Refrigerant charge control system for heat pump systems

Abstract

Air sourced or water sourced packaged self-contained heat pump units having indoor and outdoor sections are provided. The heat pump unit distributes its total charge of refrigerant between a main refrigerant system and a refrigerant charge control system while keeping the total charge of refrigerant in the heat pump unit constant. The refrigerant charge control system has a refrigerant reservoir, an inlet conduit, and an outlet conduit that extends into the reservoir such that its lowest point is close to the bottom of the reservoir.

Claims

1. A heat pump unit that distributes its total charge of refrigerant between a main refrigerant system and a refrigerant charge control system conductively engaged to the main refrigerant system, wherein the total charge of refrigerant in the heat pump unit is constant; and the refrigerant charge control system comprises at least the following conductively engaged components: at least one refrigerant reservoir, at least one inlet conduit with a tip, and at least one outlet conduit with a tip that extends into the reservoir such that the tip of the inlet pipe is located at a higher location relative to the tip of the outlet pipe; wherein the system further comprises a hot gas reheat system that dehumidifies air and is conductively engaged to the main refrigerant system, wherein the heat pump unit distributes its total charge of refrigerant between said main refrigerant system, said refrigerant charge control system conductively engaged to the main refrigerant system, and said hot gas reheat system; wherein said main refrigerant system is a variable-refrigerant-charge main refrigerant system; and wherein the heat pump unit operates with a first amount of refrigerant in the main refrigerant system during a cooling or heating cycle and a smaller second amount of refrigerant in the main refrigerant system during a heating or cooling cycle, respectively; and wherein the unit is an air sourced heat pump unit that during a heating cycle operation of the heat pump unit no more than about 50% of the refrigerant charge is in the main refrigerant system and at least about 50% of the refrigerant charge is in the refrigerant charge control system, and during a cooling cycle operation of the heat pump unit at least about 50% of the refrigerant charge is in the main refrigerant system and no more than about 50% of the refrigerant charge is in the refrigerant charge control system, and wherein during a hot gas reheat mode of operation, excess refrigerant is discharged from the refrigerant charge control system back to the main refrigerant system; or wherein the unit is a water sourced heat pump unit that during a cooling cycle operation of the heat pump unit no more than about 50% of the refrigerant charge is in the main refrigerant system and at least about 50% of the refrigerant charge is in the refrigerant charge control system, and during the heating cycle operation of the heat pump unit at least about 50% of the refrigerant charge is in the main refrigerant system and no more than about 50% of the refrigerant charge is in the refrigerant charge control system, and wherein during a hot gas reheat mode of operation, excess refrigerant is collected in the refrigerant charge control system.

2. The heat pump unit of claim 1 wherein the refrigerant charge control system draws refrigerant away from the main refrigerant system during either a cooling cycle or heating cycle of the heat pump unit.

3. The heat pump unit of claim 1, wherein the hot gas reheat cycle system comprises: at least one heat exchanger, and at least one flow control valve.

4. The heat pump unit of claim 1, wherein: the main refrigerant system comprises at least the following conductively engaged components: at least one compressor, at least one high pressure heat exchanger, at least one low pressure heat exchanger, at least one expansion valve, and at least one reversing valve.

5. The heat pump of claim 4, wherein: the heat pump unit is an air source heat pump unit; the at least one high pressure heat exchanger is an outdoor heat exchanger; and the low pressure heat exchanger is an indoor heat exchanger.

6. The heat pump of claim 4, wherein: the heat pump unit is a water source heat pump unit; the at least one high pressure heat exchanger is an indoor heat exchanger; and the low pressure heat exchanger is an outdoor heat exchanger.

7. The heat pump unit of claim 1, wherein: the refrigerant charge control system further comprises at least the following conductively engaged components: at least one flow control valve, and at least one check valve; wherein the check valve is downstream of the reservoir, and the reservoir is downstream of the flow control valve.

8. The heat pump unit of claim 1, wherein the heat pump unit is a packaged air source or water source heat pump unit.

9. The heat pump unit of claim 1, wherein the heat pump unit is adapted to cool or heat air or water.

10. The heat pump unit of claim 1 further comprising at least one blower fan.

11. The heat pump of claim 1, wherein the reservoir is located at a height that is at or near the lowest point of the heat pump unit.

12. The heat pump of claim 1, wherein a majority of the refrigerant in the refrigerant charge control system is vertically lower than a majority of the charge of refrigerant in the main refrigerant.

13. A heat pump unit that distributes its total charge of refrigerant between a main refrigerant system and a refrigerant charge control system conductively engaged to the main refrigerant system, wherein the total charge of refrigerant in the heat pump unit is constant; and the refrigerant charge control system comprises at least the following conductively engaged components: at least one flow control valve, at least one refrigerant reservoir downstream of the flow control valve, at least one check valve downstream of the reservoir, at least one inlet conduit with a tip that extends into the reservoir, and at least one outlet conduit with a tip such that the tip of the inlet pipe is located at a higher location relative to the tip of the outlet pipe; wherein said main refrigerant system is a variable-refrigerant-charge main refrigerant system comprising at least one indoor heat exchanger, at least one outdoor heat exchanger, at least one compressor, at least one expansion valve, and at least one reversing valve; the heat pump unit operates with a first amount of refrigerant in the main refrigerant system during a cooling or heating cycle and a smaller second amount of refrigerant in the main refrigerant system during a heating or cooling cycle, respectively; and wherein the reservoir is located at a height that is at or near the lowest point of the heat pump unit; and wherein the unit is an air sourced heat pump unit that during a heating cycle operation of the heat pump unit no more than about 50% of the refrigerant charge is in the main refrigerant system and at least about 50% of the refrigerant charge is in the refrigerant charge control system, and during a cooling cycle operation of the heat pump unit at least about 50% of the refrigerant charge is in the main refrigerant system and no more than about 50% of the refrigerant charge is in the refrigerant charge control system; or wherein the unit is a water sourced heat pump unit that during a cooling cycle operation of the heat pump unit no more than about 50% of the refrigerant charge is in the main refrigerant system and at least about 50% of the refrigerant charge is in the refrigerant charge control system, and during the heating cycle operation of the heat pump unit at least about 50% of the refrigerant charge is in the main refrigerant system and no more than about 50% of the refrigerant charge is in the refrigerant charge control system.

14. The heat pump unit of claim 13, wherein the heat pump unit is a packaged air source or water source heat pump unit further comprising an indoor hot gas reheat system that dehumidifies air and is conductively engaged to the main refrigerant system, and the heat pump unit distributes its total charge of refrigerant between said main refrigerant system, said refrigerant charge control system conductively engaged to the main refrigerant system, and said hot gas reheat system.

15. A heat pump unit comprising a main refrigerant system (MRS), a hot gas reheat system (HGRS) conductively engaged to the main refrigerant system, and a refrigerant charge control system (RCCS) conductively engaged to the main refrigerant system and comprising at least one refrigerant reservoir, wherein the heat pump unit distributes its total charge of refrigerant between said MRS, said HGRS, and said RCCS, and wherein the MRS comprises an indoor heat exchanger and an outdoor heat exchanger; the HGRS a heat exchanger that dehumidifies air; the reservoir is placed at a relative height such that at least a major portion of its volume is below the MRS; and wherein the unit is an air sourced heat pump unit that during a heating cycle operation of the heat pump unit no more than about 50% of the refrigerant charge is in the main refrigerant system and at least about 50% of the refrigerant charge is in the refrigerant charge control system, and during a cooling cycle operation of the heat pump unit at least about 50% of the refrigerant charge is in the main refrigerant system and no more than about 50% of the refrigerant charge is in the refrigerant charge control system, and wherein during a hot gas reheat mode of operation, excess refrigerant is discharged from the refrigerant charge control system back to the main refrigerant system; or the unit is a water sourced heat pump unit that during a cooling cycle operation of the heat pump unit no more than about 50% of the refrigerant charge is in the main refrigerant system and at least about 50% of the refrigerant charge is in the refrigerant charge control system, and during the heating cycle operation of the heat pump unit at least about 50% of the refrigerant charge is in the main refrigerant system and no more than about 50% of the refrigerant charge is in the refrigerant charge control system, and wherein during a hot gas reheat mode of operation, excess refrigerant is collected in the refrigerant charge control system.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The following drawings are part of the present specification and are included to further demonstrate certain aspects of the invention. The invention may be better understood by reference to one or more of these drawings in combination with the detailed description of the specific embodiments presented herein.

(2) FIG. 1A depicts a schematic diagram of an ASHP unit (15) illustrating the flow of refrigerant during the cooling mode.

(3) FIG. 1B depicts a schematic diagram of the ASHP unit of FIG. 1A illustrating the flow of refrigerant during the heating mode.

(4) FIG. 1C depicts a schematic diagram of the ASHP unit of FIG. 1A illustrating the flow of refrigerant during the hot gas reheat mode.

(5) FIG. 2A depicts a schematic diagram of a WSHP unit (20) illustrating the flow of refrigerant during the cooling mode.

(6) FIG. 2B depicts a schematic diagram of the WSHP unit of FIG. 2A illustrating the flow of refrigerant during the heating mode.

(7) FIG. 2C depicts a schematic diagram of the WSHP unit of FIG. 2A illustrating the flow of refrigerant during the hot gas reheat mode.

(8) FIG. 3A depicts an exemplary embodiment of a refrigerant charge control system (45).

(9) FIG. 3B depicts the sectional view of the refrigerant charge control system unit of FIG. 3A illustrating the position of the reservoir inlet and outlet pipes.

(10) FIG. 4 depicts a cross-sectional side elevation view of an exemplary ASHP packaged unit of the invention (56).

(11) FIG. 5 depicts a cross-sectional side elevation view of an exemplary WSHP packaged unit of the invention (60).

(12) FIG. 6 depicts a righthand end elevation view of an exemplary ASHP packaged unit of the invention (66).

DETAILED DESCRIPTION OF THE INVENTION

(13) With reference to the drawings (FIGS. 1A, 1B, and 1C) a packaged heat pump (air conditioning) system (unit) (15) comprises: at least one compressor (1), at least one outdoor heat exchanger (2), at least one indoor heat exchanger (3), at least one hot gas heat exchanger (4), at least one reversing valve (6), refrigerant charge control reservoir (5), expansion valves (7, 8), flow control (e.g. solenoid) valves (9, 10 and 11), check valves (12, 13) and filter drier (14). The indoor heat exchanger (3) along with the hot gas coil (4) forms part of the indoor section of the unit and is used to heat/cool and condition the building space.

(14) FIG. 1A depicts the refrigerant cycle flow for the ASHP unit (15) operating in a cooling mode. The conduits depicted in hashed lines denote conduits through which refrigerant does not flow; although, refrigerant might be contained therein. The compressor (1) compresses and discharges the refrigerant in the form of high pressure vapor typically in the range of 250 psig to 575 psig; although, other pressure ranges may also be suitable. During the cooling mode, the flow control valve (9) is open and the flow control valve (10) is closed. The super-heated refrigerant vapor (direction of Arrow A1) passes through the reversing valve (6), which directs the flow (direction of Arrow A2) to the outdoor heat exchanger (2), which now acts as a condenser. Heat is removed from the refrigerant by the outdoor heat exchanger by blowing air across or through the heat exchanger (2) using a fixed or variable speed blower fan (30, not depicted in FIG. 1A). This moves air over the condenser coils to the outdoor environment. High pressure refrigerant from the outdoor heat exchanger (2) is conducted through (direction of Arrow A3) the outdoor expansion valve (7), through the filter drier (14) and finally (in the direction of Arrow A3) through the indoor electronic expansion valve (8) where the refrigerant is allowed to expand causing it to change its phase from subcooled liquid to saturated liquid. From the expansion valve (8), the refrigerant is then conducted through the indoor heat exchanger (3) where it absorbs heat from the surroundings and then exits the indoor heat exchanger (in the direction of Arrow A4). The filter drier (14) removes any contaminants present in the refrigerant before it passes through the indoor heat exchanger. Air is blown over or through the indoor heat exchanger using a fixed or variable speed blower fan (29, not depicted in FIG. 1A) which is directed towards the cooling space. Flow control valve (11) is closed during cooling mode; hence no refrigerant is collected in the refrigerant charge control reservoir (5) during this cooling mode. During this cooling mode, the unit allows the flow (in direction of Arrow A5) of refrigerant, if any is present, from the refrigerant charge control reservoir (5) back to the main refrigerant loop (16). The outlet of the reservoir (5) is conductively connected to the suction line of the indoor heat exchanger (3). The low pressure, typically in there range of 110 psig-150 psig, in these lines during the cooling cycle in the ASHP unit pulls (draws) the refrigerant from the reservoir tank (5) to the main refrigerant loop. The check valve (12) prevents the refrigerant from returning back to the reservoir tank (5) through the outlet line. The refrigerant is then directed (in the direction of Arrow A6), optionally through the reversing valve (6), towards the compressor (1) intake (suction) (in the direction of Arrow A7) and pass through the flow control valve (9) again (in the direction of Arrow A1) to complete the cycle.

(15) The heating cycle in the ASHP unit is depicted in FIG. 1B. During the heating or heat pump mode, the reversing valve (6) directs (in the direction of Arrow B2) the flow of high pressure (typically in the range of 250 psig to 575 psig) super-heated refrigerant to the indoor heat exchanger (3), which now acts as a condenser and transfers heat to the internal ambient space. The high pressure liquid refrigerant from the indoor heat exchanger (3) is now distributed by the expansion valve (8) and conducted (in the direction of Arrow B3) to the filter drier (14) and then conducted to the outdoor electronic expansion valve (7). The refrigerant expands and vaporizes as it picks up heat from the ambient air source in the outdoor coil (2). The saturated refrigerant vapor from the outdoor coil is now conducted (in the direction of Arrow B5) to the compressor (1) intake (suction) through the reversing valve (in the direction of Arrow B6). The compressor forces compressed refrigerant back through the flow control valve (9) and ultimately (in the direction of Arrow B1) back through the reversing valve. When the heating cycle is activated, the flow control valve (11) is open which allows a predetermined amount of high pressure saturated refrigerant liquid from the condenser discharge to be collected (in the direction of Arrow B4) in the reservoir (5). The excess refrigerant thus collected in the heating cycle is later fed back into the closed loop system when the system changes to cooling mode. The higher pressure in the reservoir outlet lines does not allow the refrigerant collected in the reservoir tank (5) to mix with the main loop. The check valve (12) also prevents the reverse flow of refrigerant through the reservoir outlet lines. The reservoir flow control valve (11) is open for the entire (or at least a majority of the) duration of the heating cycle. As in the case of the cooling cycle, the solenoid valve (10) leading to the hot gas coil remains closed while the valve (9) remains open.

(16) With reference to FIG. 2A, a WSHP unit (20) comprises components similar to those of the ASHP unit, including hot gas coil (24), except for a notable change in piping from the discharge of the charge compensation reservoir (25). The WSHP unit utilizes a comparatively smaller and more compact outdoor heat exchanger (22), e.g. a brazed plate heat exchanger. Therefore, the WSHP system requires a lower volume of refrigerant when operating in cooling mode when the outdoor heat exchanger (22) acts as a condenser. The outdoor heat exchanger (22) removes the heat from the refrigerant by exchanging heat to the outdoor water/brine mixture. During the cooling cycle in the WSHP unit as shown in FIG. 2A, the flow control valve (31) is open; allowing the excess refrigerant in the main refrigerant loop (35) to be collected in the charge control reservoir (25). The rest of the cycle follows similar to that of the ASHP unit. More specifically, the compressor (21) forces refrigerant through conduit (in the direction of Arrow D1), through flow control valve (29), through the reversing valve (26) and toward (in the direction of Arrow D2) the outdoor heat exchanger (22). Refrigerant then pass through the expansion valve (27) and (in the direction of Arrow D3) through the filter drier (34), through the expansion valve (28) and into the indoor heat exchanger (23). The refrigerant charge control reservoir (25) collects excess refrigerant conducted through (in the direction of Arrow D4) flow control valve (31) between the filter drier and the expansion valve (28). Refrigerant in the main refrigerant loop exits the indoor heat exchanger and is conducted (in the direction of Arrow D5) through the reversing valve (26) back to the compressor (in the direction of Arrow D6) to complete the cycle.

(17) Conversely, during the heating cycle in the WSHP unit, the flow control valve (31) is closed (see FIG. 2B). The pressure differential between the reservoir and the conduit on the downstream side of the check valve (32) causes excess refrigerant collected in the reservoir tank (25) to pass through the check valve (32) and mix with the refrigerant from the outdoor heat exchanger (22) suction, leading back to the compressor. More specifically, the compressor (21) forces refrigerant through conduit (in the direction of Arrow E1), through flow control valve (29), through the reversing valve (26) and toward (in the direction of Arrow E2) the indoor heat exchanger (23). Refrigerant then pass through the expansion valve (28) and (in the direction of Arrow E3) through the filter drier (34), through the expansion valve (27) and into the outdoor heat exchanger (22). The refrigerant charge control reservoir (25) releases (discharges) its refrigerant through the check valve (32) (in the direction of Arrow E5) to a conduit between the outdoor heat exchanger (22) and the reversing valve (26) such that the refrigerant from the reservoir (25) joins refrigerant exiting the outdoor heat exchanger (22) (in the direction of Arrow E4) to be conducted (in the direction of Arrow E6) through the reversing valve (26) and back to the compressor (21) (in the direction of Arrow E7) to complete the heating cycle.

(18) The refrigerant charge control system functions to remove the excess refrigerant in the main refrigerant loop during the heating cycle in the case of ASHP unit and during the cooling cycle in the case of WSHP unit. It also increases the amount of refrigerant in the main refrigerant loop during the cooling cycle in the case of ASHP unit and during the heating cycle in the case of WSHP unit, respectively.

(19) FIG. 3A depicts an exemplary refrigerant charge control system comprising at least one reservoir (40), at least one flow control valve (42), at least one check valve (44), at least one inlet conduit (41), and at least one outlet conduit (43). The flow control valve (42) (which is also denoted as (11) in FIG. 1A) controls the flow of refrigerant to the inlet conduit (41). During the heating cycle, in the case of the ASHP unit, the flow control valve (42) remains open to allow the refrigerant to be collected in the reservoir tank. The reservoir can be insulated to reduce the influence of external temperature conditions on the stored refrigerant. The outlet pipe (43) extends to the bottom (or almost to the bottom) of the reservoir (40). When operation of the ASHP changes from the heating cycle to the cooling cycle, the entire (or substantially the entire or a predetermined amount of) refrigerant stored in the reservoir is fed back to the main refrigerant loop. The check valve (44) (which is also denoted as (12) FIG. 1A) prevents the back flow of any refrigerant to the reservoir through its outlet piping (23).

(20) FIG. 3B depicts a cross-sectional side elevation view of the reservoir of FIG. 3A. The outlet pipe (43) extends into the reservoir such that its lowest point is close to the bottom of the interior of the reservoir (40). The vertical distance (H2) between the tip of the inlet pipe (41) and the lowest point of the reservoir can be as desired. The tip of the inlet pipe (41) is located such that it is at a higher location relative to the lower tip of the outlet pipe. The vertical distance (H1) between the tip of the outlet pipe and the lowest point of the reservoir can be as desired. The difference in vertical position (.sub.1) between the H2 and H1 can be as desired, whereby increasing .sub.1 increases the amount of refrigerant collected in the reservoir and decreasing .sub.1 decreases the amount of refrigerant collected in the reservoir. Increasing H2 increases the amount of refrigerant remaining in the reservoir after it has been discharged. Increasing H1 also decreases the amount of refrigerant collected in the reservoir. In some embodiments, the volume of the reservoir is constant (fixed). In some embodiments, the vertical distance H1 is fixed (meaning the vertical position of the inlet is fixed), the vertical system H2 is fixed (meaning the vertical position of the lowest point of the outlet pipe is fixed), or the vertical distances H1 and H2 are fixed.

(21) When charging (collecting) refrigerant in the reservoir by gravity feed, it is preferable to place the reservoir at a vertical position that is relatively lower than (below) most or all of the other components conductively engaged with the main refrigerant loop. In other words, the reservoir would be placed such that at least a major portion of, or all, of its volume (or of its charge of refrigerant) is placed at a relative height that is below the indoor heat exchanger, outdoor heat exchanger, hot gas heat exchanger, filter drier and at least a majority of the remaining volume of the conduits of the main refrigerant loop.

(22) In some embodiments, the entire charge of refrigerant in the heat pump unit is dividable into at least to portions: a first portion of refrigerant in the main refrigerant loop and a second portion of refrigerant in the RCC system (inclusive of the reservoir and respective conduit(s) and components thereof).

(23) In some embodiments, at least a majority of the refrigerant in the RCC system is vertically lower than at least a majority of the charge of refrigerant in the main refrigerant loop (which comprises components and conduit(s) that are not part of the RCC system).

(24) The heat pump unit is designed such that during a first mode of operation a majority of refrigerant charge in the heat pump unit is present in the main refrigerant loop and little to no refrigerant is in the RCC and during a second mode of operation a significant portion of refrigerant is still in the main refrigerant loop and a substantial portion of refrigerant is in the RCC. For example, during a first mode of operation at least 50%, at least 60%, at least 70%, at least 80%, at least 90%, at least 95%, at least 97%, at least 98%, at least 99% of the entire charge of refrigerant is in the main refrigerant loop, with the remainder, if any, being present in the RCC system. Then during a second mode of operation not more than 1%, not more than 2%, not more than 5%, not more than 7.5%, not more than 10%, not more than 20%, not more than 25%, not more than 30%, not more than 35%, not more than 40%, or not more than 50% of the entire charge of refrigerant is in the RCC system.

(25) In some embodiments, the RCC reservoir is located at a height that is at or near the lowest point of the heat pump unit so that the refrigerant is collected to its full capacity. Referring to FIG. 6, the reservoir assembly (65) could be seen placed at the lowest point and on the indoor side of the ASHP and WSHP unit.

(26) The reservoir of the RCC can be any container that can safely retain a charge of pressurized refrigerant (in either liquid or vapor form). The reservoir of FIG. 6 is depicted as a hollow cylinder (65) which is capped off at both its ends; however, other containers can be used as the reservoir, e.g. a cylindrical container, rectangular container with flat or sloped ends, or even straight conduits or conduits wound to form coils.

(27) In some embodiments, the heat pump unit comprises a hot gas reheat system comprising at least a flow control valve, and a hot gas heat exchanger.

(28) A hot gas reheat (HGRH) dehumidification mode is enabled when there is a call for dehumidification during cooling mode. In HGRH mode, the unit is not actively involved in heating or cooling. The mode of operation of ASHP and WSHP unit during hot gas reheat mode can be referred in FIG. 1C and FIG. 2C respectively. In this method solenoid valve (9) is first closed and after a short time delay solenoid valve (10) is open. This directs the refrigerant towards the hot gas coil (4) before entering the outdoor heat exchanger (2). During HGRH mode the compressor (1) is engaged and ramped up to maximum allowed speed and the indoor fan blower (54) is set to medium speed. The high pressure refrigerant vapor from the compressor discharge is fed to the HGRH coil (4). The refrigerant vapor from the HGRH coil (4) outlet enters the reversing valve (6) and is directed to the outdoor heat exchanger (2) and completes the rest of the cycle similar to cooling mode. The solenoid valve (11) follows the regular cooling cycle and hence is closed in the case of ASHP (FIG. 1C) and open in the case of WSHP (FIG. 2C) unit. Referring to FIG. 4; which illustrates the cross-sectional view of the ASHP unit complete with indoor coil (51), hot gas coil (52), outdoor coil (50), electric heat coil (53), indoor variable speed fan blower (54) and outdoor variable speed fan blower (55). As the indoor fan blower (51) runs, it forces the stream of cold air to pass through the hot gas coil (52) which is heated before entering the indoor air space. The outdoor fan blower (55) is used to regulate the compressor discharge pressure in the case of the HGRH cycle. The control logic utilized in the ASHP unit varies the outdoor fan blower (55) speed to maintain the supply air temperature slightly less than the room temperature to prevent over cooling the space. HGRH cycle will be disengaged when either the humidity condition in the room is satisfied or if there is a sustained call for comfort conditioning. In the case of the WSHP unit as referred in FIG. 5, the compressor discharge pressure is not controlled by varying the flow rate of the water/brine mixture. The electric elements (52) is used as an auxiliary source of heating in both ASHP and WSHP units, which is used when additional heating is required or to provide heat to the living space when the coil is undergoing a de-icing procedure.

(29) Although the present invention and its advantages have been described here in detail, it should be taken into consideration that there will several variations in the unit, alterations and minor changes that can be made herein without departing from the scope of the invention as defined by the claims. For example, although the cross-sectional views of ASHP and WSHP packaged units as shown in FIG. 4 and FIG. 5 show that the units have both hot-gas coil (52) and electric heat elements (53), it is to be understood that these units could be manufactured with just cooling and heat pump operations, or having a cooling operation with reheat mode without any auxiliary heater. In other words, the hot gas coil (52) and the electric heat elements (53) could still be eliminated, and those units will still be within the scope of our invention. Also, the implementation of our invention of the refrigerant charge compensation device along with hot gas reheat in packaged ASHP and WSHP units could be slightly modified to be implemented in other HVAC applications such as split systems, rooftop units, and other systems using air-handlers. It is also to be noted that the shape and size of our refrigerant charge compensation device could be modified in the future as we continuously improve our unit. Hence, the scope of our invention is to be determined by reference to our claims.

(30) All values disclosed herein may have standard technical measure error (standard deviation) of 10%. The term about is intended to mean10%, 5%, 2.5% or 1% relative to a specified value, i.e. about 20% means 202%, 201%, 200.5% or 200.25%.

(31) The above is a detailed description of particular embodiments of the invention. It will be appreciated that, although specific embodiments of the invention have been described herein for purposes of illustration, various modifications may be made without departing from the spirit and scope of the invention. Accordingly, the invention is not limited except as by the appended claims. All embodiments disclosed and claimed herein can be made and executed without undue experimentation in light of the present disclosure.