9 to a chamber 40 in head 21, connected to the open .lower end l of course, the pressure to' oset the spring pressure (say from V4 to the top limit permitted assassin of valve sleeve 30, said chamber being closed at its outer end by a plug 4 I.

In the modified form of Fig. 3, the parts I8', I3', 20', 23', and 25' to 4I' are or may be identical with parts I9, 20, 23, and 25 to 4I of Fig. 2. This form of the invention includes also a third restricted tube 42 leading from sleeve 23' to head 2' where it connects with a conduit 43. This conduit leads into the open end of an auxiliary valve sleeve 44, mounted in a horizontal recess in the head 21' and provided with a valve 45 held in closed position by a spring 4S that is adjustable by a plug 41 and is covered by a cap 41', all parts being generally similar to those of the main valve structure, but the valve sleeve having a side opening leading to a conduit 48 that connects at its upper end to passage 32.

Preferably, I select units of the kind illustrated by Figure 2 for most of the refrigerating systems that operate under average conditions. However, there are numerous conditions that are y handled more satisfactorily by a unit builtvaccoi-ding to Figure 3. Also, for certain future needs I will use tubes of differing sizes, i. e., tube I8' or 42 or both of them may be larger or smaller than tube I8 and, where it appears desirable, I will use any one of the tubes, or all of them, in multiple, i. e., two tubes 42 instead of one. and so on.

' In operation of my device the liquid supply from condenser I2 flows into` all capillary tubes alike, having first passed through screen 24. By reason of their very small size, the tubes cause a great deal of pressure loss which is the desired result. Therefore, the volatile refrigerant liquid fiows from the opposite end of all tubes at muchlower pressure and at a correspondingly lower temperature. The diameter of the tubes is such as to pass a stream of liquid of predetermined cross section at the entrance end. The

due to weather and condensing pressure changes and in other cases to actual mechanical devices on the refrigerating machine that change its capacity while operating. The changes due to the former causes will generally be between minimum and maximum limits not too far apart, while those due to the latter causes will sometimes have moderate limits and at other times will have minimum and maximum limits widely separated.

For the former cases I generally use devices in which all tubes are ofthe same diameter and length and'thus provide devices that may vary in capacity as much as 100%, i. e., tube I8 alone could have a capacity equaling two tons refrigeration and both tubes I8 and I9 would then have a capacity equaling four tons refrigeration, when working together. In this case the device could adjust itself to load changes o f that scope.

For other cases where the load changes vary between wider limits I generally use a device in which'tube I8 will be of smaller size while the length is made such as to create a given pressure reduction with a given entering pressure.

Tube I8 will have a constant flow whenever the refrigerating compressor Ill is operating and taking the vapor away from the evaporator I5. If tube I8 is designed to pass less than the quantity of liquid required for the refrigerating compressor then soon be reduced. 'Up to. this time tube I9 has remained closed 'at its outlet end because of the spring pressure on the valve 3|.

However, when the evaporator pressure and, in pipe 20, conduit 32 and I is reduced just enough to 1 pound per square inch) the valve will lift and in the space over valve 3 liquid will thenow from tube I9 to v:loin that flowing from tube I8. This will very soon become an over-supply and raise the evaporator pressure and will unbalanc the pressure ove'r valve 3|/ so that the springl pressure will close this valve. Then tube I8 again' becomes the' sole supply for the evaporator. This procedurewill be repeated as frequently as the evaporator and refrigerating compressor require it.

In practice many refrigerating systems (compresser, condenser; evaporator and associated parts through which refrigerant flows) have to meet varyingcapacity conditions. Andthis requires that thel liquid feed, o r control, shall yhave a varying capacity, also that it must meet such variations frequently-sometimes every hour.

In some cases the load variations'will be those v3%, tons.

other tube or tubes will be of larger size or in lieu of this there will be two of the tubes I9 functioning together at one such tube. Thus, if

tube I8 was of a capacity for 2 tons refrigeration the larger tube I9 or the pair of smaller tubes having the function of tube I9 could have a capacity of 4 tons and the total capacity of bothwould then be 6 tons.

If-adevice be made wherein tube I8 equals 2 tons and tube I9 equal 2 tons, I will preferably apply the device to a refrigerating machine in which the capacity may vary from 21A tons to The condenser pressure changes due to weather and seasons will `hardly ever reach such wide limits. They will generally be confined to 25 per cent variation. Itherefore have ample margin.

In like manner, if tube I8 equal 2 tons refrigeration and tube I9 equals 4 tons I will preferably apply the device to a refrigerating machine use it with one size refrigerating machine having moderate capacity limits from 2%, tons to 3 tons l or. with another size having moderate limits from the pressure in the evaporator will,l v

3 to 35A tons or another size' having moderate limits from 4' tons to 5 'tons or thereabouts.

I preferably use wider capacity limits when designing my devices so as to broaden the operating scope of each device and thus reduce the number of devices that are needed to satisfy the require-1 ments of the usual line of refrigerating machine sizes. This leads to the use of three tubes for some devices sucha's tubes I8', I9', and 42, shown in Figure 3. In this 'case tube 42 may be opened to operate jointly with tube I9' or it may remain closed and be inoperative. This is to provide for wider scope of operation and'also for the transfer of the same device from one machine 'to another having somewhat different capacity and other characteristics.

While a device having a given length of tube will have a given pressure drop when the entering liquid pressure from the condenser is at a. given pressure I am able to apply my device to machines having several evaporator pressures and yet retain the self-adjusting ability for meeting ordinary variations of condenser pressure due, to weather and seasonal changes. One method of accomplishing this result is by tightening the screw plug 33 over the spring 34 so that greater pressure is exerted against valve 3|/ Thus, for example, if one of my devices' is to a im operated in central er an evaporator in which the pressure is pounds per square inch less than the pressure under which it has been operating, the spring may be set down so that it holds' the valve closed until such lower evaporator pressure has been reached under the limited supply from tube Ilv after which tube it opens.- But it will remain open only until the evaporator pressure has increased a small amount andV it then closes. Thus it functions in open and closed Having thus fully described my invention, what I claim is:

1. In a mechanical refrigerator, the combination of a compressor. a condenser, and an evaporatonpipe connections between them in the or- A der specified. the pipe connections between the positions at the lower pressure levelsiust as it did at the higher levels.

The same method maybe Aused when a unit is to be transferred from one evaporator to another. Of course, for any of these cases it is also possible to apply a unit having tubes of smaller diameter, thus offsetting to some extent the effect of the greater vpressure ratio to push more liquid through the unrestrainedtube I8. However, I prefer to use a unit having longer tubes when there is a substantiallylarge change of pressure ratio. .y

In order to further spread the `scope of pressure limits within which my device is able to function and exert its control, I will, for some cases, use an addltional'valvelikevalve 45 (Fig. 3) and its related parts, for controlling the outlet this additional valve will be independent of valve 3| and will send its supply directly to `passage 32' and pipe 20. In that ,case tube I8 will feed without restraint, just as in any other case, and

kend of tube 42. In such acase the outlet from ifk the inlet pressure is higher or the outlet pressureis lower, or if any combination oi' these creates a greater pressure ratior thanthe unit has been handling there will be some increase vof liquid flow through it.

When such conditions are to be met I select a unit in which thecapacity of tube I8' for the initial conditions will not be over 2,5 of the'compresser capacity so that itslcapacity under the later conditions will still be less than that of the compressor. Then tube i8' cannot supply all capacltythat the evaporator demands and the pressure in the evaporator will soon drop as before. Now by setting the plug, or stop 33', so as to further compress spring 34 the valve 3|' that controls the outlet of tubel I9' will not open until the pressure (and temperature) in the -evapora tor has been reduced to the desired level. l

At this point the increased pressure difference affecting valve 3|' and spring 34 will cause tube I9 to ow. However, tube Il' will only ow j until the over-supply of liquid raises the evaporator pressure a small amount when it will close. Thus itwill function intermittently as before but at the lower pressure levels. Obviously, I can combine tube sizes that will provide a considerable range of pressure ratios to be handled by one unit.

I may combine a tube I2 with a tube I8' and a tube I9 so that for an increase over the initial pressure conditlonsplus larger capacity increases or for similar capacity under much lower pressure.

ratios, I may set the adjustment on tube i9' so that it functions with tube I8 andthen tubel! will be adjusted to provide the intermittent control. i

It will be apparent that my device lends itself to agreat variety of applications and may be selected so as to provide self-acting control for any of them.l Therefore, I do not confine myself 'to the device as illustrated in the drawing and described in the specification, but only-as indicated in the appended claims.

condenser and the evaporator including pressure reducing means having a.' series of restricter tubes leading from the condenser to the evaporator, one or more of said restricter tubes being unobstructed and having a capacity short of that necting said source to said evaporator, at least one of said restricter pipes having a pressure-operated automaticv valve therein normally serving to prevent refrigerant from passing through said pipe, and means for opening said valve when the diierence in pressures at opposite ends of said last-named pipe exceeds a-predetermined value.

3. In a refrigerating mechanism, a 'source of vaporizablerefrigerant under pressure, an evaporator, and'a plurality of restricter pipes connecting said source to said evaporator, atleast one of said pipes being continuously open from end to end, and means normally closing at least one of said pipes while a normal ratio is mainF -tained between the pressures at the inlet and outlet ends of said open pipes, said closing means being so constructed as to open when the pressure at said outlet end falls below a predetermined amount.

4. The combination of afsource of fluid under pressure, van evaporator, a plurality of restricter tubes leading from said source to said receiver, at least one of said tubes having an automatically releasable valve biased toward closed position, said valve being constructed to open upon change of pressure at opposite sides thereof beyond a predetermined value, and at least one of said tubes being continuously open. f

5. The combination of a source of fluid under pressure, a chamber, a plurality of restricter tubes leading from said source to said chamber, and a valve normally closing Aat least one of said tubes, said valve being constructed to open when the pressure in said chamber falls below a predetermined minimum.

6. `The combination of a source of iluid under pressure, a chamber, an attachment comprising a plurality of restricter tubes leading from said source to said chamber, at least one of said tubes being constantly open to permit fluid to pass to said chamber, and at least one other of said tubes having a normally-closed valve arranged to be opened by the pressure of fluid from said source when the pressure in said chamber falls below a predetermined minimum. I

'7. In a refrigerating mechanism of the kind that successively compresses, condenses, expands, and evaporates a volatile substance, a feed control for the evaporator having two or more restrictive tubes arranged for parallel ilow of the substancaat least one of said tubes having a pressure actuated closing valve at its outlet end functioning according to the pressure in the evaporator.

8. In a refrigerating plant, an evaporator, a gas compressor. a gas condenser, and an expander in the liquid pipe leading to the evaporator, said expander including at least two restrictive tubes arranged to work in parallel, with a pressure actuated stop for the outlet of at least one of said tubes, said stop being constructed and arranged to function according to evaporator pressure. I

9. An expansion device for a compressor-cgi? denser-evaporator type of refrigerating mec A, nism including two or more parallel restrictive tubes adapted to receive refrigerant liquid /from the condenser, and a yieldable pressure o rated throttling stop in at least one of said tubes for controlling the'ow of refrigerant to the evaporator.

10. A pressure reducing d vice for liquid re- V frigerant including a plurality of restrictive tubes adapted to be connected to a common higher pressure liquid supply and a common lower pressure receptacle, and flow controlling means in at least one of said tubes, said flow controlling means being arranged to open when the pressure in said lower pressure receptacle falls below a predetermined point.

means in position to shut of! theow through 12. A liquid feed control for refrigerant evaporators, including a plurality of restrictive tubes adapted to receive liquid at a higher pressure and to deliver it to an evaporator at a lower pressure, in combination with closing devices for only part of the tubes, and means arranged to open said closing-means upon undue decrease in such lower pressure.

, '13. A device as in claim 12, including yieldable means for normally holding said closing .their tubes, and adjusting means for varying the action of said yieldable means.

14. An expansion device for a compressor-condenser-evaporator type of'refrigerating cycle including two or more parallel restrictive tubes for receiving refrigerant liquid from the condenser, at least one of said tubes having therein a yieldable throttling stop arranged between the inlet and outlet of the tube for controlling the flow of refrigerant to the evaporaton and adjustable means for varying the throttling action of'said 11. In a control for a refrigerating mechanism -employing a volatile refrigerant, a control throat comprising a series of two or more restrictive tubes, at least one of said tubes being constantly stop.

15. In a refrigerating mechanism, a source of vaporizable refrigerant under pressure,an evaporator, a plurality of restricter vpipes connecting said source to said evaporator, at least one of said restricter pipes having a pressure-operated au-v tomatic valve therein normally. serving to prevent refrigerant from passing through said pipe, means for opening said valve ,when the difference in pressures at opposite ends of said last-named open, and a restraining meansfor each of one or more of the other tubes of theseries, said restraining means being arranged to be relieved upon lowering of' the pressure of refrigerant beyond said throat.

.pipe exceeds a predetermined value, and adjustable means for acting on said valve to alter the point at which it is Opened.


Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US2452441 *Jun 17, 1944Oct 26, 1948Alco Valve CoRegulator valve having a capillary tube expansion passage
US2675683 *Jun 22, 1950Apr 20, 1954 Control means fob refrigeration
US2709340 *Oct 13, 1953May 31, 1955Robert C WebberRefrigerating system with low temperature stabilization
US2742768 *Feb 12, 1952Apr 24, 1956Alvin H BaerControl valve for liquid pressure reduction
US2939473 *Aug 13, 1956Jun 7, 1960Franklin M McdougallValve for refrigeration equipment
US3493012 *Sep 15, 1967Feb 3, 1970NasaFluid flow restrictor
US5893273 *Jun 17, 1997Apr 13, 1999Aeroquip Vickers, Inc.Shut-off valve with incorporated expansion nozzle, for pressurized fluids of air cooling/heating apparatus
EP0541157A1 *Oct 28, 1992May 12, 1993Whirlpool Europe B.V.Refrigerating device
EP0821210A1 *Jun 14, 1997Jan 28, 1998Finimpresa S.r.l.Shut-off valve with incorporated expansion nozzle, for pressurised fluids of air cooling/heating apparatus
EP1279911A1 *Jul 23, 2001Jan 29, 2003Zexel Valeo Climate Control CorporationRefrigerant tubing for a vehicle air conditioning system
EP1701117A2 *Jul 23, 2001Sep 13, 2006Zexel Valeo Climate Control CorporationRefrigerant tubing for a vehicle air conditioning system
U.S. Classification62/224, 138/46, 62/474, 62/216
International ClassificationF25B41/06
Cooperative ClassificationF25B2341/0661, F25B41/06
European ClassificationF25B41/06