EP0916914A2 - A refrigerating cycle - Google Patents
A refrigerating cycle Download PDFInfo
- Publication number
- EP0916914A2 EP0916914A2 EP98118939A EP98118939A EP0916914A2 EP 0916914 A2 EP0916914 A2 EP 0916914A2 EP 98118939 A EP98118939 A EP 98118939A EP 98118939 A EP98118939 A EP 98118939A EP 0916914 A2 EP0916914 A2 EP 0916914A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- refrigerant
- refrigerating cycle
- accumulator
- expansion valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
Definitions
- the present invention relates to a refrigerating cycle with a by-pass duct capable of using an evaporator, which usually is used for cooling purposes, for auxiliary heating as required.
- the refrigerating cycle preferably is intended for an automobile.
- an automotive air-conditioner a general refrigerating cycle is used for cooling purposes while an engine refrigerating cycle is used for cooling the engine and heating cooling water of the engine which cooling water when heated is used for heating e.g. the passenger compartment.
- an engine refrigerating cycle is used for cooling the engine and heating cooling water of the engine which cooling water when heated is used for heating e.g. the passenger compartment.
- recent engine developments resulted in engines with improved efficiency, for example gasoline injection type engines and direct injection diesel engines, in which the temperature of the cooling water does not rise as high as in the past. This leads to the inconvenience that particularly in winter time the heating temperature or heating capacity is no more sufficient for the passenger compartment.
- EP-A-0197839 corresponding to US 4.893,748 relates to a heating method using an air-conditioner provided on board of a vehicle and comprising at least a compressor and an evaporator wherein the total or a part of the fluid is derived from the air-conditioning circuit after compression and then re-injected after pressure relief at the inlet of the evaporator in order to gain in a heating operational mode of said air-conditioner additional heating capacity for the passenger compartment.
- the structure of said heating device actually constituted by the slightly modified air-conditioner of conventional design includes an element for deriving a discharge fluid of the compressor towards a depression element for re-heating the atmospheric airflow across the evaporator prior to the entry of the atmospheric airflow into the cabin.
- Said depression element is able to deviate the condenser, the fluid receiver and the expansion valve of the air-conditioner by means of a by-pass duct connecting the exit of the compressor and the inlet of the evaporator.
- Said by-pass duct contains a depression element insuring an isoenthalpic pressure relief e.g. in the form of a flow rate regulator alone or in association with at least one additional parallel jet nozzle or including a jet nozzle having an adjustable flow section.
- a pre-heating device can be provided either in the airflow entering the evaporator or for pre-heating a buffer tank located downstream the condenser and/or the evaporator itself.
- a climatization system of an automobile as known from DE A 3635353 is equipped with an additional heat exchanger located downstream of the main evaporator and upstream of an accumulator in front of the suction side of the compressor.
- a by-pass duct is branching off to a junction in the main circuit located downstream the expansion valve situated downstream of the condenser.
- a further by-pass duct is connecting the exit of the evaporator and said accumulator and contains a motor-driven on/off-valve.
- the additional heat exchanger is also passed by the cooling medium of the engine. Upstream of said additional heat exchanger an additional expansion valve is provided. In the cooling mode said first by-pass duct and said second expansion valve and the heat exchanger are isolated.
- said second by-pass duct and the condenser with its downstream expansion valve are isolated.
- the airflow entering the passenger compartment is passing the evaporator.
- Said second heat exchanger is functioning as an additional evaporator for the refrigerant in the heating mode.
- An air-conditioner as know from US A 5,291,941 is structurally modified for a heating mode by a by-pass duct deviating the condenser, a receiver, a check valve and an expansion valve all located downstream of said condenser, and is connecting the exit of the compressor with the inlet of the evaporator.
- Said by-pass duct is containing an on/off valve and a heating expansion valve.
- an accumulator is provided between the evaporator and the inlet of the compressor.
- the evaporator is situated within an air duct to the passenger compartment upstream of a heater core connected to the engine and passed by the cooling water.
- a further automotive air-conditioner known from FR A 2720982, figure 2 is functionally similar represented as a schematic block diagram in figure 9 of this application.
- a by-pass duct 5 is placed in juxtaposition to supply high-pressure refrigerant gas supplied from compressor 1 of the refrigerating cycle to an evaporator 4 within a car room without passing the refrigerant in the heating mode through condenser 2 provided outside the car room, for performing heat exchange by taking sensibly heat from the evaporator or, as an auxiliary heating.
- the refrigerating cycle of this conventional design contains an expansion valve 3, a liquid tank 10 for temporarily storing high-pressure refrigerant liquid, a check valve 7 between liquid tank 10 and expansion valve 3, a duct selector valve 8 for guiding high-pressure refrigerant delivered by the compressor 1 either to condenser 2 or to deviate it (heating mode) via by-pass duct 5.
- a constant differential pressure regulating valve 9 is situated in by-pass duct 5 which operates as expansion valve when the refrigerant flows through the by-pass duct 5.
- the refrigerating cycle designed in accordance with the features in claim 1.
- said by-pass duct serves to supply the refrigerant from the compressor to the evaporator without passing through the condenser.
- An accumulator for temporarily storing low-pressure refrigerant liquid and gas is connected between the outlet of the evaporator and the inlet of the compressor so that the amount of the refrigerant circulated in the heating mode is controlled by the accumulator while the refrigerant circulates through the by-pass duct without passing through the condenser.
- the provision of the accumulator in the low-pressure line of the refrigeration cycle ensures easier control of the refrigerant flow during the heating mode.
- the accumulator at the inlet side of the compressor eliminates the necessity of a charge mode being indispensable in known refrigeration systems.
- the refrigerant flow that needs to be controlled in discharge mode in known systems is very weak, e.g. 0.5g, but simply can be enlarged by a e.g. factor 100 by the provision of the accumulator at the inlet side of the compressor.
- the accumulator located there the refrigerant flow that needs to be controlled in the discharge mode easily can be as much as 25g. Said strong refrigerant flow automatically offers a means to control the refrigerant flow in a much easier way.
- the accumulator located close to the inlet of the compressor has to be designed with sufficient storing capacity for the gaseous and liquid phases of the refrigerant in order to be able to cope with varying load conditions, must have a predetermined and preferably low through-flow resistance and must be able to not only fulfil an oil separating function but also a predetermined oil re-delivery function in order to supply sufficient oil to the compressor together with the gaseous refrigerant sucked in by the compressor.
- a heating expansion valve along the by-pass flow path from the exit of the compressor into the evaporator for adiabatically expanding the refrigerant before it enters the evaporator when being supplied to the evaporator through the by-pass duct without passing through the condenser after being compressed by the compressor.
- a further expansion valve between the evaporator and its associated accumulator for adiabatically expanding the refrigerant before entering the accumulator and after it has passed the evaporator without previously passing through the condenser.
- a heating expansion valve is provided in the by-pass duct and the further expansion valve is provided between the evaporator and its associated accumulator.
- a heat exchanger may be incorporated into the accumulator for performing heat exchange between heat from an energy source for the automobile on which the refrigerating cycle is mounted and the refrigerant in the refrigeration cycle.
- a heat exchanger may be interposed in the refrigerant duct on the upstream side of the accumulator and connected adjacent thereto for performing heat exchange between heat from an energy source of the automobile on which the refrigerating cycle is mounted and the refrigerant circulating in the refrigeration cycle.
- the main expansion valve provided for the cooling mode may include a mechanical expansion valve or an orifice tube with fixed orifice cross-section or an adjustable control valve maintaining constant supercooling by varying the valve opening, or a motor-driven controlled expansion valve.
- a specific supercooling expansion valve is used, e.g. instead of a conventionally provided orifice tube.
- said heating expansion valve may be designed as a pressure regulating valve apt to regulate its delivery pressure below a specified value by throttling its valve opening small when its delivery side pressure exceeds a specified value (e.g. 10 x the atmospheric pressure) and/or a variable pressure regulating valve capable of varying its setting pressure by electromagnetic force.
- a specified value e.g. 10 x the atmospheric pressure
- said heating expansion valve in said by-pass duct may be designed as a fixed or constant differential pressure regulating valve like a pressure reducing valve or a motor-or solenoid-driven multi-stage-pressure differential switching valve or a motor-or solenoid-driven control valve apt to be adjusted stepwise or steplessly.
- said further expansion valve provided downstream of the evaporator may be designed as a finite differential pressure valve for reducing pressure between the evaporator and the accumulator, or as an intake pressure regulating valve for maintaining the pressure on the outlet side at a certain level or less by reducing the valve opening when the outlet side pressure exceeds a predetermined pressure value(e.g. 4 x atmospheric pressure) or as a variable intake pressure regulating valve capable of varying the pre-set pressure by an electromagnetic force, or as a motor-driven control valve.
- a predetermined pressure value e.g. 4 x atmospheric pressure
- a further expansion valve downstream the evaporator may be designed with a fixed orifice only throttling the channel sectional area.
- a further by-pass duct is deviating said further expansion valve located between the evaporator and the accumulator, said further by-pass duct containing a switchable on/off valve.
- a further by-pass duct may deviate both said further expansion valve and said heat exchanger, said further by-pass duct containing a switchable on/off valve.
- said heat exchanger is passed by a heat transferring medium such as water.
- the flow rate of the heat transferring medium in said heat exchanger can be controlled by an associated flow control valve.
- shut-off valves for directing the refrigerant flow are provided in the main duct between the compressor and the condenser, in the by-pass duct upstream the heating expansion valve, and in said by-pass duct deviating either the further expansion valve or the further expansion valve and the heat exchanger, wherein said shut-off valves are integrated into one structural valve block or block body. This facilitates installation of the cycle and allows to property control both modes of operation.
- the accumulator is provided with a thermal insulation in order to avoid heat losses as far as possible.
- Said thermal insulation can be constituted by producing the body of the accumulator from heat insulating resin or similar plastic material and e.g. by applying an insulating cover on the body of said accumulator.
- Said cover is of particular advantage in case of a body of the accumulator made of aluminium alloy or a similar light metal alloy.
- Said cover can be made of a resin or similar plastic material or of rubber.
- the high pressure duct section of the cycle connecting said switching valve and said check valve is structured as an intermediate storing section for excessive refrigerant during the oscillatory heating mode and in functional co-operation with said accumulator having a predetermined storing capacity only.
- the amount of refrigerant contained in the evaporator is different between the cooling mode and the auxiliary heating modes. In the auxiliary heating mode the amount of refrigerant contained in the evaporator will be less. The difference of the amounts between both operating modes could be stored in the accumulator. However, it would neither be economical or practical to increase the accumulator size and capacity accordingly.
- the cycle is structured such that by functional co-operation between the accumulator and the high pressure duct section of the cycle during auxiliary heating mode excessive refrigerant is stored in the high pressure duct section connecting said selector valve and said check valve, including said condenser.
- the size and storing capacity of the accumulator can be the same as in conventional refrigerating cycles using an orifice tube system.
- the accumulator is equipped with a signal generating liquid level gauge, e.g. connected with the control system of the cycle or directly with the actuation of selector valves.
- a signal generating liquid level gauge e.g. connected with the control system of the cycle or directly with the actuation of selector valves.
- signals originating from said level gauge can be used to reduce the refrigerant flow to be circulated in the auxiliary heating circuit by opening the selector valve for a short period of time (in the range of one to five seconds) and thus diverting the refrigerant flow towards the condenser if the refrigerant needs to be stored exceeding the refrigerant storing capacity of the accumulator.
- said liquid level gauge is constituted by a self-heating thermistor or an equivalent electronic component integrated into said accumulator.
- a self-heating thermistor is able to dissipate a certain heat amount when drawing a certain current. Its characteristic is to significantly change its heat dissipation factor when it is immersed in the liquid refrigerant or left in the gaseous refrigerant. Said change easily can be detected by the current supplied to the thermistor gaining an output signal useful to control e.g. the selector valve accordingly and temporarily.
- Fig. 1 the general structure of a refrigerating cycle used in an automotive air-conditioner contains (first embodiment of the invention) a compressor 1, a condenser 2 arranged outside a car room, an expansion valve 3 downstream of said condenser 2 in the main circuit, an evaporator 4 arranged in an air duct leading to the car room and an accumulator 6 for temporarily storing low-pressure refrigerant, all of which constitute an ordinary refrigerating cycle.
- Expansion valve 3 can be a general mechanical expansion valve.
- an orifice tube e.g.
- Said supercooling control valve or supercooling expansion valve, respectively, is designed to maintain the degree of supercooling constant by enlarging the valve opening when the degree of supercooling at the valve's inlet side tends to become high.
- a by-pass duct 5 is placed in juxtaposition for supplying high-pressure refrigerant gas delivered by the compressor 1 into the evaporator 4 without passing it through the condenser 2 in order to perform auxiliary heating by using the evaporator.
- check valve 7 is provided in the main duct downstream of condenser 2 and upstream of main expansion valve 3.
- a duct selector valve 8 (a three-way valve e.g.) is provided at the junction between the main circuit and the branching off by-pass duct 5 for guiding high-pressure refrigerant supplied from the compressor 1 either to the condenser 2 or (heating mode) via by-pass duct 5 directly to the evaporator 4.
- By-pass duct 5 contains e.g. a constant differential pressure regulating valve 9 for reducing the pressure. Said valve 9 operates as an expansion valve in said by-pass duct 5.
- Said valve 9 may be a valve capable of switching the controlled differential pressure to two stages (e.g. 13 and 7 atmospheres) or three or more stages by means of a solenoid or the like. Even a motor-driven control valve may be used, which can be adjustable in steps or steplessly.
- the duct selector valve 8 is set so that all the high-pressure refrigerant supplied from the compressor does not flow into by-pass duct 5 but is supplied to condenser 2. Then the evaporator 4 (either arranged in the car room or in the air path into the car room) operates as a conventional evaporator performing cooling by means of heat exchange between the surrounding air and the refrigerant.
- auxiliary heating duct selector valve 8 is set so that all high-pressure refrigerant supplied from the compressor 1 does not flow to the condenser 2 but flows through by-pass duct 5 and returns to the compressor 1 via evaporator 4 and the accumulator 6.
- accumulator 6 can be thermally insulated, e.g.
- a liquid level gauge G ought to be provided in accumulator 6. This can be current supplied and thus self-heating thermistor which significantly changes its heat dissipation factor when immersed in the liquid refrigerant or left in the gaseous refrigerant. The current consumed by the thermistor then will vary. This variation can be taken as a signal for e.g.
- Fig. 2 shows the characteristics of the cycle in operation in solid line.
- Numeral 1 ⁇ denotes the outlet of the compressor 1
- numeral 2 ⁇ denotes the inlet of the evaporator 4
- numeral 3 ⁇ denotes the outlet of the evaporator 4
- numeral 4 ⁇ denotes the inlet of the accumulator 6
- numeral 5 ⁇ denotes the inlet of the compressor 1
- between 1 ⁇ - 2 ⁇ shows expansion
- between 2 ⁇ - 3 ⁇ shows radiation
- 5 ⁇ - 1 ⁇ shows compression.
- the accumulator 6 When the refrigerant flows via by-pass duct 5 and through evaporator 4 in the auxiliary heating mode the accumulator 6 is apt to receive refrigerant in the circulation duct. Accordingly, when the load is small, a large amount of refrigerant is stored in accumulator 6. To the contrary, when the load is high the amount of refrigerant delivered by the accumulator 6 to compressor 1 is increased so that the amount of refrigerant circulating varies depending on the load. As a result, an auxiliary heating effect corresponding to the needs or demands can be obtained.
- the location of accumulator 6 in the low-pressure section of the refrigerating cycle between the evaporator and the compressor 1 ensures easy control of the refrigerant flow in the heating mode.
- the accumulator with its storing capacity may eliminate the necessity for a so-called charge mode.
- the refrigerant flow that needs to be controlled in the discharge mode is extremely high, compared to conventional systems. In conventional systems the refrigerant flow in the discharge mode may be as low as 0.25g only.
- the refrigerant flow in the discharge mode can be e.g. 100 times greater and can be as much as 25g. Such high flow is offering a means for controlling the refrigerant flow in a much easier way.
- the refrigerating cycle is equipped with a further or second expansion valve 19 between the evaporator 4 and the accumulator 6.
- Said expansion valve 19 can consist, e.g., of a finite differential pressure valve for reducing the pressure.
- no finite differential pressure valve is provided between compressor 1 and evaporator 4, i.e. in by-pass duct 5.
- the further structural design of this embodiment is the same as in the first embodiment.
- Fig. 4 represents the operation of the second embodiment in the heating mode, i.e. when the refrigerant flows through by-pass duct 5.
- Evaporator 4 functions as a condenser in the case of a general refrigerating cycle as shown in Fig 4. Radiation is performed between 2 ⁇ - 3 ⁇ to obtain said auxiliary heating effect.
- the amount of refrigerant circulating is controlled in response to the load by accumulator 6 located in the refrigerant circulating duct.
- a finite differential pressure valve 9 (expansion valve) is interposed in by-pass duct 5 between duct selector valve 8 and evaporator 4.
- a further second expansion valve 19 (for the heating mode) is provided.
- the third embodiment contains an on/off control valve 20 in a by-pass duct deviating the further expansion valve 19.
- valve 20 is opened in order to allow the refrigerant to deviate expansion valve 19.
- refrigerant also is not passing through by-pass duct 5.
- the further components of the refrigeration cycle in Fig. 5 are the same as in the first embodiment.
- the further expansion valve 19 a valve may be used which functions as a finite differential pressure valve. It even is possible to use intake pressure regulating valve for maintaining the pressure at the outlet side of said valve at a certain level or lower by reducing the valve opening as soon as the outlet side pressure exceeds a predetermined pressure value (e.g. 4 x atmospheric pressure). Alternatively a variable intake pressure regulating valve could be used apt to vary the pre-set pressure by electromagnetic force or the like. Even a motor-driven control valve or the like may be used instead or in addition.
- a predetermined pressure value e.g. 4 x atmospheric pressure
- said expansion valve may be used as the pressure regulating valve 9.
- This valve is capable of maintaining its outlet pressure at a specified pressure value or lower by reducing the degree of its opening if its outlet pressure has exceeded a specified level (e.g. 10 times that of the atmospheric pressure).
- the evaporator 4 will be immune to potential damage if said pressure regulating value 9 is provided, since this is capable of maintaining the evaporating pressure in the evaporator 4 at a specified pressure or lower.
- a simple orifice can be used as the expansion valve 19 if said pressure regulating valve is provided in addition to said expansion valve 9.
- a variable pressure regulating valve could be used as said pressure regulating valve being capable of being adjusted in its setting by electromagnetic force.
- a heat exchanger 21 is provided at or within accumulator 6.
- Heat exchanger 21 exchanges heat discharged from an automobile engine, from any type of motor or from batteries with the refrigerant received in the accumulator 6.
- a flow control valve 22 can be provided to control the flow rate of a waste heat transferring medium, such as water, etc. in heat exchanger 21. Further components of the refrigerating cycle correspond to the other embodiments.
- heat exchanger 21 at or in accumulator 6 heat is transferred to a refrigerant and as such also can be used for auxiliary heating.
- a refrigerant flows through by-pass duct 5 a large quantity of radiation is carried out in evaporator 4 between 2 ⁇ and 3 ⁇ as shown in Fig. 7, i.e. the characteristic diagram of the operation of this embodiment.
- the auxiliary heating affect can be improved therewith.
- the circulation rate of the refrigerant is easily controlled by accumulator 6 in the refrigerant circulating line and in view to an adaptation of the auxiliary heating affect to the necessity or need in the car room.
- heat exchanger 21' is provided between further expansion valve 19 and accumulator 6.
- Heat exchanger 21' serves to exchange heat discharged from the automobile engine, from another type of motor or via batteries with the refrigerant between the further expansion valve 19 and the accumulator 6.
- This embodiment is capable of performing the same heating affect as the fourth embodiment.
- Both the further expansion valve 19 and heat exchanger 21' are deviated in their refrigerant duct by a parallel by-pass duct containing a controlled on/off valve 20. Said on/off valve 20 is closed in the auxiliary heating mode, but is open during the normal cooling mode.
- duct selector valve 8 instead of duct selector valve 8 as shown with the other embodiments, said duct selector valve 8 is replaced by functionally similar shut-off valves 28, 29 and 20 for respectively directing the refrigerant flow in the cooling mode and in the auxiliary heating mode.
- Those three valves 28, 29 and 20 preferably are incorporated into one block or valve block or structural unit.
- the refrigerant delivered from the compressor directly can be supplied to the evaporator without passing the condenser.
- the accumulator is provided between the outlet of the evaporator and the inlet of the compressor in order to temporarily store low-pressure refrigerant liquid and also refrigerant in its gaseous phase.
- the amount of refrigerant circulating is controlled when the refrigerant circulates through the by-pass duct without passing the condenser. Therefore, even in the case of heat exchange for heating in the evaporator without passing the refrigerant through the condenser, the amount of refrigerant circulating is property controlled in response to the load and the like so that a heating effect corresponding to the conditions can be obtained.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air-Conditioning For Vehicles (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Central Heating Systems (AREA)
Abstract
Description
Claims (20)
- A refrigerating cycle with a by-pass duct (5) in juxtaposition with said refrigerating cycle in which after it is compressed by a compressor (1) and is condensed by a condenser (2), a refrigerant is supplied to an evaporator (4) while being adiabatically expanded by an expansion valve (3) and is evaporated to be returned to said compressor (1), said by-pass duct (5) is provided for supplying the refrigerant from said compressor (1) to said evaporator (4) without passing it through said condenser (2),
characterized in that
an accumulator (6) for temporarily storing low-pressure refrigerant liquid is connected between the outlet of said evaporator (4) and the inlet of said compressor (1) so that an amount of the refrigerant circulating at least in the heating mode via said by-pass duct in said refrigerating cycle is controlled by said accumulator (6) at least while the refrigerant circulates through said by-pass duct (5) without passing through said condenser (2). - A refrigerating cycle as in claim 1, characterized in that there is provided a heating-expansion valve (9) in said by-pass duct (5) for adiabatically expanding, before entering said evaporator (4), the refrigerant which is supplied to said evaporator (4) via said by-pass duct (5) without passing through said condenser (2) after delivered by said compressor (1), said heating-expansion valve (9) being associated to said evaporator (4) and said accumulator (6).
- A refrigerating cycle as in claim 1, characterized in that there is provided a further expansion valve (19) for adiabatically expanding, before entering said accumulator (6), the refrigerant which is supplied into said accumulator (6) after passing said evaporator (4) without passing through said condenser (2).
- A refrigerating cycle as in claim 1, characterized in that there is provided a heating expansion valve (9) in said by-pass duct (5) and a further expansion valve (19) between the outlet of the evaporator (4) and said accumulator (6).
- The refrigerating cycle as in one of claims 1 to 4, characterized in that at or in said accumulator (6) there is provided a heat exchanger (21) for performing heat exchange between heat from an energy source for an automobile on which said refrigerating cycle is mounted and the refrigerant as circulating the refrigeration cycle.
- A refrigerating cycle as in at least one of claims 1 to 5, characterized in that in the refrigerant duct on the upstream side of the accumulator (6) and connected adjacent thereto a heat exchanger (21') is provided for performing heat exchange between heat from an energy source from an automobile on which said refrigerating cycle is mounted and the refrigerant flowing into said accumulator (6).
- A refrigerating cycle as in claim 1, characterized in that the main expansion valve (3) provided for the cooling mode between said condenser (2) and said evaporator (4) is designed as any one of the following devices:a mechanical expansion valve,an orifice tube with fixed orifice cross-section of its opening, ora motor-driven proportional control valve apt to maintain the supercooling of the refrigerant at the valve inlet at a specified level by adjusting the degree of opening at the valve inlet.
- A refrigerating cycle as in claim 1, characterized in that the main expansion valve (3) is structured as a supercooling expansion valve, apt to maintain the supercooling of the refrigerant at the supercooling expansion valve inlet at a specified level by adjusting the degree of opening at said supercooling valve inlet, preferably as an adjustable supercooling control valve apt to maintain constant supercooling of the refrigerant by varying its valve opening.
- A refrigerating cycle as in at least one of claims 2, 4, 5 or 6, its characterized in that said heating expansion valve (9) is designed as a pressure regulating valve apt to regulate its delivery pressure below a specified value by throttling its valve opening towards smaller when its delivery side pressure exceeds a specified value and/or as a variable pressure regulating valve capable of varying its setting by electromagnetic force.
- A refrigerating cycle as in one of claims 2 or 4 or 5 or 6, characterized in that said heating expansion valve (9) in said by-pass duct (5) is designed as any one of the following devices:a differential pressure regulating valve apt to maintain the pressure differential across the valve inlet and outlet at a specified level;a motor or solenoid-driven multiple step pressure differential regulating valve;a motor or solenoid-driven proportional regulating valve, orcontrol valve similar to a pressure regulating valve apt to maintain the valve outlet pressure at a specified level or lower by reducing the degree of its opening when the valve outlet pressure has exceeded a specified level.
- A refrigerating cycle as in claim 3 or 4 or 5 or 6, characterized in that said further expansion valve (19) is designed as a finite differential pressure valve or as an intake pressure regulating valve for maintaining the pressure on the outlet side at a certain level or less by reducing the valve opening when the outlet side pressure exceeds a predetermined pressure value, and/or as a variable intake pressure regulating valve capable of varying the pre-set pressure by an electromagnetic force, and/or as a motor-driven control valve.
- A refrigerating cycle as in at least one of claims 1 to 11, characterized in that said heating expansion valve (9) being a control valve apt to maintain the valve outlet pressure at a specified level or lower be reducing the degree of opening when its outlet pressure has exceeded a specified level, and the further expansion valve (19) being a simple fixed orifice tube.
- A refrigerating cycle as in one of claims 3 or 4, characterized in that a further by-pass duct is provided for deviating said further expansion valve (19) located between said evaporator (4) and said accumulator (6), said further by-pass duct containing a switchable on/off valve (20).
- A refrigerating cycle as in at least one of claims 3, 4 or 6, characterized in that a further by-pass duct is provided deviating both said further expansion valve (19) and said heat exchanger (21') located between said evaporator (4) and said accumulator (6), said further by-pass duct containing a switchable on/off valve (20).
- A refrigerating cycle as in at least one of claims 5 or 6, characterized in that said heat exchanger (21, 21') is passed by a heat transferring medium such as water and the like and that the flow rate of said heat transferring medium in said heat exchanger (21, 21') is controllable by means of a control valve (22).
- A refrigerating cycle as in at least one of claims 1 to 15, characterized in that controllable shut-off valves (28, 29, 20) are provided in the main duct between said compressor (1) and said condenser (2), in the by-pass duct (5) upstream of the heating expansion valve (9), and in said by-pass duct deviating either the further expansion valve (19) or the further expansion valve (19) and the heat exchanger (21'), and that said valves (28, 29, 20) are incorporated into one structural valve block or block body.
- A refrigerating cycle as in at least one of claims 1 to 16, characterized in that the accumulator (6) is thermally insulated, preferably by either producing the accumulator body from heat insulating resin or similar plastic material and/or by covering the accumulator body, e.g. when made from aluminium alloy or plastic material, with an insulating cover (T), e.g. made of a resin or similar plastic material or rubber.
- A refrigerating cycle as in at least one of claims 1 to 17, characterized in that the high pressure cycle duct section connecting said selector valve (8) and said check valve (7) is structured as an intermediate storing section of the refrigerating cycle for temporarily storing excessive liquid refrigerant in functional co-operation with said accumulator (6) in the auxiliary heating mode.
- A refrigerating cycle as in at least one of claims 1 to 18, characterized in that the accumulator (6) equipped with a signal generating liquid level gauge (G), preferably connected with a control unit of said cycle or at least with the switch actuation of said selector valve (8) or valves (28, 29, 20).
- A refrigerating cycle as in claim 19, characterized in that said liquid level gauge (G) is constituted by a current supplied, self-heating thermistor or an equivalent electronical component integrated into said accumulator (6) for detecting the liquid level by a change of the heat dissipating factor upon contact either with liquid refrigerant or with gaseous refrigerant.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/179,775 US6192695B1 (en) | 1997-11-14 | 1998-10-27 | Refrigerating cycle |
Applications Claiming Priority (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP313261/97 | 1997-11-14 | ||
JP31326197 | 1997-11-14 | ||
JP31326197 | 1997-11-14 | ||
JP8863798 | 1998-04-01 | ||
JP88637/98 | 1998-04-01 | ||
JP8863798 | 1998-04-01 | ||
JP17042398 | 1998-06-18 | ||
JP17042398A JP3481138B2 (en) | 1997-11-14 | 1998-06-18 | Refrigeration cycle with bypass line |
JP170423/98 | 1998-06-18 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0916914A2 true EP0916914A2 (en) | 1999-05-19 |
EP0916914A3 EP0916914A3 (en) | 2002-01-02 |
Family
ID=27305866
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98118939A Withdrawn EP0916914A3 (en) | 1997-11-14 | 1998-10-07 | A refrigerating cycle |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0916914A3 (en) |
JP (1) | JP3481138B2 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
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EP1039250A2 (en) | 1999-03-25 | 2000-09-27 | TGK Co., Ltd. | Refrigerating cycle with a by-pass line |
WO2013120735A1 (en) * | 2012-02-15 | 2013-08-22 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigeration device and refrigeration machine therefor |
CN104713274A (en) * | 2015-03-19 | 2015-06-17 | 合肥天鹅制冷科技有限公司 | Energy adjustment refrigerating device |
CN105588354A (en) * | 2015-04-23 | 2016-05-18 | 海信(山东)空调有限公司 | Air conditioner and refrigerating method thereof |
EP3658836A4 (en) * | 2017-07-23 | 2021-03-03 | Zuta-Core Ltd. | Systems and methods for heat exchange |
CN115500049A (en) * | 2022-08-03 | 2022-12-20 | 北京无线电测量研究所 | Environment control equipment, environment control system and environment control method |
WO2024032116A1 (en) * | 2022-08-08 | 2024-02-15 | 上海能源建设工程设计研究有限公司 | Constant-temperature water chilling unit |
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JP2007191057A (en) * | 2006-01-19 | 2007-08-02 | Sanden Corp | Refrigeration system, and air conditioner for vehicle |
JP5786212B2 (en) * | 2011-04-14 | 2015-09-30 | 株式会社テージーケー | Air conditioning system for vehicles |
CN106524607A (en) * | 2016-11-25 | 2017-03-22 | 广东申菱环境系统股份有限公司 | Compressor high-temperature operation device |
CN106766423B (en) * | 2016-12-30 | 2019-04-12 | 石家庄国祥运输设备有限公司 | The method of the high pressure storage and transportation mechanism security monitoring of rail traffic air-conditioning system |
CN113945018A (en) * | 2020-06-30 | 2022-01-18 | 上海海立电器有限公司 | Refrigeration power system of air conditioner |
CN111854119B (en) * | 2020-07-21 | 2021-09-14 | 珠海格力电器股份有限公司 | Stepless regulation control method for load output of water chilling unit and water chilling unit |
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Publication number | Priority date | Publication date | Assignee | Title |
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EP1039250A2 (en) | 1999-03-25 | 2000-09-27 | TGK Co., Ltd. | Refrigerating cycle with a by-pass line |
US6351959B1 (en) | 1999-03-25 | 2002-03-05 | Tgk Co. Ltd. | Refrigerating cycle with a by-pass line |
WO2013120735A1 (en) * | 2012-02-15 | 2013-08-22 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigeration device and refrigeration machine therefor |
CN104713274A (en) * | 2015-03-19 | 2015-06-17 | 合肥天鹅制冷科技有限公司 | Energy adjustment refrigerating device |
CN105588354A (en) * | 2015-04-23 | 2016-05-18 | 海信(山东)空调有限公司 | Air conditioner and refrigerating method thereof |
CN105588354B (en) * | 2015-04-23 | 2018-11-09 | 海信(山东)空调有限公司 | A kind of air-conditioning and its refrigerating method |
EP3658836A4 (en) * | 2017-07-23 | 2021-03-03 | Zuta-Core Ltd. | Systems and methods for heat exchange |
US11365906B2 (en) | 2017-07-23 | 2022-06-21 | Zuta-Core Ltd. | Systems and methods for heat exchange |
CN115500049A (en) * | 2022-08-03 | 2022-12-20 | 北京无线电测量研究所 | Environment control equipment, environment control system and environment control method |
WO2024032116A1 (en) * | 2022-08-08 | 2024-02-15 | 上海能源建设工程设计研究有限公司 | Constant-temperature water chilling unit |
Also Published As
Publication number | Publication date |
---|---|
JPH11344263A (en) | 1999-12-14 |
EP0916914A3 (en) | 2002-01-02 |
JP3481138B2 (en) | 2003-12-22 |
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