EP2320158A1 - Heat pump system - Google Patents
Heat pump system Download PDFInfo
- Publication number
- EP2320158A1 EP2320158A1 EP09802833A EP09802833A EP2320158A1 EP 2320158 A1 EP2320158 A1 EP 2320158A1 EP 09802833 A EP09802833 A EP 09802833A EP 09802833 A EP09802833 A EP 09802833A EP 2320158 A1 EP2320158 A1 EP 2320158A1
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- EP
- European Patent Office
- Prior art keywords
- refrigerant
- cycle
- heat
- heat source
- cascade condenser
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- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/04—Refrigeration circuit bypassing means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
Definitions
- a series of heat cycles is formed. Each heat cycle corresponds to a stage of the system.
- the stages are called the higher stage (higher temperature side) and the lower stage (lower temperature side); thus, in a multistage cooling/heating system, a sequence structure is defined.
- the sequence structure is defined also in a case where the number of the stages is more than two.
- a heat cycle of a higher stage is connected to the heat cycle of the adjacent lower stage via a cascade connection (i.e. a cascade condenser as a heat exchanger).
- a certain heat cycle comprises a compressor that compresses and feeds the refrigerant (heat carrier) of the heat cycle.
- the load on the environment can be reduced and a high degree of safety can be achieved.
- to cool the objective space or material means to absorb the heat to be cooled (i.e. to absorb the heat corresponding to the objective heat load or the cooling demand load).
- the heat carrier NH 3 in the higher stage is prevented from entering the heat carrier CO 2 in the lower stage, thanks to the adoption of the indirect cooling approach by use of the a relay e heat exchanger (the cascade condenser).
- the present invention aims at providing a heat pump system; whereby, a superior level of safety can be offered; high heat-transfer efficiency can be achieved; the existing facility can be effectively made use of; the lubricating oil for the system_can be easily maintained and managed; the amount of the refrigerant can be restrained to a minimal level.
- the present invention discloses a heat pump system, being provided with:
- the secondary NH 3 refrigerant circulated in the secondary NH 3 refrigerant cycle absorbs the objective heat load (or absorbs the refrigeration load through the evaporator), by the head difference part or by both the head difference part and the circulating pump; in addition, the line system of the NH 3 refrigerant in the heat source cycle and the line system of the NH 3 refrigerant in the secondary NH 3 refrigerant cycle are completely separated from each other by the cascade condenser between the NH 3 heat source cycle and the secondary NH 3 refrigerant cycle; thus, the lubricating oil associated with the compressor in the NH 3 heat source cycle can be prevented from entering the secondary NH 3 refrigerant cycle. Accordingly, the maintenance work in relation to the lubricating oil can be confined within the machine room (the NH 3 heat source cycle), and the safety of the heat pump system can be ensured with simple maintenance.
- a preferable embodiment according to the present invention as described above is the heat pump system whereby secondary NH 3 refrigerant cycle that is directly connected to the heat source cycle via the cascade condenser of the heat source cycle; and, the NH 3 refrigerant in the heat source cycle and the NH 3 refrigerant in the secondary NH 3 refrigerant cycle are separated from each other at the cascade condenser.
- Another preferable embodiment according to the present invention as described above is the heat pump system whereby the secondary NH 3 refrigerant cycle that is indirectly connected to the heat source cycle via a second secondary refrigerant cycle.
- the second secondary refrigerant cycle is provided between the heat source cycle and the secondary NH 3 refrigerant cycle.
- the existing liquid pump approach or a direct expansion system can be used as a configuration of the heat source cycle; further, the secondary NH 3 refrigerant cycle that absorbs the objective load can be additionally provided.
- the components of the existing facility can be made best use of.
- the cascade condenser separates the secondary NH 3 refrigerant cycle from the NH 3 heat source cycle; and the NH 3 refrigerant in a clean condition is used in the secondary NH 3 refrigerant cycle, being free from contamination and aged deterioration; thus, the efficiency of the evaporator can be kept high.
- the cascade condenser completely separates the line system of the secondary NH 3 refrigerant cycle from the line system of the NH 3 heat source cycle; thus, the amount of the refrigerant in the secondary NH 3 refrigerant cycle can be pertinently established in response to the objective heat load (the cooling demand load) to be cooled; accordingly, the amount of the refrigerant in the secondary NH 3 refrigerant cycle can be restrained to a minimum level.
- Fig. 1 shows a configuration example regarding the heat pump system in which a heat source cycle using NH 3 refrigerant and a secondary NH 3 refrigerant cycle using NH 3 refrigerant are combined.
- the symbol A denotes a heat source cycle using NH 3 refrigerant as the heat source
- the symbol B denotes a secondary NH 3 refrigerant cycle using NH 3 refrigerant, the secondary NH 3 refrigerant cycle including an evaporator 8 that generates an output (an absorption heat amount) corresponding to the objective heat load (the cooling demand load) to be cooled.
- the heat source cycle A and the secondary NH 3 refrigerant cycle B are connected to each other so as to perform heat transfer via a cascade condenser 4; namely, the heat source cycle A and the secondary NH 3 refrigerant cycle B are directly connected to each other via the cascade condenser 4.
- the secondary NH 3 refrigerant cycle B comprises the cascade condenser 4 and an evaporator 8; thereby, the cascade condenser 4 functions as a heat absorbing device in the cycle B, and the evaporator 8 functions as a cooling device that absorbs the heat corresponding to the cooling demand load.
- a head (liquid head) difference part H and a circulating pump 6 are provided between the evaporator 8 and the heat absorbing part (namely, the cascade condenser 4 in the example of Fig. 1 ) on the upstream side of the evaporator, in the cycle B.
- a by-pass conduit line is provided in the cycle B so as to bypass the circulating pump 6; a flow rate control valve 5 is provided on the by-pass conduit line so as to be placed parallel to the circulating pump 6.
- the flow rate control valve 5 the NH 3 refrigerant in the secondary NH 3 refrigerant cycle B can be circulated only with the liquid head of the head difference part H; or, the NH 3 refrigerant in the cycle B can be circulated with both the liquid head and the head of the pump 6.
- it can be chosen whether the liquid in the cycle B can be circulated by only the liquid head H or by both the liquid head and the pump head.
- a flow rate control valve 7 is arranged on the downstream side of the circulating pump 6 as well as the flow rate control valve 5.
- the flow rate control valves 5 and 7 are controlled either manually or automatically; thereby, the opening of each valve 5 or 7 is regulated so that the flow rate of the NH 3 refrigerant streaming into the evaporator 8 is maintained within an appropriate range; in addition, the flow rate may be measured by a flow meter or estimated on the basis of the temperatures of the NH 3 refrigerant at the inlet and the outlet of the evaporator 8.
- the heat source cycle A may be configured according to a NH 3 liquid pump approach or a NH 3 direct expansion system; thereby, the heat source cycle (to be modernized) can be configured with the existing liquid pump system or the existing NH 3 direct expansion system; further, the secondary NH 3 refrigerant cycle that absorbs the objective load can be additionally provided.
- the components of the existing facility can be made best use of.
- Fig. 2 shows a heat pump system in which a second secondary refrigerant cycle is arranged between the heat source cycle using NH 3 refrigerant and the secondary NH 3 refrigerant cycle using NH 3 refrigerant; hereby, the configurations of the heat source cycle and the secondary NH 3 refrigerant cycle are the same as those in Fig. 1 ; and the second secondary refrigerant used in the second secondary refrigerant cycle C may be, for instance, NH 3 and CO 2 .
- the symbol A denotes the heat source cycle (of Fig. 2 ) using NH 3 refrigerant as the heat carrier in the heat source cycle, as is the case with the heat source cycle A in Fig. 1 ;
- the symbol B denotes a secondary NH 3 refrigerant cycle (of Fig. 2 ) using NH 3 refrigerant;
- the secondary NH 3 refrigerant cycle is connected to the heat source cycle A (of Fig. 2 ) via the second secondary refrigerant cycle C.
- the heat of second secondary refrigerant cycle C is absorbed in (transferred to) the heat source cycle A via the cascade condenser 4 thereof; the second secondary refrigerant circulates in the second secondary refrigerant cycle C that comprises: the cascade condenser 4 that functions as the heat absorbing device which absorbs heat from the cycle C and transfers the heat to the cycle A; and, a cascade condenser 9 (an evaporator) that functions as a cooling heat supplying device which absorbs heat from the cycle B and transfers the heat to the cycle C.
- the refrigerant to be circulated in the second secondary refrigerant cycle C is not limited to, for instance, NH 3 or CO 2 ; however, natural refrigerants such as NH 3 or CO 2 are preferably used.
- a head (liquid head) difference part H and a circulating pump 10 are provided between the cascade condenser (an evaporator) 9 and the heat absorbing part (namely, the cascade condenser 4 in the example of Fig. 2 ) on the upstream side of the cascade condenser 4, in the cycle B.
- a by-pass conduit line is provided in the second secondary refrigerant cycle C so as to bypass the circulating pump 10; a flow rate control valve 11 is provided on the by-pass conduit line so as to be placed parallel to the circulating pump 10.
- a flow rate control valve 12 is arranged on the downstream side of the circulating pump 10 as well as the flow rate control valve 11, a flow rate control valve 12 is arranged; by controlling the opening of the flow rate control valve 12, the flow rate regarding the second secondary refrigerant streaming into the cascade condenser (the evaporator) 9 is controlled so that the second secondary refrigerant circulates in the second secondary refrigerant cycle C, with a necessary flow rate in response to the required refrigeration load.
- the refrigerant cycle that supplies refrigeration heat to (or absorbs the refrigeration load from) the secondary NH 3 refrigerant cycle B is diversified into multi-stages (i.e. the cycles A and C); thus, the heat pump system as described can easily optimize the amount of refrigerants in contrast to the lumped (single) stage approach. Accordingly, the saving (or minimization) of the refrigerants can be further promoted.
- the refrigerant NH 3 has the properties superior to those of the other general refrigerants; for instance, the evaporative latent heat of the refrigerant NH 3 is higher than that of other general refrigerant.
- the refrigerant NH 3 is applied to the heat source cycle A and the secondary NH 3 refrigerant cycle B; therefore, the power consumption required for circulating the refrigerant NH 3 can be smaller than that required for circulating other brine refrigerant; thus, the performance of the cycle using the refrigerant NH 3 can be enhanced.
- the secondary NH 3 refrigerant is circulated in the secondary NH 3 refrigerant cycle B absorbs the objective heat load (or absorbs the refrigeration load through the evaporator 8), by the head difference part H or by both the head difference part H and the circulating pump 6; in addition, the line system of the NH 3 refrigerant in the cycle A and the line system of the NH 3 refrigerant in the cycle B are completely separated from each other by the cascade condenser 4 (as well as the cascade condenser 9) between the NH 3 heat source cycle A and the secondary NH 3 refrigerant cycle B; thus, the lubricating oil associated with the compressor 1 in the NH 3 heat source cycle A can be prevented from entering the secondary NH 3 refrigerant cycle B. Accordingly, the maintenance work in relation to the lubricating oil can be confined within the machine room (the NH 3 heat source cycle A), and the safety of the heat pump system can be ensured with simple maintenance.
- the cascade condenser 4 (as well as the cascade condenser 9) separates the secondary NH 3 refrigerant cycle B from the NH 3 heat source cycle A; and the NH 3 refrigerant in a clean condition can be used in the cycle B, being free from contamination and aged deterioration; thus, the efficiency of the evaporator 8 can be kept high.
- the cascade condenser 4 (as well as the cascade condenser 9) completely separates the line system of the secondary NH 3 refrigerant cycle B from the line system of the NH 3 heat source cycle A; thus, the amount of the refrigerant in the secondary NH 3 refrigerant cycle B can be pertinently established in response to the objective heat load (the cooling demand load) to be cooled; accordingly, the amount of the refrigerant in the secondary NH 3 refrigerant cycle B can be restrained to a minimum level.
- the NH 3 heat source cycle A and the secondary NH 3 refrigerant cycle B may be connected via a pair (a series pair) of second secondary refrigerant cycles in two stage, although the NH 3 heat source cycle A and the secondary NH 3 refrigerant cycle B in Fig. 2 are connected via the second secondary refrigerant cycle C that itself forms a single stage.
- the flow rate control valves 5 and 11 as well as the circulating pumps 6 and 10 are arranged on the downstream side of the cascade condensers 4 and 9, respectively; thereby, no special apparatus other than pipes are placed between the cascade condenser and the flow rate control valve (or the circulating pump).
- a liquid refrigerant reservoir may be provided just on the down stream side of the cascade condenser 4 or 9. In this way, a stable liquid level regarding the refrigerant is ensured so that the liquid head of the head difference part H can be accurately controlled.
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Abstract
Description
- The present invention relates to a multistage heat pump system using NH3 cooling medium (heat carrier) as a refrigerant at least on a certain lower stage side of the multistage heat pump system.
- In a multistage cooling/heating system, a series of heat cycles is formed. Each heat cycle corresponds to a stage of the system. When the system forms two stages, the stages are called the higher stage (higher temperature side) and the lower stage (lower temperature side); thus, in a multistage cooling/heating system, a sequence structure is defined. In a similar way, the sequence structure is defined also in a case where the number of the stages is more than two. Further, a heat cycle of a higher stage is connected to the heat cycle of the adjacent lower stage via a cascade connection (i.e. a cascade condenser as a heat exchanger). Further, a certain heat cycle comprises a compressor that compresses and feeds the refrigerant (heat carrier) of the heat cycle. Hence, it is inevitable that lubricating oil indispensable for the operation of the compressor gets mixed with the refrigerant, whatever little the amount of the oil is.
- For the sake of improving the above-described technology (heat pump system), a patent reference
JP2005-140349 - a heat pump system source (a higher stage) that includes a compressor, a condenser, and an evaporator; and
- a heat cycle system (a lower stage) that performs an objective heat transfer,
whereby a relay heat exchanger, i.e. a cascade condenser performs heat transfer from the heat cycle system to the heat pump system source, and a heat carrier fluid head and/or a circulating pump feeds the heat carrier, while the heat cycle system is not provided with a compressor. - However, the mentioned patent reference does not refer to any specific heat carrier (refrigerant). This point, on the contrary, makes a skilled person in the field be puzzled about how the technology can be applied to actual subjects.
- In other words, in the patent reference, there is neither teaching nor indication regarding concrete examples of heat carriers or system applications. On the other hand, in this application, a practical heat pump system of a multi-stage type will be disclosed; thereby, for instance, NH3 is used for the higher (temperature) stage and CO2 is used for the lower (temperature) stage, each of the NH3 and CO2 being a natural heat-carrying medium. By applying the heat pump system of two stages where NH3 is used for the higher (temperature) stage so as to cool and liquefy the heat carrier in the adjacent lower stage and CO2 is used for the lower (temperature) stage (e.g. secondary or lower stage) so as to cool the objective space or material, the load on the environment can be reduced and a high degree of safety can be achieved. Hereby, to cool the objective space or material means to absorb the heat to be cooled (i.e. to absorb the heat corresponding to the objective heat load or the cooling demand load). Further, in applying the heat pump system just described, there is another advantage that the heat carrier NH3 in the higher stage is prevented from entering the heat carrier CO2 in the lower stage, thanks to the adoption of the indirect cooling approach by use of the a relay e heat exchanger (the cascade condenser). In this way, only after concrete heat carriers for the multi-medium (heat carrier) and multi-stage heat pump system are determined, the practical system such as a NH3-CO2 (brine) heat pump system as described above can be discussed and planned so as to apply the heat pump system to refrigerating facility and the like.
- In making use of CO2 refrigerant (as a brine heat carrier), however, the pressure of the CO2 refrigerant in the temperature range of the heat exchange process of the CO2 refrigerant cycle is higher than the pressure of the general refrigerant in the temperature range of a heat exchange process of the general refrigerant cycle; accordingly, if the general refrigerant in existing refrigerant facility is planned to be exchanged into CO2 refrigerant, it is needed that the existing piping system corresponding to the existing refrigerant be replaced by a newly build piping system corresponding to CO2 refrigerant. Thus, in this situation, the renewal work is not easily promoted because of high expenditure as to equipment replacement, even though the natural refrigerant such as CO2 is socially desired, in view of environment load reduction.
- Further, in making use of CO2 refrigerant instead of a conventional refrigerant used in the existing facility, there may be a case where the CO2 refrigerant causes a cooling capacity shortage in dealing with a large cooling capacity (refrigeration load).
- Further, in the conventional NH3 refrigeration system (of a multi-stage type) that uses a natural refrigerant such as NH3 refrigerant, the refrigeration device (system) adopts a liquid pump approach or a direct expansion approach (system) in a stage of the multi-stage system; and, it is unavoidable that there remains a very small amount of refrigerator oil in the NH3 refrigerant. The very small amount of refrigerator oil included in the NH3 refrigerant remains in the evaporator, the oil causing performance degradation due to aging deterioration. Thus, the control of the oil becomes a prerequisite matter in order to evade the performance degradation. And, the oil control accompanies complicated procedures or troublesome maintenance work.
- In view of the above-described background, the present invention aims at providing a heat pump system; whereby, a superior level of safety can be offered; high heat-transfer efficiency can be achieved; the existing facility can be effectively made use of; the lubricating oil for the system_can be easily maintained and managed; the amount of the refrigerant can be restrained to a minimal level.
- In order to achieve the above-described objectives, the present invention discloses a heat pump system, being provided with:
- a heat source cycle that comprises a compressor, a condenser, an expansion means, and a cascade condenser, thereby NH3 refrigerant is used as a heat carrier of the heat source cycle;
- a secondary NH3 refrigerant cycle that is directly or indirectly connected to the heat source cycle via the cascade condenser of the heat source cycle, thereby the heat in the secondary NH3 refrigerant cycle is directly or indirectly absorbed through the cascade condenser, the heat in the secondary NH3 refrigerant cycle absorbing an objective heat load;
- a heat absorption part in which the heat in the secondary NH3 refrigerant cycle is directly or indirectly absorbed through the cascade condenser of the heat source cycle, and the secondary NH3 refrigerant is condensed;
- an evaporator that absorbs the objective heat load by the evaporation of the secondary NH3 refrigerant which is condensed through the heat absorption part;
- a head difference part and a circulating pump that are placed between the heat absorption part and the evaporator, so that the head difference part and the circulating pump circulate the secondary NH3 refrigerant;
- a by-pass conduit line that bypasses the circulating pump;
- a flow rate control valve that is placed on the by-pass conduit line.
- In general, the refrigerant NH3 has the properties superior to those of the other general refrigerants. For instance, the evaporative latent heat of the refrigerant NH3 is higher than that of other general refrigerant. According to the heat pump system as described above, the refrigerant NH3 is applied to the heat source cycle and the secondary NH3 refrigerant cycle; therefore, the power consumption required for circulating the refrigerant NH3 can be smaller than that required for circulating other brine refrigerant; thus, the performance of the cycle using the refrigerant NH3 can be enhanced.
- Further, in a case where an existing heat pump system is modernized (improved) with the secondary refrigerant cycle using CO2 refrigerant, namely, in a case where refrigerant CO2 is used instead of the refrigerant NH3 of the secondary NH3 refrigerant cycle from which the heat to be cooled (i.e. the objective heat load or the cooling demand load) is absorbed, the reuse of the components in the existing secondary NH3 refrigerant cycle has to be given up. However, according to the heat pump system of the present invention as described above, the refrigerant NH3 is used for the secondary refrigerant cycle; thus, the existing components in the heat pump system can be reused as they are.
- Further, according to the present invention, the secondary NH3 refrigerant circulated in the secondary NH3 refrigerant cycle absorbs the objective heat load (or absorbs the refrigeration load through the evaporator), by the head difference part or by both the head difference part and the circulating pump; in addition, the line system of the NH3 refrigerant in the heat source cycle and the line system of the NH3 refrigerant in the secondary NH3 refrigerant cycle are completely separated from each other by the cascade condenser between the NH3 heat source cycle and the secondary NH3 refrigerant cycle; thus, the lubricating oil associated with the compressor in the NH3 heat source cycle can be prevented from entering the secondary NH3 refrigerant cycle. Accordingly, the maintenance work in relation to the lubricating oil can be confined within the machine room (the NH3 heat source cycle), and the safety of the heat pump system can be ensured with simple maintenance.
- Further, according to the present invention, the cascade condenser separates the secondary NH3 refrigerant cycle from the NH3 heat source cycle; and the NH3 refrigerant in a clean condition is used in the secondary NH3 refrigerant cycle, being free from contamination and aged deterioration; thus, the efficiency of the evaporator can be kept high.
- Moreover, according to the present invention as described above, the cascade condenser completely separates the line system of the secondary NH3 refrigerant cycle from the line system of the NH3 heat source cycle; thus, the amount of the refrigerant in the secondary NH3 refrigerant cycle can be pertinently established in response to the objective heat load (the cooling demand load) to be cooled; accordingly, the amount of the refrigerant in the secondary NH3 refrigerant cycle can be restrained to a minimum level.
- A preferable embodiment according to the present invention as described above is the heat pump system whereby secondary NH3 refrigerant cycle that is directly connected to the heat source cycle via the cascade condenser of the heat source cycle; and, the NH3 refrigerant in the heat source cycle and the NH3 refrigerant in the secondary NH3 refrigerant cycle are separated from each other at the cascade condenser.
- Another preferable embodiment according to the present invention as described above is the heat pump system whereby the secondary NH3 refrigerant cycle that is indirectly connected to the heat source cycle via a second secondary refrigerant cycle. In other words, the second secondary refrigerant cycle is provided between the heat source cycle and the secondary NH3 refrigerant cycle.
- Further, another preferable embodiment according to the present invention as described above is the heat pump system whereby the refrigerant of the heat source cycle is NH3 and the configuration of the heat source cycle is replaced by a configuration of a liquid pump approach or a direct expansion system.
- As described above, the existing liquid pump approach or a direct expansion system can be used as a configuration of the heat source cycle; further, the secondary NH3 refrigerant cycle that absorbs the objective load can be additionally provided. Thus, the components of the existing facility can be made best use of.
- In general, the refrigerant NH3 has the properties superior to those of the other general refrigerants. For instance, the evaporative latent heat of the refrigerant NH3 is higher than that of other general refrigerant. According to the heat pump system of the present invention, the refrigerant NH3 is applied to the heat source cycle and the secondary NH3 refrigerant cycle; therefore, the power consumption required for circulating the refrigerant NH3 can be smaller than that required for circulating other brine refrigerant; thus, the performance of the cycle using the refrigerant NH3 can be enhanced.
- Further, in a case where an existing heat pump system is modernized (improved) with the secondary refrigerant cycle using CO2 refrigerant, namely, in a case where refrigerant CO2 is used instead of the refrigerant NH3 of the secondary NH3 refrigerant cycle from which the heat to be cooled (i.e. the objective heat load or the cooling demand load) is absorbed, the reuse of the components in the existing secondary NH3 refrigerant cycle has to be given up. However, according to the heat pump system of the present invention as described above, the refrigerant NH3 is used for the secondary refrigerant cycle; thus, the existing components in the heat pump system can be reused as they are.
- Further, according to the present invention, the secondary NH3 refrigerant circulated in the secondary NH3 refrigerant cycle absorbs the objective heat load (or absorbs the refrigeration load through the evaporator), by the head difference part or by both the head difference part and the circulating pump; in addition, the line system of the NH3 refrigerant in the heat source cycle and the line system of the NH3 refrigerant in the secondary NH3 refrigerant cycle are completely separated from each other by the cascade condenser between the NH3 heat source cycle and the secondary NH3 refrigerant cycle; thus, the lubricating oil associated with the compressor in the NH3 heat source cycle can be prevented from entering the secondary NH3 refrigerant cycle. Accordingly, the maintenance work in relation to the lubricating oil can be confined within the machine room (the NH3 heat source cycle), and the safety of the heat pump system can be ensured with simple maintenance.
- Further, according to the present invention, the cascade condenser separates the secondary NH3 refrigerant cycle from the NH3 heat source cycle; and the NH3 refrigerant in a clean condition is used in the secondary NH3 refrigerant cycle, being free from contamination and aged deterioration; thus, the efficiency of the evaporator can be kept high.
- Moreover, according to the present invention as described above, the cascade condenser completely separates the line system of the secondary NH3 refrigerant cycle from the line system of the NH3 heat source cycle; thus, the amount of the refrigerant in the secondary NH3 refrigerant cycle can be pertinently established in response to the objective heat load (the cooling demand load) to be cooled; accordingly, the amount of the refrigerant in the secondary NH3 refrigerant cycle can be restrained to a minimum level.
- The present invention will now be described in greater detail with reference to the preferred embodiments of the invention and the accompanying drawings, wherein:
-
Fig. 1 shows a configuration example regarding the heat pump system in which a heat source cycle using NH3 refrigerant and a secondary NH3 refrigerant cycle using NH3 refrigerant are combined; -
Fig. 2 shows a configuration example regarding the heat pump system in which a second secondary refrigerant cycle is arranged between the heat source cycle using NH3 refrigerant and the secondary NH3 refrigerant cycle using NH3 refrigerant. - Hereafter, the present invention will be described in detail with reference to the embodiments shown in the figures. However, the dimensions, materials, shape, the relative placement and so on of a component described in these embodiments shall not be construed as limiting the scope of the invention thereto, unless especially specific mention is made.
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Fig. 1 shows a configuration example regarding the heat pump system in which a heat source cycle using NH3 refrigerant and a secondary NH3 refrigerant cycle using NH3 refrigerant are combined. - In
Fig. 1 , the symbol A denotes a heat source cycle using NH3 refrigerant as the heat source; the symbol B denotes a secondary NH3 refrigerant cycle using NH3 refrigerant, the secondary NH3 refrigerant cycle including anevaporator 8 that generates an output (an absorption heat amount) corresponding to the objective heat load (the cooling demand load) to be cooled. The heat source cycle A and the secondary NH3 refrigerant cycle B are connected to each other so as to perform heat transfer via a cascade condenser 4; namely, the heat source cycle A and the secondary NH3 refrigerant cycle B are directly connected to each other via the cascade condenser 4. - The heat source cycle A comprises a
compressor 1, acondenser 2, an expansion means 3 (an expansion valve, a capillary tube, etc.), and a cascade condenser 4; thereby, the cascade condenser 4 functions as an evaporator in the heat source cycle A. Further, the heat source cycle A comprises the compression process, the condensation process, the expansion process, and the evaporation process regarding the NH3 refrigerant cycle; thereby, the heat source cycle A absorbs heat from the secondary NH3 refrigerant cycle B, via the cascade condenser 4. - The secondary NH3 refrigerant cycle B comprises the cascade condenser 4 and an
evaporator 8; thereby, the cascade condenser 4 functions as a heat absorbing device in the cycle B, and theevaporator 8 functions as a cooling device that absorbs the heat corresponding to the cooling demand load. A head (liquid head) difference part H and a circulating pump 6 are provided between theevaporator 8 and the heat absorbing part (namely, the cascade condenser 4 in the example ofFig. 1 ) on the upstream side of the evaporator, in the cycle B. - Further, a by-pass conduit line is provided in the cycle B so as to bypass the circulating pump 6; a flow
rate control valve 5 is provided on the by-pass conduit line so as to be placed parallel to the circulating pump 6. By use of the flowrate control valve 5, the NH3 refrigerant in the secondary NH3 refrigerant cycle B can be circulated only with the liquid head of the head difference part H; or, the NH3 refrigerant in the cycle B can be circulated with both the liquid head and the head of the pump 6. In other words, by setting the opening of the flowrate control valve 5, it can be chosen whether the liquid in the cycle B can be circulated by only the liquid head H or by both the liquid head and the pump head. Thus, in a case where the liquid head cannot afford to feed a sufficient flow rate of the NH3 refrigerant streaming through theevaporator 8, a necessary flow rate required from the side of theevaporator 8 can be ensured by the pressure transport with not only the liquid head but also the pump head. - Further, on the downstream side of the circulating pump 6 as well as the flow
rate control valve 5, a flowrate control valve 7 is arranged. - The flow
rate control valves valve evaporator 8 is maintained within an appropriate range; in addition, the flow rate may be measured by a flow meter or estimated on the basis of the temperatures of the NH3 refrigerant at the inlet and the outlet of theevaporator 8. - Further, as described above, the heat source cycle A may be configured according to a NH3 liquid pump approach or a NH3 direct expansion system; thereby, the heat source cycle (to be modernized) can be configured with the existing liquid pump system or the existing NH3 direct expansion system; further, the secondary NH3 refrigerant cycle that absorbs the objective load can be additionally provided. Thus, the components of the existing facility can be made best use of.
-
Fig. 2 shows a heat pump system in which a second secondary refrigerant cycle is arranged between the heat source cycle using NH3 refrigerant and the secondary NH3 refrigerant cycle using NH3 refrigerant; hereby, the configurations of the heat source cycle and the secondary NH3 refrigerant cycle are the same as those inFig. 1 ; and the second secondary refrigerant used in the second secondary refrigerant cycle C may be, for instance, NH3 and CO2. - In
Fig. 2 , the symbol A denotes the heat source cycle (ofFig. 2 ) using NH3 refrigerant as the heat carrier in the heat source cycle, as is the case with the heat source cycle A inFig. 1 ; the symbol B denotes a secondary NH3 refrigerant cycle (ofFig. 2 ) using NH3 refrigerant; the secondary NH3 refrigerant cycle is connected to the heat source cycle A (ofFig. 2 ) via the second secondary refrigerant cycle C. - The heat of second secondary refrigerant cycle C is absorbed in (transferred to) the heat source cycle A via the cascade condenser 4 thereof; the second secondary refrigerant circulates in the second secondary refrigerant cycle C that comprises: the cascade condenser 4 that functions as the heat absorbing device which absorbs heat from the cycle C and transfers the heat to the cycle A; and, a cascade condenser 9 (an evaporator) that functions as a cooling heat supplying device which absorbs heat from the cycle B and transfers the heat to the cycle C.
- The refrigerant to be circulated in the second secondary refrigerant cycle C is not limited to, for instance, NH3 or CO2; however, natural refrigerants such as NH3 or CO2 are preferably used.
- A head (liquid head) difference part H and a circulating
pump 10 are provided between the cascade condenser (an evaporator) 9 and the heat absorbing part (namely, the cascade condenser 4 in the example ofFig. 2 ) on the upstream side of the cascade condenser 4, in the cycle B. - Further, a by-pass conduit line is provided in the second secondary refrigerant cycle C so as to bypass the circulating
pump 10; a flowrate control valve 11 is provided on the by-pass conduit line so as to be placed parallel to the circulatingpump 10. By setting the opening of the flowrate control valve 11, it can be chosen whether the liquid in the cycle C can be circulated by only the liquid head or by both the liquid head and the pump head. - Further, on the downstream side of the circulating
pump 10 as well as the flowrate control valve 11, a flowrate control valve 12 is arranged; by controlling the opening of the flowrate control valve 12, the flow rate regarding the second secondary refrigerant streaming into the cascade condenser (the evaporator) 9 is controlled so that the second secondary refrigerant circulates in the second secondary refrigerant cycle C, with a necessary flow rate in response to the required refrigeration load. - Thus, according to the heat pump system (sometimes called a diversified system or approach) depicted in
Fig. 2 , the refrigerant cycle that supplies refrigeration heat to (or absorbs the refrigeration load from) the secondary NH3 refrigerant cycle B is diversified into multi-stages (i.e. the cycles A and C); thus, the heat pump system as described can easily optimize the amount of refrigerants in contrast to the lumped (single) stage approach. Accordingly, the saving (or minimization) of the refrigerants can be further promoted. - As a principle, the refrigerant NH3 has the properties superior to those of the other general refrigerants; for instance, the evaporative latent heat of the refrigerant NH3 is higher than that of other general refrigerant. According to the heat pump systems described on the basis of the examples in
Figs. 1 and 2 , the refrigerant NH3 is applied to the heat source cycle A and the secondary NH3 refrigerant cycle B; therefore, the power consumption required for circulating the refrigerant NH3 can be smaller than that required for circulating other brine refrigerant; thus, the performance of the cycle using the refrigerant NH3 can be enhanced. - Further, when refrigerant CO2 is used instead of the refrigerant NH3 of the secondary NH3 refrigerant cycle B from which the refrigeration load is absorbed, then the reuse of the components in the existing secondary NH3 refrigerant cycle B has to be given up. According to the heat pump systems described on the basis of the examples in
Figs. 1 and 2 , however, the refrigerant NH3 is used for the secondary refrigerant cycle B; thus, the existing components in the heat pump system can be reused as they are. - Further, according to the present invention, the secondary NH3 refrigerant is circulated in the secondary NH3 refrigerant cycle B absorbs the objective heat load (or absorbs the refrigeration load through the evaporator 8), by the head difference part H or by both the head difference part H and the circulating pump 6; in addition, the line system of the NH3 refrigerant in the cycle A and the line system of the NH3 refrigerant in the cycle B are completely separated from each other by the cascade condenser 4 (as well as the cascade condenser 9) between the NH3 heat source cycle A and the secondary NH3 refrigerant cycle B; thus, the lubricating oil associated with the
compressor 1 in the NH3 heat source cycle A can be prevented from entering the secondary NH3 refrigerant cycle B. Accordingly, the maintenance work in relation to the lubricating oil can be confined within the machine room (the NH3 heat source cycle A), and the safety of the heat pump system can be ensured with simple maintenance. - Further, as described above, the cascade condenser 4 (as well as the cascade condenser 9) separates the secondary NH3 refrigerant cycle B from the NH3 heat source cycle A; and the NH3 refrigerant in a clean condition can be used in the cycle B, being free from contamination and aged deterioration; thus, the efficiency of the
evaporator 8 can be kept high. - Further, as described above, the cascade condenser 4 (as well as the cascade condenser 9) completely separates the line system of the secondary NH3 refrigerant cycle B from the line system of the NH3 heat source cycle A; thus, the amount of the refrigerant in the secondary NH3 refrigerant cycle B can be pertinently established in response to the objective heat load (the cooling demand load) to be cooled; accordingly, the amount of the refrigerant in the secondary NH3 refrigerant cycle B can be restrained to a minimum level.
- Thus far, the explanation in relation to the embodiments according to the present invention is given in detail; incidentally, the present invention shall not be construed as limiting the scope thereof to the embodiments as is described above; it is needless to say that there may be various kinds of modified embodiments within the bounds of the features of the present invention.
- For instance, the NH3 heat source cycle A and the secondary NH3 refrigerant cycle B may be connected via a pair (a series pair) of second secondary refrigerant cycles in two stage, although the NH3 heat source cycle A and the secondary NH3 refrigerant cycle B in
Fig. 2 are connected via the second secondary refrigerant cycle C that itself forms a single stage. - In addition, in the examples of
Figs. 1 and 2 , the flowrate control valves pumps 6 and 10 are arranged on the downstream side of thecascade condensers 4 and 9, respectively; thereby, no special apparatus other than pipes are placed between the cascade condenser and the flow rate control valve (or the circulating pump). However, a liquid refrigerant reservoir may be provided just on the down stream side of thecascade condenser 4 or 9. In this way, a stable liquid level regarding the refrigerant is ensured so that the liquid head of the head difference part H can be accurately controlled.
Claims (4)
- A heat pump system, being provided with:a heat source cycle that comprises a compressor, a condenser, an expansion means, and a cascade condenser, thereby NH3 refrigerant is used as a heat carrier of the heat source cycle;a secondary NH3 refrigerant cycle that is directly or indirectly connected to the heat source cycle via the cascade condenser of the heat source cycle, thereby the heat in the secondary NH3 refrigerant cycle is directly or indirectly absorbed through the cascade condenser, the heat in the secondary NH3 refrigerant cycle absorbing an objective heat load;wherein, the secondary NH3 refrigerant cycle comprises:a heat absorption part in which the heat in the secondary NH3 refrigerant cycle is directly or indirectly absorbed through the cascade condenser of the heat source cycle, and the secondary NH3 refrigerant is condensed;an evaporator that absorbs the objective heat load by the evaporation of the secondary NH3 refrigerant which is condensed through the heat absorption part;a head difference part and a circulating pump that are placed between the heat absorption part and the evaporator, so that the head difference part and the circulating pump circulate the secondary NH3 refrigerant;a by-pass conduit line that bypasses the circulating pump; a flow rate control valve that is placed on the by-pass conduit line.
- The heat pump system according to claim 1, whereby the secondary NH3 refrigerant cycle that is directly connected to the heat source cycle via the cascade condenser of the heat source cycle; and, the NH3 refrigerant in the heat source cycle and the NH3 refrigerant in the secondary NH3 refrigerant cycle are separated from each other at the cascade condenser.
- The heat pump system according to claim 1, whereby the secondary NH3 refrigerant cycle that is indirectly connected to the heat source cycle via a second secondary refrigerant cycle.
- The heat pump system according to any one of claims 1 to 3, whereby the refrigerant of the heat source cycle is NH3 and the configuration of the heat source cycle is replaced by a configuration of a liquid pump approach or a direct expansion system.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US8406508P | 2008-07-28 | 2008-07-28 | |
PCT/JP2009/062469 WO2010013590A1 (en) | 2008-07-28 | 2009-07-08 | Heat pump system |
Publications (3)
Publication Number | Publication Date |
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EP2320158A1 true EP2320158A1 (en) | 2011-05-11 |
EP2320158A4 EP2320158A4 (en) | 2014-05-07 |
EP2320158B1 EP2320158B1 (en) | 2017-11-15 |
Family
ID=41610289
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP09802833.5A Not-in-force EP2320158B1 (en) | 2008-07-28 | 2009-07-08 | Heat pump system |
Country Status (4)
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EP (1) | EP2320158B1 (en) |
JP (1) | JP5246891B2 (en) |
NO (1) | NO2320158T3 (en) |
WO (1) | WO2010013590A1 (en) |
Families Citing this family (6)
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JP5758913B2 (en) | 2010-12-24 | 2015-08-05 | 株式会社前川製作所 | Operation control method of heat pump device |
KR101327818B1 (en) * | 2011-12-16 | 2013-11-08 | 부경대학교 산학협력단 | A hybrid type cascade refrigeration system |
JP5905278B2 (en) * | 2012-01-31 | 2016-04-20 | 株式会社前川製作所 | Monitoring system and monitoring method for refrigeration equipment |
JP6319902B2 (en) * | 2014-07-08 | 2018-05-09 | 株式会社前川製作所 | Ice rink cooling equipment and cooling method |
JP6559339B2 (en) * | 2016-05-10 | 2019-08-14 | 三菱電機株式会社 | Heat pump system |
CN112460863A (en) * | 2020-12-10 | 2021-03-09 | 珠海格力电器股份有限公司 | Water chilling unit and refrigeration control method and device thereof |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0539963A (en) * | 1991-08-02 | 1993-02-19 | Sanki Eng Co Ltd | Cooling and heating device |
JP2005030622A (en) * | 2003-07-07 | 2005-02-03 | Mayekawa Mfg Co Ltd | Ice cream freezer |
WO2006038354A1 (en) * | 2004-09-30 | 2006-04-13 | Mayekawa Mfg. Co., Ltd | Ammonia/co2 refrigeration system |
JP2006214611A (en) * | 2005-02-01 | 2006-08-17 | Nissin Kogyo Kk | Refrigerating device |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2005140349A (en) | 2003-11-04 | 2005-06-02 | Hachiyo Engneering Kk | Heat pump system removing malfunction caused by lubricant intrusion |
-
2009
- 2009-07-08 NO NO09802833A patent/NO2320158T3/no unknown
- 2009-07-08 WO PCT/JP2009/062469 patent/WO2010013590A1/en active Application Filing
- 2009-07-08 JP JP2010522670A patent/JP5246891B2/en not_active Expired - Fee Related
- 2009-07-08 EP EP09802833.5A patent/EP2320158B1/en not_active Not-in-force
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0539963A (en) * | 1991-08-02 | 1993-02-19 | Sanki Eng Co Ltd | Cooling and heating device |
JP2005030622A (en) * | 2003-07-07 | 2005-02-03 | Mayekawa Mfg Co Ltd | Ice cream freezer |
WO2006038354A1 (en) * | 2004-09-30 | 2006-04-13 | Mayekawa Mfg. Co., Ltd | Ammonia/co2 refrigeration system |
JP2006214611A (en) * | 2005-02-01 | 2006-08-17 | Nissin Kogyo Kk | Refrigerating device |
Non-Patent Citations (1)
Title |
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See also references of WO2010013590A1 * |
Also Published As
Publication number | Publication date |
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NO2320158T3 (en) | 2018-04-14 |
JPWO2010013590A1 (en) | 2012-01-12 |
WO2010013590A1 (en) | 2010-02-04 |
JP5246891B2 (en) | 2013-07-24 |
EP2320158B1 (en) | 2017-11-15 |
EP2320158A4 (en) | 2014-05-07 |
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