US3861166A - Heat pump system - Google Patents

Heat pump system Download PDF

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US3861166A
US3861166A US337131A US33713173A US3861166A US 3861166 A US3861166 A US 3861166A US 337131 A US337131 A US 337131A US 33713173 A US33713173 A US 33713173A US 3861166 A US3861166 A US 3861166A
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working fluid
free piston
condenser
small diameter
directing
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US337131A
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Fred L Goldsberry
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Lone Star Gas Co
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Lone Star Gas Co
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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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant

Definitions

  • ABSTRACT In a heat pump system, a dual diameter, double-acting free piston apparatus is utilized as an expandercompressor. Working fluid is compressed in the large diameter portion of the free piston apparatus and is directed to a condenser.
  • Part of the working fluid flowing from the condenser is directed through an expansion valve and an evaporator, and is then alternately admitted to the opposite ends of the large diameter portion of the free piston apparatus.
  • the remainder of the working fluid flowing from the condenser is directed through a pump and a boiler and is then alternately admitted to the small diameter portions of the free piston apparatus, whereupon-the working fluid is expanded to effect actuation of the apparatus.
  • the flow of high temperature, high pressure working fluid into the small diameter portions of the free piston apparatus is controlled by disk valves which also.
  • the free piston apparatus further comprises a housing which forms a hermetic seal enclosing all of the reciprocating and rotating components of the system.
  • the compression type system typically employs an electric motor to operate a compressor.
  • a refrigerant is forced from the compressor through a condenser, through an expansion valve, through an evaporator and back to the compressor.
  • a fuel such as natural gas is utilized to boil a refrigerant out of a carrier liquid.
  • the refrigerant is directed through a condenser and an evaporator and then is recombined with the carrier liquid in an absorber.
  • Heat pump systems of the compression type utilizing a fuel such as natural gas as the basic energy source have also been provided heretofore.
  • Such systems have employed both turbines and free pistons as expanders for high temperature, high pressure working fluid.
  • One difficulty that has often been experienced in the use of these systems involves the lack of a hermetic seal surrounding the reciprocating and/or rotating components. This permits leakage of the working fluid at various sliding and rotating seals, and thereby necessitates relatively frequent maintenance of the system merely to replenish the working fluid.
  • the present invention relates to a heat pump system wherein a dual diameter, double-acting free piston apparatus is utilized both as a working fluid expander and as a working fluid compressor.
  • working fluid is partially compressed in the large diameter portion of the free piston apparatus and is then directed through a condenser.
  • Part of the working fluid flowing from the condenser is directed through an expansion valve and an evaporator, and is then alternately admitted to the opposite ends of the large diameter portion of the free piston apparatus.
  • the remainder of the working fluid flowing from the condenser is directed through a pump and a boiler, and is then alternately admitted to opposed small diameter portions of the free piston apparatus, wherein the working fluid is expanded to effect reciprocation of the free piston.
  • Spent working fluid from the small diameter portions of the free piston apparatus is returned to the condenser.
  • the flow of working fluid through the small diameter portions of the free piston apparatus is controlled by rotating disk valves.
  • the valves are rotated by an induction motor which may also be utilized to drive the pump.
  • the required phase relationship between the disk valves is maintained by a timing rod interconnecting the valves and extending through the free piston.
  • the free piston apparatus includes a housing defining a dual diameter cylinder which receives the free piston.
  • the housing also encloses the disk valves, the induction motor, and the pump. That is, the housing effects a hermetic seal enclosing all of the working components of the heat pump system.
  • a seal is useful in substantially reducing the loss of the working fluid which normally occurs at rotating and sliding seals. This in turn substantially reduces the frequency of maintenance which is necessary in the use of the present invention as compared with prior heat pump systems.
  • the heat pump system 10 comprises a dual diameter, double-acting free piston apparatus 12 includ ing a housing 14.
  • the housing 14 comprises a dual diameter, double-ended cylinder and includes a central,
  • the small diameter portions 18 are equal in length and are coaxial with the large diameter port-ion 16.
  • the free piston assembly 12 further includes a free piston 20 which is mounted in the cylinder of the housing 14 for reciprocation with respect thereto.
  • the free piston 20 comprises a dual diameter, double-acting piston and includes a relatively large diameter portion 22 which reciprocates in the large diameter portion of the cylinder and opposed relatively small diameter portions 24 which reciprocate in the small diameter portions of the cylinder.
  • the small diameter portions 24 of the free piston are coaxial with the large diameter portion 22 and are equal in length.
  • the free piston 20 is provided with suitable piston rings 26 adapted for cooperation with the interior walls of the housing 14 to effect sliding seals.
  • the heat pump system 10 is charged with a suitable working fluid, such as FREON lll, FREON l 12, FREON l 13, etc.
  • a suitable working fluid such as FREON lll, FREON l 12, FREON l 13, etc.
  • Low pressure, relatively warm working fluid is alternatively received in the opposite ends of the large diameter portion 16 of the housing 14 through a line 28 and a pair of suitable check valves 30.
  • the working fluid upon reciprocation of the free piston 20, the working fluid is simultaneously partially compressed in one end of the large diameter portion 16 and is simultaneously drawn into the opposite end.
  • the relatively warm, partially compressed working fluid then flows out of the cylinder 14 through a pair of check valves 32 and a line 34.
  • the arrangement of the inlet and outlet portions relative to the side and end walls of the large diameter portion 16 of the housing 14 comprises an important feature of the invention. That is, since the outlet ports are arranged in the side walls, one of the outlet ports is closed by the free piston 20 at the terminus of each reciprocation thereof. By this means a quantity of working fluid is trapped in the end of the large diameter portion 16, thereby providing the fluid cushion which functions to decelerate the piston. This in turn assures that the terminus of each reciprocation of the free piston 20 will be smooth and that the piston is not forcefully driven into engagement with eitherend of the cylinder l4.
  • the line 34 extends to a condesner 36.
  • a blower 38 or equivalent apparatus is provided for directing a secondary fluid such as air through the condenser 36, thereby cooling the working fluid by heat transfer to the secondary fluid.
  • the condenser 36 and the blower 38 preferably have sufficient capacity that the working fluid is transformed from the gaseous phase to the liquid phase within the condenser 36.
  • both the free piston apparatus 12 and the condenser 36 will be located outside of a zone to be cooled.
  • Relatively high pressure, relatively low temperature working fluid in the liquid phase flows from the condenser 36 through a line 40. Part of the working fluid flowing from the condenser 36 is directed through an expansion valve 42. The valve 42 functions to substantially reduce the pressure of, and thereby simultaneously substantially cool the working fluid. The low temperature, low pressure working fluid flowing from the valve 42 is directed through an evaporator 44 wherein the working fluid returns to the gaseous phase.
  • the evaporator 44 is positioned within or at least in direct communication with the zone to be cooled.
  • a blower 46 or equivalent apparatus directs a secondary fluid such as air through the evaporator 44.
  • heat transfer between the secondary fluid and the working fluid is effected, whereby the secondasry fluid is cooled, and the working fluid is partially heated.
  • Low pressure, relatively warm working fluid flowing from the evaporator 44 is directed to the large diameter portion 16 of the cylinder 14 through the line 28.
  • the remainder of the liquid phase working fluid flowing from the condenser 36 through the line 40 is directed to a gear pump 48.
  • the pump 48 is driven by an induction motor 50 and functions to substantially pressurized the working fluid flowing therethrough.
  • the high pressure working fluid flowing from the pump 48 is directed through a check valve 51 and a line 52 to a boiler 54.
  • both the pump and the boiler are located outside of the zone to be cooled.
  • the boiler 54 is actuated by a gas burner 56 and functions to substantially heat the working fluid.
  • High pressure, high temperature working fluid flows from the boiler 54 in the gaseous phase through a line 57.
  • Working fluid from the line 57 is alternately admitted to the small diameter portions 18 of the cylinder 14 by means of a pair of disk valves 58.
  • Each valve 58 functions to admit high temperature, high pressure working fluid to the adjacent small diameter portion 18 of the cylinder 14 during travel of the free piston 20 away from the valve in question, and to release spent working fluid from the adjacent small diameter portion 18 of the cylinder during travel of the free piston toward the valve in question.
  • Spent working fluid from the small diameter portions 18 of the cylinder 14 passes through a line 60 which extends to the line 34 and hence to the condenser 36.
  • the disk valves 58 of the free piston assembly 12 are maintained in a predetermined angular phase relationship with respect to each other by a shaft 62 which interconnects the valves.
  • the shaft 62 extends through the free piston 20 along the axis thereof and a passageway of sufficient clearance is provided in the free piston to permit reciprocation of the piston relative to the shaft.
  • the shaft 62 and the disk valves 58 are rotated by the induction motor 50 which drives the gear pump 48.
  • a suitable transmission 64 may be provided.
  • the heat pump system 10 further includes a number of components which function to provide control over the operation of the system and which are actuated by a suitable power source (not shown).
  • a pressure switch 65 is provided for actuating a start/stop switch 66 to terminate operation of the system in the event of an inadequate pressure drop across the expansion valve 42.
  • the pressure switch 65 may be of the type manufactured by the Powers Regulator Co. of Skokie, Illinois under Model Number SW1 34-1450 A65. Both the expansion valve 42 and the blower 46 are operated under the control of a thermostat 68 whereby the output of the heat pump system 10 may be regulated.
  • a pressure responsive switch 70 is provided for monitoring the pressure within each small diameter portion 18 at the terminus of the travel of the small diameter portions of the free piston 20 therein.
  • the switch 70 controls the operation of a throttle valve 72 and thereby regulates the flow of high temperature, high pressure working fluid through the line 57 and into the small diameter portions 18 of the cylinder 14. By this means dissipation of the entire energy of the working fluid entering the small diameter portions of the cylinder during each reciprocation of the free piston is assured, thereby preventing a pop when the disk valves are opened.
  • the switch 70 may be of the type manufactured and sold by Powers Regulator Co. as Model Number SWI 34-1455, and the throttle vavle 72 may be a motor actuated two-way single seat valve of the type manufactured and sold by Powers Regulator Co.
  • the boiler 54 is provided with a float controlled switch 74 which is responsive to the level of liquid working fluid within the boiler.
  • the switch 74 operates a bypass valve 76 which functions to return at least a portion of the output of the gear pump 48 to the inlet thereof. By this means a predetermined level of liquid working fluid within the boiler 54 is assured.
  • the switch 74 may be of the type supplied by McDonnel & Miller Inc., of Chicago, Illinois under Model Number 150.
  • the gas burner 56 of the boiler 54 is provided with a pressure actuated gas valve 78.
  • the valve 78 is also responsive to a high temperature limit switch including a temperature responsive member 80 positioned within the boiler 54. By this means operation of the gas burner 56 is terminated in the event that either the pressure or the temperature within the boiler 54 exceeds a predetermined limit.
  • the valve 78 may be of the type manufactured and sold by Honeywell Inc. of Minneapolis, Minnesota as a v58194E Powerpile combination gas control valve.
  • the housing 14 encloses all of the reciprocating and rotating components of the system. That is, the housing 14 hermetically seals the free piston 20, the disk valves 58, the pump 48 and the apparatus for actuating the same. By this means loss of working fluid from the system is completely prevented.
  • the heat pump system 10 incorporates certain sliding and rotating seals. However, since all of the working components of the system are enclosed by the housing 14, any flow of working fluid around such seals merely causes the working fluid to enter another portion of the system. While such flow may cause a certain loss of operating efficiency in the system, there is absolutely no'loss of working fluid. This is important in eliminating a problem that has been encountered in the use of prior art heat pump systems, wherein periodic maintenance has been required merely to replenish the working fluid.
  • the embodiment of the heat pump system 10 illustrated in the Drawing utilizes the same motor 50 to actuate the pump 48 and the disk valves 58.
  • an alternative construction may be provided wherein separate motors are utilized to drive the pump and to rotate the valves.
  • the housing 14 may enclose only the motor which actuates the disk valves, and a separate housing may be provided for enclosing the pump and its operating motor.
  • Such an alternative construction does not, however, deviate from the basic concept of providing a hermetic seal extending around all of the reciprocating and rotating components of the heat pump system.
  • the present invention comprises a heat pump system utilizing a dual diameter, double-acting free piston apparatus as an expander-compressor.
  • the system is further characterized by the use of a fuel such as natural gas as the basic energy source.
  • a highly advantageous characteristic of the system is that the reciprocating and rotating components thereof are entirely enclosed in a hermetic seal, thereby preventing loss of the working fluid utilized in the system.
  • a boiler adapted to provide the working fluid at a high pressure and temperature:
  • a housing having first and second pairs of opposed chambers with a dual radius piston therein having oppositely directed faces;
  • valve means within said housing for controlling alternate admission of fluid from said first fluid path to the oppositely directed faces of said piston in said first opposed chambers and directing spent fluid from said chambers ofsaid pistons to the condenser, said valve means comprising rotating disk valves driven by motor means and disposed adjacent the first opposed chambers in said housing with a shaft extending through said piston for maintaining a predetermined angular phase relationship between the valves; and
  • the system according to claim 1 further including an expansion valve for directing fluid from the condenser to the evaporator and a pump for directing fluid from the condenser to said boiler.
  • a heat pump system comprising:
  • a housing having a dual diameter cylinder including a central relatively large diameter portion and concentric relatively small diameter portions extending axially from the opposite ends of the large diameter portion;
  • a dual diameter free piston including a central relatively large diameter portion received in the large diameter portion of said cylinder and relatively small diameter portions extending from the opposite ends of the relatively large diameter portion into the small diameter portions of said cylinder;
  • an evaporator adapted to effect heat transfer between a working fluid and a secondary fluid
  • a condenser adapted to effect heat transfer between said working fluid and a third fluid
  • a pair of disk valves mounted within said housing adjacent the opposite ends of the small diameter portions of said cylinder for alternately and cyclically directing the high pressure, high temperature working fluid flowing from said boiler to the opposed small diameter portions of said cylinder to reciprocate said free piston therein and means for directing spent working fluid from said small diameter portions of said cylinder means to said condenser;
  • the heat pump system according to claim 4 further including means responsive to the level of working fluid within the boiler for selectively bypassing high pressure, relatively low temperature working fluid flowing from the outlet of said pump to the inlet of said pump.
  • a heat pump system comprising:
  • a free piston including a relatively large diameter portion and concentric relatively small diameter portions extending coaxially from the opposite ends of the large diameter portions;
  • cylinder means surrounding the free piston and including a central relatively large diameter portion for receiving the large diameter portion of said free piston and opposed relatively small diameter portions for receiving the small diameter portions of said piston;
  • said cylinder means forming a hermetic seal which encloses at least said free piston, said disk valves, and said valve rotating means;
  • an evaporator for flow of low pressure, low temperature working fluid flowing from said expansion valve to cool a secondary fluid by heat transfer to said working fluid
  • valve rotating means comprises:
  • an induction motor including a rotor enclosed by said cylinder means
  • the heat pump system according to claim 8 further including means responsive to the pressure within the small diameter portions of said cylinder at the terminus of each reciprocation of the free piston therein for regulating the flow of high pressure, high temperature working fluid into the small diameter portions of said cylinder means.
  • the heat pump system according to claim 10 further including means responsive to the level of working fluid within said boiler for recirculating a portion of the pump output to the inlet thereof.
  • a heat pumping process comprising:
  • the heat pumping processing according to claim 12 further characterized by the step of regulating the rate of fluid flow from the boiler into the opposite ends of the small diameter portions of the free piston assembly in accordance with the pressure of the spent working fluid within the small diameter portions of the free piston assembly at the end of each reciprocation of the free piston.
  • step of directing the high pressure working fluid flowing from the pump through a boiler is further characterized by returning a portion of the pump output to the input thereof in accordance with the level of working fluid within the boiler.
  • a heat pumping process comprising: cooling relatively high pressure, relatively warm working fluid in a condenser;
  • step of rotating disk valves at the opposite ends of the small diameter portion of the free piston assembly is further characterized by maintaining the disk valves in synchronism by means of a rod interconnecting the disk valves and extending through the free piston of the free piston apparatus.
  • a heat pump system comprising:
  • a housing having a dual diameter cylinder including a central relatively large diameter portion and concentric relatively small diameter portions extending axially from the opposite ends of the large diameter portion;
  • a dual diameter free piston including a central relatively large diameter portion received in the large diameter portion of said cylinder and relatively small diameter portions extending from the opposite ends of the relatively large diameter portion into the small diameter portions of said cylinder;
  • an evaporator adapted to effect heat transfer between a working fluid and a secondary fluid
  • a condenser adapted to effect heat transfer between said working fluid and a third fluid

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Abstract

In a heat pump system, a dual diameter, double-acting free piston apparatus is utilized as an expander-compressor. Working fluid is compressed in the large diameter portion of the free piston apparatus and is directed to a condenser. Part of the working fluid flowing from the condenser is directed through an expansion valve and an evaporator, and is then alternately admitted to the opposite ends of the large diameter portion of the free piston apparatus. The remainder of the working fluid flowing from the condenser is directed through a pump and a boiler and is then alternately admitted to the small diameter portions of the free piston apparatus, whereupon the working fluid is expanded to effect actuation of the apparatus. The flow of high temperature, high pressure working fluid into the small diameter portions of the free piston apparatus is controlled by disk valves which also function to direct spent working fluid from the small diameter portions of the free piston apparatus to the condenser. The free piston apparatus further comprises a housing which forms a hermetic seal enclosing all of the reciprocating and rotating components of the system.

Description

United States Patent [1 1 Golds berry HEAT PUMP SYSTEM [75] Inventor: Fred L. Goldsberry, Dallas, Tex.
[73] Assignee: Lone Star Gas Company, Dallas,
Tex.
[22] Filed: Mar. 1, 1973 [21] Appl. No.: 337,131
[52] U.S. Cl 62/115, 62/116, 62/467, 62/498, 62/500, 60/36, 417/396, 417/404 [51] Int. Cl. F25b l/00 [58] Field of Search 62/115, 116, 467,498, 62/500, DIG. 2; 417/396 X, 403, 404 X; 60/24, 36 X [56] References Cited UNITED STATES PATENTS 2,204,040 7/1940 Pierotti et a1. 62/323 X 2,441,632 7/1961 Rogers 62/467 2,637,981 5/1953 Russell 62/501 X 2,986,898 6/1961 Wood, Jr. 417/404 2,986,907 6/1961 Hoop 62/116 x 2,992,636 7/1961 Sampie'tro 91/305 3,137,144 6/1964 Kaufman et a1. 62/141 3,710,586 Maudcin 62/498 X Primary Examiner-William F. ODea Assistant Examiner-Peter D. Ferguson Attorney, Agent, or Firm-Richards, Harris & Medlock [111 3,861,166 [451 Jan. 21 1975 57] ABSTRACT In a heat pump system, a dual diameter, double-acting free piston apparatus is utilized as an expandercompressor. Working fluid is compressed in the large diameter portion of the free piston apparatus and is directed to a condenser. Part of the working fluid flowing from the condenser is directed through an expansion valve and an evaporator, and is then alternately admitted to the opposite ends of the large diameter portion of the free piston apparatus. The remainder of the working fluid flowing from the condenser is directed through a pump and a boiler and is then alternately admitted to the small diameter portions of the free piston apparatus, whereupon-the working fluid is expanded to effect actuation of the apparatus. The flow of high temperature, high pressure working fluid into the small diameter portions of the free piston apparatus is controlled by disk valves which also.
function to direct spent working fluid from the small diameter portions of the free piston apparatus to the condenser. The free piston apparatus further comprises a housing which forms a hermetic seal enclosing all of the reciprocating and rotating components of the system.
19 Claims, 1 Drawing Figure HEAT PUMP SYSTEM BACKGROUND AND SUMMARY OF THE INVENTION This invention relates to heat pump systems, and more particularly to a heat pump system utilizing a dual diameter, double-acting free piston apparatus as an expander-compressor.
Commercially available refrigerators and similar heat pump systems have heretofore usually been either of the compression type or the absorption type. The compression type system typically employs an electric motor to operate a compressor. By this means a refrigerant is forced from the compressor through a condenser, through an expansion valve, through an evaporator and back to the compressor. In the absorption type refrigerator a fuel such as natural gas is utilized to boil a refrigerant out of a carrier liquid. The refrigerant is directed through a condenser and an evaporator and then is recombined with the carrier liquid in an absorber.
Heat pump systems of the compression type utilizing a fuel such as natural gas as the basic energy source have also been provided heretofore. Such systems have employed both turbines and free pistons as expanders for high temperature, high pressure working fluid. One difficulty that has often been experienced in the use of these systems involves the lack of a hermetic seal surrounding the reciprocating and/or rotating components. This permits leakage of the working fluid at various sliding and rotating seals, and thereby necessitates relatively frequent maintenance of the system merely to replenish the working fluid.
The present invention relates to a heat pump system wherein a dual diameter, double-acting free piston apparatus is utilized both as a working fluid expander and as a working fluid compressor. In accordance with the broader aspects of the invention, working fluid is partially compressed in the large diameter portion of the free piston apparatus and is then directed through a condenser. Part of the working fluid flowing from the condenser is directed through an expansion valve and an evaporator, and is then alternately admitted to the opposite ends of the large diameter portion of the free piston apparatus. The remainder of the working fluid flowing from the condenser is directed through a pump and a boiler, and is then alternately admitted to opposed small diameter portions of the free piston apparatus, wherein the working fluid is expanded to effect reciprocation of the free piston. Spent working fluid from the small diameter portions of the free piston apparatus is returned to the condenser.
In accordance with other aspects of the invention, the flow of working fluid through the small diameter portions of the free piston apparatus is controlled by rotating disk valves. The valves are rotated by an induction motor which may also be utilized to drive the pump. The required phase relationship between the disk valves is maintained by a timing rod interconnecting the valves and extending through the free piston.
In accordance with still other aspects of the invention, the free piston apparatus includes a housing defining a dual diameter cylinder which receives the free piston. The housing also encloses the disk valves, the induction motor, and the pump. That is, the housing effects a hermetic seal enclosing all of the working components of the heat pump system. Such a seal is useful in substantially reducing the loss of the working fluid which normally occurs at rotating and sliding seals. This in turn substantially reduces the frequency of maintenance which is necessary in the use of the present invention as compared with prior heat pump systems.
DESCRIPTION OF THE DRAWING A more complete understanding of the invention may be had by referring to the following Detailed Description when taken inconjunction with the accompaning DRAWING, wherein a heat pump system incorporating the invention is schematically illustrated.
DETAILED DESCRIPTION Referring now to the Drawings, a heat pump system 10 incorporating the invention is schematically illustrated. The heat pump system 10 comprises a dual diameter, double-acting free piston apparatus 12 includ ing a housing 14. The housing 14 comprises a dual diameter, double-ended cylinder and includes a central,
relatively large diameter cylindricalportion l6 and opposed relatively small diameter cylindrical portions 18. The small diameter portions 18 are equal in length and are coaxial with the large diameter port-ion 16.
The free piston assembly 12 further includes a free piston 20 which is mounted in the cylinder of the housing 14 for reciprocation with respect thereto. The free piston 20 comprises a dual diameter, double-acting piston and includes a relatively large diameter portion 22 which reciprocates in the large diameter portion of the cylinder and opposed relatively small diameter portions 24 which reciprocate in the small diameter portions of the cylinder. The small diameter portions 24 of the free piston are coaxial with the large diameter portion 22 and are equal in length. The free piston 20 is provided with suitable piston rings 26 adapted for cooperation with the interior walls of the housing 14 to effect sliding seals.
The heat pump system 10 is charged with a suitable working fluid, such as FREON lll, FREON l 12, FREON l 13, etc. Low pressure, relatively warm working fluid is alternatively received in the opposite ends of the large diameter portion 16 of the housing 14 through a line 28 and a pair of suitable check valves 30. Thus, upon reciprocation of the free piston 20, the working fluid is simultaneously partially compressed in one end of the large diameter portion 16 and is simultaneously drawn into the opposite end. The relatively warm, partially compressed working fluid then flows out of the cylinder 14 through a pair of check valves 32 and a line 34.
The arrangement of the inlet and outlet portions relative to the side and end walls of the large diameter portion 16 of the housing 14 comprises an important feature of the invention. That is, since the outlet ports are arranged in the side walls, one of the outlet ports is closed by the free piston 20 at the terminus of each reciprocation thereof. By this means a quantity of working fluid is trapped in the end of the large diameter portion 16, thereby providing the fluid cushion which functions to decelerate the piston. This in turn assures that the terminus of each reciprocation of the free piston 20 will be smooth and that the piston is not forcefully driven into engagement with eitherend of the cylinder l4.
The line 34 extends to a condesner 36. A blower 38 or equivalent apparatus is provided for directing a secondary fluid such as air through the condenser 36, thereby cooling the working fluid by heat transfer to the secondary fluid. The condenser 36 and the blower 38 preferably have sufficient capacity that the working fluid is transformed from the gaseous phase to the liquid phase within the condenser 36. As will be apparent to those skilled in the art, in the case of an air conditioning system, a refrigeration system, or the like, both the free piston apparatus 12 and the condenser 36 will be located outside of a zone to be cooled.
Relatively high pressure, relatively low temperature working fluid in the liquid phase flows from the condenser 36 through a line 40. Part of the working fluid flowing from the condenser 36 is directed through an expansion valve 42. The valve 42 functions to substantially reduce the pressure of, and thereby simultaneously substantially cool the working fluid. The low temperature, low pressure working fluid flowing from the valve 42 is directed through an evaporator 44 wherein the working fluid returns to the gaseous phase.
In the case of an air conditioning system, a refrigeration system, or the like, the evaporator 44 is positioned within or at least in direct communication with the zone to be cooled. A blower 46 or equivalent apparatus directs a secondary fluid such as air through the evaporator 44. By this means heat transfer between the secondary fluid and the working fluid is effected, whereby the secondasry fluid is cooled, and the working fluid is partially heated. Low pressure, relatively warm working fluid flowing from the evaporator 44 is directed to the large diameter portion 16 of the cylinder 14 through the line 28.
The remainder of the liquid phase working fluid flowing from the condenser 36 through the line 40 is directed to a gear pump 48. The pump 48 is driven by an induction motor 50 and functions to substantially pressurized the working fluid flowing therethrough. The high pressure working fluid flowing from the pump 48 is directed through a check valve 51 and a line 52 to a boiler 54. In the case of a refrigerator, an air conditioner, or the like, both the pump and the boiler are located outside of the zone to be cooled.
The boiler 54 is actuated by a gas burner 56 and functions to substantially heat the working fluid. High pressure, high temperature working fluid flows from the boiler 54 in the gaseous phase through a line 57. Working fluid from the line 57 is alternately admitted to the small diameter portions 18 of the cylinder 14 by means of a pair of disk valves 58. Each valve 58 functions to admit high temperature, high pressure working fluid to the adjacent small diameter portion 18 of the cylinder 14 during travel of the free piston 20 away from the valve in question, and to release spent working fluid from the adjacent small diameter portion 18 of the cylinder during travel of the free piston toward the valve in question. Spent working fluid from the small diameter portions 18 of the cylinder 14 passes through a line 60 which extends to the line 34 and hence to the condenser 36.
The disk valves 58 of the free piston assembly 12 are maintained in a predetermined angular phase relationship with respect to each other by a shaft 62 which interconnects the valves. The shaft 62 extends through the free piston 20 along the axis thereof and a passageway of sufficient clearance is provided in the free piston to permit reciprocation of the piston relative to the shaft. The shaft 62 and the disk valves 58 are rotated by the induction motor 50 which drives the gear pump 48. In the event that it is desired to rotate the disk valves 58 at a different speed from that of the gear pump 48, a suitable transmission 64 may be provided.
It will thus be understood that in the operation of the heat pump system 10, the energy of the high temperature, high pressure working fluid flowing from the boiler 54 is utilized to reciprocate the free piston 20 within the housing 14. During the initial portion of each reciprocation, energy from the working fluid is im parted to the free piston. Thereafter, both energy from the working fluid and the momentum of the free piston cause the piston to complete the reciprocation. By this means working fluid is compressed in the large diameter portion 16, and spent working fluid is expelled from the opposite small diameter portion 18. At the terminus of each reciprocation, the outlet port in the large diameter portion 16 is closed by the piston, whereupon trapped working fluid functions to decelerate the piston before it engages the adjacent end of the housing. The piston is then ready for reciprocation in the opposite direction.
The heat pump system 10 further includes a number of components which function to provide control over the operation of the system and which are actuated by a suitable power source (not shown). For example, a pressure switch 65 is provided for actuating a start/stop switch 66 to terminate operation of the system in the event of an inadequate pressure drop across the expansion valve 42. The pressure switch 65 may be of the type manufactured by the Powers Regulator Co. of Skokie, Illinois under Model Number SW1 34-1450 A65. Both the expansion valve 42 and the blower 46 are operated under the control of a thermostat 68 whereby the output of the heat pump system 10 may be regulated.
A pressure responsive switch 70 is provided for monitoring the pressure within each small diameter portion 18 at the terminus of the travel of the small diameter portions of the free piston 20 therein. The switch 70 controls the operation of a throttle valve 72 and thereby regulates the flow of high temperature, high pressure working fluid through the line 57 and into the small diameter portions 18 of the cylinder 14. By this means dissipation of the entire energy of the working fluid entering the small diameter portions of the cylinder during each reciprocation of the free piston is assured, thereby preventing a pop when the disk valves are opened. The switch 70 may be of the type manufactured and sold by Powers Regulator Co. as Model Number SWI 34-1455, and the throttle vavle 72 may be a motor actuated two-way single seat valve of the type manufactured and sold by Powers Regulator Co.
The boiler 54 is provided with a float controlled switch 74 which is responsive to the level of liquid working fluid within the boiler. The switch 74 operates a bypass valve 76 which functions to return at least a portion of the output of the gear pump 48 to the inlet thereof. By this means a predetermined level of liquid working fluid within the boiler 54 is assured. The switch 74 may be of the type supplied by McDonnel & Miller Inc., of Chicago, Illinois under Model Number 150.
The gas burner 56 of the boiler 54 is provided with a pressure actuated gas valve 78. The valve 78 is also responsive to a high temperature limit switch including a temperature responsive member 80 positioned within the boiler 54. By this means operation of the gas burner 56 is terminated in the event that either the pressure or the temperature within the boiler 54 exceeds a predetermined limit. The valve 78 may be of the type manufactured and sold by Honeywell Inc. of Minneapolis, Minnesota as a v58194E Powerpile combination gas control valve.
One of the important features of the heat pump system is the fact that the housing 14 encloses all of the reciprocating and rotating components of the system. That is, the housing 14 hermetically seals the free piston 20, the disk valves 58, the pump 48 and the apparatus for actuating the same. By this means loss of working fluid from the system is completely prevented.
It will of course be appreciated that the heat pump system 10 incorporates certain sliding and rotating seals. However, since all of the working components of the system are enclosed by the housing 14, any flow of working fluid around such seals merely causes the working fluid to enter another portion of the system. While such flow may cause a certain loss of operating efficiency in the system, there is absolutely no'loss of working fluid. This is important in eliminating a problem that has been encountered in the use of prior art heat pump systems, wherein periodic maintenance has been required merely to replenish the working fluid.
The embodiment of the heat pump system 10 illustrated in the Drawing utilizes the same motor 50 to actuate the pump 48 and the disk valves 58. As will be apparent to those skilled in the art, an alternative construction may be provided wherein separate motors are utilized to drive the pump and to rotate the valves. In such cases, the housing 14 may enclose only the motor which actuates the disk valves, and a separate housing may be provided for enclosing the pump and its operating motor. Such an alternative construction does not, however, deviate from the basic concept of providing a hermetic seal extending around all of the reciprocating and rotating components of the heat pump system.
From the foregoing, it will be understood that the present invention comprises a heat pump system utilizing a dual diameter, double-acting free piston apparatus as an expander-compressor. The system is further characterized by the use of a fuel such as natural gas as the basic energy source. A highly advantageous characteristic of the system is that the reciprocating and rotating components thereof are entirely enclosed in a hermetic seal, thereby preventing loss of the working fluid utilized in the system.
Although specific embodiments of the invention have been illustrated in the Drawing and described in the foregoing Detailed Description, it will be understood that the invention is not limited to the embodiments disclosed, but is capable of numerous rearrangements, modifications, and substitutions of parts and elements without departing from the spirit of the invention.
What is claimed is:
1. In combination with a heat pump system wherein a secondary fluid is cooled by contact with an evaporator supplied with working fluid from a condenser, the improvement which comprises:
a boiler adapted to provide the working fluid at a high pressure and temperature:
a housinghaving first and second pairs of opposed chambers with a dual radius piston therein having oppositely directed faces;
structure forming a first fluid path connected from said boiler alternately to apply high pressure gas from said boiler to the oppositely directed faces of said piston in said first opposed chambers in said housing to reciprocate said piston;
structure forming a second path connected from the evaporator alternately to apply low pressure gas to saidsecond pair of opposed chambers to deliver compressed fluid from the evaporator to the conden ser;
valve means within said housing for controlling alternate admission of fluid from said first fluid path to the oppositely directed faces of said piston in said first opposed chambers and directing spent fluid from said chambers ofsaid pistons to the condenser, said valve means comprising rotating disk valves driven by motor means and disposed adjacent the first opposed chambers in said housing with a shaft extending through said piston for maintaining a predetermined angular phase relationship between the valves; and
structure forming a third path connected from the condenser to said boiler for supplying working fluid to said boiler.
2. The system according to claim 1 wherein said housing forms a hermetic seal which encloses said piston and the valve means.
3. The system according to claim 1 further including an expansion valve for directing fluid from the condenser to the evaporator and a pump for directing fluid from the condenser to said boiler.
4. A heat pump system comprising:
a housing having a dual diameter cylinder including a central relatively large diameter portion and concentric relatively small diameter portions extending axially from the opposite ends of the large diameter portion;
a dual diameter free piston including a central relatively large diameter portion received in the large diameter portion of said cylinder and relatively small diameter portions extending from the opposite ends of the relatively large diameter portion into the small diameter portions of said cylinder;
an evaporator adapted to effect heat transfer between a working fluid and a secondary fluid;
means for directing low pressure, relatively warm working fluid flowing from said evaporator into the relatively large diameter portion of said cylinder partially to compress the working fluid upon reciprocation of the free piston;
a condenser adapted to effect heat transfer between said working fluid and a third fluid;
means for directing relatively high pressure, relatively warm working fluid from the large diameter portion of said cylinder to said condenser to cool the working fluid;
an expansion valve;
means for directing part of the relatively high pressure, relatively cool working fluid flowing from said condenser through said expansion valve simultaneously substantially to reduce the pressure and temperature of said working fluid;
means for directing the low temperature, low pressure working fluid from said expansion valve through saidevaporator to cool the second fluid by heat transfer to said working fluid;
a pump;
means for directing the remainder of the relatively cool, relatively high pressure working fluid from said condenser to said pump substantially to increase the pressure of said working fluid;
a boiler;
means for directing the high pressure, relatively low temperature working fluid flowing from said pump to said boiler substantially to heat said working fluid;
a pair of disk valves mounted within said housing adjacent the opposite ends of the small diameter portions of said cylinder for alternately and cyclically directing the high pressure, high temperature working fluid flowing from said boiler to the opposed small diameter portions of said cylinder to reciprocate said free piston therein and means for directing spent working fluid from said small diameter portions of said cylinder means to said condenser; and
means for rotating said disk valves in synchronism to control flow of working fluid alternately through the small diameter portions of said cylinder.
5. The heat pumping system according to claim 4 wherein the disk valves are rotated in synchronism by a shaft extending between the valves and through the free piston.
6. The heat pump system according to claim 5 wherein said cylinder forms a hermetic seal enclosing at least said free piston, said disk valves, and said valve rotating means.
7. The heat pump system according to claim 4 further including means responsive to the level of working fluid within the boiler for selectively bypassing high pressure, relatively low temperature working fluid flowing from the outlet of said pump to the inlet of said pump.
8. A heat pump system comprising:
a free piston including a relatively large diameter portion and concentric relatively small diameter portions extending coaxially from the opposite ends of the large diameter portions;
cylinder means surrounding the free piston and including a central relatively large diameter portion for receiving the large diameter portion of said free piston and opposed relatively small diameter portions for receiving the small diameter portions of said piston;
a pair of disk valves mounted in said cylinder means adjacent to opposite ends of said small diameter portions thereof;
means for rotating said disk valves in synchronism for alternate flow of working fluid into and out of the small diameter portions of said cylinder means to reciprocate said free piston within said cylinder means;
said cylinder means forming a hermetic seal which encloses at least said free piston, said disk valves, and said valve rotating means;
a condenser;
a pump;
means for directing part of the working fluid flowing from said condenser to said pump substantially to pressurize said working fluid;
a boiler;
means for directing at least part of said working fluid flowing from said pump to said boiler substantially to heat said working fluid;
means for directing spent working fluid flowing out of said small diameter portions of said cylinder means under control of said disk valves to the condenser;
an expansion valve;
means for directing the remainder of said working fluid flowing from said condenser through said expansion valve and substantially to reduce the pressure and temperature of said working fluid;
an evaporator for flow of low pressure, low temperature working fluid flowing from said expansion valve to cool a secondary fluid by heat transfer to said working fluid;
means for alternately admitting working fluid flowing from said evaporator intothe opposite ends of the large diameter portion of the cylinder means partially to compress the working fluid; and
means for directing compressed working fluid flowing from the large diameter portion of said cylinder means to said condenser.
9. The heat pump system according to claim 8 wherein the valve rotating means comprises:
an induction motor including a rotor enclosed by said cylinder means; and
a shaft extending through said free piston along the axis thereof for interconnecting said disk valves and thereby maintaining a predetermined angular phase relationship between said valves.
10. The heat pump system according to claim 8 further including means responsive to the pressure within the small diameter portions of said cylinder at the terminus of each reciprocation of the free piston therein for regulating the flow of high pressure, high temperature working fluid into the small diameter portions of said cylinder means.
11. The heat pump system according to claim 10 further including means responsive to the level of working fluid within said boiler for recirculating a portion of the pump output to the inlet thereof.
12. A heat pumping process comprising:
alternately receiving low pressure, relatively warm working fluid from an evaporator in the opposite ends of the large diameter portion of a dual diameter, double-acting free piston assembly and thereby partially compressing the working fluid;
directing the partially compressed working fluid from the large diameter portion of the free piston assembly through a condenser and thereby partially cooling the working fluid; directing a portion of the partially cooled working fluid flowing from the condenser through an expansion valve and thereby simultaneously substantially reducing the pressure of and substantially cooling the working fluid; directing the low pressure, low temperature working fluid flowing from the expansion valve through the evaporator and thereby cooling a secondary fluid;
directing the remainder of the partially cooled working fluid flowing from the condenser through a pump and thereby substantially compressing the working fluid;
directing the high pressure working fluid flowing from the pump through a boiler and thereby substantially heating the working fluid;
alternately admitting the high temperature, high pressure working fluid from the boiler to the opposed small diameter portions of the free piston assembly by means of rotating disk valves located at the opposite ends of the free piston assembly and thereby reciprocating the free piston;
releasing the spent working fluid from the small diameter portions of the free piston through said rotating disk valves; and
directing the spent fluid to the condenser.
13. The heat pumping process according to claim 12 wherein the steps of admitting high temperature, high pressure working fluid to the opposite ends of the small diameter portion of the free piston assembly and directing spent working fluid from the free piston assembly to the condenser are further characterized by simultaneously rotating the disk valves located at the opposite ends of the free piston assembly by means of a rod extending through the free piston and interconnecting the two disk valves.
14. The heat pumping processing according to claim 12 further characterized by the step of regulating the rate of fluid flow from the boiler into the opposite ends of the small diameter portions of the free piston assembly in accordance with the pressure of the spent working fluid within the small diameter portions of the free piston assembly at the end of each reciprocation of the free piston.
15. The heat pumping process according to claim 12 wherein the step of directing the high pressure working fluid flowing from the pump through a boiler is further characterized by returning a portion of the pump output to the input thereof in accordance with the level of working fluid within the boiler.
16. A heat pumping process comprising: cooling relatively high pressure, relatively warm working fluid in a condenser;
substantially reducing the pressure of and thereby substantially cooling part of the relatively high pressure, relatively low temperature working fluid flowing from the condenser in an expansion valve;
partially heating the low temperature, low pressure working fluid flowing from the expansion valve in an evaporator and thereby substantially cooling a secondary fluid;
partially compressing the low pressure, relatively warm working fluid flowing from the evaporator in the large diameter portion of a dual diameter, double-acting free piston apparatus;
directing the partially compressed, relatively warm working fluid from the large diameter portion of the free piston apparatus to the condenser;
substantially pressurizing the remainder of the rela- I tively high pressure, relatively cool working fluid flowing from the condenser in a pump;
substantially heating the high pressure, relatively low temperature working fluid flowing from the pump in a boiler;
rotang disk valves at the opposite ends of the small diameter portion of the free piston assembly and thereby cyclically admitting the high temperature, high pressure working fluid flowing from the boiler to opposed small diameter portions of the free piston apparatus to reciprocate the free piston;
rotating said disk valves at the opposite ends of the small diameter portion of the free piston assembly and releasing spent working fluid through said disk valves from the small diameter portions of the free piston apparatus; and
returning the spent working fluid to the condenser.
17. The heat pumping process according to claim 16 wherein the step of rotating disk valves at the opposite ends of the small diameter portion of the free piston assembly is further characterized by maintaining the disk valves in synchronism by means of a rod interconnecting the disk valves and extending through the free piston of the free piston apparatus.
18. The heat pumping process according to claim 16 wherein the step of admitting high temperature, high pressure working fluid from the boiler to the small diameter portions of the free piston apparatus is further characterized by monitoring the pressure within the small diameter portions of the free piston apparatus at the end of each reciprocation of the free piston and regulating the flow of high temperature, high pressure fluid into the small diameter portions of the free piston assembly in accordance with such pressure.
19. A heat pump system comprising:
a housing having a dual diameter cylinder including a central relatively large diameter portion and concentric relatively small diameter portions extending axially from the opposite ends of the large diameter portion;
a dual diameter free piston including a central relatively large diameter portion received in the large diameter portion of said cylinder and relatively small diameter portions extending from the opposite ends of the relatively large diameter portion into the small diameter portions of said cylinder;
an evaporator adapted to effect heat transfer between a working fluid and a secondary fluid;
means for directing low pressure, relatively warm working fluid flowing from said evaporator into the relatively large diameter portion of said cylinder partially to compress the working fluid upon reciprocation of the free piston;
a condenser adapted to effect heat transfer between said working fluid and a third fluid;
means for directing relatively high pressure, relatively warm working fluid from the large diameter portion of said cylinderto said condenser to cool the working fluid;
an expansion valve;
means for directing part of the relatively high pressure, relatively cool working fluid flowing from said condenser through said expansion valve simultaneously substantially to reduce the pressure and temperature of said working fluid;
means for directing the low temperature, low pressure working fluid from said expansion valve through said evaporator to cool the secondary fluid by heat transfer to said working fluid;
a pump;
means for directing the remainder of the relatively cool, relatively high pressure working fluid from said condenser to said pump substantially to increase the pressure of said working fluid;
a boiler;
means for directing the high pressure, relatively low temperature working fluid flowing from said pump to said boiler substantially to heat said working fluid;
means located within said housing for alternately and cyclically directing the high pressure, high temperature working fluid flowing from said boiler to the opposed small diameter portions of said cylinder to reciprocate said free piston therein;
means responsive to pressures within the small diameter portions of said cylinder at the terminus of each stroke of said free piston for controlling the flow of high pressure, high temperature working fluid into said small diameter portions of said cylinsaid cylinder means to said condenser.

Claims (19)

1. In combination with a heat pump system wherein a secondary fluid is cooled by contact with an evaporator supplied with working fluid from a condenser, the improvement which comprises: a boiler adapted to provide the working fluid at a high pressure and temperature: a housing having first and second pairs of opposed chambers with a dual radius piston therein having oppositely directed faces; structure forming a first fluid path connected from said boiler alternately to apply high pressure gas from said boiler to the oppositely directed faces of said piston in said first opposed chambers in said housing to reciprocate said piston; structure forming a second path connected from the evaporator alternately to apply low pressure gas to said second pair of opposed chambers to deliver compressed fluid from the evaporator to the condenser; valve means within said housing for controlling alternate admission of fluid from said first fluid path to the oppositely directed faces of said piston in said first opposed chambers and directing spent fluid from said chambers of said pistons to the condenser, said valve means comprising rotating disk valves driven by motor means and disposed adjacent the first opposed chambers in said housing with a shaft extending tHrough said piston for maintaining a predetermined angular phase relationship between the valves; and structure forming a third path connected from the condenser to said boiler for supplying working fluid to said boiler.
2. The system according to claim 1 wherein said housing forms a hermetic seal which encloses said piston and the valve means.
3. The system according to claim 1 further including an expansion valve for directing fluid from the condenser to the evaporator and a pump for directing fluid from the condenser to said boiler.
4. A heat pump system comprising: a housing having a dual diameter cylinder including a central relatively large diameter portion and concentric relatively small diameter portions extending axially from the opposite ends of the large diameter portion; a dual diameter free piston including a central relatively large diameter portion received in the large diameter portion of said cylinder and relatively small diameter portions extending from the opposite ends of the relatively large diameter portion into the small diameter portions of said cylinder; an evaporator adapted to effect heat transfer between a working fluid and a secondary fluid; means for directing low pressure, relatively warm working fluid flowing from said evaporator into the relatively large diameter portion of said cylinder partially to compress the working fluid upon reciprocation of the free piston; a condenser adapted to effect heat transfer between said working fluid and a third fluid; means for directing relatively high pressure, relatively warm working fluid from the large diameter portion of said cylinder to said condenser to cool the working fluid; an expansion valve; means for directing part of the relatively high pressure, relatively cool working fluid flowing from said condenser through said expansion valve simultaneously substantially to reduce the pressure and temperature of said working fluid; means for directing the low temperature, low pressure working fluid from said expansion valve through said evaporator to cool the second fluid by heat transfer to said working fluid; a pump; means for directing the remainder of the relatively cool, relatively high pressure working fluid from said condenser to said pump substantially to increase the pressure of said working fluid; a boiler; means for directing the high pressure, relatively low temperature working fluid flowing from said pump to said boiler substantially to heat said working fluid; a pair of disk valves mounted within said housing adjacent the opposite ends of the small diameter portions of said cylinder for alternately and cyclically directing the high pressure, high temperature working fluid flowing from said boiler to the opposed small diameter portions of said cylinder to reciprocate said free piston therein and means for directing spent working fluid from said small diameter portions of said cylinder means to said condenser; and means for rotating said disk valves in synchronism to control flow of working fluid alternately through the small diameter portions of said cylinder.
5. The heat pumping system according to claim 4 wherein the disk valves are rotated in synchronism by a shaft extending between the valves and through the free piston.
6. The heat pump system according to claim 5 wherein said cylinder forms a hermetic seal enclosing at least said free piston, said disk valves, and said valve rotating means.
7. The heat pump system according to claim 4 further including means responsive to the level of working fluid within the boiler for selectively bypassing high pressure, relatively low temperature working fluid flowing from the outlet of said pump to the inlet of said pump.
8. A heat pump system comprising: a free piston including a relatively large diameter portion and concentric relatively small diameter portions extending coaxially from the opposite ends of the larGe diameter portions; cylinder means surrounding the free piston and including a central relatively large diameter portion for receiving the large diameter portion of said free piston and opposed relatively small diameter portions for receiving the small diameter portions of said piston; a pair of disk valves mounted in said cylinder means adjacent to opposite ends of said small diameter portions thereof; means for rotating said disk valves in synchronism for alternate flow of working fluid into and out of the small diameter portions of said cylinder means to reciprocate said free piston within said cylinder means; said cylinder means forming a hermetic seal which encloses at least said free piston, said disk valves, and said valve rotating means; a condenser; a pump; means for directing part of the working fluid flowing from said condenser to said pump substantially to pressurize said working fluid; a boiler; means for directing at least part of said working fluid flowing from said pump to said boiler substantially to heat said working fluid; means for directing spent working fluid flowing out of said small diameter portions of said cylinder means under control of said disk valves to the condenser; an expansion valve; means for directing the remainder of said working fluid flowing from said condenser through said expansion valve and substantially to reduce the pressure and temperature of said working fluid; an evaporator for flow of low pressure, low temperature working fluid flowing from said expansion valve to cool a secondary fluid by heat transfer to said working fluid; means for alternately admitting working fluid flowing from said evaporator into the opposite ends of the large diameter portion of the cylinder means partially to compress the working fluid; and means for directing compressed working fluid flowing from the large diameter portion of said cylinder means to said condenser.
9. The heat pump system according to claim 8 wherein the valve rotating means comprises: an induction motor including a rotor enclosed by said cylinder means; and a shaft extending through said free piston along the axis thereof for interconnecting said disk valves and thereby maintaining a predetermined angular phase relationship between said valves.
10. The heat pump system according to claim 8 further including means responsive to the pressure within the small diameter portions of said cylinder at the terminus of each reciprocation of the free piston therein for regulating the flow of high pressure, high temperature working fluid into the small diameter portions of said cylinder means.
11. The heat pump system according to claim 10 further including means responsive to the level of working fluid within said boiler for recirculating a portion of the pump output to the inlet thereof.
12. A heat pumping process comprising: alternately receiving low pressure, relatively warm working fluid from an evaporator in the opposite ends of the large diameter portion of a dual diameter, double-acting free piston assembly and thereby partially compressing the working fluid; directing the partially compressed working fluid from the large diameter portion of the free piston assembly through a condenser and thereby partially cooling the working fluid; directing a portion of the partially cooled working fluid flowing from the condenser through an expansion valve and thereby simultaneously substantially reducing the pressure of and substantially cooling the working fluid; directing the low pressure, low temperature working fluid flowing from the expansion valve through the evaporator and thereby cooling a secondary fluid; directing the remainder of the partially cooled working fluid flowing from the condenser through a pump and thereby substantially compressing the working fluid; directing the high pressure working fluid flowing from the pump through a boiler and thereby suBstantially heating the working fluid; alternately admitting the high temperature, high pressure working fluid from the boiler to the opposed small diameter portions of the free piston assembly by means of rotating disk valves located at the opposite ends of the free piston assembly and thereby reciprocating the free piston; releasing the spent working fluid from the small diameter portions of the free piston through said rotating disk valves; and directing the spent fluid to the condenser.
13. The heat pumping process according to claim 12 wherein the steps of admitting high temperature, high pressure working fluid to the opposite ends of the small diameter portion of the free piston assembly and directing spent working fluid from the free piston assembly to the condenser are further characterized by simultaneously rotating the disk valves located at the opposite ends of the free piston assembly by means of a rod extending through the free piston and interconnecting the two disk valves.
14. The heat pumping processing according to claim 12 further characterized by the step of regulating the rate of fluid flow from the boiler into the opposite ends of the small diameter portions of the free piston assembly in accordance with the pressure of the spent working fluid within the small diameter portions of the free piston assembly at the end of each reciprocation of the free piston.
15. The heat pumping process according to claim 12 wherein the step of directing the high pressure working fluid flowing from the pump through a boiler is further characterized by returning a portion of the pump output to the input thereof in accordance with the level of working fluid within the boiler.
16. A heat pumping process comprising: cooling relatively high pressure, relatively warm working fluid in a condenser; substantially reducing the pressure of and thereby substantially cooling part of the relatively high pressure, relatively low temperature working fluid flowing from the condenser in an expansion valve; partially heating the low temperature, low pressure working fluid flowing from the expansion valve in an evaporator and thereby substantially cooling a secondary fluid; partially compressing the low pressure, relatively warm working fluid flowing from the evaporator in the large diameter portion of a dual diameter, double-acting free piston apparatus; directing the partially compressed, relatively warm working fluid from the large diameter portion of the free piston apparatus to the condenser; substantially pressurizing the remainder of the relatively high pressure, relatively cool working fluid flowing from the condenser in a pump; substantially heating the high pressure, relatively low temperature working fluid flowing from the pump in a boiler; rotang disk valves at the opposite ends of the small diameter portion of the free piston assembly and thereby cyclically admitting the high temperature, high pressure working fluid flowing from the boiler to opposed small diameter portions of the free piston apparatus to reciprocate the free piston; rotating said disk valves at the opposite ends of the small diameter portion of the free piston assembly and releasing spent working fluid through said disk valves from the small diameter portions of the free piston apparatus; and returning the spent working fluid to the condenser.
17. The heat pumping process according to claim 16 wherein the step of rotating disk valves at the opposite ends of the small diameter portion of the free piston assembly is further characterized by maintaining the disk valves in synchronism by means of a rod interconnecting the disk valves and extending through the free piston of the free piston apparatus.
18. The heat pumping process according to claim 16 wherein the step of admitting high temperature, high pressure working fluid from the boiler to the small diameter portions of the free piston apparatus is further characterIzed by monitoring the pressure within the small diameter portions of the free piston apparatus at the end of each reciprocation of the free piston and regulating the flow of high temperature, high pressure fluid into the small diameter portions of the free piston assembly in accordance with such pressure.
19. A heat pump system comprising: a housing having a dual diameter cylinder including a central relatively large diameter portion and concentric relatively small diameter portions extending axially from the opposite ends of the large diameter portion; a dual diameter free piston including a central relatively large diameter portion received in the large diameter portion of said cylinder and relatively small diameter portions extending from the opposite ends of the relatively large diameter portion into the small diameter portions of said cylinder; an evaporator adapted to effect heat transfer between a working fluid and a secondary fluid; means for directing low pressure, relatively warm working fluid flowing from said evaporator into the relatively large diameter portion of said cylinder partially to compress the working fluid upon reciprocation of the free piston; a condenser adapted to effect heat transfer between said working fluid and a third fluid; means for directing relatively high pressure, relatively warm working fluid from the large diameter portion of said cylinder to said condenser to cool the working fluid; an expansion valve; means for directing part of the relatively high pressure, relatively cool working fluid flowing from said condenser through said expansion valve simultaneously substantially to reduce the pressure and temperature of said working fluid; means for directing the low temperature, low pressure working fluid from said expansion valve through said evaporator to cool the secondary fluid by heat transfer to said working fluid; a pump; means for directing the remainder of the relatively cool, relatively high pressure working fluid from said condenser to said pump substantially to increase the pressure of said working fluid; a boiler; means for directing the high pressure, relatively low temperature working fluid flowing from said pump to said boiler substantially to heat said working fluid; means located within said housing for alternately and cyclically directing the high pressure, high temperature working fluid flowing from said boiler to the opposed small diameter portions of said cylinder to reciprocate said free piston therein; means responsive to pressures within the small diameter portions of said cylinder at the terminus of each stroke of said free piston for controlling the flow of high pressure, high temperature working fluid into said small diameter portions of said cylinder to assure dissipation of the energy of the working fluid during each reciprocation of said free piston; and means located within said housing for directing spent working fluid from said small diameter portions of said cylinder means to said condenser.
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US10001301B2 (en) 2014-11-17 2018-06-19 Brad Daviet Automated, oscillating dual-chambered heat pump, electricity generating, and/or water heating method employing such
US10156203B2 (en) 2009-06-16 2018-12-18 1158988 Bc Ltd. Energy transfer machines

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US3988901A (en) * 1975-02-18 1976-11-02 Scientific-Atlanta, Inc. Dual loop heat pump system
US4304736A (en) * 1980-01-29 1981-12-08 The Coca-Cola Company Method of and apparatus for making and dispensing a carbonated beverage utilizing propellant carbon dioxide gas for carbonating
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US4580414A (en) * 1985-08-15 1986-04-08 Engelhard Friedrick R Refrigeration system
US4779427A (en) * 1988-01-22 1988-10-25 E. Squared Incorporated Heat actuated heat pump
US4917335A (en) * 1988-03-31 1990-04-17 Gt-Devices Apparatus and method for facilitating supersonic motion of bodies through the atmosphere
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US5809784A (en) * 1995-03-03 1998-09-22 Meta Motoren- und Energie-Technik GmbH Method and apparatus for converting radiation power into mechanical power
US5520520A (en) * 1995-03-28 1996-05-28 Nakamoto; Tomijiko Pneumatically operated double acting pump for viscous food stuffs
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US10156203B2 (en) 2009-06-16 2018-12-18 1158988 Bc Ltd. Energy transfer machines
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US9746215B2 (en) * 2011-10-14 2017-08-29 Thermanalysis Engineering Corp. Heat powered reciprocating piston engine
US10001301B2 (en) 2014-11-17 2018-06-19 Brad Daviet Automated, oscillating dual-chambered heat pump, electricity generating, and/or water heating method employing such

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