JP2012093087A - Condenser and air conditioner using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a condenser which condenses a refrigerant at high efficiency and has high productivity, and an air conditioner using the same.SOLUTION: The condenser 1 is provided with a heat exchanger 2 which has a refrigerant path 5 to allow a refrigerant to pass from upstream to downstream, one end connection pipe 3, and another end connection pipe 4. The heat exchanger 2 includes a first group of pipes 21A, a header pipe 23, and a second group of pipes 21B. The heat exchanger 2 is arranged between an upstream side end portion 6 and a downstream side end portion 7 of the refrigerant path 5, and includes a wall portion 8 formed in the header pipe 23. The wall portion 8 is structured so as to reduce the cross-section area of the refrigerant path 5, and the refrigerant flowing from upstream to downstream in the refrigerant path 5 collides with the wall portion 8 to facilitate refrigerant condensation.

Description

  The present invention relates to a condenser and an air conditioner using the same, and more particularly to a condenser in which condensation is promoted and an air conditioner using the same.

  For example, Japanese Patent Application Laid-Open No. 2000-97519 (Patent Document 1) has proposed an air conditioner improved so as to efficiently condense the refrigerant of high-temperature and high-pressure gas coming out of the compressor. In the air conditioner of this publication, the existing first stage condenser for condensing the refrigerant is additionally provided with a second stage condenser provided with a condensation accelerating portion, thereby preventing a decrease in the function of air conditioning. .

JP 2000-97519 A

  However, in the air conditioner of the above publication, since the second condenser provided with the condensation promoting part is additionally installed, there is a problem that additional work takes time and the cost is increased.

  This invention is made | formed in view of the said subject, The objective is to provide a condenser which can condense a refrigerant | coolant with high efficiency and high productivity, and an air conditioner using the same.

  The condenser of the present invention is a condenser for condensing refrigerant, and is connected to a heat exchange section having a refrigerant passage for allowing the refrigerant to pass from upstream to downstream, and an upstream end of the refrigerant passage. And one connecting pipe portion serving as the refrigerant inlet to the condenser, and the other connecting pipe portion connected to the downstream end of the refrigerant passage and serving as the refrigerant outlet from the condenser. The heat exchange part has a wall part located between the upstream edge part and downstream edge part of a refrigerant path. The wall portion is configured to reduce the cross-sectional area of the refrigerant passage, and is configured to promote the refrigerant condensing action by causing the refrigerant flowing in the refrigerant passage from upstream to downstream to collide with the wall portion. Has been.

According to the condenser of the present invention, the wall portion positioned between the upstream end portion and the downstream end portion of the refrigerant passage in the heat exchange portion is configured to reduce the cross-sectional area of the refrigerant passage. The refrigerant flowing from the upstream to the downstream in the refrigerant passage collides with the wall portion, so that the refrigerant is easily condensed and the refrigerant condensing action is promoted. Since the air conditioner is configured using the condenser of the present invention, the condensation effect can be maintained even if the air conditioner deteriorates. Since the condensing capacity does not drop, the CO ₂ (carbon dioxide) reduction effect can be increased. For this reason, it is not necessary to additionally install a device for promoting condensation. Therefore, it is possible to provide a condenser that can condense the refrigerant with high efficiency and has high productivity.

  In the condenser described above, the wall portion includes a plurality of wall members, and the plurality of wall members are arranged along the direction in which the refrigerant flows. For this reason, the refrigerant collides with the wall member a plurality of times along the direction in which the refrigerant flows. As a result, the refrigerant can be more easily condensed, and the condensing action of the refrigerant can be further promoted.

  In the above-described condenser, the plurality of wall members include a first wall member and a second wall member, and the first wall member is disposed on the upstream side of the refrigerant passage from the second wall member. The second wall member is configured to reduce the cross-sectional area of the refrigerant passage as compared with the first wall member. For this reason, the second wall member can further reduce the bundle of refrigerant flows as compared with the first wall member. Therefore, the second wall member can make the refrigerant more easily condensed.

  In the above condenser, the maximum cross-sectional area of the refrigerant passage between the first wall member and the second wall member is smaller than the cross-sectional area of the refrigerant passage upstream of the first wall member. It has become. For this reason, it is possible to cause the refrigerant to collide with the second wall member in a state in which the bundle of refrigerant flows condensed by the first wall member is contracted. As a result, the refrigerant can be further easily condensed.

  Preferably, in the above-described condenser, the wall portion is disposed on the downstream side from the upstream end portion along the refrigerant passage with respect to a position of three quarters of the total length of the refrigerant passage. When the fin is deteriorated, the refrigerant is not sufficiently condensed on the downstream side of the position of three-quarters of the entire length of the refrigerant passage, and the residual degree of the refrigerant in the gas phase becomes higher than the case where the fin is not deteriorated. In the present invention, by providing the wall portion on the downstream side of the three-fourths of the total length of the refrigerant passage, the refrigerant having a high residual gas phase collides with the wall portion to easily condense the refrigerant. Therefore, the condensation effect can be maintained.

  In the condenser described above, the wall portion is formed by drawing so as to reduce the cross-sectional area of the refrigerant passage. For this reason, a wall part can be manufactured easily. Thereby, productivity can be improved.

  In the above-described condenser, the heat exchanging unit has a first pipe group composed of a plurality of pipes extending in parallel to divide and flow the refrigerant, and one refrigerant flow divided by the first pipe group. A header pipe for collecting the flow and a second pipe group including a plurality of pipes extending in parallel to divide and flow the refrigerant combined into one flow by the header pipe, and the header pipe has a wall portion Is formed.

  Since each of the first tube group and the second tube group has a plurality of tubes extending in parallel, the refrigerant can be used in the first tube group and the second tube as compared with the case of one tube. The area in contact with the tube group can be increased. Therefore, the refrigerant condensing action can be promoted. Further, by providing a wall portion on the header pipe, manufacturing becomes easy, so that production efficiency can be improved.

  Preferably, in the above-described condenser, the refrigerant passage includes at least two straight portions and a folded portion for joining the two straight portions so that the directions of the refrigerant flowing through the two straight portions are opposite to each other. And a wall portion is formed at the folded portion.

  Since the flow of the refrigerant is folded in the reverse direction at the folding portion, the resistance of the refrigerant increases. Therefore, the refrigerant pressure can be increased. Thereby, a refrigerant | coolant can be made into the state which is more easily condensed by providing a wall part in a folding | turning part. Moreover, since it becomes easy to form a wall part, production efficiency can be improved.

  An air conditioner according to the present invention is an air conditioner that changes the state of a refrigerant and circulates to perform heat exchange, and has an expansion valve for depressurizing the refrigerant and an evaporation for evaporating the refrigerant depressurized by the expansion valve. A compressor, a compressor for compressing the refrigerant evaporated by the evaporator, and any one of the above condensers for condensing the refrigerant compressed by the compressor.

Thereby, the air conditioner with which the condensing effect | action of the refrigerant | coolant was accelerated | stimulated can be provided. Therefore, the condensation effect can be maintained even if the air conditioner deteriorates. Since the condensing capacity does not decrease, the CO ₂ reduction effect can be increased. In addition, since the refrigerant condensing action is promoted, an increase in required power of the compressor can be suppressed. Therefore, the amount of CO ₂ emitted can be reduced. For this reason, it is not necessary to additionally install a device for promoting condensation. Therefore, it is possible to provide an air conditioner that can condense the refrigerant with high efficiency and has high productivity.

  As described above, according to the present invention, it is possible to provide a condenser capable of condensing refrigerant with high efficiency and high productivity, and an air conditioner using the same.

It is the schematic which shows the structure of the air conditioner in Embodiment 1 of this invention. It is the schematic which shows the structure of the air conditioner which can be air-conditioned in Embodiment 1 of this invention. It is the schematic which shows the structure of the condenser in Embodiment 1 of this invention. It is a schematic sectional drawing which shows the mode in the refrigerant path in the P1 part of FIG. It is a schematic sectional drawing of the structure of the condenser in which the wall part was formed by drawing, The cross-sectional position respond | corresponds to FIG. It is a schematic sectional drawing which shows the mode in the refrigerant path in the part corresponding to the P2 part of FIG. It is the schematic which shows the basic cycle at the time of air_conditionaing | cooling operation of an air conditioner. It is a schematic sectional drawing which shows the structure of the condenser in Embodiment 2 of this invention. It is a schematic sectional drawing which shows the mode in the refrigerant path in the P3 part of FIG. It is a schematic sectional drawing of the pipe | tube along XX of FIG. It is a schematic sectional drawing which shows the mode in the refrigerant path of the condenser in Embodiment 3 of this invention, Comprising: The cross-sectional position respond | corresponds to FIG. It is a schematic sectional drawing which shows the mode in the refrigerant path of the condenser in the modification 1 of Embodiment 3 of this invention, Comprising: The cross-sectional position respond | corresponds to FIG. It is a schematic sectional drawing which shows the mode in the refrigerant path of the condenser in the modification 2 of Embodiment 3 of this invention, Comprising: The cross-sectional position respond | corresponds to FIG. It is a schematic sectional drawing which shows the mode in the refrigerant path of the condenser in the modification 3 of Embodiment 3 of this invention, Comprising: The cross-sectional position respond | corresponds to FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(Embodiment 1)
1 to 4, in air conditioner 100 of the present embodiment, condenser 1 has wall portion 8 (FIG. 4) that promotes the refrigerant condensing action in the middle of the refrigerant passage of the heat exchange portion. is doing. First, an air conditioner 100 using the condenser 1 will be described.

  With reference to FIG. 1, an air conditioner 100 includes a condenser 1, an expansion valve 10, an evaporator 20, and a compressor 30. The air conditioner 100 is configured to perform heat exchange by changing the state of the refrigerant and circulating it.

  The expansion valve 10 is configured to depressurize the refrigerant, and includes, for example, an electronic expansion valve and a capillary tube. The evaporator 20 is connected to the expansion valve 10 and has a heat exchange unit for evaporating the refrigerant decompressed by the expansion valve 10. The compressor 30 is connected to the evaporator 20 and is configured to compress the refrigerant evaporated by the evaporator 20. The condenser 1 is connected to the compressor 30 and has a heat exchange unit for condensing the refrigerant compressed by the compressor 30. The condenser 1 and the expansion valve 10 are connected so that the refrigerant condensed in the condenser 1 is sent to the expansion valve 10.

Next, the structure of the condenser 1 of the air conditioner 100 of this Embodiment is demonstrated.
The condenser 1 of the present embodiment may be either a so-called serpent type or a multi-flow type, but in this embodiment, the serpen type condenser 1 will be described.

  Referring to FIG. 3, the condenser 1 mainly has a heat exchange part 2, one connection pipe part 3, and the other connection pipe part 4. The condenser 1 is configured such that the refrigerant flows from the upstream US of the condenser 1 and flows out of the downstream DS as in the refrigerant flow RF indicated by an arrow in the drawing. The condenser 1 is configured to change the state of the refrigerant from gas to liquid when the refrigerant passes through the heat exchange unit 2 from the upstream US toward the downstream DS.

  The heat exchanging unit 2 includes a refrigerant passage 5 for allowing the refrigerant to pass from the upstream end 6 toward the downstream end 7, and fins 9 disposed on the outer periphery of the pipe of the refrigerant passage 5. . Refrigerant passage 5 is constituted by a pipe which can send a refrigerant, for example. In the case of the serpen type, the refrigerant passage 5 has a shape in which a single pipe is meandered, for example. The meandering refrigerant passage 5 has at least two straight portions 5a and a folded portion 5b for joining the two straight portions 5a. The folded portion 5b joins the two straight portions 5a such that the directions of the refrigerant flowing through the two straight portions 5a are opposite to each other, for example. The fins 9 are arranged on the outer periphery of the tube of the straight portion 5a of the refrigerant passage 5, and may not be arranged on the outer periphery of the tube of the folded portion 5b of the refrigerant passage 5, but on the outer periphery of the tube of the folded portion 5b. It may be arranged.

  On the other hand, the connecting pipe portion 3 is connected to the upstream end portion 6 of the refrigerant passage 5. On the other hand, the connecting pipe portion 3 is configured to serve as a refrigerant inlet 1 </ b> A to the condenser 1. The other connecting pipe 4 is connected to the downstream end 7 of the refrigerant passage 5. The other connecting pipe portion 4 is configured to be a refrigerant outlet 1 </ b> B from the condenser 1. Each of the one connection pipe part 3 and the other connection pipe part 4 may be a pipe provided integrally and continuously with the pipe of the refrigerant passage 5, or a separate pipe connected to the refrigerant passage 5. There may be.

  In the present specification, the heat exchanging unit 2 is the condenser 1 in which the last fin 9 on the refrigerant outlet side is arranged from the place where the first fin 9 on the refrigerant inlet side is arranged along the refrigerant flow path. Means the part up to

  Referring to FIG. 3, the heat exchanging portion 2 has a wall portion 8 located at, for example, a portion P <b> 1 in the straight portion 5 a between the upstream end 6 and the downstream end 7 of the refrigerant passage 5. . As shown in FIG. 4, the wall portion 8 is configured to reduce the cross-sectional area of the refrigerant passage 5 by protruding from the inner peripheral surface of the pipe of the refrigerant passage 5 toward the inner peripheral side. The wall portion 8 is configured to promote the refrigerant condensing action by causing the refrigerant flowing in the refrigerant passage 5 from the upstream US toward the downstream DS to collide with the wall portion 8.

  The shape and arrangement of the wall portion 8 are configured in consideration of the type of coolant and the coolant. The wall portion 8 may be constituted by a member separate from the pipe constituting the refrigerant passage 5. The wall portion 8 may be configured to incline toward the traveling direction of the refrigerant. As inclination angle (theta) with respect to the advancing direction of the refrigerant | coolant of the wall part 8, the range of 90 degrees-75 degrees is preferable. When the inclination angle θ is 90 °, drawing processing described later is easy. The inclination angle θ is more preferably 75 °. When the inclination angle θ is 75 °, the shock wave increases and the refrigerant bubbles can be further subdivided. Further, the ratio between the inner diameter DA of the portion of the refrigerant passage 5 where the wall portion 8 is not provided and the inner diameter DB of the wall portion 8 is based on the relationship between the resistance of the refrigerant and the shock wave when the refrigerant collides with the wall portion 8. 100 (DA): The range of 40-60 (DB) is preferable. This ratio is more preferably 100 (DA): 50 (DB).

  Further, as shown in FIG. 3, the position where the wall portion 8 is provided (P1 portion in FIG. 3) is from the upstream end 6 along the refrigerant passage 5 to a position that is three quarters of the total length of the refrigerant passage 5. Is also preferably on the downstream DS side. When the fins 9 are deteriorated on the downstream DS side from the upstream end 6 along the refrigerant passage 5 at a position corresponding to three quarters of the total length of the refrigerant passage 5, the residual degree of the gas phase of the refrigerant increases.

  In addition, referring to FIG. 5, wall portion 8 may be configured integrally with a pipe that forms refrigerant passage 5. The wall portion 8 may be formed by drawing the pipe of the refrigerant passage 5 so as to reduce the cross-sectional area of the refrigerant passage 5. In this case, the wall part 8 can be manufactured easily. When the inclination angle θ of the wall portion 8 with respect to the traveling direction of the refrigerant is 90 °, drawing is easy.

  The refrigerant passage 5 is configured to improve the heat exchange capability between the condensed refrigerant in a high-temperature / high-pressure liquid phase and a coolant (for example, air around the fins 9 (FIG. 3)). Also good. The amount of heat released from the refrigerant passage 5 is proportional to the product of the surface area of the inner periphery of the refrigerant passage 5 and the speed of the refrigerant in the refrigerant passage 5. The speed of the refrigerant is inversely proportional to the cross-sectional area of the refrigerant passage 5. Therefore, the values of the inner diameter of the refrigerant passage 5 before and after the wall portion 8, the surface area per unit length of the inner circumference of the refrigerant passage 5, the cross-sectional area of the inner circumference of the refrigerant passage 5, and the flow velocity of the refrigerant in the refrigerant passage 5 are represented. It may be configured as shown in FIG. With reference to FIG. 4, in the refrigerant passage 5, the pipe line A <b> 1 is a part upstream of the wall part 8, and the pipe line A <b> 2 is a part in which the wall part 8 is provided.

  With reference to FIG. 4 and Table 1, the pipe line A2 is obtained by halving the inner diameter of the pipe line A1. The surface area of the pipe A2 is 1.57 with respect to 3.14 of the pipe A1. The flow rate of the refrigerant is about four times as high as that in the pipe A1 in the pipe A2. Since the heat radiation amount in the pipe is proportional to the product of the surface area per unit length of the inner circumference of the pipe and the speed of the refrigerant in the pipe, the heat radiation capacity of the pipe A2 is twice that of the pipe A1 (1 .57 ÷ 3.14 × 4).

  Note that the ratio K1 / K2 between the average heat transfer coefficient K1 when the refrigerant is completely in the liquid phase and the average heat transfer coefficient K2 when the refrigerant is mixed with gas and liquid is much larger than 1. Depending on the type and specific volume of the refrigerant, the ratio may be double digits, and the heat dissipation capability increases with that ratio.

  The cross-sectional shape of the refrigerant passage 5 is not limited to a circle, and any shape such as a rectangle or an ellipse can be applied as long as the cross-sectional shape and material are suitable for heat exchange. . Depending on the type of refrigerant and the specific volume of the refrigerant, the trumpet / conical cross-sectional shape may be better for the effect of contraction.

  In the above description, the case where the wall portion 8 is provided in the linear portion 5a of the refrigerant passage 5 as shown in P1 portion of FIG. 3 has been described. However, the folded portion (curved portion) of the refrigerant passage 5 as shown in P2 portion of FIG. Part) 5b may be provided with a wall 8. Moreover, when the wall part 8 is provided in the folding | returning part 5b of the refrigerant path 5, as shown in FIG. 6, the width | variety TW of the folding | returning part 5b of the refrigerant path 5 is the width | variety of the linear parts 5a of the refrigerant path 5 in parallel. You may be comprised so that it may become larger than SW. Thereby, arrangement | positioning of the wall part 8 to the refrigerant path 5 becomes easy.

Next, the effect of this Embodiment is demonstrated.
First, the basic cycle for condensing the refrigerant with the condenser of the air conditioner will be described. The air conditioner can perform a cooling operation and a heating operation. By changing the flow of the refrigerant with the four-way valve, if the outdoor unit is a condenser, cooling is performed, and if the indoor unit is a condenser, heating is performed.

  Referring to FIG. 7, the refrigerant becomes low-temperature / low-pressure wet steam G <b> 4 at expansion valve 10. The low-temperature / low-pressure wet steam G4 absorbs heat from the outside (heat absorption) by the evaporator 20. Subsequently, the low temperature / low pressure wet steam G4 exits the evaporator 20 and changes to a low temperature / low pressure superheated steam G1. The low temperature / low pressure superheated steam G <b> 1 changes to the high temperature / high pressure gas G <b> 2 via the compressor 30. The high-temperature / high-pressure gas G2 releases the heat amount of the sum of the refrigeration amount of the evaporator 20 and the thermal equivalent of the compression work to the outside (heat radiation) from the condenser 1, and changes to the normal temperature / high-pressure liquid G3. Thereafter, the room temperature / high pressure liquid G3 is changed to low temperature / low pressure wet steam G4 by the expansion valve 10. In this way, the basic cycle of condensing the refrigerant with the condenser of the air conditioner is executed.

  The refrigerant releases heat in the condenser 1 to the outside by the action of a coolant (for example, air corresponding to fins (FIG. 3)). At this time, if the refrigerant is replaced with another new refrigerant, a problem occurs when the capacity of the compressor 30 cannot cope with the performance of the refrigerant. A problem also arises when the coolant temperature is high and the capacity of the condenser 1 is insufficient. That is, before and after the outlet 1 </ b> B of the condenser 1, the refrigerant is in a state with a high degree of residual gas phase. In this state, when the refrigerant reaches the evaporator 20 through the expansion valve 10, there arises a problem that the cooling capacity is lowered. Further, the compressor 30 is overloaded and stopped, or problems such as damage to the bearings in the compressor 30 occur, resulting in a problem that the function of the air conditioner 100 is lost.

  Therefore, it is required that the refrigerant in a state where the gas phase residual degree is high be changed to a state where the gas phase residual degree is low.

  Referring to FIG. 4, in the condenser 1 of the present embodiment, the wall portion 8 reduces the cross-sectional area of the refrigerant passage 5 so that the refrigerant is easily condensed. When the refrigerant collides with the wall portion 8 in the state of wet saturated steam, the gas remaining in the refrigerant is compressed and the refrigerant is easily condensed. Referring to FIG. 4, the incident wave F1 of the refrigerant from the upstream US direction collides with the wall portion 8, and a part thereof is reflected as the reflected wave f1. The energy of the reflected wave f1 increases the pressure of the refrigerant in the direction of the reflected wave f1, and compresses the refrigerant. The remaining energy of the refrigerant travels in the direction of the downstream DS as the passing wave F2, and in the process of contracting the flow bundle, the gas remaining in the refrigerant is compressed and the refrigerant is easily condensed.

  The pressure change and the refrigerant condensation efficiency described above vary depending on the type of refrigerant, the coolant, and the specific volume of the refrigerant. The above phenomenon can be explained by hydrodynamics. In other words, this phenomenon can be explained as the energy change of the pressure, velocity and position of the fluid before and after the place where the cross-sectional area of the pipe is changed. The phenomenon in which the refrigerant suddenly changes from the gas / liquid mixture state to the liquid state is a transient phenomenon in which the specific gravity of the refrigerant changes significantly irregularly before and after the reduced cross-sectional area. Therefore, although the pressure and speed of the refrigerant change abruptly, the operation state of the refrigeration cycle is performed very smoothly except before and after the cross-sectional area changes.

  According to the condenser 1 of the present embodiment, the wall portion 8 located between the upstream end 6 and the downstream end 7 of the refrigerant passage 5 in the heat exchanging portion 2 has a cross-sectional area of the refrigerant passage 5. It is configured to decrease. Then, the refrigerant flowing from the upstream toward the downstream in the refrigerant passage 5 collides with the wall portion 8 to promote the refrigerant condensing action.

  When the air conditioner is used for cooling, the wall portion 8 reduces the cross-sectional area of the place where the refrigerant is present in the state of saturated steam in the refrigerant passage 5 that radiates heat from the condenser 1. For this reason, gas phase separation is performed by generating a large amount of turbulent flow before and after the wall portion 8 with respect to the flow of the refrigerant. At the same time, the gas-phase / liquid-phase mixed refrigerant collides with the wall portion 8, and a part of the energy that the refrigerant fluid has reflects in the upstream US direction. Therefore, the refrigerant pressure increases. Thereby, the compression effect is given to the refrigerant in the upstream gas phase state. As a result, the refrigerant is easily condensed.

  Moreover, the wall part 8 can disassemble | disassemble the bubble of a refrigerant | coolant finely with the shock wave which generate | occur | produces by making a refrigerant | coolant collide with the wall part 8 in a gas-liquid two-phase state. Thereby, since the surface area of the fragmented bubble-like bubble increases, it can thermally radiate efficiently. For this reason, the condensing effect | action of a refrigerant | coolant can be accelerated | stimulated.

  In the downstream DS direction, the refrigerant flow bundle is reduced, so that the refrigerant is easily condensed. Thereby, the heat transfer rate from the refrigerant to the refrigerant passage 5 is improved.

When the fin 9 is deteriorated due to corrosion and chipping of the fin 9, the heat exchange rate of the condenser 1 is lowered. For this reason, the condenser 1 becomes difficult to dissipate heat. Therefore, it is difficult for the condenser 1 to liquefy the refrigerant. Therefore, the ratio of the bubbles of the refrigerant increases. Since the air conditioner 100 is configured using the condenser 1 of the present embodiment, the condensation effect can be maintained even if the fins 9 are deteriorated. Since the condensing capacity does not decrease, the CO ₂ reduction effect can be increased. For this reason, it is not necessary to additionally install a device for promoting condensation. Therefore, there is no need for time required for the additional work, and no additional cost is required. Therefore, productivity can be improved. Therefore, it is possible to provide a condenser that can condense the refrigerant with high efficiency and has high productivity.

  According to the condenser 1 of the present embodiment, the wall portion 8 is arranged on the downstream side from the upstream end portion 6 along the refrigerant passage 5 from the position of three quarters of the total length of the refrigerant passage 5. Also good. When the fins 9 are deteriorated, the refrigerant is not sufficiently condensed on the downstream DS side from the position of three-quarters of the total length of the refrigerant passage 5, and the residual degree of the gas phase of the refrigerant is higher than that when the fins are not deteriorated. . In the condenser 1 of the present embodiment, the wall portion 8 is provided on the downstream DS side of the three-fourths of the total length of the refrigerant passage 5 so that the refrigerant having a high residual gas phase collides with the wall portion 8. Thus, the refrigerant is easily condensed, so that the condensation effect can be maintained.

  According to the condenser 1 of the present embodiment, the wall portion 8 may be formed by drawing so as to reduce the cross-sectional area of the refrigerant passage 5. For this reason, the wall part 8 can be manufactured easily. Thereby, productivity can be improved.

  Moreover, in the condenser 1 of this Embodiment, when the wall part 8 is provided in the part in which the fin 9 in the refrigerant | coolant channel | path 5 exists in an outer periphery, in a state with which the refrigerant | coolant is condensed with the fin 9, a refrigerant | coolant is walled. By making it collide with the part 8, condensation can be promoted efficiently.

  According to the condenser 1 of the present embodiment, the wall portion 8 is provided on the folded portion 5b for joining the two straight portions 5a so that the directions of the refrigerant flowing through the two straight portions 5a are opposite to each other. Is formed.

  Since the folding | returning part 5b is a part which changes the flow of a refrigerant | coolant to a reverse direction, the pressure of a refrigerant | coolant tends to become high. The refrigerant that has collided with the wall portion 8b formed in the folded portion 5b is further compressed by an increase in pressure caused by changing the flow of the refrigerant in the reverse direction, and the refrigerant can be easily condensed. In addition, since the wall portion 8 is provided in the folded portion 5b, the manufacturing becomes easy, so that the production efficiency can be improved.

  According to the air conditioner 100 of the present embodiment, the expansion valve 10, the evaporator 20, the compressor 30, and the condenser 1 of the present embodiment are provided, the refrigerant is circulated by changing its state, and heat exchange is performed. Can be performed.

Therefore, the condensing action of the refrigerant is promoted, so that an increase in required power of the compressor 30 can be suppressed. The required power of the compressor 30 is, for example, power consumption of an electric motor that drives the compressor 30 and fuel consumption of a heat engine that drives the compressor 30. Therefore, since the efficiency of the required power of the compressor 30 is improved, the amount of CO ₂ discharged can be reduced.

  Moreover, the air conditioning apparatus 100 of this Embodiment may be used as an air conditioning apparatus. When the air conditioner is used as an air conditioner, the cooling function and the heating function are realized by switching the flow of the refrigerant from the compressor between the cooling time and the heating time by the four-way valve. With reference to FIG. 2, the case where the air conditioning apparatus 100 of this Embodiment is used as an air conditioning apparatus is demonstrated. The air conditioner 100 includes a four-way valve 40 in addition to the condenser 1, the expansion valve 10, the evaporator 20, and the compressor 30. The four-way valve 40 serves to switch the refrigerant path between the cooling operation and the heating operation. In the cooling operation, the refrigerant is sent from the evaporator 20 to the compressor 30 via the four-way valve 40 as shown by the solid line in the figure. Then, the refrigerant is sent from the compressor 30 to the condenser 1 via the four-way valve 40 as shown by a solid line in the figure.

  In the heating operation, the condenser 1 acts as an evaporator that evaporates the refrigerant, and the evaporator 20 acts as a condenser that condenses the refrigerant. However, for convenience of explanation, the condenser 1 and the evaporator 20 are continued. This is explained using the terminology. In the case of the heating operation, the route for sending the refrigerant of the four-way valve 40 is switched from the route during the cooling operation, and the refrigerant is sent along the broken line route in the figure. That is, the refrigerant is sent from the compressor 30 to the evaporator 20 via the four-way valve 40 as indicated by a broken line in the figure. The refrigerant is sent from the condenser 1 to the compressor 30 via the four-way valve 40 as indicated by a broken line in the figure.

(Embodiment 2)
The second embodiment of the present invention is mainly different from the first embodiment in the configuration of the condenser. In this embodiment, a so-called multiflow type condenser will be described.

  First, the structure of the condenser of this Embodiment is demonstrated. Referring to FIG. 8, the multiflow type condenser 1 includes a heat exchanging portion 2, an inlet side portion 22 </ b> A of the first header pipe 22, one connecting pipe portion 3, and an outlet of the first header pipe 22. It mainly has a side portion 22C and the other connecting pipe portion 4. The heat exchange part 2 is connected to the one connection pipe part 3 with the inlet side part 22A of the first header pipe 22 in between, and the other connection pipe with the outlet side part 22C of the first header pipe 22 in between. Connected to the unit 4.

  The heat exchanging unit 2 includes a refrigerant passage 5 for allowing the refrigerant to pass from the upstream end 6 toward the downstream end 7 and fins 9 disposed on the outer periphery of a plurality of tubes in the refrigerant passage 5. is doing. The refrigerant passage 5 includes a plurality of tube groups 21A to 21D (linear portions 5a), a central portion 22B (folded portion 5b) of the first header pipe 22, and a second header pipe 23 (folded portion 5b). is doing.

The plurality of tube groups have, for example, four tube groups of first to fourth tube groups 21A to 21D. The first tube group 21A has a plurality of tubes 21A _{1 to} 21A ₄ arranged in parallel. The first tube group 21A is connected to the inlet side portion 22A of the first header pipe 22, so that a plurality of flows of the refrigerant flowing into the inlet side portion 22A are generated in the first tube group 21A. The flow is divided.

The second tube group 21B has a plurality of tubes 21B _{1 to} 21B ₄ arranged in parallel. The second tube group 21B is connected to the first tube group 21A with the upstream portion 23A of the second header pipe 23 interposed therebetween. As a result, the refrigerant flowing separately in the first tube group 21A is combined into one flow in the upstream portion 23A, and further divided into a plurality of flows in the second tube group 21B. The second tube group 21B is connected to the upstream portion 23A so that the refrigerant flow direction in the second tube group 21B is opposite to the refrigerant flow direction in the first tube group 21A.

The third tube group 21C has a plurality of tubes 21C _{1 to} 21C ₄ arranged in parallel. The third tube group 21C is connected to the second tube group 21B with the central portion 22B of the first header pipe 22 interposed therebetween. As a result, the refrigerant flowing separately in the second tube group 21B is combined into one flow in the central portion 22B, and further divided into a plurality of flows in the third tube group 21C. The third tube group 21C is connected to the central portion 22B so that the direction of refrigerant flow in the third tube group 21C is opposite to the direction of refrigerant flow in the second tube group 21B.

The fourth tube group 21D has a plurality of tubes 21D _{1 to} 21D ₄ arranged in parallel. The fourth tube group 21D is connected to the third tube group 21C with the downstream portion 23B of the second header pipe 23 interposed therebetween. As a result, the refrigerant flowing separately in the third tube group 21C is combined into one flow in the downstream portion 23B, and further divided into a plurality of flows in the fourth tube group 21D. The fourth pipe group 21D is connected to the downstream portion 23B so that the direction of refrigerant flow in the fourth pipe group 21D is opposite to the direction of refrigerant flow in the third pipe group 21C.

  The outlet side portion 22C of the first header pipe 22 is connected to the fourth tube group 21D, so that the refrigerant that has flowed separately in the fourth tube group 21D flows in the outlet side portion 22C. Are summarized in

  The wall portion 8 is provided in the refrigerant passage 5. As shown in part P3, for example, the wall 8 is formed in the downstream portion 23B of the header pipe 23. The wall portion 8 may be disposed on the downstream DS side from the upstream end portion 6 along the refrigerant passage 5 rather than the three-quarter position of the entire length of the refrigerant passage 5. Specifically, it may be provided in the second header pipe 23 between the third tube group 21C and the fourth tube group 21D.

Wall 8 may be formed in the first to fourth tube groups 21A to 21D, for example, as shown in P4 parts, a plurality of pipes 21D ₁ ～21D ₄ of the fourth tube bank 21D It is preferable to be formed.

With reference to FIG. 9, the wall portion 8 is disposed on the inner periphery of the second header pipe 23 of the refrigerant passage 5. The wall 8 is configured to reduce the cross-sectional area of the second header pipe 23. Referring to FIG. 10, the tube 21 </ _b > D ₂ of the fourth tube group 21 </ _b > D has a plurality of passages 24. By flowing through the plurality of passages 24 is the refrigerant, increases the contact area between the tube 21D ₂ and the refrigerant. In addition, the other pipes of the first to fourth pipe groups 21A to 21D may be configured similarly. In addition, since the structure of this embodiment other than this is the same as that of Embodiment 1 mentioned above, the same code | symbol is attached | subjected about the same structure and the description is not repeated.

  In addition, although the case where there are four tube groups has been described above, the tube group may be divided into two or more.

Next, the effect of the condenser 1 of this Embodiment is demonstrated. According to the condenser of the present embodiment, the heat exchanging unit 2 includes a third tube group 21C composed of a plurality of tubes 21C _{1 to} 21C ₄ extending in parallel to divide and flow the refrigerant, and a third tube. A second header pipe 23 for collecting the refrigerant flows divided by the group 21C into one flow, and a plurality of pipes extending in parallel for dividing and flowing the refrigerant combined into one flow by the second header pipe 23 And a _fourth tube group 21D composed of the two tubes 21D _{1 to} 21D ₄ . A wall portion 8 is formed on the second header pipe 23.

In the case of the multi-flow type, the plurality of tubes 21C _{1 to} 21C ₄ and the tubes 21D _{1 to} 21D ₄ are arranged in parallel. And the area which contacts the 4th pipe group 21D can be enlarged. Therefore, the refrigerant condensing action can be promoted. In addition, since the flow of the refrigerant is folded in the reverse direction by the second header pipe 23, the resistance of the refrigerant tends to increase. The refrigerant that has collided with the wall portion 8 formed in the second header pipe 23 is further compressed by an increase in pressure caused by turning the refrigerant flow in the opposite direction, so that the refrigerant is easily condensed. Can do. In addition, since the wall portion 8 is provided in the second header pipe 23, the manufacturing becomes easy, so that the production efficiency can be improved.

  8, when the wall portion 8 is provided in a portion where the fin 9 in the refrigerant passage 5 is on the outer periphery, the refrigerant is condensed in the fin 9 in the state where the refrigerant is condensed. Condensation can be efficiently promoted by colliding with the wall portion 8.

(Embodiment 3)
As in the third embodiment of the present invention, a plurality of wall members may be provided instead of the wall portions in the first and second embodiments. Referring to FIG. 11, in condenser 1 of the present embodiment, wall portion 8 includes a plurality of wall members 8 </ b> A as wall portion 8, and the plurality of wall members 8 </ b> A extend along the direction in which the refrigerant flows. Are lined up. The plurality of wall members 8A are formed so that the cross-sectional areas of the refrigerant passages 5 are the same. The wall member 8A may be formed separately from the pipe of the refrigerant passage 5 or may be formed integrally. In addition, since the structure of this embodiment other than this is the same as the structure of Embodiment 1 or 2 mentioned above, the same code | symbol is attached | subjected about the same structure and the description is not repeated.

  In the condenser 1 of the present embodiment, the incident wave F1 of the refrigerant from the upstream US direction collides with the wall member 8A on the upstream US side, and a part thereof is reflected as the reflected wave f1. The energy of the reflected wave f1 increases the pressure of the refrigerant in the direction of the reflected wave f1, and compresses the refrigerant. The remaining energy of the refrigerant travels in the downstream DS direction as a passing wave F2. The passing wave F2 collides with the wall member 8A on the downstream DS side as an incident wave, and a part thereof is reflected as a reflected wave f2. The energy of the reflected wave f2 causes the refrigerant pressure to increase in the direction of the reflected wave f2, and compresses the refrigerant. The remaining energy of the refrigerant becomes a passing wave F3 and travels in the direction of the downstream DS, and the gas remaining in the refrigerant is compressed in the process of contracting the flow bundle. As a result, the refrigerant is easily condensed.

  According to the present embodiment, since the plurality of wall members 8A are arranged along the direction in which the refrigerant flows, the refrigerant collides with the wall member 8A a plurality of times along the direction in which the refrigerant flows. Thereby, the condensation effect | action of a refrigerant | coolant can further be accelerated | stimulated.

  Further, the plurality of wall members are such that the downstream wall member of the refrigerant flow when the condenser 1 functions as a condenser reduces the cross-sectional area of the refrigerant passage as compared with the upstream wall member. It may be configured. Referring to FIG. 12, in the condenser 1 of Modification 1 of the present embodiment, the plurality of wall members 8 </ b> A have a first wall member 81 and a second wall member 82. The first wall member 81 is disposed on the upstream US side of the refrigerant passage 5 with respect to the second wall member 82. The second wall member 82 is configured to reduce the cross-sectional area of the refrigerant passage 5 compared to the first wall member 81. The plurality of wall members 8A may be formed separately from the pipe of the refrigerant passage 5 or may be formed integrally.

  According to the condenser 1 of the first modification of the present embodiment, the sectional area D2 of the refrigerant passage 5 of the second wall member 82 is smaller than the sectional area D1 of the refrigerant passage 5 of the first wall member 81. . For this reason, the second wall member 82 can further reduce the bundle of refrigerant flows as compared with the first wall member 81. Therefore, the second wall member 82 can make the refrigerant more easily condensed. The gas phase of the refrigerant is subdivided by the first wall member 81. The second wall member 82 further subdivides the gas phase of the refrigerant whose gas phase is subdivided by the first wall member 81. As a result, the refrigerant can be further easily condensed.

  Further, the plurality of wall members continuously have a sectional area of the refrigerant passage between the first wall member and the second wall member that is continuously smaller than the sectional area of the refrigerant passage upstream of the first wall member. It may be configured as follows. Referring to FIG. 13, in the condenser 1 of Modification 2 of the present embodiment, the maximum cross-sectional area DM of the refrigerant passage 5 between the first wall member 81 and the second wall member 82 is 1 is smaller than the cross-sectional area DU of the refrigerant passage 5 on the upstream US side from the wall member 81. The plurality of wall members 8A may be formed integrally with the pipe of the refrigerant passage 5 or may be formed separately.

  According to the condenser 1 of the second modification of the present embodiment, the maximum cross-sectional area DM of the refrigerant passage 5 between the first wall member 81 and the second wall member 82 is the first wall member 81. Since the cross-sectional area DU of the refrigerant passage 5 on the upstream US side is smaller than that of the refrigerant passage 5, the refrigerant is supplied to the second wall member 82 in a state where the bundle of refrigerant flows condensed by the first wall member 81 is contracted. Can collide with. As a result, the refrigerant can be further easily condensed.

  The plurality of wall members may be configured such that the cross-sectional area of the refrigerant passage between the first wall member and the second wall member decreases from the upstream side toward the downstream side. Referring to FIG. 14, the cross-sectional area DM of the refrigerant passage 5 between the first wall member 81 and the second wall member 82 is tapered so as to decrease from the upstream US side toward the downstream DS side. Has been. A second wall member 82 projects from the tapered downstream end to the inner peripheral side. The plurality of wall members 8A may be formed integrally with the pipe of the refrigerant passage 5 or may be formed separately.

  As a result, the bundle of refrigerant flows condensed by the first wall member 81 can collide with the second wall member 82 in a state of being further contracted along the taper shape. As a result, the refrigerant can be further easily condensed.

  Further, the plurality of wall members may be arranged on the downstream side from the upstream end portion along the refrigerant passage, at a position that is three quarters of the total length of the refrigerant passage. When the fins 9 are deteriorated, the refrigerant is not sufficiently condensed on the downstream DS side from the position of three-quarters of the total length of the refrigerant passage 5, and the residual degree of the gas phase of the refrigerant is higher than when the fins 9 are not deteriorated. Become.

  When the fins 9 start to deteriorate, the residual degree of the gas phase of the refrigerant increases as described above, and therefore, the upstream wall member 8A among the plurality of wall members 8A first makes the refrigerant easy to condense. When the fins 9 are further deteriorated, the wall member 8A on the downstream side makes the refrigerant easily condensed. Thereby, when the fin 9 deteriorates, the condensation effect can be further maintained.

The above embodiments can be combined in a timely manner.
The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  The present invention can be applied particularly advantageously to a condenser in which condensation is promoted and an air conditioner using the condenser.

  DESCRIPTION OF SYMBOLS 1 Condenser, 2 Heat exchange part, 3 One connection part, 4 Other connection part, 5 Refrigerant passage, 5a Straight line part, 5b Folding part, 6 Upstream side edge part, 7 Downstream side edge part, 8 Wall part, 8A Wall member , 9 Fin, 10 Expansion valve, 20 Evaporator, 21 1st tube group, 2nd tube group 22, 30 Compressor, 31 Protrusion part, 51 Pipe line, 81 1st wall member, 82 2nd wall Member, 100 air conditioner.

Claims (6)

A condenser for condensing refrigerant,
A heat exchange section having a refrigerant passage for allowing the refrigerant to pass from upstream to downstream;
One connecting pipe connected to the upstream end of the refrigerant passage and serving as an inlet of the refrigerant to the condenser;
Connected to the downstream end of the refrigerant passage, and the other connecting pipe part serving as an outlet of the refrigerant from the condenser,
The heat exchange part is
A first tube group comprising a plurality of tubes extending in parallel to flow the refrigerant separately;
A header pipe for collecting the refrigerant flow divided by the first tube group into one flow;
A second pipe group consisting of a plurality of pipes extending in parallel to divide and flow the refrigerant combined into one flow by the header pipe;
The header pipe includes the first pipe group and the second pipe group so that the direction of the refrigerant flow in the first pipe group and the direction of the refrigerant flow in the second pipe group are reversed. Connected to the tube group,
The heat exchanging part is located between the upstream end part and the downstream end part of the refrigerant passage, and has a wall part formed in the header pipe,
The wall portion is configured to reduce a cross-sectional area of the refrigerant passage, and the refrigerant flowing in the refrigerant passage from the upstream toward the downstream collides with the wall portion. A condenser configured to promote the condensing action of. The wall portion includes a plurality of wall members,
The condenser according to claim 1, wherein the plurality of wall members are arranged along a direction in which the refrigerant flows. The plurality of wall members include a first wall member and a second wall member,
The first wall member is disposed on the upstream side of the refrigerant passage from the second wall member,
The condenser according to claim 2, wherein the second wall member is configured to reduce a cross-sectional area of the refrigerant passage more than the first wall member.   The maximum cross-sectional area of the refrigerant passage between the first wall member and the second wall member is smaller than the cross-sectional area of the refrigerant passage upstream of the first wall member. The condenser according to claim 3.   The said wall part is arrange | positioned in the downstream from the position of 3/4 of the full length of the said refrigerant path along the said refrigerant path from the said upstream edge part. Condenser. An air conditioner that changes the state of the refrigerant and circulates it to perform heat exchange,
An expansion valve for decompressing the refrigerant;
An evaporator for evaporating the refrigerant decompressed by the expansion valve;
A compressor for compressing the refrigerant evaporated by the evaporator;
An air conditioner comprising: the condenser according to any one of claims 1 to 5 for condensing the refrigerant compressed by the compressor.

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