JP2005022611A - Refrigerating cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating cycle device capable of improving a cooling performance in a refrigerating path connecting function parts of a heat exchanger and the like. <P>SOLUTION: This device comprises a condenser 2 for heat exchanging outside air and refrigerant and condensing and liquifying the refrigerant, and piping 12, 23 on an upstream side and a downstream side of the refrigerant. At least one of the piping 12 on the upstream side of the refrigerant and the piping 23 on the downstream side of the refrigerant comes into contact with a low temperature member 9 with lower temperature than that of one of the piping. The low temperature member 9 is preferably a body on a vehicle side mounting a refrigerating cycle device. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a refrigeration cycle apparatus, and is suitable for use in, for example, a vehicle air conditioner.

  The refrigeration cycle apparatus is used for, for example, an air conditioner for automobiles, and is known to include a compressor, a condenser, an expansion valve, and an evaporator. In recent years, this type of refrigeration cycle apparatus has been required to improve cooling performance in order to improve the efficiency of car air conditioners. For this reason, functional parts such as heat exchangers such as condensers and evaporators are being developed every day to improve performance.

  However, with respect to parts other than functional parts, for example, pipes connecting functional parts, development of technology for preventing performance degradation has been promoted, but no consideration has been given to structures that actively improve performance.

  The present invention has been made in consideration of such circumstances, and an object of the present invention is to improve the cooling performance in a refrigerant path connecting functional parts such as a heat exchanger.

  Another object is to provide a refrigeration cycle apparatus capable of improving the cooling performance in a refrigerant path connecting functional parts such as a heat exchanger and saving space.

  According to a first aspect of the present invention, the apparatus includes a condenser that exchanges heat between the outside air and the refrigerant to condense and liquefy the refrigerant, and a pipe on the refrigerant upstream side and the refrigerant downstream side that guides the circulating refrigerant to the condenser. At least one of the upstream pipe and the downstream refrigerant pipe is in thermal contact with a low temperature member having a temperature lower than that of the one pipe.

  Thus, when one of the pipes is a pipe on the upstream side of the refrigerant that guides the circulating refrigerant to the condenser, the pipe on the upstream side of the refrigerant is in thermal contact with the low-temperature member having a lower temperature than that. It is possible to exchange heat between the refrigerant flowing through the pipe and the low-temperature member so that the refrigerant upstream pipe has the function of a condenser. In addition, when one pipe is a refrigerant downstream pipe that sends out the refrigerant from the condenser, the refrigerant downstream pipe is in thermal contact with the low temperature member, so heat exchange is performed between the refrigerant flowing through the refrigerant downstream pipe and the low temperature member. Thus, the refrigerant downstream pipe can have the function of a supercooler.

  Therefore, at least one of the refrigerant upstream side pipe and the refrigerant downstream side pipe that guides the refrigerant to the condenser is in thermal contact with the low-temperature member having a lower temperature than one of the refrigerant. At least one of the supercooling sections having the function of the cooler is additionally added to the condenser, and as a result, the cooling performance can be improved.

  According to claim 2 of the present invention, the low temperature member is a vehicle-side body on which the refrigeration cycle apparatus is mounted.

  This eliminates the need for a gap between the refrigerant upstream pipe or the refrigerant downstream pipe and the vehicle-side body, thereby saving space.

  According to claim 3 of the present invention, one of the pipes is in contact with the low-temperature member via a heat transfer material capable of absorbing vibration.

  As a result, at least one of the refrigerant upstream side pipe and the refrigerant downstream side pipe and the low temperature member are in contact with each other via the heat transfer material capable of absorbing vibration, so that the compressor and the internal combustion engine mounted on the vehicle It is possible to prevent the excitation force from being transmitted to the one pipe through the body. Even if resonance vibration occurs in one of the pipes, the resonance vibration can be reduced by the heat transfer material. As a result, it is possible to reduce vibration transmission of the refrigerant upstream side pipe and the refrigerant downstream side pipe, that is, the cooling cycle device, ensure vibration resistance strength and improve the cooling performance.

  Hereinafter, the embodiment which applied the refrigerating cycle device of the present invention to the refrigerating cycle device in vehicles air-conditioners, such as a car, and explained concretely is described according to drawings. FIG. 1 is a refrigeration cycle diagram showing this embodiment. FIG. 2 is an external view showing a structure around the condenser in FIG. 3 is a cross-sectional view as seen from the direction of III-III in FIG. FIG. 4 is a Mollier diagram showing the operation of the refrigeration cycle in the embodiment of the present invention.

  As shown in FIG. 1, the refrigeration cycle apparatus includes a compressor 1, a condenser 2, an expansion valve 3, and an evaporator 4. In this refrigeration cycle apparatus, a refrigerant is enclosed, and a closed circuit in which the refrigerant sequentially flows to the compressor 1, the condenser 2, the expansion valve 3, and the evaporator 4 is formed. The compressor 1, the condenser 2, the expansion valve 3, and the evaporator 4 constitute functional parts of the refrigeration cycle apparatus. These functional parts are connected by a refrigerant pipe made of a metal pipe or a rubber pipe. Here, the refrigerant piping constitutes a refrigerant path that connects the functional components.

  The compressor 1 is a fluid device that compresses the refrigerant in the refrigeration cycle to high temperature and pressure. The compressor 1 is driven by an internal combustion engine (not shown) for driving an automobile or an auxiliary internal combustion engine dedicated to cooling, and a driving force is transmitted from the internal combustion engine via an electromagnetic clutch 1a and the like. The compressor is a fixed capacity compressor in which the discharge capacity per one rotation is a predetermined amount. Note that a variable capacity type in which the discharge capacity is variable by a control device (not shown) may be used.

  The condenser 2 is connected to a refrigerant pipe made of metal and rubber pipes on the discharge side of the compressor 1 (see FIG. 2), and exchanges heat with outside air (specifically, air blown by a cooling fan not shown). This is a heat exchanger that condenses and liquefies the refrigerant. The condenser 2 has a configuration in which, for example, a corrugated fin (not shown) is interposed between flat tubes (not shown) through which refrigerant flows, and a plurality of flat tubes and fins are stacked.

  As shown in FIGS. 1 and 2, the refrigerant pipe that guides the refrigerant flowing through the condenser 2 to the condenser 2 is upstream of the refrigerant that guides the refrigerant compressed to high temperature and high pressure from the compressor 1 to the inlet side of the condenser 2. A pipe (hereinafter referred to as a high-pressure liquid refrigerant pipe) 12 and a refrigerant downstream pipe (hereinafter referred to as a high-pressure liquid refrigerant pipe) led from the outlet side of the condenser 2 so that the condensed and liquefied refrigerant flows into the expansion valve 3. ) 23. The high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 are formed from metal pipes having relatively excellent thermal conductivity. This metal pipe is made of, for example, aluminum or an aluminum alloy.

  As shown in FIG. 1, the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 are in thermal contact with the low-temperature member 9 having a lower temperature than the pipes 12 and 23. As a result, the high-pressure gas refrigerant pipe 12 can perform heat exchange between the high-temperature and high-pressure refrigerant flowing through the high-pressure gas refrigerant pipe 12 and the low-temperature member 9. As a result, it is possible to give the high-pressure gas refrigerant pipe 12 the function of a condenser capable of condensing and liquefying the refrigerant compressed to high temperature and high pressure by heat exchange with the low temperature member. Note that the high-pressure gas refrigerant pipe 12 is referred to as a condensing unit in distinction from the condenser 2. Here, the high-pressure gas refrigerant pipe 12 and the condenser 2 constitute high-pressure gas refrigerant condensing means for condensing and liquefying the refrigerant compressed to high temperature and high pressure from the compressor 1. Further, the high-pressure liquid refrigerant pipe 23 can exchange heat between the low-temperature member 9 and the condensed liquid refrigerant flowing through the high-pressure liquid refrigerant pipe 23. As a result, the high-pressure liquid refrigerant pipe 23 can have a function of a supercooler capable of supercooling the condensed and liquefied refrigerant by heat exchange with the low temperature member. Note that the high-pressure liquid refrigerant pipe 23 is referred to as a supercooling section in distinction from the condenser 2. Here, the high-pressure liquid refrigerant pipe 23 and the condenser 2 constitute high-pressure liquid refrigerant supercooling means for supercooling the cooled, condensed or condensed liquid refrigerant.

  In the present embodiment, the low temperature member 9 is a vehicle-side body on which the refrigeration cycle apparatus is mounted, as shown in FIG. This eliminates the need for a gap between the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 and the vehicle-side body, thereby saving space. In the case of the body, the temperature is normally about 60 ° C. or lower, and the temperature of the low temperature member 9 is lower than the temperatures of the high pressure gas refrigerant pipe 12 and the high pressure liquid refrigerant pipe 23.

  Furthermore, in this embodiment, as shown in FIG. 3, the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 are in contact with the low-temperature member 9 via the heat transfer material 8 that can absorb vibration. As a result, the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 are in contact with the low-temperature member (specifically, the vehicle-side body) 9 via the heat transfer material 8 capable of absorbing vibration, so that they are mounted on the vehicle. It is possible to reduce the transmission of the vibration force of the compressor and the internal combustion engine transmitted to the refrigerant pipes 12 and 23 via the body 9. Further, even if resonance vibration occurs in any one of the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23, the resonance vibration generated by the heat transfer material 8 can be absorbed. As a result, it is possible to achieve both reduction in vibration transmission of the refrigerant upstream side pipe 12 and the refrigerant downstream side pipe 23, that is, the cooling cycle device, ensuring vibration resistance strength and improving cooling performance.

  The expansion valve 3 expands the refrigerant condensed and liquefied from the condenser 2 under reduced pressure. In the present embodiment, the refrigerant is decompressed in an enthalpy manner and the superheat degree of the refrigerant sucked into the compressor 1 becomes a predetermined value. A temperature type expansion valve that controls the throttle opening is employed.

  The evaporator 4 is disposed in a case (ventilation path) of an air conditioning unit (not shown), evaporates the refrigerant decompressed and expanded by the expansion valve 3, and blowers (not shown) by the latent heat of evaporation at that time. It is a heat exchanger which cools the conditioned air from.

  In the case (ventilation passage), a heater circuit (not shown) is connected to a cooling water circuit (not shown) for cooling the water-cooled internal combustion engine, and the flow of the cooling water (warm water) branches from the cooling water circuit. The heater core (not shown) which comprises a heater core (not shown) is arrange | positioned, and this heater core heats the air-conditioning air ventilated with an air blower by heat exchange with warm water.

  For the conditioned air cooled by the evaporator 4 and the conditioned air heated by the heater core, for example, the amount of conditioned air flowing through the heater core is variable according to the opening of an air mix door (not shown) provided in the heater core. By adjusting, the mixing ratio is varied and adjusted to a predetermined temperature set by an occupant or the like who gets on the vehicle.

  The operation of the refrigeration cycle apparatus having the above-described configuration will be described with reference to FIG. FIG. 4 shows a Mollier diagram. The upwardly convex curve in the figure is a saturated liquid line on the left side of the critical point at the substantially convex top, and the saturated curve is on the right side. Represents.

  The high-temperature and high-pressure gas refrigerant compressed by the compressor 1 (see the state point a in FIG. 4) flows through the high-pressure gas refrigerant pipe 12 and is led to the inlet side of the condenser 2. At this time, the high-pressure gas refrigerant pipe 12 operates as a condensing part, and acts to cool and condense the high-temperature and high-pressure gas refrigerant by heat exchange with the low-temperature member (state point a → state point in FIG. 4). b). When this refrigerant flows into the condenser 2, in the condenser 2, the refrigerant is distributed to each flat tube, and heat is exchanged with the outside air by the fins to be condensed and liquefied (state point b → state point c in FIG. 4). reference). Further, the condensed and liquefied refrigerant that has flowed out from the outlet side of the condenser 2 flows through the high-pressure liquid refrigerant pipe 23 and is guided to the expansion valve 3. At this time, the high-pressure liquid refrigerant pipe 23 operates as a supercooling section, and acts to further cool and supercool the condensed and liquefied refrigerant by heat exchange with the low temperature member (state point c → in FIG. 4). (See state point d). In FIG. 4, the degree of supercooling is indicated by SC.

  And the refrigerant | coolant which distribute | circulates the temperature type expansion valve 4 is decompressed | expanded by isoenthalpy, and is guide | induced to the evaporator 4 (refer the state point d-> state point e in FIG. 4). When this refrigerant flows into the evaporator 4, the refrigerant flowing through the evaporator 4 takes heat from the surrounding air (absorbs heat) and evaporates (see state point e → state point f in FIG. 4). It is sucked into the suction side of the compressor 1.

  Thereby, since the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 are in thermal contact with the low temperature member 9, the degree of supercooling SC is compared with the Mollier diagram of the conventional configuration (broken line in FIG. 4). Thus, the refrigerant pipes 12 and 23 increase by the amount that is in thermal contact with the low temperature member 9 in a low temperature state (Ti = 60 ° C. in this embodiment). Therefore, the cooling performance of the cooling cycle device can be improved.

  Since the temperature type expansion valve 3 is used, the throttle opening is controlled so that the refrigerant is decompressed in an enthalpy manner and the superheat degree of the refrigerant sucked into the compressor 1 becomes a predetermined value. The middle state point f is the same as the state point of the conventional Mollier diagram.

  According to the present embodiment described above, the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 are in thermal contact with the low-temperature member 9 having a lower temperature than the refrigerant pipes 12 and 23. Furthermore, the condensing part and the supercooling part which function by each operation | movement are additionally increased, As a result, the cooling performance can be improved.

  In the present embodiment described above, the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 have been described as being in thermal contact with the low-temperature member 9, respectively. It is sufficient that at least one of the refrigerant pipes is in thermal contact with the low temperature member 9. Even in this configuration, when one of the refrigerant pipes is the high-pressure gas refrigerant pipe 12, it is possible to increase the degree of supercooling SC by additionally increasing the condenser 2 due to the operation of the high-pressure gas refrigerant pipe 12 in the condenser 2. it can. Moreover, when one refrigerant | coolant piping is the high pressure liquid refrigerant | coolant piping 23, the supercooling part by operation | movement of the high pressure liquid refrigerant | coolant piping 23 can be additionally increased to the condenser 2, and the supercooling degree SC can be increased.

  Furthermore, in the present embodiment described above, the low temperature member 9 has been described as a vehicle-side body on which the refrigeration cycle apparatus is mounted. However, as long as it is at a lower temperature than the high pressure gas refrigerant pipe 12 and the high pressure liquid refrigerant pipe 23. The mating member may be in thermal contact with any one of the refrigerant pipes 12 and 23.

  Furthermore, in a refrigeration cycle apparatus mounted on a vehicle such as an automobile, when the vehicle-side body suspended in cooperation with an excitation source such as an internal combustion engine mounted on the vehicle is used as a low temperature member, The high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23 are preferably in contact with the body via the heat transfer material 8 capable of absorbing vibration. Thereby, it is possible to prevent the vibration of the vibration source from being transmitted to the refrigerant pipes 12 and 23. Further, even if resonance vibration occurs in any one of the high-pressure gas refrigerant pipe 12 and the high-pressure liquid refrigerant pipe 23, the resonance vibration generated by the heat transfer material 8 can be absorbed. Therefore, it is possible to ensure both the vibration resistance strength of the refrigerant upstream pipe 12 and the refrigerant downstream pipe 23, that is, the refrigeration cycle apparatus, and the improvement of the cooling performance.

It is a refrigerating cycle figure showing an embodiment of the present invention. It is an external view which shows the structure around the condenser in FIG. It is sectional drawing seen from the III-III direction in FIG. It is a Mollier diagram which shows the action | operation of the refrigerating cycle in embodiment of this invention.

Explanation of symbols

1 Compressor 12 High-pressure gas refrigerant pipe (pipe upstream of refrigerant)
2 Condenser 23 High-pressure liquid refrigerant piping (piping downstream of the refrigerant)
3 Thermal expansion valve (expansion valve)
4 Evaporator 8 Heat transfer material 9 Low temperature member (vehicle body)

Claims (3)

A condenser for exchanging heat between the outside air and the refrigerant to condense and liquefy the refrigerant;
A refrigerant upstream side and a refrigerant downstream side pipe for guiding the circulating refrigerant to the condenser;
The refrigeration cycle apparatus, wherein at least one of the refrigerant upstream pipe and the refrigerant downstream pipe is in thermal contact with a low-temperature member having a temperature lower than that of the one pipe. The refrigeration cycle apparatus according to claim 1, wherein the low-temperature member is a vehicle-side body on which the refrigeration cycle apparatus is mounted. 3. The refrigeration cycle apparatus according to claim 1, wherein the one pipe is in contact with the low-temperature member via a heat transfer material capable of absorbing vibration.

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