US20150159919A1 - Heat pump unit - Google Patents
Heat pump unit Download PDFInfo
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- US20150159919A1 US20150159919A1 US14/624,970 US201514624970A US2015159919A1 US 20150159919 A1 US20150159919 A1 US 20150159919A1 US 201514624970 A US201514624970 A US 201514624970A US 2015159919 A1 US2015159919 A1 US 2015159919A1
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- Prior art keywords
- discharge
- refrigerant
- discharge chamber
- refrigerant liquid
- chamber
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/062—Cooling by injecting a liquid in the gas to be compressed
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/08—Cooling; Heating; Preventing freezing
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
- F25B31/008—Cooling of compressor or motor by injecting a liquid
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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
- F25B2400/13—Economisers
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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
- F25B2400/23—Separators
Definitions
- the present invention relates to a heat pump unit and a reciprocating compressor which avoids temperature rise of refrigerant gas being discharged from the reciprocating compressor integrated in a heat pump unit such as a refrigeration unit so as to improve volumetric efficiency of the reciprocating compressor and further enhance capacity of the heat pump unit.
- the present invention also relates to a heat pump unit (including a refrigeration unit) using a reciprocating type compressor for NH 3 which is applicable to all kinds of reciprocating compressors regardless of whether it is a single-stage compressor or a two-stage compressor.
- ammonia gas has a relatively-high ratio of specific heat with such characteristics that the discharge temperature is high and the specific volume becomes larger as shown in FIG. 11 .
- this type of refrigerant it is necessary to suppress the heating (temperature rise) of the intake gas inside the casing of the compressor.
- the heat pump unit of the present invention further comprises an intercooler which is provided in the refrigerant circulating path between the condenser and the expansion valve, the intercooler being connected to the refrigerant circulating path so that refrigerant gas discharged from the lower stage compressor is supplied to the intake chamber or intake area of the upper stage compressor through the intercooler,
- the supply port is provided in the discharge chamber or area for receiving the portion of the refrigerant gas obtained by condensing the discharge gas is provided; the refrigerant liquid is supplied to the discharge chamber or area via the supply port; the discharge chamber or area is cooled by the evaporative latent heat of the refrigerant liquid; and the insulating material is interposed between the discharge chamber and intake chamber so as to effectively suppress the heat transfer from the discharge chamber to the intake chamber.
- valve plate and gasket are widen at edges thereof so as to grip and hold outer edges of the valve plate and the insulation gasket at a joint part of the head cover and the cylinder exterior body from both sides.
- FIG. 3 is a perspective interior elevation of the cylinder top assembly of the reciprocating compressor of the first embodiment.
- FIG. 6 is a system diagram of a refrigeration unit relating to fourth embodiment of the present invention.
- the exterior body 23 of the cylinder is constructed to include two cylinders.
- the exterior body 23 has two openings 23 a in which two cylinders are fitted. And between the pair of the openings 23 a , a depressed portion 46 is provided so as to form an insulation space i between the exterior body 23 and the insulation gasket 39 .
- the temperature of the intake chamber 24 is ⁇ 20 to 0° C., the intake pressure being 0.2 to 0.4 Mpa, the temperature of the discharge chamber 36 being 120 to 140° C. and the discharge pressure being 1.3 to 1.6 Mpa.
- the refrigerant liquid of the refrigerant circulating path 2 a passes through the expansion valve 92 so as to be decompressed and then introduced to the intercooler 91 .
- the refrigerant liquid evaporates in the intercooler absorbing the evaporative latent heat of the discharge gas of the lower stage compressor 3 a inside the intercooler.
- the intercooler 91 of the present embodiment is formed like a closed vessel with a hollow space inside and contact heat exchange takes place between the refrigerant liquid and the discharge gas inside the hollow space.
- a head cover 121 is arranged so as to form a discharge chamber 116 on top of the valve cage 112 .
- the discharge chamber 116 is in communication with the discharge gas passageway 116 a and also feeds the high-pressure discharge gas being discharged from the cylinder 101 to the refrigerant circulating path.
- the temperature rise of the intake refrigerant gas inside the reciprocating compressor is suppressed and the refrigerant gas of high density can be introduced, thereby improving the volumetric efficiency and further enhancing the performance of the heat pump unit such as a refrigeration unit having the reciprocating compressor integrated therein. Therefore, the highly efficient heat pump unit and refrigeration unit of the reciprocating unit in which the temperature rise of the intake gas in the compressor is suppressed and at the same time cooling water is not used, can be obtained.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
Abstract
To prevent the decline in the volumetric efficiency and the decline in the performance of the heat pump having the reciprocating compressor integrated therein by decreasing the temperature of discharge gas in the reciprocating compressor with a simple construction, a heat pump unit 1 constituting a heat pump cycle in which the reciprocating compressor 3, a condenser 5, an expansion valve 7 and an evaporator 8 are interposed in a refrigerant circulating path 2,comprises a refrigerant-liquid returning path 9 for returning a portion of the refrigerant liquid having been condensed by the condenser 5 to a discharge chamber provided in a cylinder top assembly 20 of the reciprocating compressor 3 so that a portion of the refrigerant liquid is supplied to the discharge chamber 36 via the refrigerant-liquid returning path 9 and a discharge gas passageway 36a is cooled by evaporative latent heat of the refrigerant liquid.
Description
- This application is a continuation-in-part of prior application Ser. No. 12/712,553, filed on Feb. 25, 2010, the disclosure of which, in its entirety, including the drawings, claims, and the specification, is incorporated herein by reference.
- The present invention relates to a heat pump unit and a reciprocating compressor which avoids temperature rise of refrigerant gas being discharged from the reciprocating compressor integrated in a heat pump unit such as a refrigeration unit so as to improve volumetric efficiency of the reciprocating compressor and further enhance capacity of the heat pump unit. The present invention also relates to a heat pump unit (including a refrigeration unit) using a reciprocating type compressor for NH3 which is applicable to all kinds of reciprocating compressors regardless of whether it is a single-stage compressor or a two-stage compressor.
- A reciprocating type compressor that compresses gas by alternately opening and closing an intake valve and a discharge valve provided in a cylinder head or an upper part of a cylinder (hereinafter referred as a cylinder top assembly) by reciprocating the piston in the cylinder is well known in the art. Such reciprocating type compressor includes a single-stage reciprocating compressor in which gas drawn into the cylinder by the intake valve is compressed in a single stage and the compressed gas is discharged from the discharge valve, and a two-stage reciprocating compressor in which a compressing part thereof comprising the piston reciprocating in the cylinder includes a lower stage and an upper stage so that the gas compressed at the lower stage is further compressed at the upper stage. It is common that both the single-stage and the two-stage reciprocating compressors are provided with an intake gas passageway as well as a discharge gas passageway in a casing comprising a cylinder block. It is common in conventional cases to provide an intake gas passageway and a discharge gas passageway inside a casing thereof. In the reciprocating compressor integrated in the heat pump unit such as the refrigeration unit, heat exchange happens via a wall surface between discharge gas of high temperature and intake gas of low temperature and thus the temperature of the intake gas rises before being drawn into a cylinder. Therefore, the intake gas expands before reaching the cylinder and specific volume thereof becomes bigger and circulating mass flow decreases significantly. This brings decreased volumetric efficiency in the compressor and decline in cooling capacity of the refrigeration device in which the reciprocating compressor is integrated, or heating capacity of the heat pump unit.
- Especially, ammonia gas has a relatively-high ratio of specific heat with such characteristics that the discharge temperature is high and the specific volume becomes larger as shown in
FIG. 11 . When using this type of refrigerant, it is necessary to suppress the heating (temperature rise) of the intake gas inside the casing of the compressor. -
Patent Reference 1 P2000-18154A) discloses a means to suppress excessive temperature rise in the cylinder during the compression and to eliminate the problem of the deterioration of the lubricant and seizing. This means has cavities at the periphery of the cylinder and by introducing returning refrigerant (cooling medium) returning from an accumulator to the cavities so as to cool a cylinder room. The returning refrigerant passes the cavities and then leads to the intake chamber through communication holes. - [Patent Reference 1] JP2000-18154A
- The means disclosed in
Patent Reference 1 cools the cylinder by introducing the returning cooling media to the cavities provided at the periphery of the cylinder. Therefore, as the discharge gas is not cooled, there is heat exchange between the intake gas and the discharge gas via the wall surface of the casing and the temperature of the intake gas before reaching the cylinder inevitably rises. This brings decreased volumetric efficiency in the compressor and decline in cooling capacity of the refrigeration device in which the reciprocating compressor is integrated, or heating capacity of the heat pump unit. - Moreover, the cavities to which the refrigerant is introduced are provided around the cylinder room, resulting in a larger and heavier compressor, and a large amount of refrigerant is introduced to the cavities, resulting in decreasing the capacity of the heat pump device such as refrigeration device with the compressor.
- In view of the problems above, embodiments of the present invention provide a heat pump unit (including a refrigeration unit) that prevents the temperature rise of the intake gas before being drawn into the cylinder, the heat pump unit being applicable to all kinds of reciprocating compressors for NH3 regardless of whether it is a single-stage compressor or a two-stage compressor. In view of the problems above, embodiments of the present invention prevent the decline in the volumetric efficiency of the reciprocating compressor and the decline in the performance of the heat pump having the reciprocating compressor integrated therein by decreasing the temperature of the discharge gas in the reciprocating compressor with a simple construction.
- Specifically, embodiments of the present invention provide a high-efficient heat pump device and refrigeration device using a reciprocating compressor in which cooling water is not used, the heating of the intake gas being suppressed, and the cooling capacity (volumetric efficiency) being improved.
- To solve the problem above, a heat pump of the present invention, is constructed so that the refrigerant liquid (condensed liquid) is injected to a refrigerant gas space of high temperature of the discharge side (discharge chamber or discharge area in communication with the discharge chamber) of the compressor so as to lower the temperature of the refrigerant gas being discharged, and comprises:
- a heat pump cycle which includes a reciprocating compressor, a condenser, an expansion valve and an evaporator provided in a refrigerant circulating path: and
- a first returning path for refrigerant liquid which returns a portion of the refrigerant liquid having been condensed in the condenser to a discharge chamber provided in a cylinder top assembly of the reciprocating compressor or a discharge area that is in communication with the discharge chamber,
- wherein the portion of the refrigerant liquid is returned to the discharge chamber or discharge area via the first returning path so as to cool the discharge chamber or discharge area by evaporative latent heat of the refrigerant liquid.
- The heat pump unit of the present invention is constructed to return a portion of the refrigerant liquid having been condensed in the condenser to the discharge chamber provided in the cylinder top assembly of the reciprocating compressor or the discharge area that is in communication with the discharge chamber. The refrigerant liquid is evaporated by the heat from the discharge gas in the discharge room or discharge area, and taking the evaporative latent heat from the discharge gas, thereby cooling the discharge chamber or discharge area. By cooling the discharge chamber or area, the heat transfer from the discharge chamber or area to the intake chamber or to the gas passageway is suppressed.
- By this, the temperature rise of the refrigerant gas before being introduced to the cylinder is prevented, thereby suppressing the volume expansion and preventing the decline in the volumetric efficiency of the reciprocating compressor and the decline in the performance of the heat pump having the reciprocating compressor integrated therein.
- In this manner, as the discharge chamber or discharge area being in communication with the discharge chamber is cooled by the evaporative latent heat of the refrigerant and there is no need for cooling water or the like, it is possible to use the heat pump in the desert or other places where the cooling water is hard to get. And this is very inexpensive and causes no damage to the environment.
- The heat pump of the present invention preferably further comprises an injection nozzle which is arranged in the discharge chamber or discharge area and is connected to the first returning path for the refrigerant liquid,
- wherein the refrigerant liquid is injected through the injection nozzle to the discharge chamber or discharge area. By this the evaporation of the refrigerant liquid at the discharge chamber or discharge area is promoted, thereby improving the cooling effect.
- It is preferable in the heat pump unit of the present invention that the reciprocating compressor includes an upper stage compressor and a lower stage compressor, the first returning path for the refrigerant liquid returns the portion of the refrigerant liquid which have been discharged from the upper stage compressor and then condensed in the condenser, to the discharge chamber of the lower stage compressor or the discharge area that is in communication with the discharge chamber, and the portion of the refrigerant liquid is returned to the discharge chamber or discharge area of the lower stage compressor via the first returning path.
- The refrigerant having been discharged from the upper stage compressor and then condensed in the condenser has higher pressure than the discharge chamber or discharge area of the lower stage compressor, and thus the refrigerant can be supplied to the discharge chamber or discharge area of the lower stage compressor without using an intensifier. Therefore, this pump unit does not require a power source or device for supplying the refrigerant liquid.
- In addition to the configurations as described above, it is also preferable that the pump unit further comprises:
- a second returning path for the refrigerant liquid which returns the portion of the refrigerant liquid having been discharged from the upper stage compressor and then condensed in the condenser, to the discharge chamber or discharge area; and
- a pressure booster which is provided in the second returning path,
- wherein the portion of the refrigerant liquid is returned to the discharge chamber or discharge area of the upper stage compressor via the second returning path.
- When the portion of the refrigerant liquid is returned to the discharge chamber or discharge area of the upper stage compressor, a pressure booster such as a liquid pump needs to be provided in the returning path as the pressure booster and the discharge chamber or area of the upper stage compressor have the same pressure.
- By this, the intake gas of the lower stage compressor and the upper stage compressor can be cooled.
- The heat pump unit of the present invention preferably further comprises a heat exchanger for the refrigerant liquid which is provided in the refrigerant circulating path between the condenser and the expansion valve, the heat exchanger being connected to the refrigerant circulating path so that refrigerant gas discharged from the lower stage compressor is introduced to the intake chamber or intake area of the upper stage compressor through the heat exchanger, the refrigerant liquid from the condenser being cooled with the refrigerant gas discharged from the lower stage compressor.
- By this, the refrigerant liquid moving in the circulating path from the condenser to the expansion valve is cooled by the refrigerant gas having been discharged from the upper stage compressor and having been cooled, thereby improving the performance of the heat pump such as refrigeration unit.
- It is preferable that the heat pump unit of the present invention further comprises a heat exchanger for the refrigerant liquid which is provided in the refrigerant circulating path between the condenser and the expansion valve,
- wherein the heat exchanger is connected to the refrigerant circulating path so that refrigerant gas discharged from the lower stage compressor is introduced to the intake chamber or intake area of the upper stage compressor, the refrigerant liquid from the condenser being cooled with the refrigerant gas discharged from the lower stage compressor,
- wherein the heat exchanger for the refrigerant liquid is provided in the refrigerant circulating path in an upstream side of the first or second returning path, and
- wherein a portion of the refrigerant liquid having been cooled in the heat exchanger is supplied to the first or second returning path.
- By this, the refrigerant having been cooled by the heat exchanger can be supplied to the intake chamber or intake area of the lower stage or upper stage compressor, thereby making the upper stage compressor more effective in cooling the discharge gas.
- It is preferable that the heat pump unit of the present invention further comprises an intercooler which is provided in the refrigerant circulating path between the condenser and the expansion valve, the intercooler being connected to the refrigerant circulating path so that refrigerant gas discharged from the lower stage compressor is supplied to the intake chamber or intake area of the upper stage compressor through the intercooler,
- wherein a portion of the refrigerant liquid from the condenser is evaporated in the intercooler so as to cool other refrigerant liquid and the refrigerant gas discharged from the lower stage compressor.
- By this, the performance of the heat pump unit is enhanced and the portion of the high-pressure refrigerant liquid having been over-cooled by the intercooler is supplied to the intake chamber or area of the lower stage compressor so as to improve the cooling effect of the discharge gas of the lower stage compressor and reduce the supply of the refrigerant liquid. Thus, the injection nozzle provided in the discharge chamber or area of the lower stage compressor can be downsized.
- In the case of using NH3 which has high ratio of specific heat as refrigerant, there is such characteristic that when the temperature rises, the specific volume of NH3 gets bigger than other types of refrigerant. The volume expansion of the refrigerant due to the temperature rise of the intake gas before reaching the cylinder is significant. However, with the present invention, the temperature rise of NH3 before being introduced to the cylinder is securely suppressed, thereby avoiding the declined performance of the heat pump unit.
- Next, a first reciprocating compressor of the present invention that can be applied to the heat pump unit of the present invention is a reciprocating compressor for refrigerant which is equipped with an intake chamber connected to a cylinder via an intake valve at a cylinder top assembly and a discharge chamber connected to the cylinder via a discharge valve, the reciprocating compressor comprising:
- a supply port for refrigerant liquid which is provided in the discharge chamber or a discharge area that is in communication with the discharge chamber and through which a portion of the refrigerant liquid obtained by condensing discharge gas is supplied to the discharge chamber or discharge area,
- wherein the supplied refrigerant liquid evaporates in the discharge chamber or discharge area so that the discharge chamber or discharge area is cooled by evaporative latent heat of the refrigerant liquid.
- With the configuration described above, the portion of the refrigerant liquid obtained from condensing the discharge gas is supplied to the discharge chamber or area, thereby cooling the discharge chamber or area by the evaporative latent heat of the refrigerant liquid. Consequently the temperature rise in the discharge chamber or area is diminished and the temperature rise of the intake gas before being introduced to the cylinder is prevented. Thus, the increase of the specific volume of the intake gas is suppressed and the declined volumetric efficiency is avoided.
- In the first reciprocating compressor of the present invention, the compressor further comprises an injection nozzle which is arranged in the discharge chamber or discharge area and is connected to the supply port for the refrigerant liquid,
- wherein the refrigerant liquid is injected through the injection nozzle to the discharge chamber or discharge area.
- By this, the evaporation of the refrigerant liquid in the discharge chamber or area is enhanced, thereby improving the cooling effect of the refrigerant liquid.
- Moreover, a second reciprocating compressor of the present invention that can be applied to the heat pump unit of the present invention for refrigerant which is equipped with an intake chamber connected to a cylinder via an intake valve at a cylinder top assembly and a discharge chamber connected to the cylinder via a discharge valve, is unique in that a heat insulating material is interposed between the intake chamber and the discharge chamber so as to suppress heat transfer between the intake chamber and discharge chamber.
- With the configuration described above, by simply interposing a heat insulating material between the intake chamber and the discharge chamber, the heat transfer between the intake chamber and discharge chamber is prevented. Consequently, the temperature rise of the refrigerant gas before reaching the cylinder is prevented, thereby suppressing the increase of the specific volume of the refrigerant gas and suppressing the decline in the volumetric efficiency. Thus, the performance of the heat pump unit integrating the reciprocating compressor is maintained.
- Furthermore, by combining the first reciprocating compressor and the second reciprocating compressor, it is possible to suppress the heat transfer from the discharge chamber to the intake chamber in a synergistic manner.
- Specifically, the supply port is provided in the discharge chamber or area for receiving the portion of the refrigerant gas obtained by condensing the discharge gas is provided; the refrigerant liquid is supplied to the discharge chamber or area via the supply port; the discharge chamber or area is cooled by the evaporative latent heat of the refrigerant liquid; and the insulating material is interposed between the discharge chamber and intake chamber so as to effectively suppress the heat transfer from the discharge chamber to the intake chamber.
- In the first or second reciprocating compressor of the present invention, it is preferable that
- the cylinder top assembly comprises: a closure plate which closes the cylinder so as to form a discharge gas passage and having the discharge valve at the discharge gas passage; a head cover which covers over the closure plate so as to form the discharge chamber; a valve plate which is arranged under the closure plate so as to enclose the cylinder and in which the intake valve is provided; a cylinder exterior body which is arranged under the valve plate and forms the intake chamber, and
- wherein an insulation gasket is interposed between the valve plate and the cylinder exterior body,
- wherein the valve plate and gasket are widen at edges thereof so as to grip and hold outer edges of the valve plate and the insulation gasket at a joint part of the head cover and the cylinder exterior body from both sides.
- With the configuration described above, the insulation gasket can be easily fixed between the valve plate and the cylinder exterior body. And by interposing the insulation gasket between the valve plate and the cylinder exterior body, the blocking between the intake chamber formed by the cylinder exterior body and the discharge chamber formed above the closure plate is effectively done.
- Furthermore, when the cylinder exterior body encloses a plurality of the cylinders, it is preferable to form an insulation space between the cylinder exterior body and the gasket in an area interposed by the cylinders. By this, the insulation effect can be further enhanced.
- With the heat pump unit of the present invention comprising a heat pump cycle which includes a reciprocating compressor, a condenser, an expansion valve and an evaporator provided in a refrigerant circulating path: and a first returning path for refrigerant liquid which returns a portion of the refrigerant liquid having been condensed in the condenser to a discharge chamber provided in a cylinder top assembly of the reciprocating compressor or a discharge area that is in communication with the discharge chamber, wherein the portion of the refrigerant liquid is returned to the discharge chamber or discharge area via the first returning path so as to cool the discharge chamber or discharge area by evaporative latent heat of the refrigerant liquid, the heat transfer from the discharge chamber or area to the intake chamber or area of the reciprocating compressor is suppressed and the temperature rise and volume expansion of the intake gas before being introduced to the cylinder is suppressed, and the volumetric effect of the reciprocating compressor is prevented from declining. By this, even when the refrigerant with high specific volume such as NH3 is used, the performance of the heat pump unit is maintained. Furthermore, by not using the cooling water, it is possible to use the heat pump in the desert or other places where the cooling water is hard to get. And this is very inexpensive and causes no damage to the environment.
- With the first reciprocating compressor of the present invention for refrigerant which is equipped with an intake chamber connected to a cylinder via an intake valve at a cylinder top assembly and a discharge chamber connected to the cylinder via a discharge valve, the reciprocating compressor comprising: a supply port for refrigerant liquid which is provided in the discharge chamber or a discharge area that is in communication with the discharge chamber and through which a portion of the refrigerant liquid obtained by condensing discharge gas is supplied to the discharge chamber or discharge area, wherein the supplied refrigerant liquid evaporates in the discharge chamber or discharge area so that the discharge chamber or discharge area is cooled by evaporative latent heat of the refrigerant liquid, the heat transfer from the discharge chamber or area to the intake chamber or area of the reciprocating compressor is suppressed and the temperature rise and volume expansion of the intake gas before being introduced to the cylinder is suppressed, and the volumetric effect of the reciprocating compressor is prevented from declining. And by applying this to the aforementioned heat pump unit of the present invention, it is possible to maintain the performance of the heat pump unit.
- With the second reciprocating compressor of the present invention that can be applied to the heat pump unit of the present invention for refrigerant which is equipped with an intake chamber connected to a cylinder via an intake valve at a cylinder top assembly and a discharge chamber connected to the cylinder via a discharge valve, wherein a heat insulating material is interposed between the intake chamber and the discharge chamber so as to suppress heat transfer between the intake chamber and discharge chamber, the heat transfer from the discharge chamber or area to the intake chamber or area of the reciprocating compressor is suppressed with a simple means and the effects similar to that of the first reciprocating compressor of the present invention is obtained.
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FIG. 1 is a system diagram of a refrigeration unit relating to first embodiment of the present invention. -
FIG. 2 is an elevation plan of a cylinder top assembly of the reciprocating compressor to be integrated in the refrigeration unit of the first embodiment. -
FIG. 3 is a perspective interior elevation of the cylinder top assembly of the reciprocating compressor of the first embodiment. -
FIG. 4 is a system diagram of a refrigeration unit relating to second embodiment of the present invention. -
FIG. 5 is a system diagram of a refrigeration unit relating to third embodiment of the present invention. -
FIG. 6 is a system diagram of a refrigeration unit relating to fourth embodiment of the present invention. -
FIG. 7 is a system diagram of a refrigeration unit relating to fifth embodiment of the present invention. -
FIG. 8 is a system diagram of a refrigeration unit relating to sixth embodiment of the present invention. -
FIG. 9 is an elevation plan of a cylinder top assembly of the reciprocating compressor to be integrated in the refrigeration unit of a seventh embodiment. -
FIG. 10 is a system diagram of a refrigeration unit relating to an eighth embodiment of the present invention. -
FIG. 11 is a graph showing the change of specific volume of ammonia gas. -
FIG. 12 is a system diagram of a refrigeration unit relating to ninth embodiment of the present invention. - 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.
- A first embodiment of the present invention which is applied to the refrigeration unit is explained in reference to
FIG. 1 toFIG. 3 .FIG. 1 is a system diagram of a refrigeration unit relating to first embodiment of the present invention (areciprocating compressor 3 being a single-stage compressor). - In
FIG. 1 arefrigeration unit 1 is equipped with a refrigerant circulating passageway for refrigerant MH3, and on the passageway thereciprocating compressor 3, from there down, anoil separator 4, acondenser 5, aliquid receiver 6, anexpansion valve 7, anevaporator 8 are interposed so as to configure a cooling cycle. - The
reciprocating compressor 3 has adischarge chamber 303 being connected to thecylinder 301 via adischarge valve 302 and an intake chamber 305 being connected to the cylinder via aintake valve 304. Thedischarge chamber 303 is provided at an immediate exit side of thedischarge valve 302 and being connected to therefrigerant circulating passageway 2. The intake chamber 305 is provided at an immediate exit side of the intake valve and being connected to therefrigerant circulating passageway 2. The refrigerant gas having been compressed to high pressure in the cylinder is discharged via thedischarge valve 302 to thedischarge chamber 303. - The refrigerant gas having been discharged from the discharge chamber to the
refrigerant circulating passageway 2 is passed through theoil separator 4 so as to separate lubricant oil, and then is sent to thecondenser 5 so as to promote heat loss and condense the refrigerant gas. The condensed refrigerant gas is temporarily stored in theevaporator 8 where evaporative latent heat is absorbed from a load. Subsequently, the refrigerant gas is introduced to the intake chamber 305 of thereciprocating compressor 3 and then to thecylinder 301 via theintake valve 304. The temperatures shown at each part on the circulating passageway inFIG. 1 are the temperatures of the refrigerant (NH3) at those parts. - In the embodiment, a branching
path 9 for diverging the refrigerant liquid from the refrigerant circulating passageway in the downstream of theliquid receiver 6 is provided. The branchingpath 9 is connected to aninjection nozzle 306 located on an inner wall of thedischarge chamber 303. Aliquid pump 11 and a pressure-regulatingvalve 12 located in the downstream side of the liquid pump are interposed in the branchingpath 9. A portion of the refrigerant liquid passes through the branchingpath 9 so as to adjust the pressure thereof by the rotation speed control of theliquid pump 11, and the pressure-regulatingvalve 12, becoming high-pressure in thedischarge chamber 303, and being sprayed from theinjection nozzle 306 into thedischarge chamber 303. The refrigerant liquid having been injected into thedischarge chamber 303 evaporates while absorbing evaporative latent heat if the refrigerant gas in thedischarge chamber 303. - In this manner, the heat transfer from the discharge chamber to the intake chamber is suppressed so as to lower the temperature inside the discharge chamber. Thus, the temperature rise of the refrigerant gas before being introduced into the
cylinder 301 is suppressed. - In the embodiment, an air condensing apparatus is used for the
condenser 5 and a high pressure type or expansion type oil cooler (not shown in the drawings) is used for cooling the lubricant oil of thereciprocating compressor 3 so that a high efficient heat pump unit or refrigeration unit having the reciprocating compressor which does not use cooling water is achieved. - Moreover, it is also possible to arrange the
liquid receiver 6 in an upstream side of thereciprocating compressor 3 in the direction of gravitational force and provide a liquid head so as to omit the liquid pump 11 (this can be applied to other embodiments described below) -
FIG. 2 andFIG. 3 illustrate detailed constructions of a cylinder top assembly of thereciprocating compressor 3. Thereciprocating compressor 3 of the present embodiment has two cylinders. - In
FIG. 2 , apiston 22 is slidably positioned in thecylinder 21. Thecylinder 21 is placed on anexterior body 23. On top of the cylinderexterior body 23, avalve plate 31 is positioned which hasopenings 31 a. Theopenings 31 a are positioned to correspond to the top opening of thecylinders 21. Thevalve plate 31 has cavities in which the plate-type intake valve 25 forming a ring shape and avolute spring 26 on top of the intake valve are housed. - An elastic force of the
volute spring 26 works on theintake valve 25 so as to press theintake valve 25 against avalve seat 27 located on top of thecylinder 21. The intake chamber is located under the intake valve and the intake chamber is in communication with thecylinder 21 by lifting theintake valve 25 with the refrigerant gas against the elastic force of the volute spring working on theintake valve 25. - A
valve cage 32 in a shape of circular plate is provided above thevalve plate 31 so as to close the opening 31 a of thevalve plate 31. Avalve plate 34 in a shape of a conical frustum is joined to the bottom of thevalve cage 32 with abolt 33. Apositioning pin 35 is inserted in a positioning hole of thevalve plate 34 and a positioning hole of thevalve cage 32 so as to position thevalve plate 34 in respect with thevalve cage 32. Thevalve plate 34 is shaped to fit in the top part of thepiston 22 and when thepiston 22 reaches the top limit of thecylinder 21, there is no space in the cylinder. - A
discharge gas passage 36 a is formed in thevalve cage 32 and thevolute spring 37 is provided in thedischarge gas passageway 36 a. Under the volute spring, adischarge valve 38 in a shape of a ring plate is provided. Under thedischarge valve 38, a the valve seat 34 a and anothervalve seat 31 b integral with thevalve plate 31 are arranged. When the pressure of the discharge gas of thecylinder 21 is small, the elastic force of thevolute spring 37 works on thedischarge valve 38 so as to press thedischarge valve 38 against the valve seats 34 a and 31 b, thereby closing thedischarge gas passageway 36 a. When thepiston 22 is lifted and the pressure of the discharge gas becomes larger, the discharge gas lifts thedischarge valve 38 so as to open thedischarge gas passageway 36 a. - A plate-
like insulation gasket 39 made of insulation material is interposed between thevalve plate 31 and the cylinderexterior body 23. Above thevalve cage 32, ahead cover 40 is arranged so as to form adischarge chamber 36 on top of thevalve cage 32. Thedischarge chamber 36 is in communication with thedischarge gas passageway 36 a and also feeds the high-pressure discharge gas being discharged from thecylinder 21 to the refrigerant circulatingpath 2. The branchingpath 9 is connected to a through-bore 40 a formed in the head cover, and aninjection nozzle 306 is provided in the opening of an inner wall of the head cover. By this, the refrigerant liquid of the branchingpath 9 is sprayed into thedischarge chamber 36. - As shown in
FIG. 3 , abolt seat 41 is arranged at the outer edge of thehead cover 40, and boltholes bolt seat 41,valve plate 31,insulation gasket 39 and cylinderexterior body 23 respectively which are integrally connected with bots not shown in the drawings. - Moreover, in the present embodiment, the
exterior body 23 of the cylinder is constructed to include two cylinders. Thus, theexterior body 23 has twoopenings 23 a in which two cylinders are fitted. And between the pair of theopenings 23 a, adepressed portion 46 is provided so as to form an insulation space i between theexterior body 23 and theinsulation gasket 39. - In the reciprocating compressor of
FIG. 2 andFIG. 3 , thepiston 22 moves downward and thus forming low pressure in thecylinder 21 and the intake gas g1 pushes up theintake valve 25 against the elastic force of thespring 26 so as to introduce the intake gas g1 into thecylinder 21. Next thepiston 22 moved upward and it becomes high pressure inside the cylinder, and the discharge gas g2 pushes up thedischarge valve 38 against the elastic force of thevolute spring 37 so as to discharge the discharge gas g2 of high pressure to thedischarge chamber 36 via thedischarge gas passageway 36 a. - When the reciprocating unit is housed in the
refrigeration unit 1, for instance, the temperature of theintake chamber 24 is −20 to 0° C., the intake pressure being 0.2 to 0.4 Mpa, the temperature of thedischarge chamber 36 being 120 to 140° C. and the discharge pressure being 1.3 to 1.6 Mpa. - The cylinder
top assembly 20 is heated by the heated discharge gas g2. However, in the present embodiment, the refrigerant liquid is sprayed from the branchingpath 9 into thedischarge chamber 36 via theinjection nozzle 306, the sprayed refrigerant liquid cooling the discharge gas by the evaporative latent eat of the discharge gas, and theinsulation gasket 39 being interposed between the valve plate and the cylinderexterior body 23 so as to suppress effectively the heat transfer from the discharge gas g2 through theexterior body 23 to the intake gas g1 moving through the intake chamber. - In this manner, the temperature rise of the intake gas g1 before being introduced to the
cylinder 21 is suppressed, thereby inhibiting the volumetric expansion of the intake gas g1. For instance, as shown inFIG. 1 , the refrigerant liquid of 35° C. is injected to theinjection nozzle 306 so as to reduce the temperature of the discharge gas inside thedischarge chamber 303 to 50° C. and reduce the temperature of the intake gas inside the intake chamber 305 to −10° C. Thus, the volume expansion of the refrigerant gas being introduced to the cylinder is prevented, thereby suppressing the decline of the volumetric efficiency of thereciprocating compressor 3. In this manner, the performance of the reciprocating compressor integrated in therefrigeration unit 1 is maintained. - Especially, NH3 which is used as refrigerant has high ratio of specific heat and the volume expansion due to the temperature rise is significant and thus the decline of the volumetric efficiency of the reciprocating unit becomes large. However, with the present invention, the decline of the volumetric efficiency of the reciprocating unit is suppressed and the performance of the
refrigeration unit 1 is sustained. - Moreover, in the present embodiment, the temperature of the intake gas is suppressed by the evaporative latent heat of the refrigerant liquid and the insulation gasket 19 and does not require cooling water. Therefore, it is possible to use the heat pump in the desert or other places where the cooling water is hard to get. And this is very inexpensive and causes no damage to the environment.
- In the present embodiment, the refrigerant liquid is sprayed to the
discharge chamber 36 in a form of fine particles through theinjection nozzle 306 so as to improve the absorption effect of the evaporative latent heat of the discharge gas. Moreover, theinsulation gasket 39 is installed from theintake chamber 24 to the outer edge of the cylinderexterior body 23 so as to shut off the heat of the discharge gas in a wide range where theinsulation gasket 39 is installed. Therefore, the heat transfer of the discharge gas to the cylinderexterior body 23 is effectively prevented. - Additionally, the insulation space i is provided in the cylinder
exterior body 23 and between theplural cylinders 21 so as to improve the heat insulation effect. - Next, a second embodiment of the present invention (the
reciprocating compressors refrigerant path 2 a between aliquid receiver 6 and anexpander 7 in the two-stage compression and the single-stage expansion) is explained in reference toFIG. 4 . InFIG. 4 , arefrigeration unit 1 has a two-stage reciprocating compressor consisting of alower stage compressor 3 a and anupper stage compressor 3 b. The configuration of the cylinder top assembly of the lower andupper stage compressors FIG. 2 andFIG. 3 . - The refrigerant liquid from the
liquid receiver 6 passes through the refrigerant circulatingpath 2 a and reaches theexpansion valve 7. The refrigerant liquid is decompressed by theexpansion valve 7, the decompressed refrigerant liquid evaporating in theevaporation unit 8 by taking the evaporative latent heat from, and the evaporated refrigerant gas being introduced to the intake chamber 305 of thelower stage compressor 3 a. The refrigerant gas being introduced to the intake chamber 305 is then introduced to thecylinder 301 via theintake chamber 304 and compressed in thecylinder 301. - The refrigerant gas being compressed in the
cylinder 301 is fed to thedischarge chamber 303 via thedischarge valve 302, and then discharged from thedischarge chamber 303 to the refrigerant circulatingpath 2 b. The refrigerant gas being discharged form the refrigerant circulatingpath 2 b is filtered in theoil separator 4 a so as to separate the lubricant oil and then introduced into the intake chamber 305 of theupper stage compressor 3 b. - The refrigerant gas being introduced to the intake chamber 305 of the
upper stage compressor 3 b is compressed in thecylinder 301 of theupper stage compressor 3 b and then discharged form thedischarge chamber 303 to the circulatingpath 2 c. The refrigerant gas being discharged to the circulatingpath 2 c is filtered by theoil separator 4 b so as to separate the lubricant oil and the filtered refrigerant gas releases the heat and condensed in thecondenser 5. - In the present embodiment, a branching
path 51 is provided which branches from the refrigerant circulatingpath 2 a in the downstream side of theliquid receiver 6. In the branchingpath 51, aliquid pump 52 and apressure regulating valve 53 are provided. The terminal of the branchingpath 51 is connected to the discharge chamber of theupper stage compressor 3 b. By the rotation speed control of theliquid pump 52, and the pressure control of pressure-regulatingvalve 53, the refrigerant liquid is pressurized to a higher pressure than that of thedischarge chamber 303 of theupper stage compressor 3 b and sprayed into thedischarge chamber 303 via theinjection nozzle 306. - Another branching
path 54 branches from the circulatingpath 2 a in the downstream side of the branchingpath 51 and the branchingpath 54 is connected to theinjection nozzle 306 provided on the inner wall of thedischarge chamber 303 of thelower stage compressor 3 a. Inside of thedischarge chamber 303 of thelower stage compressor 3 a has a lower pressure than the branchingpath 54, and thus there is no need for increasing the pressure of the refrigerant liquid and the refrigerant liquid can be supplied to thedischarge chamber 303 without increasing the pressure. - In the present embodiment, the refrigerant liquid is sprayed into the
discharge chamber 303 of theupper stage compressor 3 b and thelower stage compressor 3 a from the branchingpath discharge chamber 303 with the potential heat of the discharge gas, and the evaporative latent heat is taken from the discharge gas so as to cool the discharge gas. Therefore, the heat transfer from thedischarge chamber 303 to the intake chamber 305 in thelower stage compressor 3 a and theupper stage compressor 3 b is prevented. - As shown in
FIG. 2 andFIG. 3 , in thecylinder head 20 of thelower stage compressor 3 a and theupper stage compressor 3 b, theinsulation gasket 39 is interposed between thevalve plate 31 and the cylinderexterior body 23 so as to suppress the heat transfer from the discharge chamber to the intake chamber by theinsulation gasket 39. - As shown in
FIG. 4 , the temperature of the intake chamber 305 of thelower stage compressor 3 a is suppressed to −25° C. and the temperature of the intake chamber 305 of theupper stage compressor 3 b is suppressed to 15° C. so as to prevent the decline of the volumetric efficiency of the reciprocating compressor and further maintain the performance of therefrigeration unit 1. - The pressure in the
discharge chamber 303 of theupper stage compressor 3 b and that of the branchingpath 51 are the same and thus when supplying the refrigerant liquid to thedischarge chamber 303 of theupper stage compressor 3 b from the branchingpath 51, it does not require thepressure regulating valve 53 to increase the pressure of the refrigerant liquid by theliquid pump 52 and thepressure regulating valve 53. On the other hand, thedischarge chamber 303 of thelower stage compressor 3 a has low pressure and thus when supplying the refrigerant liquid from the branchingpath 54 to thedischarge chamber 303 of thelower stage compressor 3 a, it does not need pressure intensifying. Therefore, the pressure booster is not needed and it requires less power. - The temperature of the intake gas of the
lower stage compressor 3 a is lower than that of the intake gas of the upper stage compressor. For instance, the temperature of the intake gas of thelower stage compressor 3 a is −30° C. and the temperature difference of the lower stage compressor is large compared to that of the upper stage compressor. Therefore, the temperature rise of the intake gas due to the heat transfer from the discharge gas affects thelower stage compressor 3 a more than theupper stage compressor 3 b. And by supply the refrigerant liquid to thedischarge chamber 303 of thelower stage compressor 3 a to the branchingpath 54, the temperature suppressing effect of the intake gas is enhanced and the decline of the cooling capability is avoided. - Next, a third embodiment of the present invention (
Case 1 of a single stage expansion and the twostage reciprocating compressors intercooler 61 feeds the refrigerant liquid in the side of theliquid receiver 6 to theexpansion valve 7 and theevaporation unit 8 via a heat-transfer pipe 61 and the refrigerant liquid is not decompressed in the intercooler 61) is explained in reference toFIG. 5 . InFIG. 5 , aheat exchanger 61 for liquid gas is provided in the refrigerant circulatingpath 2 a in the downstream side of theliquid receiver 6, and to the heat exchanger, connected is the refrigerant circulatingpath 2 b of the downstream side of theoil separator 4 a. And heat exchange take place in theheat exchanger 61 between the refrigerant liquid from theliquid receiver 6 and the discharged refrigerant gas in the downstream side of theoil separator 4 a, and the refrigerant liquid is cooled by the discharge refrigerant gas. - The refrigerant liquid from the
liquid receiver 6 passes through the refrigerant circulatingpath 2 a and reaches theexpansion valve 7. The refrigerant liquid is decompressed by theexpansion valve 7, the decompressed refrigerant liquid evaporating in theevaporation unit 8 by taking the evaporative latent heat from, and the evaporated refrigerant gas being introduced to the intake chamber 305 of thelower stage compressor 3 a. The refrigerant gas being introduced to the intake chamber 305 is then introduced to thecylinder 301 via theintake chamber 304 and compressed in thecylinder 301. The rest of the configuration is the same as that of the second embodiment shown inFIG. 4 and the same devices or units have the same reference numbers as the second embodiment, which will not be further explained herein. - The refrigerant liquid of the downstream side of the liquid receiver is supplied to the
discharge chamber 303 of thelower stage compressor 3 a via the branchingpath 54, and as shown inFIG. 2 , is sprayed into thedischarge chamber 303 via theinjection nozzle 306. Next, the refrigerant liquid is evaporated so as to lower the temperature of the discharge gas inside thedischarge chamber 303. For instance, if the condensation temperature is 35° C. and the evaporation temperature is −30° C., the temperature of the refrigerant liquid in thecondenser 5 and theliquid receiver 6 is 35° C. and the refrigerant liquid is evaporated in thedischarge chamber 303 and the evaporative latent heat is absorbed so as to lower the temperature of the discharge gas in thedischarge chamber 303 to 10° C. - The discharge gas having been cooled to 10° C. is introduced to the
heat exchanger 61 in which the refrigerant liquid having thetemperature 35° C. from theliquid receiver 6 is cooled to 30° C. in theheat exchanger 61. - In this manner, with the present embodiment, the similar function effect to the second embodiment is obtained and by cooling the refrigerant liquid at the exit side of the
liquid receiver 6 by the discharge gas of thelower stage compressor 3 a in theheat exchanger 61, the refrigeration capability of therefrigeration unit 1 is further enhanced and COP can be improved. - In the
upper stage compressor 3 b, the head cover (discharge chamber 303) may be cooled by water instead of injection of the refrigerant liquid (injection nozzle 306), or maybe cooled by air depending on the temperature conditions. - Next, a fourth embodiment of the present invention (
Case 2 of single stage expansion and the twostage reciprocating compressors intercooler 61 which has the configuration similar to the third embodiment) is explained in reference toFIG. 6 . InFIG. 6 , the branchingpath 71 branches off from a refrigerantexit pipe path 70 in the downstream side of theheat exchanger 61 and is connected to thedischarge chamber 303 of thelower stage compressor 3 a. The rest of the configuration is similar to the third embodiment and thus the same devices and units will not be explained further. - The terminal of the branching
path 71 is connected to theinjection nozzle 306 provided in the discharge chamber of thelower stage compressor 3 a and the configuration of thedischarge chamber 303 is the same as the first, second and third embodiments. - According to the present embodiment, in addition to the cooling effect of the discharge gas in the
discharge chamber 303 of the lower stage andupper stage compressors heat exchanger 61 is supplied to thedischarge chamber 303 of the lower stage compressor 32 a via the branchingpath 71, thereby further improving the cooling effect of the discharge gas of thedischarge chamber 303. Therefore, the supply of the refrigerant liquid to the branchingpath 71 can be reduced, thereby downsizing theinjection nozzle 306. - Moreover, in the present embodiment, in the
upper stage compressor 3 b, the head cover (discharge chamber 303) may be cooled by water instead of injection of the refrigerant liquid (injection nozzle 306), or maybe cooled by air depending on the temperature conditions as suggested in the above-described embodiments. - Next, a fifth embodiment of the present invention (
Case 3 of using single stage expansion and the twostage reciprocating compressors intercooler 61 which forcibly cool inside of theintercooler 81 by injecting the refrigerant liquid by the expansion valve 83) is explained in reference toFIG. 7 . The present embodiment replaces theheat exchanger 61 of the fourth embodiment shown inFIG. 4 with theintercooler 81 and the rest of the configuration other than theintercooler 81 and the surrounding components thereof is the same as the fourth embodiment. Theintercooler 81 has a branchingpath 82 branching from the refrigerant circulatingpath 2 a in the upstream side of theintercooler 81 and theexpansion valve 83 is provided in the branchingpath 82. - The
intercooler 81 of the present embodiment has a heat-transfer pipe path 81 a in communication with the refrigerant circulating path therein and a space in which the discharge refrigerant gas of thelower stage compressor 3 a is filled is provided outside of thepipe path 81 a and the heat exchange takes place between the refrigerant liquid moving through thepipe path 81 a and the discharge refrigerant gas through the pipe wall of thepipe path 81 a. - Moreover, the refrigerant liquid been heat-transferred in the
pipe path 81 a of theintercooler 81 is introduced to the expansion valve via the exitside pipe path 70. - Furthermore, the branching
path 71 branches off from the refrigerantexit pipe path 70 in the downstream side of theheat exchanger 61 and is in communication with the discharge chamber of thelower stage compressor 3 a. - With the configuration above, the refrigerant liquid being introduced to the branching
path 82 passes through theexpansion valve 83 so as to be decompressed and then introduced to theintercooler 81. The refrigerant liquid evaporates in the intercooler absorbing the evaporative latent heat, thereby improving the cooling effect of the refrigerant liquid introduced to thepipe path 81 a of theintercooler 81 from the refrigerant circulatingpath 2 a. The refrigerant liquid is cooled in theintercooler 81, for instance to 25° C. - Consequently, with the present embodiment in comparison with the fourth embodiment, the cooling effect of the refrigerant liquid by the
intercooler 81 is improved, thereby further reducing the temperature of the refrigerant liquid at the exit side of theintercooler 81. Thus, the temperature of the refrigerant being supplied to thedischarge chamber 303 of thelower stage compressor 3 a from the branchingpath 71 can be further reduced, thereby further improving the temperature regulating effect of the discharge gas of thelower stage compressor 3 a. Furthermore, the cooling effect of the refrigerant liquid being introduced to the expansion valve is improved, further enhancing the cooling capability of therefrigeration unit 1. - Next, a sixth embodiment of the present invention (Case of using the two stage reciprocating compressors and a two-stage expansion with an
intercooler 91. The two-stage expansion is performed such that the refrigerant liquid from theliquid receiver 6 is injected from theexpansion valve 92 to anexpansion space 91 a inside theintercooler 91 and the refrigerant liquid received in the bottom of the space is introduced to theevaporation unit 8 via theexpansion valve 7.) is explained in reference toFIG. 8 . The present embodiment replaces theheat exchanger 61 of the third embodiment with theintercooler 91. And theexpansion valve 92 is provided in the refrigerant circulatingpath 2 a in the upstream side of theintercooler 91. The rest of the configuration is the same as the third embodiment. - With this configuration, the refrigerant liquid of the refrigerant circulating
path 2 a passes through theexpansion valve 92 so as to be decompressed and then introduced to theintercooler 91. The refrigerant liquid evaporates in the intercooler absorbing the evaporative latent heat of the discharge gas of thelower stage compressor 3 a inside the intercooler. Theintercooler 91 of the present embodiment is formed like a closed vessel with a hollow space inside and contact heat exchange takes place between the refrigerant liquid and the discharge gas inside the hollow space. - According to the present embodiment in comparison with the third embodiment, by providing the
intercooler 91 instead of theheat exchanger 61, the cooling effect of the refrigerant liquid reaching the expansion valve is further enhanced (e.g. cooling to 1° C.) and the cooling effect of the refrigerant gas being supplied to the discharge chamber 305 of theupper stage compressor 3 b is enhanced as well (e.g. cooling to 6° C.). - Furthermore, in comparison with the fifth embodiment shown in
FIG. 7 , it does not require the heat transfer pipe arranged in theintercooler 91, thereby reducing equipment cost. - Next, a seventh embodiment of the present invention is explained in reference to
FIG. 9 .FIG. 9 illustrates an elevation plan of a cylindertop assembly 100 of the reciprocating compressor to be integrated in the refrigeration unit of the present invention. The reciprocating compressor of the present embodiment comprises a pair of cylinders. - As illustrated in
FIG. 9 , apiston 102 is slidably positioned in thecylinder 101. Thecylinder 101 is placed on anexterior body 103. On top of the cylinderexterior body 103, avalve plate 111 is positioned which has openings 111 a. The openings 111 a are concentrically positioned to correspond to the top opening of thecylinders 101. Thevalve plate 111 has cavities in which the plate-type intake valve 105 forming a ring shape and avolute spring 106 on top of the intake valve are housed. - An elastic force of the volute spring 1066 works on the
intake valve 105 so as to press theintake valve 105 against a top of thecylinder 101. Anintake chamber 104 and anintake gas passageway 104 a in communication with theintake chamber 104 are arranged under theintake valve 105. When thepiston 102 moves downward in thecylinder 101, the pressure in thecylinder 101 becomes small, causing the pressure difference between thecylinder 101 and theintake chamber 104. During the step, the refrigerant gas g1, lifts theintake valve 105 and is introduced into the cylinder. - A
valve cage 112 in a shape of circular plate is provided above thevalve plate 111 so as to close the opening 111 a of thevalve plate 111. A valve plate 114 in a shape of a conical frustum is joined to the bottom of thevalve cage 112 with abolt 113. - A
discharge gas passageway 116 a is formed in thevalve cage 112 and a volute spring is equipped on thevalve cage 112. Under thevolute spring 117, a plate-like discharge valve 118 in a shape of a ring is provided beside thedischarge gas passageway 116 a. - When the piston rises and the pressure of the discharge gas of the
cylinder 101 becomes large, the discharge gas g2 pushes up thedischarge valve 118 and is discharged to thedischarge gas passageway 116 a. - Above the
valve cage 112, ahead cover 121 is arranged so as to form adischarge chamber 116 on top of thevalve cage 112. Thedischarge chamber 116 is in communication with thedischarge gas passageway 116 a and also feeds the high-pressure discharge gas being discharged from thecylinder 101 to the refrigerant circulating path. - The refrigerant gas g2 being discharged from the
discharge gas passageway 116 a to thedischarge chamber 116 passes through apassageway 107 formed in the cylinderexterior body 103 and is fed to the refrigerant circulating path. Thepassageway 107 is arranged adjacent to theintake chamber 104 and theintake gas passageway 104 a via a wall of a partition wall of theexterior body 103. - As illustrated in
FIG. 9 , both of thehead cover 121 and the cylinderexterior body 103 have through-bores pipe paths pipe path 9 ofFIG. 1 . The through-bore 121 a opens to the inner wall of the head cover and the through-bore 121 b opens to thepassageway 107. And theinjection nozzles bores discharge chamber 116 and thepassageway 107 via the branchingpipe paths - On the surface of the
head cover 121, a coolingwater filling space 125 is hermetically formed such that a coolingwater jacket 124 covers the head cover. A coolingwater supply hole 124 a is provided in the coolingwater jacket 124 so as to fill thespace 125 with the cooling water w from thehole 124 a. - In the present embodiment, the refrigerant liquid is sprayed to the
discharge chamber 116 and thepassageway 107 in a form of fine particles through theinjection nozzle - The
passageway 107 is arranged adjacent to theintake chamber 104 and theintake gas passageway 104 a via a wall of a partition wall of theexterior body 103. But the heating of the discharge gas passing through theintake chamber 104 and theintake gas passageway 104 a is prevented by spraying the refrigerant liquid to thepassageway 107 through theinjection nozzle 123 b and suppressing the temperature rise of the discharge gas. - An eighth embodiment of the present invention is explained in reference to
FIG. 10 . In the present embodiment shown inFIG. 10 , in comparison with the first embodiment shown inFIG. 1 toFIG. 3 , the branchingpath 9 branching the refrigerant liquid in the downstream side of theliquid receiver 6 is omitted in therefrigeration unit 1 and the branchingpipe path 9 is not connected inside thedischarge chamber 303 of the singlestage reciprocating compressor 3, and the injection nozzle is not installed. The rest of the configuration is the same as the first embodiment of the present invention. - In the present embodiment, the cooling of the discharge gas in the
discharge chamber 36 by using the evaporative latent heat of the condensed refrigerant liquid is not conducted. - And the heat transfer between the
intake chamber 36 anddischarge chamber 24 is prevented by installing theinsulation gasket 39 between thevalve plate 31 and the cylinderexterior body 2, thereby suppressing the temperature rise of the intake gas in theintake chamber 24. Moreover as shown inFIG. 3 , the insulation space i is formed between the cylinder exterior body and the gasket in an area interposed by the cylinders, thereby enhancing the insulation effect. - By this, the temperature rise of the intake gas before reaching the cylinder is suppressed, thereby avoiding the decline in the volumetric efficiency of the reciprocating compressor and maintaining the refrigerating capability of the
refrigeration unit 1. - Next, a ninth embodiment of the present invention (in the case of using single stage expansion and the two
stage reciprocating compressors intercooler 81. Theintercooler 81 is forcibly cooled inside by injecting the refrigerant liquid by theexpansion valve 83 and the refrigerant at room temperature of theliquid receiver 6 is supplied to the discharge chamber 303) is explained in reference toFIG. 12 . The present embodiment shares the same configuration with the fifth embodiment besides theintercooler 81 and the surrounding components. The refrigerant circulatingpath 2 a comprises apathway 2 a arranged through theintercooler 81 and anotherpathways pathway 2 a to bypass the intercooler. The refrigerant at room temperature of the liquid receiver is fed to thenozzle 306 of the discharge chamber of thelower stage compressor 3 a. - With the configuration as described above, preferable effects described below can be obtained in comparison with the case of supplying the low temperature refrigerant having passed through the
intercooler 81 to thedischarge chamber 303 of thelower stage compressor 3 a. - The
intercooler 81 and the heat-transfer pipe path 81 a (for low temperature liquid) are insulated so as to avoid the heating from the external air (or the temperature of the surrounding devices). - Especially, when the heat penetrates from outside through the valve or the like to the pipe or heat exchanger which is full of liquid, it is prone to the heat expansion and thus causing explosion from where it is weak. However, in the present embodiment the
pathway 2 a arranged through the intercooler and anotherpathways pathway 2 a to bypass theintercooler 81 are provided in such a manner that the refrigerant at room temperature of theliquid receiver 6 is directly led to thedischarge chamber 303 of thelow stage compressor 3 a, thereby solving the above problem. - According to the present invention, the temperature rise of the intake refrigerant gas inside the reciprocating compressor is suppressed and the refrigerant gas of high density can be introduced, thereby improving the volumetric efficiency and further enhancing the performance of the heat pump unit such as a refrigeration unit having the reciprocating compressor integrated therein. Therefore, the highly efficient heat pump unit and refrigeration unit of the reciprocating unit in which the temperature rise of the intake gas in the compressor is suppressed and at the same time cooling water is not used, can be obtained.
Claims (8)
1. A heat pump unit comprising:
a heat pump cycle which includes a reciprocating compressor having a compression part where a piston reciprocates inside a cylinder, a condenser, an expansion valve, and an evaporator provided in a refrigerant circulating path in which NH3 refrigerant liquid is circulated; and
a first returning path for the refrigerant liquid which returns a portion of the NH3 refrigerant liquid having been condensed in the condenser to a discharge chamber provided in a cylinder top assembly of the reciprocating compressor or a discharge area that is in communication with the discharge chamber,
wherein the discharge chamber or the discharge area is provided with an injection nozzle connected to the first returning path for the refrigerant liquid such that the NH3 refrigerant liquid is discharged through the injection nozzle to the discharge chamber or the discharge area.
2. The heat pump unit according to claim 1 , further comprising a liquid pump and a pressure-regulating valve located in the first returning path for the refrigerant liquid, and the NH3 refrigerant liquid which has higher pressure than the discharge chamber is discharged through the injection nozzle to the discharge chamber or the discharge area.
3. The heat pump unit according to claim 1 , wherein the reciprocating compressor is a single-stage compressor provided with the injection nozzle in the discharge chamber or the discharge area of the single-stage compressor.
4. The heat pump unit according to claim 1 ,
wherein the reciprocating compressor is a multi-stage compressor including an upper stage compression part and a lower stage compression part, and
the injection nozzle is located in the discharge chamber or the discharge area of the upper stage compression part so as to inject the NH3 refrigerant liquid through the injection nozzle to the discharge chamber or discharge area of the upper stage compression part.
5. The heat pump unit according to claim 4 , further comprising:
a second returning path for the refrigerant liquid which returns the portion of the NH3 refrigerant liquid having been discharged from the upper stage compressor part and then condensed in the condenser, to the discharge chamber or discharge area that is in communication with the discharge chamber, the discharge chamber or the discharge area being located in the lower stage compression part;
wherein the portion of the NH3 refrigerant liquid is led to be returned to the discharge chamber or discharge area of the lower stage compression part via the second returning path.
6. The heat pump unit according to claim 5 , further comprising a heat exchanger for the refrigerant liquid which is provided in the refrigerant circulating path between the condenser and the expansion valve, the heat exchanger being connected to the refrigerant circulating path so that refrigerant gas discharged from the lower stage compressor is introduced to the intake chamber or intake area of the upper stage compressor through the heat exchanger, the refrigerant liquid from the condenser being cooled with the refrigerant gas discharged from the lower stage compressor.
7. The heat pump unit according to claim 6 , further comprising a heat exchanger for the refrigerant liquid provided in the refrigerant circulating path in an upstream side of the second returning path,
wherein a portion of the refrigerant liquid having been cooled in the heat exchanger is supplied to the first or second returning path.
8. The heat pump unit according to claim 1 , wherein the reciprocating compressor is for refrigerant and comprises an intake chamber in communication with a cylinder via an intake valve at a cylinder top assembly and a discharge chamber in communication with the cylinder via a discharge valve,
wherein the injection nozzle and a supply port for refrigerant liquid are arranged in the discharge chamber or discharge area, and the injection nozzle is connected to the supply port for the refrigerant liquid, and
wherein the refrigerant liquid is injected through the injection nozzle to the discharge chamber or discharge area.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US14/624,970 US20150159919A1 (en) | 2010-02-25 | 2015-02-18 | Heat pump unit |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/712,553 US20110203304A1 (en) | 2010-02-25 | 2010-02-25 | Heat pump unit and reciprocating compressor for refrigerant |
US14/624,970 US20150159919A1 (en) | 2010-02-25 | 2015-02-18 | Heat pump unit |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US12/712,553 Continuation-In-Part US20110203304A1 (en) | 2010-02-25 | 2010-02-25 | Heat pump unit and reciprocating compressor for refrigerant |
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US20150159919A1 true US20150159919A1 (en) | 2015-06-11 |
Family
ID=53270778
Family Applications (1)
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US14/624,970 Abandoned US20150159919A1 (en) | 2010-02-25 | 2015-02-18 | Heat pump unit |
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US (1) | US20150159919A1 (en) |
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