Heat pump refrigerant charge control system

Claim 2

An improved refrigerant charge control system for a heat pump used to temperature condition an indoor zone under variable load conditions, said heat pump having a refrigerant circuit including indoor and outdoor heat exchange coils, a refrigerant compressor, and a switchover valve adapted to reverse the flow of refrigerant through the refrigerant circuit so that the heat pump may be selectively operated in either a heating mode or a cooling mode; the circuit further including a first refrigerant flow line interconnecting one end of each of the heat exchange coils via the compressor and the switchover valve, the first flow line having suction and discharge line sections, and a second refrigerant flow line directly interconnecting the other ends of the heat exchange coils, the improvement comprising: first and second controllable expansion valves in the second refrigerant flow line; a refrigerant charge receiver, the interior of which is in thermal communication with said suction line section; a third refrigerant flow line including a controllable charge control valve connecting said charge receiver to the second refrigerant line at a point intermediate said first and second controllable expansion valves; means for sensing refrigerant temperature and pressure at predetermined points in the refrigerant circuit; and control means responsive to said sensed temperatures and pressures for controlling operation of said valves to provide bidirectonal flow of refrigerant into and out of the refrigerant circuit at said intermediate point to adjust the amount of refrigerant charge in the refrigerant circuit for efficient operation of the system in each of the heating and cooling modes, as the temperature conditioning load on the heat pump changes.

Claim 3

The control system of claim 1 in which said sensing means includes a pressure sensor in at least one of the suction and discharge line sections and a temperature sensor at the outlet of at least one of the heat exchange coils; and said control means includes means for determining, from said pressure sensor and said temperature sensor, superheat temperature of the refrigerant vapor at the outlet of the respective heat exchange coil.

Claim 4

The control system of claim 1 in which said sensing means includes a pressure sensor in each of the suction and discharge line sections and a temperature sensor at each end of both heat exchange coils; and the control means includes means for determining, from said pressure and temperature sensors, the superheat temperature of refrigerant vapor at the outlet of the heat exchange coil operating as an evaporator and the subcool temperature of the refrigerant liquid at the outlet of the heat exchange coil operating as a condenser, and for controlling the operation of said valves in response to the determind superheat and subcool temperatures.

Claim 5

The control system of claim 3 in which said control means includes means operative at shutdown of the compressor for isolating the majority of refrigerant charge in said charge receiver during an off cycle by initiating the charge control valve just prior to shutdown to transfer refrigerant charge from the circuit into the receiver, and by closing at least the charge control valve after shutdown to hold the stored charge out of the circuit.

Claim 6

The control system of claim 4 in which said control means further includes means for closing said first and second controllable expansion valves after shutdown to minimize migration of any remaining refrigerant charge in the circuit to the compressor during the off cycle.

Claim 7

The control system of claim 5 in which said control means includes means operative during compressor start-up for opening both expansion valves just prior to start-up to minimize pressure differential across the compressor and, upon start-up of the compressor, for closing the controllable expansion valve nearest the heat exchange coil serving as the condenser and opening the charge control valve to inject refrigerant into the circuit.

Claim 8

The control system of claim 6 in which said control means includes means, effective upon the heat pump entering a defrost cycle, initially for withdrawing refrigerant charge from the circuit until the switchover valve is actuated to reverse the refrigerant flow in the circuit and for adding refrigerant charge back to the circuit after the flow is reversed, to achieve a desired system capacity level whereby adverse pressure transients across the compressor are minimized, increased assurance of switching of the switchover valve is realized by maintaining minimal pressure difference across the switchover valve and large surges of refrigerant liquid into the compressor at the time the system is reversed for defrost are effectively eliminated.

Claim 9

The control system of claim 1 in which said control means includes means operative at shutdown of the compressor for isolating the majority of refrigerant charge in said charge receiver during an off cycle by initiating the charge control valve just prior to shutdown to transfer refrigerant charge from the circuit into the receiver, and by closing at least the charge control valve after shutdown to hold the stored charge out of the circuit.

Claim 10

The control system of claim 8 in which said control means further includes means for closing said first and second controllable expansion valves after shutdown to minimize migration of any remaining refrigerant charge in the circuit to the compressor during the off cycle.

Claim 11

The control system of claim 1 in which said control means includes means operative during compressor start-up for opening both expansion valves just prior to start-up to minimize pressure differential across the compressor and, upon start-up of the compressor, for closing the controllable expansion valve nearest the heat exchange coil serving as the condenser and opening the charge control valve to inject refrigerant into the circuit.

Claim 12

The control system of claim 1 in which said control means includes means, effective upon the heat pump entering a defrost cycle, initially for withdrawing refrigerant charge from the circuit until the switchover valve is actuated to reverse the refrigerant flow in the circuit and for adding refrigerant charge back to the circuit after the flow is reversed, to achieve a desired system capacity level whereby adverse pressure transients across the compressor are minimized, increased assurance of switching of the switchover valve is realized by maintaining minimal pressure difference across the switchover valve and large surges of refrigerant liquid into the compressor at the time the system is reversed for defrost are effectively eliminated.

Claim 13

An improved refrigerant charge control system for a heat pump used to temperature condition an indoor zone under the variable load conditions, said heat pump having a refrigerant circuit including indoor and outdoor heat exchange coils, a refrigerant compressor, and a switchover valve adapted to reverse the flow of refrigerant through the refrigerant circuit so that the heat pump may be selectively operated in either a heating mode or a cooling mode; the circuit furter including a first refrigerant flow line interconnecting one end of each of the heat exchange coils via the compressor and the switchover valve, the first flow line having suction and discharge line sections, and a second refrigerant flow line directly interconnecting the other ends of the heat exchange coils, said control system comprising: first and second electrically modulated expansion valves disposed in the second refrigerant flow; a refrigerant charge receiver, the interior of which isin thermal communication with said suction line section; a third refrigerant flow line including an electrically controlled valve connecting said charge receiver to the second refrigerant line at a point intermediate said first and second electrically modulated expansion valves; means for determining superheat at the suction line section of the refrigerant circuit; means for determining subcooling at the second refrigerant flow line of the refrigerant circuit; and control means for controlling operation of the first and second electrically modulated expansion valves and the electrical controlled valve in the third refrigerant flow line to adjust the proportion of refrigerant charge stored in the charge receiver and flowing in the refrigerant circuit to achieve predetermined levels of superheat and subcooling during operation of the heat pump in both the heating and cooling modes as the temperatures conditioning load changes.

Claim 14

An improved refrigerant charge control system for a heat pump used to temperature condition an indoor zone under the variable load conditions, said heat pump having a refrigerant circuit including indoor and outdoor heat exchange coils, a refrigerant compressor, and a switchover valve adapted to reverse the flow of refrigerant through the refrigerant circuit so that the heat pump may be selectively operated in either a heating mode or a cooling mode; the circuit furter including a first refrigerant flow line interconnecting one end of each of the heat exchange coils via the compressor and the switchover valve, the first flow line having suction and discharge line sections, and a second refrigerant flow line directly interconnecting the other ends of the heat exchange coils, said control system comprising: first and second electrically modulated expansion valves disposed in the second refrigerant flow; a refrigerant charge receiver, the interior of which isin thermal communication with said suction line section; a third refrigerant flow line including an electrically controlled valve connecting said charge receiver to the second refrigerant line at a point intermediate said first and second electrically modulated expansion valves; means for determining superheat at the suction line section of the refrigerant circuit; means for determining subcooling at the second refrigerant flow line of the refrigerant circuit; and control means for controlling operation of the first and second electrically modulated expansion valves and the electrical controlled valve in the third refrigerant flow line to adjust the proportion of refrigerant charge stored in the charge receiver and flowing in the refrigerant circuit to achieve predetermined levels of superheat and subcooling during operation of the heat pump in both the heating and cooling modes as the temperatures conditioning load changes.

Claim 15

The control system of claim 12 wherein the means for determining superheat and the means for determining subcooling both include means for sensing refrigerant pressure and refrigerant temperature at predefined points in the refrigerant circuit.

Claim 16

The control system of claim 13 wherein the means for sensing refrigerant pressure include pressure sensors disposed in both the suction and discharge line sections of the refrigerant circuit.

Claim 17

The control of claim 13 wherein the means for sensing temperature include temperature sensors disposed on the refrigerant circuit inlet and outlet of the indoor and the outdoor heat exchange coils and on the suction line and discharge line sections of the first frigerant flow line.