CA2143881A1 - Multiple function heat pump - Google Patents
Multiple function heat pumpInfo
- Publication number
- CA2143881A1 CA2143881A1 CA 2143881 CA2143881A CA2143881A1 CA 2143881 A1 CA2143881 A1 CA 2143881A1 CA 2143881 CA2143881 CA 2143881 CA 2143881 A CA2143881 A CA 2143881A CA 2143881 A1 CA2143881 A1 CA 2143881A1
- Authority
- CA
- Canada
- Prior art keywords
- air
- evaporator
- condenser
- fan
- outdoor
- 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.)
- Abandoned
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
- F24F1/022—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
Abstract
The invention described herein pertains to an air cycle heat pump contained in a single and compact unit which is capable to perform the functions of a heat pump, a de-humidifier, and an air exchanger with energy recovery capability.
The unit consists basically of two superimposed rectangular compartments. Two air circuits, one for the upper or condensing compartment, the other for the lower or evaporating compartment utilize their individual fan, and through an arrangement of air valves either of the circuits can communicate with the outdoors, the indoors or exclusively the indoors depending on the particular mode being asked for.
The outstanding feature of this unit is an especially designed evaporator. The latter consist of evaporator slabs arranged in a zig-zag pattern on a circular base which can be rotated with respect to the air stream supplied by the evaporator fan. Rotated into one position, the slabs will present a surface area to the air stream which is the sum total of all the slabs combined, while in the other position all the slabs are presenting a parallel arrangement so that the entire air stream will flow consecutively through each slab.
The former case is principally required when the unit is in a heating mode to reduce frost accumulation on the evaporator fins, while the latter case exhibits its main advantage during the de-humidifying mode when the air should be cooled down to maximum for greatest extraction of moisture. Placing the evaporator into any intermediate position will allow it to handle a variety of air conditions in either the cooling or de-humidifying modes.
The unit would typically be installed in a basement and would be connected to the outdoors via two ducts, the latter supplying outdoor air when the heating, cooling or fresh air exchange modes are called for.
These ducts are capable of being closed off by a pair of shut-off valves integrated into the upper compartment, the latter being placed in the closed position when the unit is not in use or the de-humidifying or de-frost modes are in demand.
Alternatively the unit could also be installed outdoors with only two ducts required to connect to the indoors ducting system.
The unit consists basically of two superimposed rectangular compartments. Two air circuits, one for the upper or condensing compartment, the other for the lower or evaporating compartment utilize their individual fan, and through an arrangement of air valves either of the circuits can communicate with the outdoors, the indoors or exclusively the indoors depending on the particular mode being asked for.
The outstanding feature of this unit is an especially designed evaporator. The latter consist of evaporator slabs arranged in a zig-zag pattern on a circular base which can be rotated with respect to the air stream supplied by the evaporator fan. Rotated into one position, the slabs will present a surface area to the air stream which is the sum total of all the slabs combined, while in the other position all the slabs are presenting a parallel arrangement so that the entire air stream will flow consecutively through each slab.
The former case is principally required when the unit is in a heating mode to reduce frost accumulation on the evaporator fins, while the latter case exhibits its main advantage during the de-humidifying mode when the air should be cooled down to maximum for greatest extraction of moisture. Placing the evaporator into any intermediate position will allow it to handle a variety of air conditions in either the cooling or de-humidifying modes.
The unit would typically be installed in a basement and would be connected to the outdoors via two ducts, the latter supplying outdoor air when the heating, cooling or fresh air exchange modes are called for.
These ducts are capable of being closed off by a pair of shut-off valves integrated into the upper compartment, the latter being placed in the closed position when the unit is not in use or the de-humidifying or de-frost modes are in demand.
Alternatively the unit could also be installed outdoors with only two ducts required to connect to the indoors ducting system.
Description
2lg388l SPECIFI~ATION
Field of the invention The rullo/.~;ng disclos~re relates to air condi~ioner:~ known as heat pumps, in particular to the category known as reverse air cycle heat pumps~ that can be used for comfort air conditioning in homes, offices, restauranb etc.
Description of the prior art The pr~oi"i"dn~ heat pump in use today utilizes the reversible r~ligerant cycle. In this kind of machinery a conder,sir-g unit, comprised of con,pr~ssor, condenser (the latter has to function as an po,~Lur in the heating mode), ouWoor fan motor and various control circuitry, is located in an ~ osed position outside the building. The indoor unit, consisling of the evaporak~r (the latter has to function as a condenser in the heating mode) and the ~ ,uansion device, is located in either an existing furnace cabinet or in a dedicated enclosure with a blower fan and connected to a duct system. The indoor and ouWoor units are interc,onne~ d by lefli~erdL,on tubing and control wiring. A change-over valve is utilized to direct liquid refrigerant into either the indoor evaporator or the outdoor evaporator depending on whether cooling or heating is being called for.
This type of system has several disadvdr,lages the principal one being as follows: A heat pump is I ~e~d to carry out the two tasks of either heating or cooling of air. Particularly in northern cli."dlas the demand for heating PY~;eeds the demand for cooling by a significant factor. A heat pump unit therefore has to be seized large enough to satisfy the heating demand, resulbng in an apparatus that is far too powerful in the cooling mode, and although capable of lov,ering the air temperature very rapidly, only r~ ly small quantities of moisture are U~ld~tl~d because de-humidifying is only carried out during operation of the unit. It is for this reason that a slightly under~ ed apparatus operating continuously would represent the ideal choice for cooling and de-humidifying. Obviously this ~rp~-~hls would only have relatively small heating capacity in the heating mode.
2l~388l My proposed heat pump design will solve this problem in two steps:
- Firstly the unit, - sized sufficiently large to handle the heat load during the heating season -, will cool down the air to the desired temperature in the cooling mode.
- Secondly the unit will switch to the de-humidifying mode and continue to remove moisture until the desired humidity level is reached.
It can thus be seen, that with this multiple-function c~p~hilily the unit can be sized for heating demand, whilst still retain the full capabiliLy to cool and de-humidify to required levels. It is this dual function that overcomes the main draw-back of the reversing refrigerant heat pump.
The second advantage is that each coo,pressor-col~denser-eYapGrcltor design can be na,(il"i,ed for operating efficiency because the condenser and evaporator are dedicc,led to their respective functions of condensing and evaporaling of the rt,r,igerdn~, whilst in todays design the evapo,dtor and condenser have to int~,rchange tasks with the resulting compromises regarding the dimensions and design of these items.
A third advantage is that the entire unit can be asse",bled in a single cabinet and typically in~t"~d in a basement. Thus the apparatus is not exposed to inclement climatic cond;Lions which also facilit~tes servicing. A coi"p!~e inst~ tion requires only two air ducts communicating with the outdoors, one serving as the inlet and the other as the outlet. In addition, the compressor is always located in the warm indoor air stream during the heating mode, thus avoiding many problems 2.ssoci~ d with liquid refrigerant accumulating in the col"pressor crankcase, which in current design has to be overcome by the ir~ llation of a crankcase heater and~or by insulating of the compressor.
Several different types of reverse air cycle heat pumps have been designed also, although none of them feature the dual capability of the evaporator to switch from a large surface area mode to a multiple row evaporator mode.
To aid in ~,~,ulaining the various air circuits inside the machine, I will resort to a series of schematic air flow diagrams, which will show the positioning of the air valves for each of the six poss.~ modes of - 2l~88l operdlion. It should be kept in mind that the evapordt~,r will always be a source of cooled air, while the condenser will always be a source of heated air.
Items are only identified in figures 1, 2 and 6 to preserve the clarity of the drc.~ gs.
Fiq. 1 - Heating Fiq. 2 - Fresh air exchange (heating mode~
Fiq 3 - Cooling Fia. 4 - Fresh air exchange ~cooling mode) Fiq. 5 - De-humidifying Fip. 6 - D~l~Jsli"g Fiqure 1 shows the unit in the heating mode. Valve ~6) is posilioned to allow condenser fan (3) to draw indoor air through intake opening (11~ to be discl)arged through the condenser (7), picking up heat in the pr.,cess; the air is then directed by air vaive (~3 through indoor air discharge (12) back into the condilioned space (1). At the same time the t~,vo valves (8) are posilioned to allow outdoor air to be drawn through opening ~9) by fan (4) and discharged through the evdpor tvr assembly (2) in its large e~,~por~ling surface mode, and back outdoors through opening ~10).
Fiaure 2 depicts the fresh air e~Pchange mode with pre-heated outdoor air. Compared with figure 1 only the orier~taLion of air valve (6) has changed for this function. Outdoor air is drawn in by condenser fan (3), passed through condenser (7) where it is heated and discharged indoors (1) via opening (12). The ev~por ~ - blower ~4l, picks up indoor air through opening (11), passes it through the evapor~h r (2) in the large evaporating surface configuration and discharges the air to the outdoors via opening ~10). In this mode of oper~Lion fresh and prehea~d outdoor air is thus introduced into the living space and stale indoor air exhausted, utilizing the latter in a heat exchange mode with the evaporator, thus realizing a substantial energy recovery.
` 21~3881 Fi~ure 3 shows the air flow conditons in the cooling mode. Valves ~5~ and (6~ have changed orient~tion, now allowing the condenser fan (3) and the condenser (7) to form an outdoor air circuit through the openings ~9) and (10). The evaporator air circuit picks up indoor air through opening (11) to be passed through the ev~po,dlur either in the multi-row or large surface configuration depending on the humidity level of the indoor air. Cooled air is returned to the indoors through opening (12~.
Fiqure 4 depicts the fresh air excllange mode with outdoor air being cooled down and introduced into the indoor space (1~. The air circuit is identical with figure 3 except that valve (6) is positioned to allow the evdpor~tur fan (4) to pick up outdoor air through opening (9) this air is being cooled down by the e~porator (2~ in the multi-row or large suRace configuration depending on outdoor air humidity levels and discharged indoors through opening (12). The condenser fan (3) in the ",eanli",e picks up indoor air through opening (11) and discharges same to outdoors through opening (10). Fresh outdoor air is thus cooled and de-hun,.Ji'ied while stale indoor air is exhausted. At the same time the condenser utilizes relatively cool indoor air to condense the ,~f,igerar,l consequently realizing an energy recovery in this mode also.
Fi~ure 5 shows the unit in the de-humidifying mode. The two outdoor air shutoff valves ~8) are now closing off the outdoor openings ~9) and (10) and at the same time opening up a bypass pa~sage allowing air to communicate b~,h~een the left and right sides of the unit. Valve ~6~ is position~ so that the evaporator fan (4) picks up indoor air through opening ~11) and passes it through the e~,~pordlor in the multi-row configuration for maximum de-humidifying e~fect. The cooled and de-humidified air is directed through the bypass passage, picked up by the condenser fan ~3) reheated by the condenser (7) and d;~ harged indoors through opening (12). This process is continued until the desired humidity level is reached.
Fiaure 6 represents the air flow during a defrost cycle. Depending on the outdoor humidity and temperature con.lilions, the evaporator will accumulate frost on it's fin surfaces and if no preventive measures are taken, the air flow through same will be blocksd colllp!~ -!y. Every heat pump requires some means for regularly def,u~ting the evapo,ator. The reversing refrigerant model swit~ hes to the cooling mode for this purpose, now turning the outdoor evaporator into the condenser the heat of condensation melting the frost. This works satisrd- torily, but with the drawback that the indoor condenser now becGmes , 21g3881 the evaporator cooling down the air that enters the living space and auxilliary heaters have to be actuated to make up for this heat loss. My design takes care of this problem by d~energizing the cGn,pressor, closing off the outdoor air openings ~9&10) placing the air valves (~3 and (6) in the positions indicated and actiYating an electric defrost heater (13l. A compl_~ly isolated internal air circuit is thus formed in which heated air can be circulated by evaporator fan ~4) until the evaporator ~2) has been completely def,osted.
Fi~ure 7 is a top view of the ev-~por~lur col~npail".e"l with the ev~pordluor ass~l"bly placed in the multiple row configuration.
Fiqure 8 shows the same conlpa,l ,.ellt with the evdpordtur placed in its large surface area configuration.
Fiqure 9 depicts the upper compartment with the top cover of the unit removed. The unit is shown with the air valves positioned in the heating mode.
Fiaure 10 depicts the upper compartment with the top cover of the unit removed. The air valves are positioned for the de-humidifying mode.
Fi~ure 11 is a side view of the entire unit with the panel on the co"lpressor side removed.
DESCRIPTION OF THE PREFEP<RED EMBODIMENT
A multiple-function heat pump consi~li"g of two supe",.,posed rectangular co,.,paill,lenb the lower one housing a multiple-mode evapordLur assembly ~2) the evaporator fan and motor (4) while the upper cG",pa,l,nent cori~~ ,s the col"p,~:ssor (19) condenser ~7) condenser fan (3~ and the various air change-over valves is shown in figures 7 through 11.
Fi~ure 7 depicts the top view of the evaporator compa-l-nent v~rith the upper compartment removed. The evaporator asse,.,bly (2~ is oriented in the multiple-row configuration mode. The evaporator fan and motor ~4) are located at the left end the air being drawn in from the upper co" ,pa, l."ent and discl aryed through baffle (14) across the evaporator assembly (2). The rotating base ~17) of this asser"bly has posilioned the evapor~lur slabs such that a seal is formed with the two fixed bames (15) and the Iwo pivoting baffles (16).
~1~3881 Air discharged from the evapor;~lùr fan ~4) thus traverses each evaporator slab in turn and is discharged to the upper coi"pailr"~nl through the interior opening (18~.
Fi~ure 8 shows the same cornpall~"er,l with the evdpor~lor assembly ~2~ now positioned in the large evaporating surface mode. The base of the assembly ~1n has been rotated 90 so that the ends of two slabs seal with the t~,vo fixed baffles (15~. The two pivoting baffles (16) are now aligned with the sides of the compartment. Air discharged by the fan (4) will pass through all slabs at the same time before being discharged through the interior opening (18) to the upper compartment.
Fi~ure 9 is a view of the upper co~npa,ln.er,L shown in the heating mode v~fith the top cover removed and displaying all the items contained therein including a partial view of the lower compartment specifically the evdporalur fan & motor (4) and a section of the rotating base ~17~ of the evapordtor assembly.
The central section of this compartment houses the compressor (19) the condenser ~7) and the condenser fan (3). This fan is driven by the condenser fan motor ~20) the latter being located on the opposite side of bulkhead (21). Air discharged from the condenser fan (3) traverses the condenser (7) and is directed onto the pivoting condenser outlet valve (5) the latter one forcing the air to exit the unit through the indoor discharge opening ~12). On the intake side of the condenser fan air is drawn in through the indoor inlet opening (11~ and directed by the pivoting evapG.dlur inlet valve ~6) to the condenser fan (3).
The two outdoor air shutoff valves (8) are opening up the outdoor inlet ~9) 8, outlet (1û) openings allowing the evapordtor fan (4) to draw in outside air through opening (9). After having been passed through the ev~pordlur assembly this air is directed through the interior opening ~18) bet~,veen the lower and upper con .pa, I"~ents towards the condenser outlet valve (5) and the outdoor outlet opening (10) to the ouWoors.
Fi~ure 10 is the same view as figure 9 with the two air valves (5) & (6) now ,eosilioned for the de-hurnidifying operation. The two outdoor shutoff valves (8) now closing off the two outdoor openings (9) &
~10~ are at the sarne time opening up a passage between the left and right sides of the upper co. ",~,a, L" ,er,l.
This pass~ge also houses the motor (20) for the condenser fan 13). The unit is thus cGmpl~tcly isolated from the outdoors. The evaporator inlet valve (6~ allows the evaporator fan (4~ to draw in indoor air through indoor inlet opening (11~. After passing through the evaporalur assembly in the de-humidifying mode, the conJilioned air is passed through interior opening ~18) and directed by air valve [5) through the bypass pacsage to the left side of the compa,L.nent. The ev~por~tur inlet valve ~6) directs the air to the condenser fan (3), the latter pushing it through the condenser (7) from where it is discl~ar~ed via the condenser outlet valve ~5) and indoor outlet opening (12) to the indoor space. The de-h~",idiried air is thus reheated by the condenser and this process is continued until a s~ c.~ory humidity level is reached.
Fi~ure 11 is an elevational view of the entire unit with the cover on the col"pressor side removed. The upper and lower compa,l"~eu~ are clearly visible. The evapor~k,r assembly ~2) is shown in the large surface area mode with one pivoting baffle ~10) shown parallel to the side of the unit. The flexible tubing (22) connecting the evaporator assembly (2) to the compressor l19) is located directly above the evaporator assembly.
The upper compartment shows the condenser fan (3), compressor (19) condenser (7), the evaporator inlet valve (6) and the condenser outlet valve (5). The opening between the upper and lower co",pa,l.nents on the evaporator discharge side is shown by (18). The defrost heater ~13) is located in the dischdrge air stream of the e~poralur assembly.
Field of the invention The rullo/.~;ng disclos~re relates to air condi~ioner:~ known as heat pumps, in particular to the category known as reverse air cycle heat pumps~ that can be used for comfort air conditioning in homes, offices, restauranb etc.
Description of the prior art The pr~oi"i"dn~ heat pump in use today utilizes the reversible r~ligerant cycle. In this kind of machinery a conder,sir-g unit, comprised of con,pr~ssor, condenser (the latter has to function as an po,~Lur in the heating mode), ouWoor fan motor and various control circuitry, is located in an ~ osed position outside the building. The indoor unit, consisling of the evaporak~r (the latter has to function as a condenser in the heating mode) and the ~ ,uansion device, is located in either an existing furnace cabinet or in a dedicated enclosure with a blower fan and connected to a duct system. The indoor and ouWoor units are interc,onne~ d by lefli~erdL,on tubing and control wiring. A change-over valve is utilized to direct liquid refrigerant into either the indoor evaporator or the outdoor evaporator depending on whether cooling or heating is being called for.
This type of system has several disadvdr,lages the principal one being as follows: A heat pump is I ~e~d to carry out the two tasks of either heating or cooling of air. Particularly in northern cli."dlas the demand for heating PY~;eeds the demand for cooling by a significant factor. A heat pump unit therefore has to be seized large enough to satisfy the heating demand, resulbng in an apparatus that is far too powerful in the cooling mode, and although capable of lov,ering the air temperature very rapidly, only r~ ly small quantities of moisture are U~ld~tl~d because de-humidifying is only carried out during operation of the unit. It is for this reason that a slightly under~ ed apparatus operating continuously would represent the ideal choice for cooling and de-humidifying. Obviously this ~rp~-~hls would only have relatively small heating capacity in the heating mode.
2l~388l My proposed heat pump design will solve this problem in two steps:
- Firstly the unit, - sized sufficiently large to handle the heat load during the heating season -, will cool down the air to the desired temperature in the cooling mode.
- Secondly the unit will switch to the de-humidifying mode and continue to remove moisture until the desired humidity level is reached.
It can thus be seen, that with this multiple-function c~p~hilily the unit can be sized for heating demand, whilst still retain the full capabiliLy to cool and de-humidify to required levels. It is this dual function that overcomes the main draw-back of the reversing refrigerant heat pump.
The second advantage is that each coo,pressor-col~denser-eYapGrcltor design can be na,(il"i,ed for operating efficiency because the condenser and evaporator are dedicc,led to their respective functions of condensing and evaporaling of the rt,r,igerdn~, whilst in todays design the evapo,dtor and condenser have to int~,rchange tasks with the resulting compromises regarding the dimensions and design of these items.
A third advantage is that the entire unit can be asse",bled in a single cabinet and typically in~t"~d in a basement. Thus the apparatus is not exposed to inclement climatic cond;Lions which also facilit~tes servicing. A coi"p!~e inst~ tion requires only two air ducts communicating with the outdoors, one serving as the inlet and the other as the outlet. In addition, the compressor is always located in the warm indoor air stream during the heating mode, thus avoiding many problems 2.ssoci~ d with liquid refrigerant accumulating in the col"pressor crankcase, which in current design has to be overcome by the ir~ llation of a crankcase heater and~or by insulating of the compressor.
Several different types of reverse air cycle heat pumps have been designed also, although none of them feature the dual capability of the evaporator to switch from a large surface area mode to a multiple row evaporator mode.
To aid in ~,~,ulaining the various air circuits inside the machine, I will resort to a series of schematic air flow diagrams, which will show the positioning of the air valves for each of the six poss.~ modes of - 2l~88l operdlion. It should be kept in mind that the evapordt~,r will always be a source of cooled air, while the condenser will always be a source of heated air.
Items are only identified in figures 1, 2 and 6 to preserve the clarity of the drc.~ gs.
Fiq. 1 - Heating Fiq. 2 - Fresh air exchange (heating mode~
Fiq 3 - Cooling Fia. 4 - Fresh air exchange ~cooling mode) Fiq. 5 - De-humidifying Fip. 6 - D~l~Jsli"g Fiqure 1 shows the unit in the heating mode. Valve ~6) is posilioned to allow condenser fan (3) to draw indoor air through intake opening (11~ to be discl)arged through the condenser (7), picking up heat in the pr.,cess; the air is then directed by air vaive (~3 through indoor air discharge (12) back into the condilioned space (1). At the same time the t~,vo valves (8) are posilioned to allow outdoor air to be drawn through opening ~9) by fan (4) and discharged through the evdpor tvr assembly (2) in its large e~,~por~ling surface mode, and back outdoors through opening ~10).
Fiaure 2 depicts the fresh air e~Pchange mode with pre-heated outdoor air. Compared with figure 1 only the orier~taLion of air valve (6) has changed for this function. Outdoor air is drawn in by condenser fan (3), passed through condenser (7) where it is heated and discharged indoors (1) via opening (12). The ev~por ~ - blower ~4l, picks up indoor air through opening (11), passes it through the evapor~h r (2) in the large evaporating surface configuration and discharges the air to the outdoors via opening ~10). In this mode of oper~Lion fresh and prehea~d outdoor air is thus introduced into the living space and stale indoor air exhausted, utilizing the latter in a heat exchange mode with the evaporator, thus realizing a substantial energy recovery.
` 21~3881 Fi~ure 3 shows the air flow conditons in the cooling mode. Valves ~5~ and (6~ have changed orient~tion, now allowing the condenser fan (3) and the condenser (7) to form an outdoor air circuit through the openings ~9) and (10). The evaporator air circuit picks up indoor air through opening (11) to be passed through the ev~po,dlur either in the multi-row or large surface configuration depending on the humidity level of the indoor air. Cooled air is returned to the indoors through opening (12~.
Fiqure 4 depicts the fresh air excllange mode with outdoor air being cooled down and introduced into the indoor space (1~. The air circuit is identical with figure 3 except that valve (6) is positioned to allow the evdpor~tur fan (4) to pick up outdoor air through opening (9) this air is being cooled down by the e~porator (2~ in the multi-row or large suRace configuration depending on outdoor air humidity levels and discharged indoors through opening (12). The condenser fan (3) in the ",eanli",e picks up indoor air through opening (11) and discharges same to outdoors through opening (10). Fresh outdoor air is thus cooled and de-hun,.Ji'ied while stale indoor air is exhausted. At the same time the condenser utilizes relatively cool indoor air to condense the ,~f,igerar,l consequently realizing an energy recovery in this mode also.
Fi~ure 5 shows the unit in the de-humidifying mode. The two outdoor air shutoff valves ~8) are now closing off the outdoor openings ~9) and (10) and at the same time opening up a bypass pa~sage allowing air to communicate b~,h~een the left and right sides of the unit. Valve ~6~ is position~ so that the evaporator fan (4) picks up indoor air through opening ~11) and passes it through the e~,~pordlor in the multi-row configuration for maximum de-humidifying e~fect. The cooled and de-humidified air is directed through the bypass passage, picked up by the condenser fan ~3) reheated by the condenser (7) and d;~ harged indoors through opening (12). This process is continued until the desired humidity level is reached.
Fiaure 6 represents the air flow during a defrost cycle. Depending on the outdoor humidity and temperature con.lilions, the evaporator will accumulate frost on it's fin surfaces and if no preventive measures are taken, the air flow through same will be blocksd colllp!~ -!y. Every heat pump requires some means for regularly def,u~ting the evapo,ator. The reversing refrigerant model swit~ hes to the cooling mode for this purpose, now turning the outdoor evaporator into the condenser the heat of condensation melting the frost. This works satisrd- torily, but with the drawback that the indoor condenser now becGmes , 21g3881 the evaporator cooling down the air that enters the living space and auxilliary heaters have to be actuated to make up for this heat loss. My design takes care of this problem by d~energizing the cGn,pressor, closing off the outdoor air openings ~9&10) placing the air valves (~3 and (6) in the positions indicated and actiYating an electric defrost heater (13l. A compl_~ly isolated internal air circuit is thus formed in which heated air can be circulated by evaporator fan ~4) until the evaporator ~2) has been completely def,osted.
Fi~ure 7 is a top view of the ev-~por~lur col~npail".e"l with the ev~pordluor ass~l"bly placed in the multiple row configuration.
Fiqure 8 shows the same conlpa,l ,.ellt with the evdpordtur placed in its large surface area configuration.
Fiqure 9 depicts the upper compartment with the top cover of the unit removed. The unit is shown with the air valves positioned in the heating mode.
Fiaure 10 depicts the upper compartment with the top cover of the unit removed. The air valves are positioned for the de-humidifying mode.
Fi~ure 11 is a side view of the entire unit with the panel on the co"lpressor side removed.
DESCRIPTION OF THE PREFEP<RED EMBODIMENT
A multiple-function heat pump consi~li"g of two supe",.,posed rectangular co,.,paill,lenb the lower one housing a multiple-mode evapordLur assembly ~2) the evaporator fan and motor (4) while the upper cG",pa,l,nent cori~~ ,s the col"p,~:ssor (19) condenser ~7) condenser fan (3~ and the various air change-over valves is shown in figures 7 through 11.
Fi~ure 7 depicts the top view of the evaporator compa-l-nent v~rith the upper compartment removed. The evaporator asse,.,bly (2~ is oriented in the multiple-row configuration mode. The evaporator fan and motor ~4) are located at the left end the air being drawn in from the upper co" ,pa, l."ent and discl aryed through baffle (14) across the evaporator assembly (2). The rotating base ~17) of this asser"bly has posilioned the evapor~lur slabs such that a seal is formed with the two fixed bames (15) and the Iwo pivoting baffles (16).
~1~3881 Air discharged from the evapor;~lùr fan ~4) thus traverses each evaporator slab in turn and is discharged to the upper coi"pailr"~nl through the interior opening (18~.
Fi~ure 8 shows the same cornpall~"er,l with the evdpor~lor assembly ~2~ now positioned in the large evaporating surface mode. The base of the assembly ~1n has been rotated 90 so that the ends of two slabs seal with the t~,vo fixed baffles (15~. The two pivoting baffles (16) are now aligned with the sides of the compartment. Air discharged by the fan (4) will pass through all slabs at the same time before being discharged through the interior opening (18) to the upper compartment.
Fi~ure 9 is a view of the upper co~npa,ln.er,L shown in the heating mode v~fith the top cover removed and displaying all the items contained therein including a partial view of the lower compartment specifically the evdporalur fan & motor (4) and a section of the rotating base ~17~ of the evapordtor assembly.
The central section of this compartment houses the compressor (19) the condenser ~7) and the condenser fan (3). This fan is driven by the condenser fan motor ~20) the latter being located on the opposite side of bulkhead (21). Air discharged from the condenser fan (3) traverses the condenser (7) and is directed onto the pivoting condenser outlet valve (5) the latter one forcing the air to exit the unit through the indoor discharge opening ~12). On the intake side of the condenser fan air is drawn in through the indoor inlet opening (11~ and directed by the pivoting evapG.dlur inlet valve ~6) to the condenser fan (3).
The two outdoor air shutoff valves (8) are opening up the outdoor inlet ~9) 8, outlet (1û) openings allowing the evapordtor fan (4) to draw in outside air through opening (9). After having been passed through the ev~pordlur assembly this air is directed through the interior opening ~18) bet~,veen the lower and upper con .pa, I"~ents towards the condenser outlet valve (5) and the outdoor outlet opening (10) to the ouWoors.
Fi~ure 10 is the same view as figure 9 with the two air valves (5) & (6) now ,eosilioned for the de-hurnidifying operation. The two outdoor shutoff valves (8) now closing off the two outdoor openings (9) &
~10~ are at the sarne time opening up a passage between the left and right sides of the upper co. ",~,a, L" ,er,l.
This pass~ge also houses the motor (20) for the condenser fan 13). The unit is thus cGmpl~tcly isolated from the outdoors. The evaporator inlet valve (6~ allows the evaporator fan (4~ to draw in indoor air through indoor inlet opening (11~. After passing through the evaporalur assembly in the de-humidifying mode, the conJilioned air is passed through interior opening ~18) and directed by air valve [5) through the bypass pacsage to the left side of the compa,L.nent. The ev~por~tur inlet valve ~6) directs the air to the condenser fan (3), the latter pushing it through the condenser (7) from where it is discl~ar~ed via the condenser outlet valve ~5) and indoor outlet opening (12) to the indoor space. The de-h~",idiried air is thus reheated by the condenser and this process is continued until a s~ c.~ory humidity level is reached.
Fi~ure 11 is an elevational view of the entire unit with the cover on the col"pressor side removed. The upper and lower compa,l"~eu~ are clearly visible. The evapor~k,r assembly ~2) is shown in the large surface area mode with one pivoting baffle ~10) shown parallel to the side of the unit. The flexible tubing (22) connecting the evaporator assembly (2) to the compressor l19) is located directly above the evaporator assembly.
The upper compartment shows the condenser fan (3), compressor (19) condenser (7), the evaporator inlet valve (6) and the condenser outlet valve (5). The opening between the upper and lower co",pa,l.nents on the evaporator discharge side is shown by (18). The defrost heater ~13) is located in the dischdrge air stream of the e~poralur assembly.
Claims (6)
1. A heat pump, capable of performing the functions of heating, cooling, de-humidifying and fresh air exchange with energy recovery, contained in a single enclosure.
2. The apparatus according to claim 1 wherein:
an upper compartment comprised of a compressor, condenser, condenser fan & motor, two independently operated air valves, two outdoor air shutoff valves, two indoor air openings and two outdoor air openings, with the mentioned items mounted on the same horizontal plane, namely the partition between the upper and lower compartments.
an upper compartment comprised of a compressor, condenser, condenser fan & motor, two independently operated air valves, two outdoor air shutoff valves, two indoor air openings and two outdoor air openings, with the mentioned items mounted on the same horizontal plane, namely the partition between the upper and lower compartments.
3. The apparatus according to claim 1 wherein:
a lower compartment containing an evaporator slab assembly, a rotating base for same assembly capable of changing the function of the evaporator from a multiple row mode to a large surface area mode, an evaporator fan & motor, an assembly of fixed and pivoted dampers for directing the air flow and a defrost heater with all said items mounted on the same horizontal plane, namely the floor of the apparatus.
a lower compartment containing an evaporator slab assembly, a rotating base for same assembly capable of changing the function of the evaporator from a multiple row mode to a large surface area mode, an evaporator fan & motor, an assembly of fixed and pivoted dampers for directing the air flow and a defrost heater with all said items mounted on the same horizontal plane, namely the floor of the apparatus.
4. The apparatus according to claim 2 wherein:
the compressor, the condenser and the condenser blower assembly are enclosed at the top by the top cover of the apparatus, on one side by an internal partition, on the other by the side panel of the apparatus and on the bottom by the partition between the upper and lower compartments;
four openings are located at the level of the uppermost compartment, two openings on one side communicating with the outdoors via two ducts, while the other two openings are located on the opposite side communicating with the indoors via two ducts;
a center pivoted air valve located on the discharge side of the condenser is directing air from the condenser fan to either the outdoor or indoor discharge opening, while at the same time air from the evaporator compartment is directed inversely to the indoor or outdoor discharge openings;
a center pivoted air valve located on the suction side of the condenser fan is directing air from either the outdoor or indoor intake opening towards the condenser fan, or inversely from the indoor or outdoor intake opening towards the evaporator fan in the lower compartment;
two outdoor air shut-off valves are attached to the central section of the side panel separating the two outdoor air openings; the said two valves are operated in unison, either sealing off the interior bypass passage between the left and right sides of the unit and opening the unit to the outdoor ducting, or sealing with the side panel of the unit and shutting off communication with the outdoors, but at the same time opening up the interior bypass passage.
the compressor, the condenser and the condenser blower assembly are enclosed at the top by the top cover of the apparatus, on one side by an internal partition, on the other by the side panel of the apparatus and on the bottom by the partition between the upper and lower compartments;
four openings are located at the level of the uppermost compartment, two openings on one side communicating with the outdoors via two ducts, while the other two openings are located on the opposite side communicating with the indoors via two ducts;
a center pivoted air valve located on the discharge side of the condenser is directing air from the condenser fan to either the outdoor or indoor discharge opening, while at the same time air from the evaporator compartment is directed inversely to the indoor or outdoor discharge openings;
a center pivoted air valve located on the suction side of the condenser fan is directing air from either the outdoor or indoor intake opening towards the condenser fan, or inversely from the indoor or outdoor intake opening towards the evaporator fan in the lower compartment;
two outdoor air shut-off valves are attached to the central section of the side panel separating the two outdoor air openings; the said two valves are operated in unison, either sealing off the interior bypass passage between the left and right sides of the unit and opening the unit to the outdoor ducting, or sealing with the side panel of the unit and shutting off communication with the outdoors, but at the same time opening up the interior bypass passage.
5. The apparatus according to claim 3 wherein:
the evaporator assembly, the evaporator fan & motor, fixed and pivoting baffles, and the defrost element are contained in a rectangular compartment, the bottom and four sides of the latter outlining the outer dimensions of the whole unit, with the top being formed by the separation between the upper and lower compartments;
the evaporator fan assembly is located directly below an opening in the separation between the upper and lower compartments, and thus able to intake air from either the indoors or the outdoors depending on the orientation of the evaporator air valve which is located also directly above the evaporator fan;
the exiting air stream from the evaporator slab assembly is passing upwards through an opening in the separation between the lower and upper compartments, and is directed onto the condenser discharge air valve, which depending upon its orientation channels the air flow to either the indoor or outdoor discharge opening.
the evaporator assembly, the evaporator fan & motor, fixed and pivoting baffles, and the defrost element are contained in a rectangular compartment, the bottom and four sides of the latter outlining the outer dimensions of the whole unit, with the top being formed by the separation between the upper and lower compartments;
the evaporator fan assembly is located directly below an opening in the separation between the upper and lower compartments, and thus able to intake air from either the indoors or the outdoors depending on the orientation of the evaporator air valve which is located also directly above the evaporator fan;
the exiting air stream from the evaporator slab assembly is passing upwards through an opening in the separation between the lower and upper compartments, and is directed onto the condenser discharge air valve, which depending upon its orientation channels the air flow to either the indoor or outdoor discharge opening.
6. The apparatus according to claim 2 wherein:
the evaporator slab assembly is mounted in a zig-zag pattern on a rotating base, with the individual slabs being placed vertically upright into the airstream of the evaporator fan;
the evaporator assembly and base can be rotated through an angle of 90°;
the assembly having been rotated to one extreme position, the orientation of the evaporator slabs is presenting a surface area to the air stream which is equal to the sum of all the individual slabs;
two fixed baffles are contacting the ends of the two evaporator slabs closest to the sides of the unit, forming a seal with the said slabs, and the air stream is being directed through all the slabs at the same time;
the assembly is rotated to the other extreme position, i.e. 90° from the orientation as mentioned previously, the evaporator slabs present a surface area to the air stream which is equal to the area of a single slab;
two fixed baffles mentioned previously now form a seal with the evaporator slab closest to the fan discharge directing the entire air stream through this slab first;
two pivoting baffles form a seal with the evaporator slab which is traversed last by the air stream, obliging all the air to exit by this slab;
the apexes of the central slabs form a seal with the side of the compartment, thus also obliging the air to pass through each slab in turn;
the exiting air stream from the evaporator slab assembly is passing upwards through an opening in the separation between the lower and upper compartments, and is directed onto the condenser discharge air valve, which depending upon its orientation channels the air flow to either the indoor or outdoor discharge opening.
the evaporator slab assembly is mounted in a zig-zag pattern on a rotating base, with the individual slabs being placed vertically upright into the airstream of the evaporator fan;
the evaporator assembly and base can be rotated through an angle of 90°;
the assembly having been rotated to one extreme position, the orientation of the evaporator slabs is presenting a surface area to the air stream which is equal to the sum of all the individual slabs;
two fixed baffles are contacting the ends of the two evaporator slabs closest to the sides of the unit, forming a seal with the said slabs, and the air stream is being directed through all the slabs at the same time;
the assembly is rotated to the other extreme position, i.e. 90° from the orientation as mentioned previously, the evaporator slabs present a surface area to the air stream which is equal to the area of a single slab;
two fixed baffles mentioned previously now form a seal with the evaporator slab closest to the fan discharge directing the entire air stream through this slab first;
two pivoting baffles form a seal with the evaporator slab which is traversed last by the air stream, obliging all the air to exit by this slab;
the apexes of the central slabs form a seal with the side of the compartment, thus also obliging the air to pass through each slab in turn;
the exiting air stream from the evaporator slab assembly is passing upwards through an opening in the separation between the lower and upper compartments, and is directed onto the condenser discharge air valve, which depending upon its orientation channels the air flow to either the indoor or outdoor discharge opening.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2143881 CA2143881A1 (en) | 1995-03-03 | 1995-03-03 | Multiple function heat pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2143881 CA2143881A1 (en) | 1995-03-03 | 1995-03-03 | Multiple function heat pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2143881A1 true CA2143881A1 (en) | 1996-09-04 |
Family
ID=4155357
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2143881 Abandoned CA2143881A1 (en) | 1995-03-03 | 1995-03-03 | Multiple function heat pump |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2143881A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009011628A1 (en) * | 2007-07-13 | 2009-01-22 | Fredric Dahl | Apparatus for heating and ventilation of indoor spaces |
-
1995
- 1995-03-03 CA CA 2143881 patent/CA2143881A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009011628A1 (en) * | 2007-07-13 | 2009-01-22 | Fredric Dahl | Apparatus for heating and ventilation of indoor spaces |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4259268A (en) | Dual radiator heat exchanger | |
| US6405549B1 (en) | Portable heating unit using a refrigerant circuit movable within a room | |
| US4285210A (en) | Self-contained heating and cooling apparatus | |
| US6167714B1 (en) | Portable cooling and heating unit using reversible refrigerant circuit | |
| US4679411A (en) | Stepped capacity constant volume building air conditioning system | |
| US6481228B1 (en) | Air conditioning module for room partition unit | |
| CA1172040A (en) | Air-conditioning apparatus | |
| KR100430278B1 (en) | Air Conditioner Applying Heatpipes | |
| US4598558A (en) | Heat pump and method | |
| KR100354132B1 (en) | Air handling unit | |
| US4803849A (en) | Refrigeration/evaporative cooler unit | |
| US4786300A (en) | Air conditioner | |
| CA2143881A1 (en) | Multiple function heat pump | |
| JPH0868568A (en) | Air conditioner | |
| US6272880B1 (en) | Air conditioner | |
| KR100567416B1 (en) | Separated type ventilation withdrawal rate adjustment waste heat withdrawal combined cold and heat air conditioner | |
| JP3207043B2 (en) | Outside air treatment unit | |
| US4644759A (en) | Heat pump and method | |
| JPH0633335Y2 (en) | Air conditioners in stores with showcases | |
| JP2004271062A (en) | Air conditioner | |
| PL191519B1 (en) | Method of as well as system and apparatus for controlling air parameters in air-conditioned rooms, in particular those intended to store products being sensitive to climatic conditions | |
| JPH06123469A (en) | Operation controller for dehumidifying unit with air conditioning and ventilating function | |
| JPH10148416A (en) | Dehumidifier | |
| JP3643664B2 (en) | Air conditioner | |
| CA2147203A1 (en) | Multiple function heat pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Dead |