EP0883784A1 - Pompe a chaleur avec entree d'air surcomprime - Google Patents

Pompe a chaleur avec entree d'air surcomprime

Info

Publication number
EP0883784A1
EP0883784A1 EP97906778A EP97906778A EP0883784A1 EP 0883784 A1 EP0883784 A1 EP 0883784A1 EP 97906778 A EP97906778 A EP 97906778A EP 97906778 A EP97906778 A EP 97906778A EP 0883784 A1 EP0883784 A1 EP 0883784A1
Authority
EP
European Patent Office
Prior art keywords
compressor
economizer
flow
booster
primary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP97906778A
Other languages
German (de)
English (en)
Inventor
David N. Shaw
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0883784A1 publication Critical patent/EP0883784A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders

Definitions

  • This invention relates to air-source heat pumps. More particularly, this invention relates to a new and improved air source heat pump especially suitable for use in normally colder climates.
  • the air-source heat pump system is the most prevalent type of heat pump used in the world today. This is the case whether one is discussing room units, residential central type, ductless splits, or rooftop commercial systems.
  • FIGURE 1 shows a plot of heating requirements vs. outdoor ambient temperature and the heating performance of a 3 Ton Lennox HP 22-41 1 fixed speed scroll compressor heat pump system. As shown in FIGURE 1, the -2-
  • supplemental heating is required.
  • the most prevalent form of supplemental heat used is electric resistance. In other than mild climates, this use of supplemental electric resistance heat puts the air-source heat pump at an economic disadvantage to a consumer as compared with other forms of heating, because of the high cost of electric resistance heating. Electric utilities are also concerned because of the associated high peak power demand during cold weather.
  • FIGURE 2 shows what happens to the specific volume of evaporator generated refrigerant vapor as the evaporating temperature falls. At a 50°F outdoor ambient supporting a 40°F evaporating temperature, the specific volume is about .46 cubic feet per pound of generated vapor whereas at 0 °F outdoor ambient with an evaporating temperature of -25 °F, the specific volume is 1.6 cubic feet per pound of generated vapor.
  • a first embodiment of the present invention is directed to a refrigeration circuit which comprises at least one first stage compressor (sometimes referred to as a booster compressor), at least one second stage compressor (sometimes referred to as a primary compressor), a condenser, an economizer, an evaporator, and conduit means bearing a compressible refrigerant working fluid and connecting the first stage compressor, the second stage compressor, the condenser, the economizer, and the evaporator, in series and in that order, in a closed loop.
  • the conduit means further comprises means for bleeding a portion of the condensed refrigerant from the closed loop downstream of the heating condenser and expanding it within the economizer for highly subcooling the liquid refrigerant within the closed loop being fed to the evaporator.
  • the expanded refrigerant from the economizer is delivered to a point between the outlet of the first stage compressor and the inlet to the second stage compressors.
  • Means are also provided for expanding the highly subcooled high pressure liquid refrigerant downstream of the economizer at the evaporator.
  • the subcooling of the liquid refrigerant in the economizer significantly increases the capacity of the refrigerant to absorb heat in the evaporator.
  • Motors are provided for driving the compressors, and the system includes means for first energizing the primary compressor motor and inhibiting booster operation unless the primary is both running and its inlet pressure has reached a satisfactory low value to enable booster operation.
  • the first stage booster compressor is preferably driven at a variable speed to effect a large variation in flow rate of the refrigerant passing therethrough
  • the second stage primary compressor can be relatively fixed in volume flow handling capacity (i.e., a fixed speed compressor), or it can be a two speed or a variable speed machine.
  • a control system includes a first transducer for sensing outdoor ambient temperature, a second transducer for sensing interstage pressure of the refrigerant circulating in the closed loop for controlling the speed of the first stage booster compressor such that control is achieved for booster speed until the interstage pressure reaches a predetermined value determined from outdoor ambient temperature, and a third transducer for sensing the temperature of the air leaving the condenser.
  • the control system also responds to primary and secondary thermostats to operate the primary and booster compressors.
  • the compressors may be positive displacement machines of any type.
  • the first stage booster compressor may also be a variable speed centrifugal compressor for larger size systems.
  • the booster is a single speed compressor (although a two speed booster could also be used), and the operation of the economizer is modulated to add capacity to the system.
  • the booster is on the low side of the primary compressor.
  • the booster of appropriately chosen size, is brought on line when the outdoor ambient temperature drops sufficiently to allow operation of the booster.
  • the economizer is physically in the system, but operation of the economizer is inhibited initially. Subsequently, when additional system capacity is required, the economizer is operated to supply this additional required capacity.
  • the economizer can be operated all at once, i.e., to its full capacity in an on/off mode to add the full additional capacity to the system in one step; or the economizer can be brought on line in a series of steps infinitely modulated to add incremental capacity to the system as required.
  • the primary compressor is on the low side of the system and the booster compressor is on the high side of the system.
  • the first pressure stage compressor is the primary compressor, and it is a variable speed compressor.
  • the second pressure stage compressor is the booster compressor, and it is either a fixed speed or a two speed compressor In this third embodiment the first pressure stage (primary) compressor operates whenever the system is in operation (i.e., for heating or for cooling).
  • the second compressor (secondary) compressor (i.e., single speed) only operates on the heating cycle, and it is prevented from operating until the outdoor ambient temperature drops sufficiently low to warrant its use.
  • economizer operation could also be modulated to meet system capacity requirements.
  • the primary compressor handles most or all of the cooling cycle. Accordingly, in those embodiments the cooling operation is essentially effected with a single speed machine.
  • the third embodiment has the advantage that most or all of the cooling operation can also be effected with a variable speed compressor. It is to be noted that in all embodiments, the first compressor to be operated is designated as the "primary" compressor, and the second compressor to be operated is designated as the "booster" compressor. This is true, regardless of whether the booster is on the low side of the system (first and second embodiments) or on the high side of the system (third embodiment).
  • FIGURE 1 is a plot of heating requirements versus outdoor ambient temperatures for a typical heat pump system.
  • FIGURE 2 is a plot showing the specific volume of evaporator generated vapor versus actual evaporating temperature in °F.
  • FIGURE 3 is a prior art heat pump system.
  • FIGURE 4 is another prior art heat pump system.
  • FIGURE 5 is a schematic diagram of a closed loop boosted air source heat pump system forming a preferred embodiment of the present invention.
  • FIGURE 5 A shows the system of FIGURE 5 configured for operation as an air conditioning system.
  • FIGURE 6 is a flow chart of the preferred control system for the boosted heat pump system of FIGURE 5.
  • FIGURE 7 is a plot illustrating aspects of the control system.
  • FIGURE 8 is a schematic of an alternative boosted heat pump system in accordance with the present invention.
  • FIGURE 9 is a view similar to FIGURE 5 showing a schematic diagram of a closed loop boosted air source heat pump system in accordance with the second embodiment of this invention.
  • FIGURES 10 and 11 are plots illustrating aspects of operation of the second embodiment of FIGURE 9.
  • FIGURE 12 is a flow chart, similar to FIGURE 6, of a control system for the second embodiment of FIGURE 9.
  • FIGURE 13 is a view similar to FIGURES 5 and 9 showing a schematic diagram of a closed loop boosted air source heat pump system in accordance with a third embodiment of this invention.
  • FIGURE 14 is a partial view of FIGURE 13 showing an alternative valving and isolation system for the third embodiment of FIGURE 13.
  • FIGURES 15a and 15b show two positions of the isolation valve of FIGURE 14 embodiment of this invention.
  • FIGURE 16 shows a schematic of a single shell compression module in accordance with the third embodiment of FIGURE 13.
  • FIGURE 17 is a plot illustrating aspects of operation of the third embodiment of this invention.
  • FIGURE 18 is a flow chart, similar to FIGURES 6 and 12 of a control system hird embodiment of this invention.
  • FIGURE 3 shows a typical prior art heat pump system 10 having an outdoor coil (evaporator) 12, a four way valve 14, a compressor 16, an indoor coil (condenser) 18, and an expansion valve 20.
  • Conduit means 22 connects these components as shown in a closed loop system or cycle.
  • a thermal fluid or refrigerant circulates through the closed loop system.
  • Compressor 16 can be any type of positive displacement machine, and it is typically a reciprocating compressor.
  • energy is picked up in outdoor coil 12, which functions as an evaporator, the thermal level and content are increased by compressor 16, and the energy is transferred by indoor coil 18, which is functioning as a condenser, to the medium to be heated.
  • the system can also function as an air conditioning system, with the functions of evaporator 12 and condenser 18 being reversed.
  • FIGURE 4 shows the prior art heat pump system of U.S. Patent 4,332,144.
  • This heat pump system employs an economizer 21 to improve the performance of the heat pump system.
  • the heat pump system of FIGURE 4 and U.S. Patent 4,332,144 employs only a single compressor, with the economizer bleed line being connected to that single compressor to deliver the bleed fluid at the end of the compressor intake stroke.
  • the present invention differs significantly in that it employs two compressors (primary and booster) in series, with the economizer bleed line being connected to a point between the two compressors for delivery to the intake to the primary compressor.
  • the heat pump system of U.S. Patent No. 4,332,144 requires modification of the compressor to admit the bleed fluid at the end of the intake stroke, whereas the heat pump system of the present invention can employ conventional compressors without any need for modification.
  • U.S. Patent 4,594,858 discloses a refrigeration system having two compressor stages in series and an economizer, with the bleed line of the economizer connected to a point between the two compressor stages. While there are structural similarities between the refrigeration system of U.S. Patent 4,594,858 and the heat pump system of the present invention, the system of U.S. Patent 4,594,858 is limited to a refrigeration system, and it cannot function as a heat pump. The system of U.S. Patent 4,594,858 is dealing with a refrigeration case of essentially constant temperature, and that refrigerated space is itself in an environment of essentially constant temperature, e.g., an air conditioned supermarket. In the refrigeration system of U.S.
  • Patent 4,594,858 the specific volume (or density) of the refrigerant vapor is essentially constant.
  • the heat pump system of the present invention must function in an environment (i.e., the outside ambient air) where the temperature can vary from 100°F or higher to 0°F or lower.
  • the present invention must deal with a specific volume of refrigerant vapor that varies over a wide range of 6: 1 or more.
  • the control system and the operation of the heat pump of the present invention are very different than the refrigeration system of U.S. Patent 4,594,858.
  • the closed loop system includes a first or booster stage compressor 22, a second or high stage primary compressor 24, an indoor coil or condenser 26 which delivers heated air to a space to be heated, an economizer 28, and an outdoor coil or evaporator 30 which, together with conduit means interconnecting these elements in a closed loop circuit, are basic components of the closed loop heat pump system.
  • High stage or primary compressor 24 is normally operating whenever the heat pump system is delivering energy, but booster compressor 22 is operated only when the ambient temperature approaches or falls below the balance point for the primary compressor.
  • Warm output vapor of the primary or second stage compressor 24 is fed to the inlet of indoor coil 26 via conduit segment 32 to warm air (indicated by the arrows) flowing over indoor coil 26 for delivery to the indoor space to be heated.
  • a variable speed fan 27 normally causes the flow of air over indoor coil 20.
  • the warm vapor is, of course, cooled and condensed in indoor coil 26.
  • the outlet of indoor coil 26 delivers the condensed refrigerant to flow via conduit segment 34 and check valve 35 to the economizer 28.
  • a bypass or bleed line 38 permits a portion of the liquid refrigerant to be bled from the primary closed loop circuit and to expand via an expansion valve 40 within economizer 28.
  • this bleed refrigerant within economizer 28 results in significant subcooling of the liquid refrigerant which flows in a closed conduit through economizer 28.
  • This subcooled liquid refrigerant then passes directly to evaporator 30 via conduit segment 42.
  • This highly subcooled liquid refrigerant expands via expansion valve 44 into and within the evaporator 30 to perform the function of absorbing energy from the outside air flowing over outdoor coil 30 (as indicated by the arrows) and vaporizing in evaporator 30.
  • a fixed speed fan 31 delivers the air to flow over outdoor coil 30.
  • the amount of energy absorbed within evaporator 30 is greatly increased because of the highly subcooled refrigerant delivered from economizer 28 to the evaporator.
  • the refrigerant vapor from evaporator 30 then flows via conduit segment 46a, 46b and 46c and check valve 47 to point 52 and via conduit segment 48 to the suction or low side of primary compressor 24 to complete the closed loop circulation in effect when only the primary compressor 24 is operating.
  • the refrigerant bled via line 38 which vaporizes within the economizer to perform the cooling effect in the economizer, passes via conduit segment 50 to point 52 in conduit 48 connected to the inlet of the primary compressor 24.
  • second or high stage compressor 24 there may be two or more high stage compressors, connected in parallel and suitably controlled (and/or two or more booster compressors connected in parallel and suitably controlled).
  • Each of compressors 22 and 24 has its own internal motor, indicated at 23 and 25, respectively, to drive directly each compressor, with at least the motor for booster compressor 22 being a variable speed motor and preferably providing at least a five to one flow range for the refrigerant passing through compressor 22.
  • the motor for primary compressor 25 is of fixed speed.
  • the heat pump system as illustrated allows highly efficient heating to take place utilizing evaporator 30 under all load conditions due to the constant use of an economizer cycle.
  • primary compressor 24 is described as a fixed speed machine, it may be a two speed machine, and it may also be a variable speed machine. At least a two stage primary compressor is preferred in order that the interstage pressure variation remains optimal.
  • the primary or high stage machine which may be a reciprocating compressor, does not normally mechanically unload and thus always operates at its peak efficiency.
  • the booster first stage compressor 22 may be a variable speed reciprocating compressor, although it could be a variable capacity machine of almost any type including such as a variable speed screw compressor, variable speed sliding vane rotary compressor, etc. It will also be possible to use a variable high speed turbo compressor, i.e., centrifugal compressor for the booster. The goal of the system is to achieve the high heating capacity combined with the high heating and cooling efficiency.
  • the heat pump system of the present invention includes a microprocessor control 54, a temperature transducer 56 at outdoor coil 30 to sense the temperature of the outdoor air flowing over outdoor coil 30, a temperature transducer 58 at indoor coil 26 to sense the temperature of air leaving indoor coil 26, a pressure transducer 60 to sense the pressure of the refrigerant at point 52 between the exit from booster compressor 22 and the inlet to primary compressor 24, and an indoor thermostat 62 which senses the temperature in the space to be heated and sends signals to microprocessor 54 when heat is required or when the desired temperature has been attained.
  • Thermostat 62 includes a primary thermostat 62' and a secondary thermostat
  • FIGURE 6 a logic system flow chart is shown for controller 54 and the heat pump system of this invention. Reference will also be made to FIGURE 7, which is a plot illustrating aspects of the control system. If the temperature of space to be heated (e.g., the interior of a house) is at or above the desired temperature, both compressors 22 and 24 are off and there is no heat flow in the system. If the temperature of the space to be heated falls below the temperature set at primary thermostat 62', the thermostat will send a signal to control panel 54 calling for heat, see block A in FIGURE 6. Controller 54 reacts to this signal from primary thermostat 62' by delivering a signal to primary compressor 24 to turn on motor 25 to operate compressor 24 (see block B of FIGURE 6).
  • FIGURE 7 is a plot illustrating aspects of the control system.
  • Compressor 24 will then deliver compressed refrigerant vapor via conduit segment 32 to indoor coil 26 to heat the air flowing into the space to be heated, with the rest of the system functioning as previously described.
  • the controller then continuously looks to see whether primary thermostat 62' is satisfied by the heat delivered to the space to be heated (block C of
  • FIGURE 6 Assuming that the operation of the primary compressor 24 supplies enough heat to satisfy primary thermostat 62', controller 54 delivers a signal to terminate the operation of primary compressor 24 (see block D of FIGURE 6).
  • controller 54 delivers a signal to terminate the operation of primary compressor 24 (see block D of FIGURE 6).
  • primary compressor 24 operates at a constant speed somewhere along line 64 of FIGURE 7, depending on the outdoor ambient temperature, with primary compressor 24 cycling on and off to supply heat as needed.
  • Line 64 is the heating capacity line relating the heating capacity of the system, in BTU's/HR, to outdoor ambient temperature which results with only constant speed compressor 24 in operation.
  • the foregoing control cycle will continue for so long as the primary compressor alone is able to deliver enough energy to satisfy primary thermostat 62'.
  • the design balance line 66 heat required to maintain 70°F inside
  • FIGURE 7 which indicates that no heat is required until outdoor ambient temperature drops to 65 °F.
  • the system will operate on line 64 at a point vertically above the outdoor ambient temperature point, with primary compressor 24 cycling on and off to supply the heat necessary to satisfy thermostat 64'.
  • thermostat 64' is set back to, e.g., 60°F for night time operation, and if the outdoor ambient temperature drops to 50 °F, eventually thermostat 64' will call for heating, and the primary compressor 24 will operate on line 64 at a point vertically above the 50 °F ambient outdoor temperature point until thermostat 64' is satisfied.
  • the design balance line will move left or right and parallel to that shown in FIGURE 7 if the temperature to be maintained is lower or higher than the 70°F of this example.
  • the primary compressor refrigerant suction pressure at point 52 (which is also referred to as the interstage pressure when booster 22 is operating as well) will drop with decreasing temperature of the ambient air. This pressure drop occurs because the boiling point of the refrigerant goes down as the ambient temperature drops. Conversely, this pressure will also rise with rising ambient air temperature when the system is operating on primary compressor 24 alone.
  • This direct relationship between ambient air temperature and the refrigerant suction pressure is used to set (i.e., define) an enabling interstage pressure above which the system will not initiate operation of booster compressor 22.
  • booster compressor 22 avoids unnecessary operation of booster compressor 22 when the ambient temperature is high enough for primary compressor 24 to handle the heating load on its own, even though the primary thermostat has not been satisfied and the secondary thermostat has called for operation of the booster compressor.
  • the pressure at point 52 is, essentially, the pressure at the discharge of outside coil (evaporator) 30, which, in turn, is a function of outdoor ambient temperature.
  • the booster enabling signal can be obtained either as a direct measurement of outdoor ambient temperature or a measurement of a parameter related to outdoor ambient temperature.
  • secondary thermostat 62" sends a signal to controller 54 to call for operation of booster compressor 22 (block E of FIGURE 6).
  • controller 54 first looks at the refrigerant vapor pressure at point 52 between booster compressor 22 and primary compressor 24 as sensed by pressure transducer 60 (block F of FIGURE 6). If this pressure is above the preselected enabling pressure, operation of booster compressor 22 is inhibited until the pressure at point 52 drops to the booster enabling pressure (see block G of FIGURE 6). If operation of booster compressor 22 is inhibited because the pressure at point 52 is above the enabling pressure, only primary compressor 24 operates (along line 64) to supply the necessary heat energy.
  • controller 54 sends a signal to turn on the variable speed motor 23 for booster compressor 22 to operate booster compressor 22 at its minimum permissible speed; and a timer is also started to count a preselected time interval, e.g., 15 minutes.
  • the ambient temperature to achieve booster enabling pressure is chosen to be 42.5 °F, a value which can be changed if desired.
  • the reaching of booster enabling pressure is indicated at block H of FIGURE 6. At this time booster compressor 22 initially operates at constant minimum speed at point B on line 68 of FIGURE 7.
  • line 68 is also a heating capacity line.
  • Line 68 relates the system heating capacity in BTU's per hour, to outdoor ambient temperature when booster 22 is operating at absolute minimum speed. Operation of compressor 22 causes a pressure rise at point 52 which closes check valve 47 so the evaporated refrigerant from outdoor coil 30 then flows directly into booster compressor 22.
  • booster compressor 22 will continue to operate until secondary thermostat 62" is satisfied. Operation of the booster compressor will then be terminated, and the system will return to operation with only primary compressor 24 at point A, as previously described. Assuming, now, that the outdoor ambient temperature has dropped to 27 °F, primary compressor 24 will be operating at a capacity level below that needed for design balance. Therefore, secondary thermostat 62" will eventually call for heat, and that will cause operation of booster compressor 22 on line BG at the point of intersection of the vertical from 27 °F. Since this point is above the design balance line, operation of booster compressor 22 at minimum speed should eventually satisfy secondary thermostat 62".
  • controller 55 is continuously looking to see whether secondary thermostat 62" has been satisfied. If it has, controller 54 will turn off booster compressor 22, and the control cycle will return to block E, with primary compressor 24 continuing to operate on line 64. At this point, the system will then cycle between operation of the primary compressor alone and operation of both the primary and booster compressors.
  • controller 54 After the selected time interval has elapsed, controller 54 looks to see whether secondary thermostat 62" is still calling for heat (block I of FIGURE 6). If, at the end of the selected time interval, secondary thermostat 62" is still calling for heat, then, as indicated at block K of FIGURE 6, controller 54 initiates variable higher speed operation of booster compressor 22 to supply greater heating capacity to the system, with this higher speed being limited by the outdoor ambient temperature between an absolute minimum speed C and an absolute maximum speed D on line 72 which is the maximum allowed heating capacity line for the boosted system. This heating capacity at higher speed operation of the booster compressor is indicated along line 70, to which the system moves from line 68 upon initiation of variable speed operation of booster compressor 22.
  • Line 70 is a predetermined maximum heating capacity line for the boosted system (primary and booster operating) as related to outdoor ambient temperature for variable speed operation of booster compressor 22. If outdoor ambient temperature continues to fall, booster compressor 22 will be allowed to operate at ever increasing speeds to supply heating capacity to the system along line 70 until the maximum speed limit for compressor 22 is reached at point D on the intersection of lines 70 and 72; and the system will then operate along line 79 between points DJ at the maximum booster compressor speed.
  • Line 70 is a heating capacity line relating the system heating capacity in BTU's per hour to outdoor ambient temperatures when booster 22 is operating at absolute maximum speed. Assuming that the ambient outdoor temperature is constant, during the second time interval, booster compressor 22 will operate at a point on of line 70 between points CD or on maximum speed line 72 at a point between points DJ of FIGURE 7 to satisfy the demands of secondary thermostat 62".
  • compressor interstage pressure rises, and this interstage pressure will increase with increasing speed of booster compressor 22.
  • An algorithm in controller 54 relates the permitted or sensed compressor interstage pressure, as sensed by transducer 60, to outdoor ambient temperature. More particularly, set or permitted compressor interstage pressure is made to be inversely proportioned to ambient temperature, so that as the temperature sensed by outdoor coil transducer 62 gets colder, the compressor interstage pressure at point 58 is allowed to go higher. That, in turn, translates to an increased maximum speed for booster compressor 22 to add heat capacity to the system as ambient temperature falls when the system is operating along line 70.
  • controller 54 also looks to see whether the secondary thermostat has been satisfied (block L of FIGURE 6). If so, then controller
  • booster compressor 22 reduces the speed of booster compressor 22 to that speed dictated by the outdoor ambient temperature. Depending on the outdoor ambient temperature, this may reduce the speed of booster 22 to a point on line 74 to an intermediate speed between the maximum booster speed at point H and the minimum booster speed at point G; or the controller may return booster compressor 22 to its absolute minimum speed along line
  • Line 74 is a predetermined minimum heating capacity line for the boosted system (primary and booster operating) as related to outdoor ambient temperature for variable speed operation of booster compressor 22.
  • controller 54 operates to turn on a source of back up heat (e.g., electric resistance heaters) until the secondary thermostat is satisfied, see block N of FIGURE 6.
  • the control cycle is then returned to block K of FIGURE 6. Assuming, now, that the outdoor ambient temperature has dropped to 8 °F, primary compressor will be operating, and booster compressor 22 will be operating at the point of intersection of the vertical from 8°F and line 72 (D-J).
  • booster compressor 22 When the secondary thermostat is satisfied during the second time interval (logic block L), the speed of booster compressor 22 is reduced and the system operates on line 74 (H-G) at the point of intersection of the vertical from 8°F.
  • Line 74 is a predetermined minimum heating capacity line for the boosted system (primary and booster operating) as related to outdoor ambient temperature.
  • Booster compressor 22 then operates at the reduced speed (logic block M) for up to a predetermined time, e.g., 15 minutes, and the logic system returns to block I, where controller 54 looks to see if secondary thermostat 62" is satisfied. If the secondary thermostat is still calling for heat, the logic system continues to loop through steps K, L, M, I.
  • a backup heat source e.g., electrical resistance heat
  • booster compressor 22 continues to operate at maximum speed along with fixed speed operation of primary compressor 24.
  • the control system cycles through steps N, K, L with booster 22 operating at maximum allowable speed until secondary thermostat 62" is satisfied (block L), whereupon the backup heat source is turned off and the control system then again cycles through steps L, M, I, K.
  • the absolute minimum and maximum operating speeds of booster compressor 22 are set and controlled by the design of compressor 22.
  • An algorithm in microprocessor 54 sets and varies the set or permissible interstage pressure in line 48 between the outlet from booster compressor 22 and the inlet to primary compressor 24 as a direct, but inverse, function of ambient air temperature as sensed by sensor 56.
  • the interstage pressure in line 48 increases, and that pressure is sensed by sensor 60 which inputs the sensed pressure level to microprocessor 54. That sensed pressure is then compared to the set or permissible interstage pressure (which is a function of ambient air temperature), and speed of booster compressor 22 is permitted, i.e., caused, to increase above the minimum speed or decrease below the maximum speed until the interstage pressure sensed by sensor 60 equals the permitted interstage pressure determined by microprocessor 54 as a function of ambient air temperature.
  • the algorithm sets the maximum allowable interstage pressure for any given ambient temperature (X°F); and that allowable interstage pressure determines the speed along line CD to which booster compressor 22 will be allowed to increase at that X°F outdoor ambient temperature.
  • X°F ambient temperature
  • the speed of booster compressor 22 will be permitted to increase to a speed commensurate with the point on line 70 vertically aligned with the value X°F.
  • booster compressor 22 is operating at a speed commensurate with a point on line 70, i.e., at a speed between absolute minimum and absolute maximum, or if compressor 22 is operating at maximum speed commensurate with a point on line 72, and if the heating requirement, as determined by secondary thermostat 62", is satisfied, the speed of booster compressor 22 will, depending on outdoor ambient temperature, be reduced either to absolute minimum booster speed commensurate with a point on line 68, or to an intermediate speed between absolute maximum and absolute minimum commensurate with a point on line 74.
  • transducer 58 senses the temperature of the air coming off indoor coil 26. If the temperature of that air falls below a predetermined level, e.g.
  • controller 54 will reduce the speed of fan 27 (down to a predetermined minimum) to reduce the flow of air over indoor coil 26. Conversely, if the temperature of the air coming off indoor coil 26 rises above the predetermined level, controller 54 will increase the speed of fan 27 to increase the flow of air over indoor coil 26 (up to a predetermined maximum). This will have the effect of avoiding either cool or hot drafts in the space to be heated.
  • the control system of the present invention functions to increase the intake (or suction) to primary compressor 24 in a linear manner as the difference between outdoor ambient temperature and the controlled environment temperature increases, with the result being a linear increase in delivered heat.
  • the pressure between booster compressor 22 and primary compressor 24, which is a function of the power input to booster compressor 22, is related to ambient outdoor temperature and is used as a control parameter.
  • compressor interstage pressure is not the only control parameter that can be used.
  • any parameter of booster compressor operation related to power input to the booster can be used; and the ambient outdoor temperature is sued to control the permissible level of the chosen parameter.
  • outdoor ambient temperature is used to set the permissible interstage pressure, which increases as power input to the booster compressor increases.
  • the sensed outdoor ambient temperature can be used to set the permissible RPM of or kilowatt input to booster compressor 22, both of these parameters being related to power input to the booster and increasing as power input to the booster increases.
  • booster RPM or booster kilowatt input as a control parameter is that the booster compressor drive usually includes sensors for both of these parameters. If a parameter such as booster RPM or booster kilowatt input is used, the outdoor ambient temperature can be used directly to set the booster enabling point. The control system would function to set permissible RPM or kilowatt input as an inverse function of ambient outdoor temperature, and the set parameter would be sensed to control booster compressor speed.
  • variable speed booster compressor 22 While a system with a variable speed booster compressor 22 and a fixed speed primary compressor has been described, other combinations of machines can be employed as long as the booster compressor is variable speed or some variable capacity combination, etc.
  • the described system having a fixed speed primary compressor and a variable speed booster compressor may be the least expensive from a component cost standpoint.
  • a system having a two speed primary compressor and a variable speed booster compressor may provide the ideal balance between component cost and operating efficiency.
  • a system having both a variable speed primary compressor and a variable speed booster may be the most efficient from an operating standpoint, but may have a higher component cost.
  • FIGURE 5 A a heat pump may also be operated a an air conditioner. This is illustrated in FIGURE 5 A.
  • the flow of refrigerant is reversed (as indicated by the arrows), and the refrigerant flows through check valve 76 and through expansion valve 78.
  • 4 way valve 80 is positioned to effect flow as shown in FIGURE 5A to reverse the direction of refrigerant flow relative to that in the heat pump system of FIGURE 5, except that the flow of refrigerant to or around booster compressor 22 and the primary compressor
  • FIGURE 8 a self contained embodiment of the heat pump of the present invention is shown.
  • self contained it is meant that the entire heat exchange system can be contained in a single enclosure 82, which could be located outside the building to be heated. Alternatively, this self contained system can be located inside the building to be heated, with a protected flow of air (i.e., protected from snow, rain, sleet, etc.) delivered to the system for conditioning.
  • a protected flow of air i.e., protected from snow, rain, sleet, etc.
  • the self contained embodiment of FIGURE 8 has a heat exchanger 26', preferably a brazed plate heat exchanger, instead of indoor coil 26, and a closed fluid loop 84 flows through this heat exchanger and then flows to and through one or more exchanger(s) 86 in the space(s) 88 to be heated.
  • the fluid is circulated in closed loop 84 by a pump 90, and the fluid circulating in closed loop 84 is preferably nontoxic propylene glycol.
  • the control system for the embodiment of FIGURE 8 is the same as that for the embodiment of FIGURE 5, except that (1) temperature transducer 58 is eliminated, and a thermostat 80, which includes a primary thermostat 80' and a secondary thermostat 80", is connected to sense the temperature of the fluid in the loop 84 at a point just downstream of condenser 26'.
  • Microprocessor 54 will respond to inputs from primary thermostat 80', secondary thermostat 80", temperature sensor 56 and pressure sensor 60 to operate primary compressor 24 and booster compressor 22 in the same way that the control system of FIGURE 5 responds to the inputs from primary thermostat 62', secondary thermostat 62", temperature sensor 56 and pressure sensor 60.
  • the space to be heated may be divided into parts 88a-88f, such as individual rooms, with each part having its separately controlled heat exchanger 86a- 86f connected in parallel.
  • Flow of the fluid through individual heat exchangers 86a-86f is controlled, e.g., by a solenoid operated valve 92 in each parallel flow path, with each solenoid valve being operated by a thermostat control in each separate room.
  • Other branch control devices such as variable speed fans, could also be used to control the heat delivered to each room.
  • the thermostat may include a selector switch to select heating or cooling operation for the system or to turn the system off. Selection of the heating mode will position four way valve 80 to flow the refrigerant as shown and discussed for the embodiments of FIGURES 5 and 8; selection of the cooling mode will position four way valve 80 to reverse the direction of refrigerant flow through coils 26 and 30.
  • FIGURES 9-12 a second embodiment of the present invention is shown. Parts of the system of the embodiment of FIGURES 9-12 which are the same as the embodiment of FIGURE 5 are numbered as in FIGURE 5.
  • primary compressor 25 is a single speed compressor
  • booster compressor 22a is either a single speed compressor or a two speed compressor.
  • Valve 40a is an electrically controlled expansion valve (EEV) through which the flow is controlled (either full
  • Valves 44a and 78a are also EEVs, the flow through which may also be modulated by signals from microprocessor 54. Valve 44a would be modulated on the heating cycle, while valve 78a would be modulated during the cooling cycle. Except as set forth in this paragraph, the physical components of the second embodiment of this invention are the same as the physical components of the first embodiment of FIGURE 5.
  • FIGURE 12 the control system for the second embodiment is shown.
  • System capacity is monitored and controlled in block K (rather than booster speed as in FIGURE 6), and in block M, booster speed goes to minimum and/or the economizer is operated "off/on" or modulated to the same level therebetween.
  • primary compressor 24 initially operates alone to meet system demand, and operation of booster 22a is prohibited until a booster enabling signal (either pressure or temperature) is reached (as described with respect to the embodiment of FIGURE 5). Operation of economizer 28 is inhibited by EEV 40a being in its full off position.
  • Booster compressor 22a is operated when called for by secondary thermostat 62" and when booster enabling pressure or temperature is reached. Assuming a single speed booster compressor, operation of the booster compressor 62a will result in a step increase in system heating capacity. If the secondary thermostat is satisfied, the operation of booster compressor 22a is terminated. If the secondary thermostat is not satisfied within a predetermined period of time (e.g., 15 minutes), then a signal from microprocessor 54 to EEV 40a opens EEV 40a to permit bleed flow through line 38 to operate the economizer, and the bleed fluid flows from economizer 28 via line 50 to interstage point 52. As previously described with respect to the embodiment of FIGURE 5, the operation of the economizer increases the heating capacity of the system.
  • a predetermined period of time e.g. 15 minutes
  • FIGURE 10 shows a plot illustrating operation of the second embodiment of this invention with a single speed booster and an "on/off' EEV valve 40a for operating the economizer 28.
  • Line 100 is the design balance line of heat (BTU/hr) required to maintain a selected temperature, e.g., 70°F, in the space to be heated.
  • BTU/hr design balance line of heat
  • the control system of FIGURE 12 operates the same as the control system of FIGURE 6.
  • microprocessor 54 delivers a signal to turn on motor 25 to operate primary compressor 24 (block B of FIGURE 12).
  • Primary compressor 24 then operates along line 102 of FIGURE 0 to deliver heat to the space to be heated (for outdoor ambient temperatures ranging, e.g., from 65 °F to 45 °F as shown in FIGURE 10).
  • the control system operates according to blocks A, B, C and D of FIGURE 12 to cycle the primary compressor off and on as required to satisfy primary thermostat 62'.
  • EEV 40a is fully closed so that no bleed line fluid is delivered for expansion and subcooling in economizer 28. That is, economizer 28 is not functioning, and all fluid in line 34 flows through economizer 28 to line 42 and to evaporator 30 without subcooling in economizer 28.
  • EEV 44a is open as necessary to expand or initiate flashing of the fluid delivered to the evaporator and EEV 78a is bypassed by check valve 35.
  • controller 54 will check pressure as sensed by pressure transducer 60 to make sure the booster enabling pressure is reached (commensurate with a sufficiently low outdoor ambient temperature) before permitting operation of booster compressor 22a. See blocks E, F, G, H of FIGURE 12. Also, in this second embodiment, controller 54 may respond to outdoor ambient temperature as sensed by sensor 56 to inhibit operation of booster compressor 22a until outdoor ambient temperature drops to a predetermined value, which is chosen at 45 °F in the illustration.
  • FIGURE 10 illustrates a situation where operation of booster 22a is initiated at an outdoor ambient temperature of 45 °F.
  • the booster compressor and the primary compressor then operate together to supply heat along line 104 of FIGURE 10.
  • the control system of FIGURE 12 then operates through blocks H, I and J, and back through blocks E, F, G, H, as long as the combined operation of the booster compressor and the primary compressor meets the heating requirements.
  • controller 54 responds to outdoor ambient temperature as sensed by sensor 56 to inhibit operation of economizer 28 until outdoor ambient temperature drops to a predetermined economizer enabling value, which is chosen at 35 °F in the illustration.
  • FIGURE 10 illustrates a situation where secondary thermostat 62" is not satisfied at an outdoor ambient temperature of 35 °F. At that point, controller 54 sends a signal to fully open EEV 40a to bring operation of economizer 28 on line.
  • EEV 40a which is two position, i.e., fully off or fully on.
  • EEV 40a could be modulated to various positions between full closed and full open, and that would result in a range of partial to full operation of economizer 28. This would result in a series of operating lines 106a, 106b, etc. between lines 104 and 106 of FIGURE 10.
  • EEV valve 40a could be modulated to one or more less than fully open positions to reduce fluid flow to evaporator 30 to provide a further degree of control to the system before discontinuing operation of booster compressor 22a.
  • valve 78a can be modulated to one or more positions less than full open so as to provide improved humidity control on humid days even when outdoor ambient temperature is not very high.
  • booster compressor 22a can be a two speed compressor.
  • FIGURE 1 1 shows an operating cycle for this modification.
  • Line 102 represents operation of the system with one speed primary compressor alone. If the outdoor ambient temperature drops to 45 °F, the booster is enabled and operated at its low speed.
  • Line 104 represents operation of the system with the one speed primary compressor and the booster compressor at low speed.
  • EEV 40a which has been fully closed up to this point, is fully opened to bring economizer 28 fully on line. The system then operates to deliver heat along line 108 with operation of the primary compressor, the booster compressor at low speed and the economizer operating.
  • booster compressor 22a is operated at its high speed level and EEV 40a is closed to terminate operation of the economizer 28.
  • the system then operates the deliver heat along line 1 10 with operation of the primary compressor and the booster at high speed.
  • EEV valve 40a is again opened to bring economizer 28 fully on line.
  • the system then operates to deliver heat along line 1 12 with operation of the primary compressor, the booster compressor at high speed and the economizer.
  • the flow chart of FIGURE 12 would be appropriately modified to operate the system as per FIGURE 11.
  • EEV 40a and economizer 28 and EEV valve 44a can be modulated at intermediate positions between full open and full closed to provide finer degrees of control of system heating capacity.
  • the second embodiment of this invention may have an initial lower cost than the first embodiment because the second embodiment does not incur the cost of a variable speed booster compressor motor. As discussed above, the second embodiment relies wholly or primarily on step or modulated operation of the system economizer to provide desired increments of system capacity control.
  • the second embodiment of this invention provides for step or modulated increases in heating capacity by control of the system economizer.
  • the primary compressor is on the low side of the system and the booster compressor is on the high side of the system. That is, the primary compressor is upstream of the booster and the booster compressor is downstream of the primary compressor.
  • the previous embodiments of this invention have discussed a system in which the primary compressor is a fixed speed compressor. Since the primary compressor alone handles most, if not all, of the cooling cycle, variable speed cooling is not realized with these previous embodiments unless a variable speed primary is used. That could significantly increase the cost of the previous embodiments relative to the prior art, especially as regards the first embodiment which also discloses the use of a variable speed booster compressor. Thus, the previous embodiments achieve greatly improved heating performance relative to the prior art but cooling performance was essentially the same as in the prior art (except that better humidity control may be realized in the cooling cycle).
  • the third embodiment of this invention achieves both variable speed cooling and variable speed boosted heating with one variable speed compressor and preferably one fixed speed compressor.
  • the primary compressor is the low side or first stage compressor.
  • the booster compressor is the high stage or second stage compressor, and it is a single speed or two speed compressor.
  • the primary compressor operates at variable speeds for both heating and cooling.
  • the booster compressor if one speed, will operate only on the heating cycle; and booster compressor operation on the heating cycle is prevented unless the outdoor ambient temperature drops sufficiently low to warrant operation of the booster.
  • the variable speed drive for the primary compressor must be capable of handling the maximum load cooling cycle requirement; and the maximum torque requirement also rises since the maximum load cooling requirement is handled by the primary compressor at a relatively low RPM. Both factors will increase the size and cost of the variable speed drive motor for the primary compressor. If a two speed booster is employed, it can operate at low speed for cooling and at either speed for heating. This will reduce the size requirement for the primary compressor motor and drive; but it incurs the cost of a two speed motor/drive for the booster compressor.
  • the booster compressor Since the booster compressor is now on the high pressure side of the refrigerant system, it now becomes necessary to isolate the booster compressor from primary compressor discharge pressure when the booster is not operating. This is necessary because it is unacceptable to have the booster compressor exposed to refrigerant system high side pressure continuously when the booster is not operating. If the booster were continuously exposed to primary compressor high side pressure, significant refrigerant charge could dissolve in the lubricant sump of the booster compressor since refrigerants and lubricants are usually very miscible in their liquid states.
  • the booster compressor will likely be equipped with a single phase induction type motor, which is not known for high starting torque capability. Because of that, and also because the primary compressor will be operating whenever booster operation is initiated, it is also necessary to ensure that the high side booster can be started in an unloaded state.
  • FIGURE 13 a schematic is shown of the third embodiment of this invention.
  • This embodiment differs from the first two embodiments in that primary compressor 24b is on the low side of the system, i.e., upstream of booster compressor
  • booster compressor 22b is on the high side of the system, i.e., downstream of primary compressor 24b.
  • Primary compressor 24b is a variable speed compressor
  • booster compressor 22b is either a fixed or two speed compressor.
  • the embodiment of FIGURE 13 also differs from the previous embodiments in that: pressure transducer 60 is omitted, and the booster enabling signal is obtained directly from outdoor ambient temperature sensor 56; check valves E and F are incorporated in the system (although check valve F could be equated to check valve 47 of FIGURES 5 and 9), check valve F being in a bypass line around booster compressor 22b and check valve E being in a discharge line downstream of booster compressor 22b; normally closed solenoid valve A is in the line between the discharge from primary compressor 24b and positioned as shown; normally open solenoid valve D is in a return line from the discharge of booster compressor 22b to the inlet of primary; and normally open solenoid valve G is in a bypass line from the discharge line from the economizer to the inlet of primary compressor 24b. Except as set
  • fluid from evaporator 30 will flow to primary compressor 24b and the compressed discharge from primary compressor 24b will be bypassed around booster compressor 22b via check valve F to flow to condenser 26.
  • normally closed valve A prevents flow from the discharge of primary compressor 24b to the inlet to booster compressor 22b.
  • the main fluid from condenser 26 is delivered through economizer back to evaporator 30. Part of the fluid from condenser 26 is bled through expansion valve 40 to subcool the main fluid flow through the economizer.
  • the expanded or flashed bleed fluid from economizer 28 flows through normally open solenoid valve G to the inlet to primary compressor 24b.
  • booster compressor 22b off it is technically unacceptable to have booster compressor 22b constantly exposed to refrigerant system discharge pressure from primary compressor 24b. Accordingly, if booster compressor 22b is not operating it must be isolated from the discharge from primary compressor 24b. Also, booster compressor 22b should be able to be started unloaded.
  • controller 54 varies the speed of primary compressor from minimum speed line 120 along variable speed line 122 of FIGURE 17 as outdoor ambient temperature drops to increase system heating capacity. This phase of operation is indicated at blocks A-D of FIGURE 18; and it will continue as long as secondary thermostat 62" does not call for more heat capacity from the system.
  • booster compressor 22b operation of booster compressor 22b is inhibited by controller 54 until controller 54 receives a signal from outdoor ambient temperature sensor 56 indicating that a booster enabling temperature has been reached, which is chosen at 37 °F in the example illustrated in FIGURE 17.
  • a booster enabling pressure could be sensed at the entrance to primary compressor 24b.
  • controller 54 Upon receipt of a signal from secondary thermostat 66" calling for more heat, controller 54 will (I ) send a signal to the drive for primary compressor to reduce the speed of primary compressor 24b to its lowest setting and (2) send a signal to the drive for booster compressor 22b to initiate operation of booster compressor 22b.
  • controller 54 will also deliver signals to open normally closed solenoid valve A and to close normally open solenoid valves D and G.
  • booster compressor 22b The initiation of operation of booster compressor 22b is indicated at blocks E, F, G and H of FIGURE 18. This, of course, adds the heating capacity of the booster compressor to the system. At this time, the system will operate along line 124 of
  • FIGURE 17 with controller 54 increasing the speed of primary compressor 24b to increase system heating capacity as outdoor ambient temperature drops.
  • controller 56 will increase the speed of primary compressor 24b to the maximum allowable speed (maximum system capacity, block K of FIGURE 18), and the system will operate along liens 124 and 126 and 128 of
  • FIGURE 17 for a set period of time, e.g., 30 minutes (block L of FIGURE 18). If the secondary thermostat is not satisfied after the set period of time, the backup heat will be turned on (block N of FIGURE 18) and the control system will recycle to block K when the secondary thermostat has been satisfied. If, however, the secondary thermostat has been satisfied (block L of FIGURE 18), system capacity will be reduced for 15 minutes (block M of FIGURE 18) by reducing the speed of primary compressor 24b either along line 130 to line 132 of FIGURE 17 or by going from any point on lines 124, 126, or 128 to line 132, and the control system will recycle to block I.
  • block M of FIGURE 18 system capacity will be reduced for 15 minutes (block M of FIGURE 18) by reducing the speed of primary compressor 24b either along line 130 to line 132 of FIGURE 17 or by going from any point on lines 124, 126, or 128 to line 132, and the control system will recycle to block I.
  • FIGURE 14 there is shown a modified portion of FIGURE 13 enclosed within the dashed line of FIGURE 13.
  • the modification involves the use of an isolation valve A instead of the solenoid valves A and G of FIGURE 13.
  • the details of isolation valve A are also shown in FIGURE 15a, where booster 22b is off and in FIGURE 15b where booster 22b is on.
  • isolation valve A is indicated generally at 150.
  • Valve 150 has a spool piston 152 which is loaded to the right to a first (booster off) position by a spring 154 (see FIGURE 15b).
  • chamber 156 on the left side of valve 150 is connected by line 158 to system low side pressure, i.e., to pressure at or upstream of the inlet to primary compressor 24b.
  • the space 160 at the right end of valve 150 is also connected to system low side pressure by line 162, normally open solenoid valve D and line 164.
  • solenoid valve D is closed. This results in chamber 160 on the right side of valve 150 being connected by lines 162 and 170 to the discharge side of booster 22b. This high pressure in chamber
  • isolation valve 150 (valve A of FIGURE 13) isolates booster compressor from the discharge from the primary compressor, so booster compressor 22b is unloaded when not operating. However, when operation of booster compressor 22b is initiated, valve 150 functions to connect the discharge from primary compressor 24b to the inlet of high side booster compressor 22b.
  • solenoid valve D remains open until some time after operation of booster compressor 22b is initiated. Valve D is closed only when booster compressor reaches or approaches operating speed, thus ensuring an unloaded start for the booster compressor.
  • the isolation valve 150 of FIGURES 14 and 15 may be preferred to the solenoid valves F and G of FIGURE 13, since relatively large, and therefore expensive, solenoid valves might be required.
  • variable speed primary/high side booster configuration of the third embodiment is contained within a single shell hermetically sealed compression module.
  • primary compressor 24b and booster compressor 22b are housed within a hermetically sealed casing or shell 180.
  • the primary and booster compressors share a common oil sump.
  • economizer vapor flow from line 168 flows through and around the drive motor of primary compressor 24b to cool the drive motor. After cooling the primary compressor drive motor, this economizer vapor flows into the interior of casing 180 and then flows through booster 22b and then through normally open valve D to join the primary compressor suction flow.
  • the discharge flow from primary compressor 24b flows through check valve F and conduit 32 directly to condenser 26.
  • Valve 150 is in the FIGURE 15b position so primary compressor discharge flow is dead ended in the valve and cannot flow into the interior of casing 180.
  • economizer 28 is normally fully operational. However, this third embodiment could, if desired, be configured and controlled with off/on or fully modulated operation of the economizer. Also, although booster compressor 22b has been described as a one speed compressor, it could also be a two speed compressor to increase the capacity of the system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un système de pompe à chaleur avec entrée d'air surcomprimé, comportant un compresseur primaire (24), un surcompresseur (22) et un économiseur (28). Après activation du système de pompe à chaleur, le compresseur primaire (24) est mis en fonctionnement. Quand il ne suffit pas à la demande, le surcompresseur (22) est activé, mais uniquement après réception d'un signal permettant son fonctionnement. Le surcompresseur (22) est de préférence un compresseur à vitesse variable, dont la vitesse est commandée de façon à être à ou entre une vitesse minimum absolue et une vitesse maximum absolue. Il peut être disposé sur le côté bas ou le côté haut du compresseur primaire (24). Le fonctionnement de l'économiseur (28) peut être modulé de façon à répondre aux besoins du système.
EP97906778A 1996-02-27 1997-02-26 Pompe a chaleur avec entree d'air surcomprime Withdrawn EP0883784A1 (fr)

Applications Claiming Priority (3)

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US60770796A 1996-02-27 1996-02-27
US607707 1996-02-27
PCT/US1997/003021 WO1997032168A1 (fr) 1996-02-27 1997-02-26 Pompe a chaleur avec entree d'air surcomprime

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US6276148B1 (en) 2000-02-16 2001-08-21 David N. Shaw Boosted air source heat pump
US6931871B2 (en) * 2003-08-27 2005-08-23 Shaw Engineering Associates, Llc Boosted air source heat pump
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AU2137997A (en) 1997-09-16
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