WO2022188668A1 - Système de pompe à chaleur - Google Patents

Système de pompe à chaleur Download PDF

Info

Publication number
WO2022188668A1
WO2022188668A1 PCT/CN2022/078712 CN2022078712W WO2022188668A1 WO 2022188668 A1 WO2022188668 A1 WO 2022188668A1 CN 2022078712 W CN2022078712 W CN 2022078712W WO 2022188668 A1 WO2022188668 A1 WO 2022188668A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
stage
heat pump
pump system
branch
Prior art date
Application number
PCT/CN2022/078712
Other languages
English (en)
Chinese (zh)
Inventor
杨春
Original Assignee
艾默生环境优化技术(苏州)有限公司
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from CN202120509779.5U external-priority patent/CN214746577U/zh
Priority claimed from CN202110260225.0A external-priority patent/CN115077133A/zh
Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Publication of WO2022188668A1 publication Critical patent/WO2022188668A1/fr

Links

Images

Classifications

    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit

Definitions

  • the present disclosure relates to the field of heat pump systems, and more particularly, to a cascade system for industrial heat pump applications.
  • high temperature heat sources above 100 °C are in great demand, such as regeneration of rotary dehumidification, drying of lithium batteries, and drying of cement.
  • this high-temperature heat source is usually realized by traditional methods such as electric heating, gas, and fuel, but there are problems such as serious energy consumption and high pollution.
  • the heat pump system can be applied in many occasions to improve the problems existing in the traditional high-temperature heat source supply method.
  • the heat pump system is used in the northern coal-to-electricity project, which absorbs heat from the air and transfers it to hot water, which can make the efficiency reach 3.0.
  • the current typical heat pump system has a condensing temperature of about 65°C.
  • the condensing temperature is very high, usually exceeding 100°C, and even reaching 135°C.
  • the high condensing temperature also leads to high temperature resistance requirements for the expansion valve, and the maximum temperature resistance of the general expansion valve is 70 °C. If a special expansion valve is used, it will lead to an increase in cost. Therefore, the tolerance temperature of the expansion valve limits the large-scale popularization and application of high-temperature heat pump systems.
  • the purpose of the present disclosure is to provide a reliable and efficient heat pump system, which adopts a cascade system design.
  • the refrigerant is cooled, thereby reducing the temperature before the valve in the second-stage circuit, which solves the problem of the temperature resistance requirement of the expansion valve in the existing heat pump system;
  • the refrigerant before the expansion valve in the circuit is cooled and then injected into the first-stage compressor as an air jet enthalpy-increasing fluid, thereby improving the energy efficiency of the system;
  • the heat pump system can also set a cooling branch in the second-stage circuit, whereby, the discharge temperature control requirement of the high-temperature compressor can be achieved with a small amount of liquid injection, and the controllability and efficiency of the system can be improved.
  • a heat pump system includes: a first-stage circuit, on which a first-stage compressor, a condensing evaporator, a first-stage compressor, a condensing evaporator, a The first-stage main circuit expansion valve and the first-stage evaporator; the second-stage loop, the second-stage compressor, the second-stage condenser, and the air jet enthalpy heat exchange are arranged in sequence along the refrigerant flow direction on the second-stage loop.
  • the condensing evaporator is used both as a condenser in the first-stage loop and as an evaporator in the second-stage loop; and a jet enthalpy increasing branch
  • the first stage compressor has a first refrigerant replenishment port
  • the jet enthalpy increasing branch extends from the first branch point on the first stage loop located downstream of the condensation evaporator and passes through the jet enthalpy increasing heat exchanger , and is connected to the first refrigerant replenishment port.
  • the heat pump system is configured such that the first refrigerant supplied to the first refrigerant replenishment port via the gas injection enthalpy branch is in a pure gaseous state.
  • a first branch expansion valve is provided between the first branch point and the jetting enthalpy increasing heat exchanger.
  • the second-stage compressor has a second refrigerant supplementary port
  • the heat pump system further includes a cooling branch
  • the cooling branch is connected from the jet enthalpy heat exchanger on the second-stage circuit and the second-stage main circuit expansion valve.
  • the heat pump system is configured such that the second refrigerant supplied to the second refrigerant replenishment port via the cooling branch is in a pure liquid state.
  • a throttle valve is provided on the cooling branch.
  • the heat pump system is configured such that the condensing temperature of the second stage condenser is higher than 100°C and the refrigerant temperature immediately upstream of the second stage main circuit expansion valve is lower than 70°C.
  • the first refrigerant in the first stage circuit is different from the second refrigerant in the second stage loop.
  • the heat pump system according to the present disclosure brings at least the following beneficial effects: the heat pump system according to the present disclosure can not only effectively reduce the second stage by means of the jet enthalpy increasing branch provided between the first stage circuit and the second stage loop
  • the temperature of the refrigerant before the expansion valve in the main circuit in the circuit ensures that the system can still operate reliably even when a common expansion valve is used, which expands the application range of the heat pump system. Injection into the first stage compressor, thereby increasing the energy efficiency of the system.
  • the heat pump system according to the present disclosure can also provide a cooling branch in the second-stage circuit, so as to realize the cooling of the exhaust gas of the high-temperature compressor with a small amount of liquid injection, thereby improving the controllability and efficiency of the system.
  • FIG. 1 shows a schematic diagram of a heat pump system according to a first embodiment of the present disclosure
  • FIGS. 2 and 3 show enthalpy-pressure diagrams of a first-stage loop and a second-stage loop, respectively, of the heat pump system according to the first embodiment of the present disclosure
  • FIG. 4 shows a schematic diagram of a heat pump system according to a second embodiment of the present disclosure
  • FIG. 5 shows an enthalpy-pressure diagram of a second stage loop of a heat pump system according to a second embodiment of the present disclosure
  • FIG. 6 shows a schematic diagram of a heat pump system according to a first comparative example
  • FIG. 9 shows a schematic diagram of a high temperature circuit of a heat pump system according to a second comparative example.
  • FIG. 10 shows an enthalpy-pressure diagram of the second-stage loop of the heat pump system according to the second comparative example.
  • the heat pump system S being a cascade system including a first stage circuit (low temperature stage loop) and a second stage loop (high temperature stage loop).
  • the refrigerant in the first-stage loop is different from the refrigerant in the second-stage loop, so as to be suitable for different working conditions.
  • the first-stage loop can use conventional HFC, HCFC refrigerants, such as R410A, R22, R134a, etc.
  • the second-stage loop can use refrigerants with a critical temperature above 100 °C, such as R245fa or R1233zde and other HFO-based refrigerants .
  • the first-stage circuit includes a low-temperature refrigerant circulation main path formed by connecting the first-stage compressor PL, the condensing evaporator EC, the first-stage main circuit expansion valve VL and the first-stage evaporator EL through pipes in sequence (in the accompanying drawings).
  • the arrow in the middle indicates the flow direction of the refrigerant). That is, the first-stage compressor PL, the condensing evaporator EC, the first-stage main circuit expansion valve VL, and the first-stage evaporator EL are sequentially arranged at the first stage along the flow direction of the low-temperature stage refrigerant (the first refrigerant). in the primary loop.
  • the second-stage circuit includes a high-temperature-grade refrigerant cycle formed by connecting the second-stage compressor PH, condenser CH, jet enthalpy heat exchanger EH, second-stage main circuit expansion valve VH and condensing evaporator EC in sequence through pipes
  • the main path (the arrow in the drawing indicates the flow direction of the refrigerant). That is, the second stage compressor PH, condenser CH, jet enthalpy heat exchanger EH, second stage main circuit expansion valve VH and condensing evaporator EC flow along the flow of the high temperature stage refrigerant (second refrigerant).
  • the directions are sequentially arranged in the second-level loop.
  • the condensing evaporator EC includes a refrigerant evaporation passage as part of a second-stage circuit and a refrigerant condensation passage as part of a first-stage circuit, in which the high temperature stage refrigerant and the low temperature stage refrigerant are condensed Heat exchange is performed, whereby the second refrigerant in the refrigerant evaporation passage is evaporated and the first refrigerant in the refrigerant condensation passage is condensed.
  • the condensing evaporator EC acts as a condenser in the first stage circuit and as an evaporator in the second stage loop.
  • the heat pump system S further includes a jetting enthalpy increasing branch, and the jetting enthalpy increasing branch may be arranged with a first branch expansion valve VX and a jetting enthalpy increasing heat exchanger EH.
  • the jet enthalpy heat exchanger EH is a refrigerant-refrigerant heat exchanger, which can be a plate heat exchanger, a casing heat exchanger, and the like.
  • the jet enthalpy heat exchanger EH includes a second refrigerant passage as part of the second stage circuit and a first refrigerant passage as part of the jet enthalpy branch.
  • the first stage compressor PL is configured as a jet enthalpy compressor.
  • the jet enthalpy compressor has a suction port and an exhaust port, There is also a first refrigerant replenishment port PLI.
  • the first-stage circuit also includes a first branch point P on the path downstream of the condensing evaporator EC and between the condensing evaporator EC and the first-stage main circuit expansion valve VL.
  • the jet enthalpy increase branch extends from the first branch point P, passes through the first refrigerant passage in the jet enthalpy heat exchanger EH, and is finally connected to the first refrigerant replenishment port PLI of the first stage compression PL (in the appendix).
  • the arrow in the figure indicates the flow direction of the refrigerant), and the first branch expansion valve VX is provided on the path between the first branch point P and the inlet (point c) of the first refrigerant passage.
  • the first refrigerant discharged from the first-stage compressor PL is in a state of high temperature and high pressure (corresponding to the state of point 2 in FIG. 2 ), and the first refrigerant is a gas at this time. Then the first refrigerant enters the condensing evaporator EC through the pipeline, and is condensed in the condensing evaporator EC to be converted into a liquid state (corresponding to the state of point 3 in FIG. 2 ).
  • the condensation temperature of the first-stage circuit is about 80°C.
  • the condensed first refrigerant is discharged from the condensing evaporator EC.
  • a part of the first refrigerant (hereinafter referred to as the first part of the first refrigerant) enters the first-stage main circuit expansion valve VL, and is converted into a low temperature and low pressure through the depressurization effect of the first-stage main circuit expansion valve VL refrigerant (corresponding to the state of point 4 in Figure 2).
  • the first portion of the first refrigerant enters the first-stage evaporator EL, where it is evaporated and transformed into a gaseous state (corresponding to the state of point 1 in FIG. 2 ).
  • the evaporation temperature of the first-stage circuit is about 30°C.
  • the first part of the evaporated first refrigerant is discharged from the first-stage evaporator EL, and then enters the intake port of the first-stage compressor PL.
  • Another part of the first refrigerant discharged from the condensing evaporator EC enters the gas injection enthalpy increasing branch from the first branch point P on the first stage circuit, and passes through the first branch
  • the expansion valve VX is throttled, the pressure of the second part of the first refrigerant is reduced, and the refrigerant is changed from a liquid refrigerant to a gas-liquid mixed refrigerant.
  • the temperature of the second part of the first refrigerant is about 53°C.
  • the second part of the first refrigerant enters the first refrigerant passage in the jet enthalpy heat exchanger EH, that is, at the inlet point c of the first refrigerant passage of the jet enthalpy heat exchanger EH, the The temperature of the second portion of a refrigerant is about 53°C.
  • the second part of the first refrigerant exchanges heat with the second refrigerant in the second refrigerant passage in the first refrigerant passage, absorbs the heat of the second refrigerant, and reduces the temperature of the second refrigerant.
  • the second part of the first refrigerant is discharged from the outlet point d of the first refrigerant passage of the jet enthalpy heat exchanger EH, and sent to the first refrigerant supplement of the first stage compressor PL, which is communicated with the middle pressure part port PLI.
  • the second part of the first refrigerant sent back to the first refrigerant replenishment port PLI of the first stage compressor PL ends up in the first stage with the first part of the first refrigerant entering from the intake port of the first stage compressor PL
  • the mixture is mixed in the compressor PL, compressed to the state of point 2 again, and discharged from the first-stage compressor PL.
  • the first refrigerant discharged from the outlet d point of the first refrigerant passage of the jet enthalpy heat exchanger EH and delivered to the first refrigerant replenishment port PLI of the first stage compressor PL is in a pure gas state, so that It further effectively reduces the refrigerant temperature immediately upstream of the main circuit expansion valve in the second stage circuit and effectively improves the system efficiency.
  • the second refrigerant discharged from the second-stage compressor PH is in a high-temperature and high-pressure gas state (corresponding to the state at point 6 in FIG. 3 ). Then, the second refrigerant enters the second-stage condenser CH through the pipeline, and is condensed in the second-stage condenser CH to be converted into a liquid state (corresponding to the state of point 7 in FIG. 3 ).
  • the condensation temperature of the second-stage circuit is about 135°C.
  • the condensed second refrigerant is discharged from the condensing evaporator EC, and then enters the jet enthalpy heat exchanger EH from the inlet point a of the second refrigerant passage of the jet enthalpy heat exchanger EH.
  • the heat of the second refrigerant in the second refrigerant passage is absorbed by the second part of the first refrigerant in the first refrigerant passage, whereby the temperature of the second refrigerant is further reduced , and then the air jet enthalpy heat exchanger EH is discharged from the outlet b of the second refrigerant passage.
  • the second refrigerant enters the second-stage main circuit expansion valve VH, and changes to a state corresponding to point 8 in FIG. 3 through the depressurization action of the second-stage main circuit expansion valve VH. Subsequently, the second refrigerant enters the refrigerant evaporation channel of the condensation evaporator EC, and in the condensation evaporator EC, the second refrigerant in the refrigerant evaporation channel exchanges heat with the first refrigerant in the refrigerant condensation channel, The second refrigerant is evaporated and transformed into a gaseous state (corresponding to the state at point 5 in FIG. 3 ). In this embodiment, the evaporation temperature of the second-stage circuit is 75°C. The evaporated second refrigerant is discharged from the condensing evaporator EC and then enters the intake port of the second stage compressor PH.
  • FIG. 6 shows a schematic diagram of a heat pump system S' according to a first comparative example, which is also a cascade system including a first-stage loop and a second-stage loop, similar to the first embodiment of the present disclosure.
  • the main components, arrangement, connection, refrigerant selection, etc. of the first-stage circuit and the second-stage circuit are the same as those in the first embodiment of the present disclosure.
  • the first-stage circuit is composed of the first-stage compressor PL.
  • the condensing evaporator EC, the first-stage main circuit expansion valve VL and the first-stage evaporator EL are connected in sequence along the flow direction of the low-temperature stage refrigerant (first refrigerant), and the second-stage loop is formed by the second-stage compression
  • the machine PH, the second stage condenser CH, the jet enthalpy heat exchanger EH, the second stage main circuit expansion valve VH and the condensing evaporator EC are connected in sequence along the flow direction of the high temperature stage refrigerant (second refrigerant), And the first stage loop and the second stage loop are thermally coupled through the condensing evaporator EC.
  • the second stage compressor PH is configured as a jet enthalpy compressor with a supplementary air port, and the jet enthalpy increase branch is derived from the jet enthalpy increase in the second stage circuit.
  • the branch point Q between the jet enthalpy heat exchanger EH and the second-stage main circuit expansion valve VH begins to extend, and is connected through the second branch expansion valve VX and the jet enthalpy heat exchanger EH To the air supply port of the second stage compressor PH.
  • a part of the second refrigerant (hereinafter referred to as the first part of the second refrigerant) discharged from the outlet b of the second refrigerant passage of the jet enthalpy heat exchanger EH enters the second stage main
  • the expansion valve VH of the main circuit is converted into a state corresponding to the point 8 in FIG.
  • the first part of the second refrigerant enters the condensing evaporator EC, is evaporated in the condensing evaporator EC to be transformed into a gaseous state (corresponding to the state at point 5 in FIG. 8 ), and is then discharged from the condensing evaporator EC and enters The intake port of the second stage compressor PL.
  • Another part of the second refrigerant (hereinafter referred to as the second part of the second refrigerant) discharged from the outlet b point of the second refrigerant passage of the jet enthalpy heat exchanger EH passes from the branch point Q on the second stage circuit
  • the pressure of the second part of the second refrigerant decreases after entering the gas injection enthalpy increasing branch and being throttled by the expansion valve VX' of the second branch.
  • the temperature of the second part of the second refrigerant is the saturation temperature corresponding to the injection pressure, that is, about 103°C.
  • the second part of the second refrigerant enters the first refrigerant passage in the jet enthalpy heat exchanger EH, that is, at the inlet point c of the first refrigerant passage of the jet enthalpy heat exchanger EH, the The temperature of the second part of the secondary refrigerant is about 103°C.
  • the second part of the second refrigerant exchanges heat with the second refrigerant in the second refrigerant passage in the first refrigerant passage, absorbs the heat of the second refrigerant and reduces the temperature of the second refrigerant, thereby reducing the temperature of the second refrigerant.
  • the temperature of the second refrigerant before the second-stage main circuit expansion valve VH The temperature of the second refrigerant before the second-stage main circuit expansion valve VH.
  • the second part of the second refrigerant is discharged from the outlet point d of the first refrigerant passage of the jet enthalpy heat exchanger EH, and sent to the supplementary air port of the second stage compressor PH which is communicated with the middle pressure part.
  • the second part of the second refrigerant sent back to the make-up port of the second stage compressor PH eventually mixes with the first part of the second refrigerant entering the second stage compressor PH from the intake port of the second stage compressor PH, and The gas that is recompressed to high temperature and high pressure (corresponding to the state of point 6) is discharged from the second stage compressor PH.
  • the condensing temperature of the second-stage loop is about 135°C
  • the temperature of the second refrigerant after being throttled by the second branch expansion valve VX' is about 103°C
  • the pre-valve temperature of the second-stage main circuit expansion valve VH is about 108°C. This temperature far exceeds the long-term use tolerance temperature of most electronic expansion valves (about 70°C), so it is difficult to find suitable electronic expansion valve products on the market, which affects the reliability of valve parts and even the system.
  • the condensing temperature of the second-stage loop may be higher than 100° C., for example, about 135° C.
  • the gas injection enthalpy increasing branch passes through the first branch expansion valve VX
  • the temperature of the first refrigerant after throttling is about 53°C (that is, the temperature of the first refrigerant at point c), so the first refrigerant can sufficiently cool the second refrigerant in the jet enthalpy heat exchanger, so that The second refrigerant reaches a sufficiently low pre-valve temperature (ie the second refrigerant temperature at point b), ie below 70°C.
  • the pre-valve temperature of the second-stage main circuit expansion valve VH (that is, the temperature of the second refrigerant at point b) is 58°C, and an ordinary electronic expansion valve can meet the temperature resistance requirements. requirements, so that the cost of the system is reduced and the reliable operation of the system is guaranteed.
  • the first refrigerant is passed through the first stage circuit.
  • the branch expansion valve VX is throttled, the first refrigerant with a lower temperature is used to fully cool the condensed second refrigerant in the second-stage circuit in the jet enthalpy heat exchanger EH, so that the second refrigerant can be fully cooled.
  • the temperature before the second-stage main circuit expansion valve VH in the first-stage circuit is significantly reduced, so that the system can use a common electronic expansion valve, which reduces the cost of the system and ensures the reliable operation of the system.
  • the first refrigerant discharged from the jet enthalpy heat exchanger EH (at point d) is delivered to the first refrigerant replenishment port PLI of the first stage compressor PL at a suitable medium temperature and pressure, compared to The related scheme of transporting the medium temperature and medium pressure first refrigerant back to the air inlet of the first stage compressor PL or on the path before the air inlet is because the medium temperature and medium pressure first refrigerant is directly supplied to the first stage compressor PL.
  • the intermediate pressure chamber of the stage compressor PL performs further compression, thus increasing the system efficiency.
  • the second embodiment of the present disclosure is a modification of the first embodiment of the present disclosure.
  • the second embodiment of the present disclosure will be described below with reference to FIGS. 4 and 5 .
  • the heat pump system S according to the second embodiment of the present disclosure is also a cascade system including a first-stage loop and a second-stage loop.
  • the main components, arrangement, connection method, refrigerant selection, etc. of the first-stage loop, the second-stage loop, and the jet enthalpy-increasing branch are the same as those in the first embodiment of the present disclosure, and will not be repeated here.
  • the second embodiment of the present disclosure is further provided with a cooling branch on the basis of the heat pump system shown in the first embodiment of the present disclosure.
  • the cooling branch extends from the downstream of the jet enthalpy heat exchanger EH of the second-stage circuit, passes through the throttle valve VY, and is finally connected to the second refrigerant replenishment port of the second-stage compressor PH, which communicates with the pressure chamber therein. PHI.
  • the cooling branch extends from the second branch point R between the jet enthalpy heat exchanger EH and the second-stage main circuit expansion valve VH, so that the refrigerant supplied to the second refrigerant supplementary port PHI has suitable temperature and pressure. Referring to FIG.
  • the second part of the second refrigerant discharged from the outlet b of the second refrigerant passage of the jet enthalpy heat exchanger EH is branched from the second branch on the second stage circuit Point R enters the cooling branch, after being throttled by the throttle valve VY, the pressure of the second part of the second refrigerant is reduced, and then the second part of the second refrigerant is injected to the second stage with a lower temperature and a suitable pressure In the middle-pressure chamber of the compressor PH, and the high-temperature gas in the middle-pressure chamber (the high-temperature gas is the part of the second refrigerant sucked in from the air inlet of the second-stage compressor PH that is compressed to the middle-pressure chamber , which is in the state corresponding to point g in FIG. 5 ) mixed to reach the
  • the cooling branch added in the second embodiment can provide refrigerant with a lower temperature to the supplementary port PHI of the second-stage compressor PH, so as to prevent the discharge of the second-stage compressor from overheating. purpose, thereby improving the controllability and efficiency of the system.
  • the second part of the second refrigerant supplied to the second refrigerant replenishment port PHI after being throttled by the throttle valve VY is in pure liquid state, so as to provide sufficient cooling effect with as little refrigerant as possible, and also It is beneficial to reduce the refrigerant temperature immediately upstream of the main circuit expansion valve in the second-stage circuit.
  • the condensing temperature of the second-stage circuit is about 135°C. Since the first refrigerant in the air-jet enthalpy-enhancing heat exchanger can sufficiently cool the second refrigerant, the air-jet increasing The temperature at the outlet b of the second refrigerant passage of the enthalpy heat exchanger is as low as 58°C, so the temperature of the second part of the second refrigerant entering the cooling branch is also low enough, and only a small amount of liquid injection is needed to meet the requirements of the first refrigerant. Requirements for secondary compressor discharge temperature control.
  • FIG. 9 shows a schematic diagram of the second stage loop of the second comparative example.
  • the cooling branch extends from the second branch point R downstream of the second stage condenser CH of the second stage circuit, between the second stage condenser CH and the second stage main circuit expansion valve VH , passes through the throttle valve VY, and is finally connected to the second refrigerant supplementary port PHI' of the second stage compressor PH that communicates with the pressure chamber therein.
  • the first part of the second refrigerant discharged from the second-stage condenser CH enters the second-stage main circuit expansion valve VH, And the state corresponding to the point 8 in FIG. 10 is changed to the state corresponding to the point 8 in FIG. Subsequently, the first part of the second refrigerant enters the condensing evaporator EC, is evaporated in the condensing evaporator EC to be transformed into a gaseous state (corresponding to the state at point 5 in FIG. 10 ), and is then discharged from the condensing evaporator EC into the intake of the second stage compressor PL.
  • Another part of the second refrigerant discharged from the condenser CH enters the cooling branch from the second branch point R on the second stage circuit, and is throttled through the throttle valve VY After that, the pressure of the second part of the second refrigerant decreases to change to a state corresponding to point f' in FIG.
  • the second part of the second refrigerant is injected into the second refrigerant through the second refrigerant supplementary port PHI' In the middle pressure chamber of the first stage compressor PH, and the high temperature gas in the middle pressure chamber (the high temperature gas is the part of the second refrigerant sucked in from the air inlet of the second stage compressor PH that is compressed to the middle pressure chamber, which In the state corresponding to point g' in Figure 10), it is mixed to reach the state corresponding to point e in Figure 10, and then compressed together to the state corresponding to point 6 in Figure 10. Compressor PH discharge.
  • the condensation temperature of the second-stage loop is about 135°C.
  • the subcooling degree of the condenser CH is 5°C
  • the refrigerant temperature is about 130°C, which is significantly higher than the temperature of the second refrigerant at point b shown in FIG. 5 (58°C).
  • the mass of the refrigerant in the intermediate pressure chamber of the second-stage compressor PH (that is, the refrigerant in the state corresponding to point g or point g') is 0.1 kg
  • the target temperature of the mixed state e is 110°C
  • the mass of the cooling refrigerant that needs to be injected according to the second embodiment of the present disclosure is about 0.015kg
  • the mass of the cooling refrigerant that needs to be injected for the second comparative example is about 0.033 kg. Therefore, the heat pump system according to the second embodiment of the present disclosure can achieve the purpose of controlling the exhaust gas temperature of the second-stage compressor with a small amount of liquid injection, which further improves the system efficiency.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente invention concerne un système de pompe à chaleur comprenant : un circuit de premier étage, un compresseur de premier étage, un condenseur/évaporateur, une soupape d'expansion de trajet principal de premier étage et un évaporateur de premier étage qui sont agencés séquentiellement sur le circuit de premier étage le long de la direction d'écoulement d'un réfrigérant ; un circuit de second étage, un compresseur de second étage, un condenseur de second étage, un échangeur de chaleur à injection de vapeur améliorée, une soupape d'expansion de trajet principal de second étage et un condenseur/évaporateur qui sont agencés de manière séquentielle sur le circuit de second étage le long de la direction d'écoulement du réfrigérant ; le condenseur/évaporateur étant utilisé comme condenseur dans le circuit de premier étage et étant utilisé comme évaporateur dans le circuit de second étage; et une branche d'injection de vapeur améliorée, le compresseur de premier étage présentant un premier orifice d'ajout de réfrigérant ; la branche d'injection de vapeur améliorée s'étendant à partir d'un premier point de ramification sur le circuit de premier étage situé en aval du condenseur/évaporateur, traversant l'échangeur de chaleur à injection de vapeur améliorée et étant reliée au premier orifice d'ajout de réfrigérant.
PCT/CN2022/078712 2021-03-10 2022-03-02 Système de pompe à chaleur WO2022188668A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN202120509779.5U CN214746577U (zh) 2021-03-10 2021-03-10 热泵系统
CN202110260225.0 2021-03-10
CN202120509779.5 2021-03-10
CN202110260225.0A CN115077133A (zh) 2021-03-10 2021-03-10 热泵系统

Publications (1)

Publication Number Publication Date
WO2022188668A1 true WO2022188668A1 (fr) 2022-09-15

Family

ID=83226349

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/078712 WO2022188668A1 (fr) 2021-03-10 2022-03-02 Système de pompe à chaleur

Country Status (1)

Country Link
WO (1) WO2022188668A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030024262A1 (en) * 2001-08-03 2003-02-06 Dieter Mosemann Arrangement for cascade refrigeration system
KR101260900B1 (ko) * 2012-12-10 2013-05-06 주식회사 이지플러스원 이원사이클 히트펌프를 이용한 누설기능을 갖는 가온 환기장치
CN105758050A (zh) * 2016-05-10 2016-07-13 合肥天鹅制冷科技有限公司 宽温区空气调节系统
CN108692475A (zh) * 2018-06-08 2018-10-23 贺吉军 一种喷气增焓制冷机
CN214746577U (zh) * 2021-03-10 2021-11-16 艾默生环境优化技术(苏州)有限公司 热泵系统

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030024262A1 (en) * 2001-08-03 2003-02-06 Dieter Mosemann Arrangement for cascade refrigeration system
KR101260900B1 (ko) * 2012-12-10 2013-05-06 주식회사 이지플러스원 이원사이클 히트펌프를 이용한 누설기능을 갖는 가온 환기장치
CN105758050A (zh) * 2016-05-10 2016-07-13 合肥天鹅制冷科技有限公司 宽温区空气调节系统
CN108692475A (zh) * 2018-06-08 2018-10-23 贺吉军 一种喷气增焓制冷机
CN214746577U (zh) * 2021-03-10 2021-11-16 艾默生环境优化技术(苏州)有限公司 热泵系统

Similar Documents

Publication Publication Date Title
US10612821B1 (en) Heat-pump system with combined vapor expansion-compression stages and single-effect vapor absorption unit
CN102128508B (zh) 喷射器节流补气系统以及热泵或制冷系统补气方法
WO2019200951A1 (fr) Système de pompe à chaleur de climatisation et procédé de commande
CN101691960B (zh) 三管制热回收空调系统
BRPI0619376B1 (pt) Sistema de ciclo térmico, central elétrica, sistema de geração de energia elétrica de ciclo térmico compósito e instalação de calor útil de geração de energia
CN109737641B (zh) 一种采用非共沸混合物带过冷器的喷气增焓热泵循环系统
CN201666686U (zh) 喷射器节流补气系统
CN109083705A (zh) 带有喷射器的变组分多压蒸发非共沸工质朗肯循环系统
CN112229085B (zh) 一种适用于大温跨的低温热泵循环系统及循环方法
CN105444476A (zh) 换热系统
CN111707017A (zh) 一种低温强热空气源热泵系统
CN210512229U (zh) 复叠式高温热泵机组
WO2018018967A1 (fr) Système combiné intégrant un système de compression d'air et un système de pompe à chaleur
CN214746577U (zh) 热泵系统
CN211316632U (zh) 一种引射器增压过冷膨胀机耦合跨临界co2系统
CN115077133A (zh) 热泵系统
WO2022188668A1 (fr) Système de pompe à chaleur
CN111947302A (zh) 一种带闪蒸器的变浓度直热式热泵热水器及其工作方法
WO2022099748A1 (fr) Système de pompe à chaleur
CN113899095B (zh) 一种带喷射器增效的准二级压缩式循环系统
CN108759157B (zh) 一次节流双级压缩热泵系统
CN214469331U (zh) 热泵系统
CN110701812A (zh) 一种引射器增压过冷膨胀机耦合跨临界co2系统及应用
CN113356952B (zh) 一种可预冷燃机入口空气的冷电联供系统及其操作方法
CN115111811A (zh) 一种全天候空气源热泵

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22766194

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 22766194

Country of ref document: EP

Kind code of ref document: A1