US3519066A

US3519066A - Heat pump

Info

Publication number: US3519066A
Application number: US703156A
Authority: US
Inventors: James H Anderson
Original assignee: Individual
Current assignee: Individual
Priority date: 1968-02-05
Filing date: 1968-02-05
Publication date: 1970-07-07
Anticipated expiration: 1987-07-07

Description

Juiy 7, 1970 J. H. ANDERSON HEAT PUMP 2 Sheets-Sheet 1 Filed Feb. 5, 1968 INVENTOR IHIHHHHHH JAMES H. ANDERSON ATTORNEYJ July 7, 1970 J. H. ANDERSON HEAT PUMP 2 Sheets-Sheet :3

Filed Feb. 5. 1968 INVENTOR JAMES H. ANDERSON ATTORNEYS United States Patent 3,519,066 HEAT PUMP James H. Anderson, 1615 Hillock Lane, York, Pa. 17403 Filed Feb. 5, 1968, Ser. No. 703,156 Int. Cl. Fd 9/00 US. Cl. 16529 7 Claims ABSTRACT OF THE DISCLOSURE A heat pump having a closed cycle refrigeration sys tem including a condenser, evaporator and compressor and a vaporized fluid power system for driving the compressor including a boiler and condenser. The condensers are arranged in such a manner that heat is transferred to the ambient when the apparatus is utilized to cool a conditioned zone and heat is transferred to the conditioned zone when the apparatus is utilized to heat a conditioned zone. The evaporator simultaneously removes heat from the conditioned zone during cooling thereof and removes heat from the ambient during heating of the conditioned zone. A fluid bypass system is provided to supply heat directly from the boiler to the condenser of the vaporized fluid power system during extreme, low ambient temperature conditions when the conditioned zone is being heated.

BACKGROUND OF THE INVENTION Heat pump apparatus are in wide use for heating and cooling buildings in the art. Prior art heat pumps generally include a refrigeration system having a condenser exposed to ambient and an evaporator exposed to the zone to be conditioned to provide cooling for the zone. Means, generally including flow control valves, are provided to transfer the evaporation portion of the process to the ambient and the condenser portion of the process to the condition zone to provide heating for the zone. Due to the relatively limited heat output capability of the refrigeration system condenser, prior art heat pumps have found application primarily in moderate climates or have necessitated the use of additional or supplementary heating apparatus in conjunction therewith.

SUMMARY OF THE INVENTION This invention relates generally to devices for transferring heat energy from a low temperature locality to a high temperature locality and more specifically to a heat pump for accomplishing such transfer by mechanical means involving the compression and expansion of a fluid by mechanical refrigeration. The invention relates more particularly to such an apparatus as applied to heating or cooling a building by transferring heat from or to the ambient air.

This invention provides a novel heat pump apparatus which avoids the disadvantages of the prior art by furnishing a vaporized fluid power system including a condenser for powering a closed cycle refrigeration system whereby the condensers of the vaporized fluid power system and of the refrigeration system are utilized to selectively transfer heat to the ambient or to the conditioned zone while the evaporator of the refrigeration system is utilized to extract heat from the ambient or the conditioned zone.

The invention also provides a novel evaporator-condenser structure which may be quickly manipulated to switch from the function of extraction of heat from, to the transfer of heat to the conditioned zone.

The invention further provides novel means for bypassing the power unit of the vaporized fluid power system for circulating heat energy directly to the condenser 3,519,066 Patented July 7, 1970 "Ice thereof to increase the heat output of the apparatus during heating of the condition zone at low ambient temperatures.

In the preferred embodiment, the invention comprises a refrigeration system comprising a condenser, expansion means, evaporator and compressor, the compressor being driven by a vaporized fluid power system comprising a rotary boiler, turbine and condenser. The condensers and evaporator are rotatably mounted in opposed relationship so that the evaporator may be mechanically moved from communication with the conditioned zone to communication with the ambient while the condensers are simultaneously moved from communication with the ambient to communication with the conditioned zone, thereby providing means to switch from transfer of heat from, to transfer of heat to the conditioned zone. A bypass is provided to communicate fluid from the boiler of the vaporized fluid power system, around the turbine, directly to the condenser thereof to increase the heat output of the vaporized fluid power system when required for heating the conditioned zone.

These and other objects of the invention will become better understood to those skilled in the art by reference to the following detailed description when viewed in light of the accompanying drawings wherein like numerals throughout the figures thereof indicate like components and wherein:

FIG. 1 is a schematic view of a heat pump apparatus in accordance with the invention;

FIG. 2 is a fragmentary plan view, in section, of the evaporator-condenser structure of the invention of FIG. 1 disposed in ducting and configured to transfer heat from the conditioned zone;

FIG. 3 is a view similar to FIG. 2 showing the evaporator with the condenser structure of the invention disposed in such a manner to transfer heat to the conditioned zone;

FIG. 4 is a schematic view similar to FIG. 1 showing another embodiment of the invention; and

FIG. 5 is a fragmentary plan view similar to FIG. 3 showing the evaporator-condenser structure of the embodiment of FIG. 4.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring now to FIG. 1 of the drawings, the heat pump comprises a refrigeration apparatus including a a condenser 10 communicating in series through a conduit 12 with an expansion valve 14, evaporator 16 and a compressor 18. Power for the compressor 18 is derived from a vaporized fluid power system comprising a turbine 20, connected to the compressor 18 through a shaft 22, and communicating in series through a conduit 24 with a condenser 26, an injector 28 and a boiler 30. The injector 28 is powered by a branch conduit 32, communicating with the conduit 24 at the portion thereof supplying fluid to the turbine 20, and serves to increase the pressure of the fluid circulating from the condenser 26 to the boiler 30 in a manner well known in the art.

A bypass conduit 34, including a valve 36, communicates with the conduit 24 on either side of the turbine 20 to provide a means to selectively bypass the turbine. Air circulating means such as

fans

38 and 40 are disposed to induce air flow over the evaporator 16 and the

condensers

10 and 26 respectively.

The aforedescribed components may be of any type commonly known in the art. Although illustrated schematically as an axial flow rotary turbine-compressor, for example, the compressor may take the form of a radial flow turbine and/or compressor or reciprocatory motor-compressor structure if so desired.

In the disclosed embodiment, it is contemplated that fluid in the refrigeration system will comprise one of the suitable conventional refrigerants such, for example, as ammonia or one of the fluorocarbons, while the fluid in the vaporized fluid power system will preferably comprise a halogenated hydrocarbon suitable for the purpose such, for example, as Freon 114 (dichlorotetrafluoroethane CClF CClF or Freon-318 (octafluorocyclobutane C 1 A vaporized fluid power system particularly suitable for this purpose is disclosed in Pat. No. 3,315,466, issued Apr. 25, 1967. In the event that such a fluid power system with a rotary turbine-compressor structure is utilized to transmit power between the vaporized fluid power system and the refrigeration system, segregation of the fluids and lubrication of the turbine-compressor may be accomplished with the bearing and seal system disclosed in Pat. No. 3,258,199, issued June 28, 1966.

In utilizing fluids such as the above-mentioned Freons as working fluids in the vaporized fluid power system, cavitation problems are encountered in transmitting the fluid from the condenser to the boiler. It is contemplated that such problems, if encountered, can be overcome by subcooling the fluid supplied to the injector 28 by means of a structure such as the subcooling column 16 disclosed in the aforementioned Pat. No. 3,315,466.

Although the boiler 30 may be of any of the types common in the art, for the purposes of compactness and efliciency as well as for particular adaptability for use with fluorocarbons, it is preferred that a boiler structure such as the rotary vapor generator disclosed in US. Pat. No. 3,260,050, issued July 12, 1966, be utilized. If such a boiler is used, as disclosed in that patent, a major portion of the pumping work necessary for circulating fluid through the vaporized fluid power system can be accomplished in the rotary boiler and the work required from the injector can thereby be reduced or eliminated. For this reason, it is possible that the injector 28 may be, in some cases, eliminated from the system by proper design.

Referring now to FIG. 2 of the drawings, the evaporator 16 and the condensers and 26 are shown mounted in opposed substantially coplanar relationship to one another on a rotatable member 42, disposed between a conditioned zone duct 44 and an ambient duct 46. The

fans

38 and 40 are mounted in the

ducts

44 and 46 respectively to circulate air as shown by the arrows through the ducts. A movable panel 48 is disposed in an opening 50, formed between the

ducts

44 and 46 and is mounted for rotation on the rotatable member 42 in perpendicular relationship to the

condensers

10 and 26 and the evaporator 16. A suitable elastic seal 52 is provided between the panel 48 and the opening 50 to block communication between the

ducts

44 and 46 when the panel 48 is aligned therewith as illustrated.

A wall 56 segregates a conditioned zone, indicated generally at 58, from an ambient area, indicated generally at 60. The duct 44 penetrates the wall 56 through

openings

62 and 64 to provide communication with the conditioned zone 58.

In operation, with the apparatus in the configuration illustrated in FIGS. 1 and 2 and the valve 36 (FIG. 1) closed, the conditioned zone 58 is cooled by energization of the boiler 30 and the

fans

38 and 40. Upon energization of the boiler, as more particularly described in aforementioned Pat. No. 3,260,050, the vaporized fluid power system operates generally in accordance with that disclosed in aforementioned Pat. No. 3,315,466 with the substitution of the injector 28 for the main pump and elimination of the recuperator 10 thereof. Heated, high pressure fluid is delivered through the conduit 24 to the turbine 20, thereby driving the compressor 18 through the shaft 22. Turbine exhaust fluid is directed through the conduit 24 to the condenser 26 whereby heat is removed therefrom by passage of air therethrough by means of the fan 40 and the duct 46. Fluid is returned to the boiler 30 through the conduit 24 by means of the influence of the injector 28 deriving energy for increasing the feed pressure to the boiler from a portion of high energy fluid diverted thereto through the branch conduit 32 as described above.

Fluid, compressed in the compressor 18, is circulated through the condenser 10 for removal of heat therefrom by air flow directed thereover by means of the fan 40 and the duct 46. The cooled high pressure fluid is then transmitted through the conduit 12 to the expansion valve 14 for expansion and cooling thereof in a conventional manner. The expanded, cooled fluid is then transmitted through the evaporator 16 for a transfer of heat thereto from conditioned zone air directed thereover by means of the fan 38 and the duct 44 in a manner well known in the refrigeration art. The expanded, warmed refrigeration fluid is then returned to the compressor 18 for recycling thereof in a closed cycle.

It should be noted at this point that the arrangement of the

condensers

10 and 26 relative to the direction of air flow through the duct 46 is particularly eflicient since the Coeflicient of Performance of a Carnot cycle is a function of the difference between the temperature of heat in and the temperature of heat rejected divided by the temperature of heat in as in the following relationship:

Cnrnot 1 while the Coeflicient of Performance of a refrigerator is a function of the temperature of heat in, divided by the difference between the temperature of heat rejected and the temperature of heat in as in the following relationship: lltefri 'q' 1" ';s The overall Coeflicient of Performance is then as follows:

T1 'T2 T3 T1 2* 3 When the heat rejector or condenser structures are placed in series, either the hot body of heat or the cold body of heat can be rejected at the higher temperature. Presuming the following:

T =temperature of heat supplied. T =temperature of heat rejected from the power condenser 26.

T =temperature of heat rejected from the refrigerator condenser 10. T =temperature of heat supplied to refrigerator.

The overall Coefficient of Performance of the heat pump then is as follows:

Totnl 1 28 T3 P o C0 T ta] T1 X 2b 3 For example, by first placing the refrigerator condenser 10 upstream to receive the coolest supply of airflow and assuming the following values (absolute):

T =101O. T =595. T =585. T =505. For these parameters, the Coeflicient of Performance is calculated as follows:

By reversing the condensers and placing the power condenser 26 upstream of the refrigeration condenser 10 with the above same assumptions, the parameters are:

The Coefficient of Performance then is as follows:

or an increase in Coeflicient of Performance of .23 by proper arrangement of the condensers, as illustrated.

Referring now to FIG. 3 of the drawings, the evaporator-condenser of FIG. 2 is shown rotated 180 to place the condensers and 26 in the conditioned zone duct 44 and the evaporator 16 in the ambient duct 46. The panel 48 once more aligns with the

ducts

44 and 46 to provide segregation of airflow therebetween.

Since fluid connection from the

condensers

10 and 26 and the evaporator 16 with the remainder of the system must be accomplished through six conduits as described above, it is preferable, in order to avoid multiple seal problems, to design the connections in such a manner that communication is provided while allowing 180 rotation of the structure. Such communication may be accomplished by providing tubes formed as helical springs twistable through 180 or communicating tubes of sufficient length to permit a 180 twist without yielding the tube material. It has been found that such can be accomplished with steel tubes of the following characteristics, for example:

E 12 10 p.s.i. S =20,000 p.s.i. d=.625 inch.

Straight length=58.9 in.

It should be noted at this point, that since the condenser side of the structure would normally have a higher resistance to airflow than the evaporator side, it is advisable to make provision for increasing the airflow through the condenser side of the structure. This could be accomplished by providing a two-speed arrangement on the

fans

38 and 40 so that the fans may be switched from a higher airflow when the condenser section is disposed in a particular duct to a lower airflow when the evaporator side is disposed therein. Another alternative would be to mount a supplementary fan on the condenser structure to automatically compensate for the additional flow resistance therethrough.

With the apparatus structured in accordance with the configuration shown in FIG. 3, heat is supplied to the conditioned zone by means of rejection from the

condensers

10 and 26 disposed in the duct 44 while heat is extracted from air circulated through the duct 46 by the evaporator 16. Heat supplied in this manner is suitable for moderate cold weather conditions and temperature may be controlled at a desired level by regulating the amount of heat supplied to either or both of the

condensers

10 or 26. In moderate weather conditions, the compressor supplies some heat to the condenser 10 while whatever additional heat is required may be extracted from the condenser 26.

In very cold weather conditions, the compressor 18 through the condenser 26 to suitably augment the heat output. Under these conditions, it is more efi'icient to remove the compressor from the line and direct heat generated by the boiler 30 directly to the condenser 26. This is accomplished by opening the valve 36 and bypassing the turbine 20 to channel the heated fluid for the boiler 30 directly through the conduit 34 to the condenser 26, thereby channeling all of the heat from the boiler 30 to the airflow directly.

Referring now to FIG. 4 of the drawings, another embodiment in accordance with the invention is illustrated. Since fluorocarbons such as the above-mentioned Freons are equally suitable for use as refrigerants, the heat pump can utilize a single fluid system. This is accomplished by joining the exhaust from the turbine and the discharge from the compressor and directing the flow to a common condenser. In such a system, illustrated in FIG. 4 components thereof corresponding to like components of the preceding figures are indicated by like numerals of the next higher order. In this figure the exhaust from the turbine is manifolded into a combined condenser 166 through the conduit 124 with the exhaust or discharge from the compressor 118. fed through the conduit 112. The condensate from the condenser 166 is divided subsequent to condensation in the conduit 124, for return to the boiler 130, and the conduit 112, for channeling through the expansion valve 114. The operation of the remainder of the system is identical to that described for the embodiment of FIG. 1.

In FIG. 5, the evaporator-condenser structure is shown disposed in the ambient duct 146 and conditioned zone duct 144 and operates in a manner identical to that described for the embodiment of FIGS. 2 and 3 for switching from cooling, as illustrated, to heating of the conditioned zone.

In the single fluid system disclosed in FIGS. 4 and 5, it is possible to substitute an injection or jet type compression apparatus for the rotary turbine-compressor illustrated. The principles ofoperation of such an apparatus are well known in the steam power plant art and are illustrated by the injector 28 utilized in the embodiment of FIG. 1. In such a device, the high energy, high tempera ture fluid from the boiler would be injected through the conduit 124 into the low energy fluid in the conduit 112 after passage thereof through the evaporator 116, thereby raising the pressure and energy level of the fluid entering the condenser 166. After cooling in the condenser 166, the high energy fluid would then be divided as described above, a portion thereof returning to the boiler 130 while the remainder thereof is expanded through the expansion valve 114 for reentry into the evaporator 116.

What has been set forth above is intended as exemplary of teachings in accordance with the invention to enable those skilled in the art in the practice thereof. It should therefore, be understood that, within the scope of the appended claims, the invention may be practiced other than as specifically described.

What is new and therefore intended to be protected by Letters Patent of the United States is:

1. A heat pump for transferring energy between a conditioned zone and an ambient zone comprising:

a closed cycle refrigeration apparatus including in series compressor means,- first condenser heat exchange means and evaporator heat exchange means;

a vaporized fluid power apparatus including in series vapor generator means, second condenser heat exchange means and means transferring energy from the output of said vapor generator means to said compressor means; and

flow control means to communicate the heat product of said condenser heat exchange means to one of said zones and the heat intake of said evaporator heat exchange means to the other of said zones including a single rotor means so positioned to selectively reverse communication of said heat exchange means with said zones.

2. A heat pump in accordance with claim 1 wherein said first and second condenser heat exchange means comprise a single condenser structure and wherein the fluid 1n said refrigeration and power apparatus is manifolded upstream and divided downstream of said condenser structure.

3. A heat pump in accordance with claim 1 wherein said means transferring energy from the output of said vapor generator means comprises a rotary turbine-compressor unit.

4. A heat pump in accordance with claim 1 wherein said vaporized fluid power apparatus further includes means including a valve for bypassing said means transferring energy from the output of said vapor generator means to thereby selectively direct fluid from said vapor generator means directly to said condenser means.

5. A heat pump in accordance with claim 1 where said flow control means further comprises means to transmit air from said zones through said heat exchange means and wherein said second condenser heat exchange means is disposed in series on the downstream side of said first condenser heat exchange means with respect to the airflow therethrough.

6. A heat pump in accordance With claim 5 wherein said flow control means further comprises parallel, adja cent ducts, each of said ducts being in communication with one of said zones, said evaporator heat exchange means being mounted in substantially coplanar adjacent relation to said condenser heat exchange means on a rotatable axis disposed between said ducts, said ducts having openings in the common wall thereof encompassing said rotatable axis and accommodating said heat exchange means for rotation therein, and a panel coextensive with said openings and mounted substantially normal to said heat exchange means on said rotatable axis to segregate flow through said ducts when said heat exchange means are substantially normal thereto.

7. A heat pump in accordance with claim 1 wherein said vapor generator comprises: an enclosure for containing a vaporizable fluid therein, a vapor exhaust standpipe disposed in said enclosure, means to control fluid communication between said enclosure and said standpipe, means to heat said enclosure to provide vaporization of the fluid therein, a rotating support in said enclosure coaxially disposed intermediate the ends of said standpipe, a vapor dome mounted on said rotating support to enclose the upper end of said standpipe, a fluid heat exchange and transmitting tube assembly disposed on said rotating support, means to transmit vapor from said assembly to said vapor dome for storage therein, a preheater tube assembly fixedly mounted around the walls of said enclosure ad- 'jacent said rotating support and fluid assembly, means to supply liquid to said preheater tube assembly for preheating therein and means to transmit preheated liquid therefrom to the fluid assembly disposed on said rotating support, and means to control the quantity of liquid and heat supplied to said generator.

References Cited UNITED STATES PATENTS 3,153,442 10/1964 Silvern 16550 2,984,087 5/1961 Folsom 62325 ROBERT A. OLEARY, Primary Examiner C. SULKALO, Assistant Examiner US. Cl. X.R.