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Publication numberUS3643460 A
Publication typeGrant
Publication dateFeb 22, 1972
Filing dateSep 11, 1970
Priority dateSep 11, 1970
Publication numberUS 3643460 A, US 3643460A, US-A-3643460, US3643460 A, US3643460A
InventorsMilton W Garland
Original AssigneeFrick Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Gravity refrigerant recirculation
US 3643460 A
A feed accumulator receives liquid refrigerant from the receiver and feeds it by gravity to the evaporator. Excess liquid refrigerant from the evaporator is temporarily stored in a lower level tank from which it is, from time to time, forced back to the accumulator by high-pressure refrigerant. Automatic controls and oil separator features are included.
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Description  (OCR text may contain errors)

lllite [151 ame Garland! 1 lieh. 22, 11972 54] GRAVITY RIEFMHGIERANT 2,952,137 9/1960 Watkins ..62/174 1 1 2,978,877 4/1961 Long ..62/174 3,164,973 1/1965 Watkins ..62/174 [72] Inventor: Milton W. Garland, Waynesboro, Pa.

. Primary Examiner-Meyer Perlin Company waynesbom' Attorney-A. Yates Dowell and A. Yates Dowel], Jr. [22] Filed: Sept. 11, 1197111 [57] SC'll I21] Appl. No.: 711,487

A feed accumulator receives liquid refrigerant from the receiver and feeds it by gravity to the evaporator. Excess [52] U.S. 1C1 ..62/174, 62/218, 62/512 li uid refrigerant from the evaporator is temporarily stored in [51] int. Cl ..FZSb 11/00 a lower level tank from which it is, from time to time, forced [58] Field oi Search ..62/218, 174, 512 back to the accumulator by high-pressure refrigerant. Automatic controls and oil separator features are included. [56] References Cited UNITED STATES PATENTS 2,590,741 3/1952 Watkins ..62/174 6 (Ilaims, 3 Drawing Figures GRAVITY REFRIGERANT RECIRCIULATION BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to refrigeration and more particularly to the circulation of refrigerant in a system in which the maintenance of the necessary head for flooding of the evaporator is accomplished by gravity.

2. Description of the Prior Art Gravity feed of evaporators has been used for approximately 40 years. The refrigerant from the evaporator is returned to an accumulator which separates liquid from vapor and prevents liquid from passing into the compressor. Since the evaporator is flooded, it is necessary that the refrigerant which is not vaporized be transferred to the accumulator. However, the latter ordinarily is remote from and located above the evaporator, thus necessitating a pressure head to move the liquid. This pressure head when used with a system operating at low temperature levels imposes a penalty on the system which may be as much as 5 to 7 F.

Prior systems in which an accumulator has been used as as means for transferring liquid back to the receiver are exemplified in US. Pats. such as Garland No. 1,954,695; Phillips No. 2,570,979; Sloan et al. No. 2,655,008; Christiansen No. 2,778,195; Kocher et al. No. 2,836,966; Richards et al. No. 2,871,673; Wood No. 2,986,898; Grant No. 3,214,932; Ross No. 3,315,484; Garland No. 3,353,367; and Grant No. 3,487,656. Gay U.S. Pat No. 1,994,037, discloses a system in which liquid from the accumulator flows into the evaporator and a portion is returned to the accumulator by using the expanded refrigerant as a propulsion means.

SUMMARY OF THE INVENTION The present invention is a refrigerating system having a feed accumulator which supplies liquid refrigerant by gravity to a flooded evaporator which returns refrigerant vapors to the accumulator and discharges liquid refrigerant into a drain separator and then to a transfer tank by gravity. When the transfer tank is filled to a predetermined capacity, automatically controlled valves will divert high-pressure vapors into the transfer tank to return the liquid refrigerant therein to the feed accumulator.

It is an object of the present invention to provide an improved refrigeration system in which a feed accumulator is provided in the liquid line from the receiver and from such feed accumulator to the compressor, Which is positioned to provide the necessary gravity head for flooding the evaporator, and which has transfer means utilizing high-pressure vapor for returning unevaporated liquid to the feed accumulator. Controls are provided for automatic operation.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic diagram ofa preferred embodiment of the invention;

FIG. 2, a schematic of a modified form of the invention; and

FIG. 3, a schematic of the control circuit.

DESCRIPTION OF THE PREFERRED EMBODIMENTS With further reference to the drawings, the refrigeration system illustrated includes a compressor 1!) with the suction line 11 and discharge line 12, and condenser 13 connected by line 14 to receiver 15 which is connected by line 16 to feed accumulator17.

Feed accumulator 17 has a liquid supply line 29 connected to a header 21. The header 21 may supply any desired number of evaporators, as for example through lines 22, 23 and 24. lllustrative is evaporator 25 which is connected to line 23. A check valve 28 is provided in line 23 and check valves 29 and 30 in lines 22 and 24 respectively. Throttling or expansion valve 29 is positioned in line 23 just ahead of evaporator 25.

Feed accumulator 17 is positioned at a sufficient elevation above the evaporators to produce a desired flow rate therein and to maintain them in flooded condition. The head of refrigerant within the feed accumulator is determined by the height of a float 32 connected by line 33 to a selected portion of the accumulator and by line 34 to the liquid line 20 beneath the accumulator. FLoat 32 controls solenoid valve 36 in line 16 to regulate the refrigerant supply from the receiver to the feed accumulator. .Iust beyond the valve 36 is a modulating or throttling valve 38. Any selected type of refrigerant feed control, such as a mechanical float or a thermal level control, may be used instead of a float switch operated solenoid valve.

From the evaporator refrigerant vapors and Unevaporated liquid refrigerant leave through line 40 having valve 41 therein. Return line 42 rises to transport the vapors back to feed accumulator 117 from which they may enter suction line 111..

Unevaporated liquid refrigerant falls in line 44 into drain separator 46 from which it gravitates through line 43 having valve 49 therein into transfer tank 50.

Transfer tank 50 has upper and lower float switches 51 and 52, respectively. When the liquid level in the transfer tank is sufficiently high, the upper float switch 51 operates causing pilot solenoid valve 53, which is normally closed, to open. Valve 53 is located in a high-pressure vapor line 12' from the compressor and when valve 53 is open, high-pressure refrigerant vapor is carried by line 54 to the normally open valve 49, applying pressure to its operating piston thereby closing valve 49 and stopping the flow of liquid refrigerant through the line 43.

Branch line 55 is connected to line 12 and line 54 at one end, and is connected at its other end to line 44 and has a solenoid controlled vent valve 57 therein which is normally open. Line 12 has a branch line 60 which is connected at its other end to branch 61 which is connected to the operating pressure switch in the normally open valve 41 in line 40 and to branch 62 which is connected through normally open solenoid controlled vent valve 63 to line 42.

Flow through line 69 is controlled by normally closed solenoid operated valve 64. Line 68 is connected at one end to the discharge line 40 from the evaporator and at its other end to line 62 intermediate valves 64 and 63.

Branch line 65 is connected to line 23 at one end and is connected at its other end to the top of drain separator 46 and has a pressure regulating valve 67 therein.

Line 12' also has branch line 70 connected through normally closed solenoid operated control valve 71 to the upper portion of transfer tank 50.

When the liquid level in transfer tank 59 is high enough, float switch 51 is closed to energize a relay R11 (FIG. 3) which in turn energizes the coil of high-pressure valve 53 and causes such valve to open, thus admitting high-pressure vapor from line 12 to line 54, applying pressure to the operating piston of normally open valve 49-, closing valve 49'. Relay R1 also energizes a holding switch 72 in the circuit of the lower float switch 52 and the coils of vent valve 57 and control valve 71 to close valve 57 and open valve 71. This permits high pressure vapor to enter transfer tank 50 through line 12 and branch line 74), forcing liquid refrigerant through return line and check valve 81 into the feed accumulator 17.

As the liquid level recedes in the transfer tank 50, the float switch 511 will open, but the switch 72 will continue to energize the relay R1. When the liquid level in transfer tank 50 falls below the lower flat switch 52, such switch will interrupt the flow of electrical energy to the relay R1 and deenergize such relay. This causes the solenoid operated control valve 71 and high-pressure valve 53 to close and causes vent solenoid valve 57 to open. Valve 49 opens due to spring action and release of the high-pressure vapor.

Thus the foregoing operation accomplishes a normal operation of the evaporator with the only pressure head imposed on it being that of the design pressure for flow of the vapors generated and any excess liquid. Valve 29 need only be preset once in order to adjust the refrigerant flow rate for the evaporator 25 at the design operation levels.

If desired, thermostat 85 may be provided responsive to the cooling action of evaporator 25 causing solenoid valve 86 to close in order to stop refrigerant flow and prevent an excessive accumulation of liquid refrigerant in the evaporators under conditions of no load.

With the use of additional evaporators as indicated in dotdash lines, through lines 22, 24, any of these may be selectively defrosted without interfering with the performance of the remainder of the system. In order to carry out defrosting, switch 90 (FIG. 3) is placed in the On position and this energizes a relay R2 and simultaneously causes the high-pressure vapor solenoid operated valve 64 to open. Relay R2 opens a switch 73 and causes the vent solenoid valve 63 to close, thereby forcing high-pressure vapor through branch line 61 and the discharge line 68. The increased vapor pressure in the branch line 61 causes the normally open valve 41 to close and increased pressure in the evaporator 25 closes check valve 28. The pressure rises to appropriate pressure temperature level of the refrigerant being used in order to cause melting of the frost from the evaporator surfaces.

The pressure regulating valve 67 responds to the increased pressure within the evaporator and passes liquid refrigerant from the evaporator into the drain separator 46. The operation of the liquid transfer system will respond to a high liquid level as previously described.

When defrosting is completed switch 90 is opened thereby causing high-pressure vapor solenoid 64 to close and deenergizing the relay R2 to permit vent solenoid 63 to open. This permits valve 41 to open and with the pressure released check valve 28 opens and evaporator 25 is again in service.

The accumulator is designed for improved oil separation. Liquid refrigerant from the receiver line 16 and from line 80 enter the accumulator at one end, indicated as the left end in the drawing. The accumulator is of substantial horizontal dimension having a main bottom 17 and a reservoir 17" which is substantially sunken below the level of the main bottom. The reservoir is located adjacent to one end or side of the accumulator remote from the end at which the liquid refrigerant enters. The liquid outlet or supply line 20 is positioned near the end of the accumulator such that liquid refrigerant entering from the lines 16 and 80 flows across reservoir 17". The outlet 20' ofthe pipe 20 projects above the bottom surface of the accumulator in order to avoid receiving oil and possibly other foreign matter.

From the bottom of reservoir 17' a discharge pipe 90 is connected through valve 91 to oil separator 92 having a drain valve 93 at its lower portion. From the upper portion vapor line 94 having valve 95 therein is connected to return the refrigerant vapor which has been separated from the oil to the top of the accumulator.

In the modification of FIG. 2, the location of the drain separator and transfer tank is different than in FIG. 1. In FIG. 1 the drain separator 46 is at a lower level than evaporator 25 and transfer tank 50 is at a lower level than the drain separator. However, in FIG. 2 drain separator 46' is just below the outlet of the evaporator and the transfer tank 50 has its vertical center on the same level as the bottom of the drain separator 46. Even though the levels are shifted, the principle of operation of the modified form is the same. However, the drain separator and transfer tanks required for FIG. 2 may need to be slightly larger than those in FIG. 1 for the same volume of liquid transfer. The evaporator, drain separator and transfer tank may be located as desired provided that there is sufficient difference in level for the necessary gravity flow.

I Claim:

1. In a refrigeration system having means for supplying liquid refrigerant and for compressing and condensing refrigerant vapor, a feed accumulator having an inlet from the supplying means for liquid refrigerant and an outlet to the compressing means for vapor, an evaporator connected to the feed accumulator, the feed accumulator positioned at a higher elevation than the evaporator, a first line form the accumulator to the evaporator for supplying liquid refrigerant thereto, a second lme from the evaporator to the accumulator for returning a refrigerant vapor to the accumulator, a drain separator and a transfer tank, said drain separator connected to said second line and positioned at a level to receive liquid refrigerant from said second line by gravity flow, said transfer tank connected to said drain separator and positioned to receive liquid refrigerant from said drain separator by gravity flow, means connecting the transfer tank to the upper portion of said accumulator, liquid level responsive means in the transfer tank, and means for connecting high-pressure vapor from the compressing means to the transfer tank for forcing liquid refrigerant therefrom into the feed accumulator.

2. The invention of claim 1 and means for selectively connecting high-pressure vapor from the compressing means to the outlet of the evaporator, and means for permitting liquid refrigerant in the evaporator to discharge into the drain separator as it is subjected to pressure from the high-pressure vapor.

3. The invention of claim 1 in which said transfer tank has upper and lower liquid level responsive means, said upper level liquid responsive means controlling valve means which connects the high-pressure vapor from the compressing means to the transfer tank and said lower liquid level responsive means operating to interrupt the flow of high-pressure vapor to the transfer tank.

4. The invention of claim I in which said first line is connected to the feed accumulator at a position which is laterally remote from the connection of said second line to the accumulator, and said feed accumulator has a well intermediate the said two connections for the collection of oil, oil separator means connected to said well, and means connecting the upper portion of the oil separator means to the upper portion of the feed accumulator for the return of any refrigerant vapor thereto.

5. The invention of claim 1 including pressure operated valve means between said drain separator and said transfer tank, and means for closing said pressure operated valve means by the high-pressure vapor from said compressor.

6. The invention ofclaim 1 including float control means for controlling the liquid level in said feed accumulator.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US2590741 *Jan 24, 1949Mar 25, 1952Watkins John ELiquid return trap in refrigerating systems
US2952137 *Jan 2, 1959Sep 13, 1960John E WatkinsLow pressure refrigerating systems
US2978877 *Aug 4, 1958Apr 11, 1961Vilter Mfg CompanyHot gas defrosting system with gravity liquid return for refrigeration systems
US3164973 *Mar 28, 1963Jan 12, 1965Watkins John ERefrigerating systems
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3827249 *Mar 12, 1973Aug 6, 1974Frick CoPressurized refrigerant recirculation system with control means
US4969495 *Jun 27, 1989Nov 13, 1990Grant David C HDirect condensation refrigerant recovery and restoration system
US5058631 *Aug 16, 1989Oct 22, 1991Ashland Oil, Inc.Flexible gas salvage containers and process for use
US5077982 *Feb 14, 1990Jan 7, 1992York International CorporationMultizone air conditioning system and evaporators therefor
US5094277 *Oct 19, 1990Mar 10, 1992Ashland Oil Inc.Direct condensation refrigerant recovery and restoration system
US5176187 *Oct 18, 1990Jan 5, 1993Ashland Oil, Inc.Flexible gas salvage containers and process for use
US5189885 *Nov 8, 1991Mar 2, 1993H. A. Phillips & Co.Recirculating refrigeration system
US5361594 *Dec 14, 1993Nov 8, 1994Young Robert ERefrigeration recovery and purification
US20100199707 *Feb 9, 2010Aug 12, 2010Star Refrigeration LimitedRefrigeration system
U.S. Classification62/174, 62/218, 62/512
International ClassificationF25B43/02, F25B45/00, F25B41/00
Cooperative ClassificationF25B2400/16, F25B45/00, F25B41/00, F25B43/02
European ClassificationF25B43/02, F25B45/00, F25B41/00
Legal Events
May 2, 1989ASAssignment
Effective date: 19881215