JP2013185790A - Heat exchanger, and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a heat exchanger, or the like, capable of properly splitting a flow according to a configuration.SOLUTION: A heat exchanger is configured such that a plurality of heat exchanger bodies are arranged to surround a fan, and the heat exchanger bodies are connected with each other through a pipe. The heat exchanger includes: a solenoid valve 1 arranged between one or more heat exchanger bodies and two or more heat exchanger bodies to control the pressure of refrigerant; and a T-shaped pipe 4 connected to the solenoid valve 1, and for splitting a flow of refrigerant to allow the refrigerant to flow into the two or more heat exchanger bodies.

Description

  The present invention relates to a heat exchanger or the like used for an air conditioner or the like.

  For example, conventionally, in a room air conditioner indoor unit, a heat exchanger has been proposed in which a three-way pipe is arranged before and after the solenoid valve so as to branch the refrigerant (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 2001-072861 (FIG. 1)

  The conventional method described above has a problem that it is difficult to adjust the diversion ratio after passing through the electromagnetic valve.

  The present invention has been made in order to solve the above-described problems, and an object of the present invention is to obtain a heat exchanger or the like that can perform a proper flow division according to the configuration.

  The heat exchanger according to the present invention is a heat exchanger in which a plurality of heat exchanger bodies are arranged so as to surround a blower, and each heat exchanger body is connected by piping, and one or more heat exchangers A flow control device that is arranged between the main body and two or more heat exchanger main bodies to control the pressure of the refrigerant and connected to the flow control device, branches the refrigerant and flows into two or more heat exchanger main bodies And a T-shaped tube.

  According to the present invention, the T-tube is connected to the flow rate control device so that the refrigerant is branched into two or more heat exchanger bodies, so that variation when the refrigerant is divided into the heat exchanger bodies is suppressed. It becomes easy to branch properly, and the heat exchanger performance can be improved. At this time, for example, the volume, the manufacturing cost, and the like can be significantly reduced as compared with the case where the valve serving as the flow rate control device and the distributor that has been cut out are joined.

It is an external view in the structure of the branch part centering on the solenoid valve 1 and the T-tube 4 which the heat exchanger of Embodiment 1 of this invention has. It is an external view in another structure of the branched part centering on the solenoid valve 1 and the T-tube 4 which the heat exchanger of Embodiment 1 of this invention has. It is a figure which shows the flow of the refrigerant | coolant in the heat exchanger by Embodiment 1 of this invention. It is a figure which shows distribution of the liquid refrigerant 17 until it passes the T-tube 4 from the solenoid valve 1. FIG. It is a figure for demonstrating the shunt ratio of the T-shaped tube 4 of Embodiment 1 of this invention. It is a figure which shows the structure of the refrigerating-cycle apparatus which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
FIG. 1 is an external view of a configuration of a branching portion centering on a solenoid valve 1 and a T-shaped tube 4 included in a heat exchanger according to Embodiment 1 of the present invention. The electromagnetic valve 1 serving as a flow control valve (expansion valve) is, for example, a control device (depicted in FIG. 1) in order to deheat and dehumidify the heat exchanger in a dehumidifying mode of the room air conditioner. The opening degree is changed based on an instruction (not shown) to control the flow of the refrigerant. When performing cooling or the like, if the valve is fully opened, it functions as an evaporator or a condenser. The solenoid valve 1 has an upstream side pipe 2 and a downstream side pipe 3 for connecting to other pipes. The upstream part side pipe 2 and the downstream part side pipe 3 are stainless steel pipes covered with an aluminum brazing material. The inflow side pipe 5 and the T-shaped pipe 4 which is a three-way pipe are aluminum pipes. Although described here as a T-shaped tube 4, a bulge three-way tube or the like may be used. Here, the direction in which the refrigerant flows from the inflow side pipe 5 to the electromagnetic valve 1 is defined as a horizontal direction, and the direction in which the refrigerant flows from the electromagnetic valve 1 to the T-shaped tube 4 is described as a vertical direction.

  And the inflow side piping 5 and the upstream part side piping 2 are brazed and joined, and the solenoid valve 1 and the inflow side piping 5 are directly connected. Similarly, the T-shaped tube 4 and the downstream side pipe 3 are brazed and joined, and the solenoid valve 1 and the T-shaped tube 4 are directly connected. The refrigerant that has passed through the electromagnetic valve 1 and has flowed into the T-tube 4 can be distributed almost evenly.

  By directly joining the solenoid valve 1 and the T-shaped tube 4, it is possible to significantly reduce the volume, manufacturing cost, etc., compared to joining the solenoid valve 1 and a machined distributor. it can. Moreover, as the upstream part side pipe 2 and the downstream part side pipe 3, it is easy to join the aluminum pipe by using a pipe covered with a stainless steel brazing material. And although the iron-type metal is used for the component in the solenoid valve 1, if the surface of the solenoid valve 1 is coat | covered with resin, corrosion resistance can be maintained.

  FIG. 2 is an external view of another configuration of a branching portion centering on the solenoid valve 1 and the T-shaped tube 4 included in the heat exchanger according to Embodiment 1 of the present invention. Here, while flowing from the solenoid valve 1 to the T-tube 4, the refrigerant once flows in the horizontal direction (direction orthogonal to the refrigerant flowing out of the solenoid valve 1). For this reason, as shown in FIG. 2, the downstream side pipe 3 (solenoid valve 1) and the downstream pipe bend 7 are connected, and the T-shaped pipe bend 6 and the T-shaped pipe 4 are connected, The bends are connected by an inter-bend pipe 8 that allows the refrigerant to flow in a straight line (in the horizontal direction). Here, the relationship between the length L1 of the inter-bend pipe 8 and the length L2 of the T-shaped pipe inlet portion 9 which becomes a connecting portion on the refrigerant inflow side in the T-shaped tube 4 and in which the direction of the tube is vertical is L1>. L2 is set. Here, the solenoid valve 1 and the T-shaped pipe 4 are connected by a downstream pipe bend 7, an inter-bend pipe 8, and a T-shaped bend 6, so that the refrigerant flow changes twice. Further, a bend may be further connected in order to make the diversion ratio appropriate.

  Next, for example, the flow of the refrigerant when performing cooling in the air conditioner in which the heat exchanger according to the present embodiment is mounted in an indoor unit will be described. The refrigerant flows in from the inflow side pipe 5 and passes through the solenoid valve 1 through the upstream side pipe 2. At this time, when functioning as an evaporator, for example, the electromagnetic valve 1 is fully opened. Then, the electromagnetic valve 1 passes through the downstream pipe 3, the downstream pipe bend 7, the inter-bend pipe 8, and the T-shaped pipe bend 6 and flows into the T-shaped pipe 4 from the T-shaped pipe inlet 9. At this time, the flow of the refrigerant is bent by approximately 90 ° by the downstream pipe bend 7 and flows from the vertical direction to the horizontal direction. Further, the flow of the refrigerant is bent by approximately 90 ° by the T-tube bend 6 and flows from the horizontal direction to the vertical direction. The refrigerant flowing into the T-shaped tube 4 branches out to the A direction side and the B direction side and flows out.

  FIG. 3 is a diagram showing a refrigerant flow in the heat exchanger according to Embodiment 1 of the present invention. In the present embodiment, a plurality of heat exchanger bodies are connected by piping to form a heat exchanger (hereinafter, the heat exchanger bodies are also referred to as heat exchangers for explanation). In this Embodiment, the heat exchanger main body is arrange | positioned at the back side in a housing | casing, the front upper part side, and the front lower part side so that an air blower (not shown) may be enclosed. And the heat exchanger main body in each place has a circular tube assist heat exchanger (auxiliary heat exchanger) and a flat tube heat exchanger, respectively. And it is made for a refrigerant | coolant to flow by connecting between each heat exchanger main body by piping.

  Next, the flow of the refrigerant in the heat exchanger will be described. For example, as described above, when cooling is performed, the refrigerant flows from the back tube assist heat exchanger 15. Then, it passes through the front upper circular tube assisted heat exchanger 14 and the front lower circular tube assisted heat exchanger 13. Then, it branches into two by the bulge three-way pipe 16 </ b> A and flows into the two bulge three-way pipes 16 </ b> B and 16 </ b> C of the front upper flat tube heat exchanger 11. After passing through the heat transfer tube in the front upper flat tube heat exchanger 11, they merge through a bulge three-way tube 16D.

  Then, as described above, the refrigerant flows in from the inflow side pipe 5 and passes through the electromagnetic valve 1 and the T-shaped tube 4. The refrigerant flowing in the A direction due to the branching in the T-shaped tube 4 flows into the front lower flat tube heat exchanger 12, and the refrigerant flowing in the B direction flows into the rear flat tube heat exchanger 10. In the front lower flat tube heat exchanger 12 and the back flat tube heat exchanger 10, after bifurcating at the bulge three-way pipes 16E and 16F, each passes through the internal heat transfer pipe, and merges and flows out at the bulge three-way pipe 16G. Here, after branching at the T-shaped tube 4, branching at the bulge three-way pipes 16 </ b> E and 16 </ b> F can reduce the number of pipes compared to branching at a distributor or the like.

  Here, the front lower circular tube assisted heat exchanger 13 on the windward side is arranged in six stages, while the rear circular pipe assisted heat exchanger 15 on the windward side is arranged in four stages. For this reason, the heat load of the back flat tube heat exchanger 10 is larger than that of the front lower flat tube heat exchanger 12. Therefore, the back flat tube heat exchanger 10 requires a larger amount of liquid refrigerant flow for cooling.

  FIG. 4 is a view showing the distribution of the liquid refrigerant 17 from the electromagnetic valve 1 to the passage through the T-shaped tube 4. The liquid refrigerant 17 that has flowed out of the solenoid valve 1 flows in the inner pipe wall of the downstream side pipe 3 with an equal liquid film thickness, and bends in the horizontal direction in the downstream pipe bend 7. When bending in the horizontal direction (90 °), centrifugal force acts on the refrigerant, so that the liquid film thickness on the inner wall on the outer peripheral side becomes thicker. Then, while passing through the inter-bend pipe 8, the liquid film thickness is slightly recovered by the steam shear force so as to be uniform in the vertical direction. After that, it flows in the T-shaped bend 6 by bending in the vertical direction. Since the centrifugal force acts on the refrigerant even when it bends in the vertical direction, the liquid film thickness on the outer peripheral side wall (B direction side) becomes thicker than the liquid film thickness on the wall on the A direction side. For this reason, the flow rate of the liquid refrigerant 17 flowing out from the T-shaped tube 4 is biased toward the B direction, and is larger in the B direction than in the A direction. Here, since the accommodation space in the gravitational direction is easy to be accommodated, it is bent 90 ° with respect to the refrigerant inflow direction here, but is not limited to the 90 ° inclination as long as centrifugal force can be applied.

  As described above, since the heat load of the back flat tube heat exchanger 10 is larger than the heat load of the front lower flat tube heat exchanger 12, the B direction side pipe is connected to the back flat tube heat exchanger 10. . Then, the pipe on the A direction side is connected to the front lower flat tube heat exchanger 12. In order to return the liquid film thickness of the inner wall as uniform as possible in the inter-bend pipe 8, the length L1 of the inter-bend pipe 8 is increased. On the other hand, in order to maintain the liquid film distribution in the T-tube bend 6 and allow the refrigerant to flow into the T-tube 9, the length L2 of the T-tube inlet 9 is shortened. For this reason, at least the relationship between the pipe lengths is set to satisfy L2> L1.

  FIG. 5 is a diagram for explaining the diversion ratio of the T-shaped tube 4 according to the first embodiment of the present invention. Even when the refrigerant flow rate changes, the liquid refrigerant flow rate ratio in the B direction is 55 to 58%, which is larger than the refrigerant flowing in the A direction. In such a case, the temperature of the refrigerant at the refrigerant outlet of the front lower flat tube heat exchanger 12 and the rear flat tube heat exchanger 10 during cooling is substantially the same, and the heat exchanger performance can be sufficiently extracted. .

  As described above, according to the heat exchanger of the first embodiment, since the refrigerant is branched by connecting the T-tube 4 to the electromagnetic valve 1, for example, the distributor (see FIG. Compared with a distributor, the volume, production cost, and the like can be greatly reduced, variation in refrigerant distribution can be suppressed, and proper branching can be facilitated, and heat exchanger performance can be improved.

  In particular, as a pipe between the solenoid valve 1 and the T-shaped pipe 4, a T-shaped pipe bend 6, a downstream pipe bend 7 and an inter-bend pipe 8 are connected so that the refrigerant once flows in the horizontal direction. Thus, the flow rate in the B direction can be increased, and the refrigerant flowing into the front lower flat tube heat exchanger 12 and the rear flat tube heat exchanger 10 can be divided in an appropriate amount. At this time, the length L1 of the inter-bend pipe 8 is made longer than the length L2 of the T-shaped pipe inlet 9, and the liquid film thickness on the inner wall caused by the centrifugal force in the downstream pipe bend 7 is determined. In this case, by returning as uniform as possible, it is possible to further suppress variation and perform proper diversion.

  Further, by using a pipe covered with a stainless steel brazing material for the upstream part side pipe 2 and the downstream part side pipe 3, it can be easily joined to the aluminum pipe.

Embodiment 2. FIG.
FIG. 6 is a diagram showing a configuration of a refrigeration cycle apparatus according to Embodiment 2 of the present invention. In the refrigeration cycle apparatus of FIG. 6, a compressor 33, a condenser 34, a throttling device 35, and an evaporator 36 are connected by piping to form a refrigerant circuit (refrigerant circulation circuit). In addition, the blower 37 forms a flow of air in order to promote heat exchange between the refrigerant passing through the condenser 34 and the evaporator 36 and air by driving the blower motor 38.

  The compressor 33 sucks the refrigerant, compresses it, and discharges it in a high temperature / high pressure state. Here, for example, it may be configured by a compressor of a type that can control the number of revolutions by an inverter circuit or the like and adjust the discharge amount of the refrigerant. The condenser 34 having a heat exchanger performs heat exchange between air supplied from a blower (not shown) and a refrigerant, for example, and condenses the refrigerant into a liquid refrigerant (condensates and liquefies). is there.

  The expansion device 35 expands the refrigerant by decompressing it. For example, it is constituted by a flow rate control means such as an electronic expansion valve, but may be constituted by an expansion valve having a temperature sensing cylinder, a refrigerant flow rate adjustment means such as a capillary tube (capillary), or the like. The evaporator 36 evaporates the refrigerant by heat exchange with air or the like to form a gas (gas) refrigerant (evaporates into gas).

  For example, the heat exchanger described in Embodiment 1 can be used for at least one of the evaporator 36 and the condenser 34. Thereby, in the apparatus of Embodiment 2, heat transfer performance can be improved. By improving the heat transfer performance, an energy-efficient and energy-saving refrigeration cycle apparatus can be obtained.

Here, energy efficiency is comprised by following Formula (1) and (2).
Heating energy efficiency = indoor heat exchanger (condenser) capacity / total input (1)
Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / total input (2)

  Next, operation | movement in each component apparatus of a refrigerating-cycle apparatus is demonstrated based on the flow of the refrigerant | coolant which circulates through a refrigerant circuit. First, the compressor 33 sucks the refrigerant, compresses it, and discharges it in a high temperature / high pressure state. The discharged refrigerant flows into the condenser 34. The condenser 34 performs heat exchange between the air supplied from the blower 37 and the refrigerant, and condenses and liquefies the refrigerant. The condensed and liquefied refrigerant passes through the expansion device 35. The expansion device 35 depressurizes the condensed and liquefied refrigerant passing therethrough. The decompressed refrigerant flows into the evaporator 36. The evaporator 36 exchanges heat between the air supplied from the blower 37 and the refrigerant to evaporate the refrigerant. The compressor 33 sucks the evaporated gas refrigerant.

  Here, the refrigeration cycle apparatus described above includes HCFC (R22) and HFC (R116, R125, R134a, R14, R143a, R152a, R227ea, R23, R236ea, R236fa, R245ca, R245fa, R32, R41, RC318, etc. Several refrigerants such as R407A, R407B, R407C, R407D, R407E, R410A, R410B, R404A, R507A, R508A, R508B, etc.), HC (butane, isobutane, ethane, propane, propylene, etc.) What kind of refrigerant is used, such as mixed refrigerant), natural refrigerant (several mixed refrigerants such as air, carbon dioxide, ammonia, etc.), low GWP refrigerants such as HFO1234yf, and several mixed refrigerants of these refrigerants , It can achieve its effect.

  Moreover, although air and a refrigerant | coolant were shown as an example as a working fluid, even if it uses other gas, a liquid, and a gas-liquid mixed fluid, there can exist the same effect.

  Furthermore, the heat transfer tube 2 and the plate-like fin 1 are usually made of different materials, but the heat transfer tube 2 and the plate-like fin 1 are made of the same material such as copper or aluminum. Also good. For example, it becomes possible to braze the plate-like fins 1 and the heat transfer tubes 2, and the contact heat transfer coefficient between the plate-like fins 1 and the heat transfer tubes 2 is greatly improved, thereby greatly increasing the heat exchange capacity. Can be improved. Moreover, recyclability can also be improved.

  Further, as a method for bringing the heat transfer tube 2 and the plate fin into close contact, when brazing in a furnace, the hydrophilic material during brazing in the case of pretreatment is performed by performing post-treatment to apply a hydrophilic material to the fin. Can prevent burnout.

  Further, the same effect can be obtained when the heat exchanger described in the first embodiment is used in an outdoor unit.

  For the heat exchanger described in the above embodiment and the air-conditioning refrigeration system using the heat exchanger, it is possible to dissolve the refrigerant and oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil. The effect can be achieved with any refrigeration oil, whether or not.

  As an application example of the present invention, it can be used in a heat pump device that requires improved heat exchange performance and improved energy saving performance.

  DESCRIPTION OF SYMBOLS 1 Solenoid valve, 2 Upstream side piping, 3 Downstream side piping, 4 T-shaped pipe, 5 Inflow side piping, 6 T-shaped bend, 7 Downstream piping bend, 8 Inter-bend piping, 9 T-shaped pipe inlet DESCRIPTION OF SYMBOLS 10 Back flat tube heat exchanger, 11 Front upper flat tube heat exchanger, 12 Front lower flat tube heat exchanger, 13 Front lower circular tube assisted heat exchanger, 14 Front upper circular tube assisted heat exchanger, 15 Back circle Pipe assist heat exchanger, 16A-16F Bulge three-way pipe, 17 liquid refrigerant, 33 compressor, 34 condenser, 35 expansion device, 36 evaporator, 37 blower, 38 blower motor.

Claims (6)

A plurality of heat exchanger bodies are arranged so as to surround the blower, and each heat exchanger body is a pipe connected to the heat exchanger,
A flow rate control device arranged between one or more heat exchanger bodies and two or more heat exchanger bodies to control the pressure of the refrigerant;
A heat exchanger comprising: a T-tube connected to the flow rate control device and branching the refrigerant to flow into the two or more heat exchanger bodies.   2. The heat exchanger according to claim 1, wherein the pipe attached to the flow rate control device is made of stainless steel with a brazing material applied on the surface thereof and connected to a pipe made of aluminum.   A straight pipe that changes the flow of the refrigerant in a direction substantially orthogonal to the direction of the refrigerant flowing through the flow control device and the T-shaped tube is connected between the flow control device and the T-shaped tube. The heat exchanger according to claim 1 or 2.   The heat exchanger according to claim 3, wherein a length of the straight pipe is longer than a length of a connection portion on the refrigerant inflow side in the T-shaped pipe.   The heat exchanger according to any one of claims 1 to 4, wherein two bulge three-way pipes are connected and branched into four between the T-shaped tube and the outlet of the heat exchanger. Pipe connection is made between a compressor that compresses and discharges the refrigerant, a condenser that condenses the refrigerant by heat exchange, a throttle device that depressurizes the refrigerant related to condensation, and an evaporator that evaporates the refrigerant by heat exchange. Configure the refrigerant circuit,
A refrigeration cycle apparatus, wherein the heat exchanger according to claim 1 functions as the evaporator and / or the condenser.

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