JP2000002495A - Containing structure for heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce noises of refrigerant flowing through a heat exchanger without requiring any modification of a containing case, in particular after a compressor is stopped in a cycle employing a variable capacity compressor. SOLUTION: A refrigerant inlet 14 and a refrigerant outlet 15 for an evaporator 4 are provided at the end part of a stack where an inlet passage and an outlet passage extend from the inlet 14 and the outlet 15 along the longitudinal direction of a tube element 12. An evaporator is disposed while locating the tank part 16 on the underside, the inlet and outlet passages are covered with a damping material 31 from the vicinity of the inlet and outlet 14, 15 to the lower part of the evaporator and a heat insulating material 32 is fixed to the outside of the damping material 31. An isobutylene-isoprene rubber having a large specific gravity where the absolute value of loss coefficient is 0.05-0.2 at a vibration frequency of audible region is employed as the clamping material 31.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a storage structure for a heat exchanger used in a vehicle air conditioner or the like.

[0002]

2. Description of the Related Art Japanese Patent Application Laid-Open No. Hei 9-145290 discloses one of the heat exchangers which have been researched and developed by the present applicant.
And Japanese Unexamined Patent Application Publication No. 9-166394 are known. This is because, in a heat exchanger in which fins and tube elements are alternately stacked, each tube element has a pair of tank portions at one end in the longitudinal direction and a return passage communicating the paired tank portions. It is formed and formed by abutting adjacent tube elements so that they can communicate with each other in the tank.
A plate formed in a bowl shape is joined to the flat plate at the lamination end, and an inflow passage facing the inflow port of the refrigerant and an outflow passage facing the outflow port are formed so as to extend in the longitudinal direction of the flat plate. The inflow passage communicates with the upstream tank portion, and the outflow passage communicates with the downstream tank portion.

[0003]

However, the above-described heat exchanger is housed in an air-conditioning case with the tank portion down, and at least a variable capacity compressor, a condenser,
It has been pointed out that when a cooling cycle is configured together with an expansion valve, the inconvenience that refrigerant flow noise is generated even after the compressor is stopped.

In a cooling cycle using a variable displacement compressor, unlike a fixed displacement compressor, it is necessary to supply oil required for sliding portions of the compressor to the compressor together with the refrigerant. In order to improve the durability of the compressor, it is necessary to increase the flow rate of the refrigerant and supply a sufficient amount of oil. To achieve this, the opening pressure of the expansion valve is reduced and the flow rate of the refrigerant is increased as much as possible. Means have been taken to do so. Therefore, even when the compressor is stopped, the expansion valve does not close completely, and the refrigerant in the high-pressure line passes through the expansion valve and enters the heat exchanger from the inlet, and the refrigerant flows so as to fall from the inlet into the inflow passage. Therefore, it is thought that flowing noise is generated.

As a countermeasure to reduce such a flow noise, it is conceivable to change the arrangement of the heat exchanger such that the refrigerant falls from the inlet, but it is necessary to change the design of the air conditioning case itself. Therefore, it is not a good idea to change the arrangement because the heat exchanger is designed to be able to fully exhibit its performance with the tank part down, with large scale measures.

Accordingly, in the present invention, the flow noise of the refrigerant in the heat exchanger is reduced without improving the storage case. In particular, in the cycle using the variable capacity compressor, the flow noise after stopping the compressor is reduced. An object of the present invention is to provide a heat exchanger storage structure that is reduced.

[0007]

In order to achieve the above object, the present inventor has proposed that the frequency of a flowing sound that can be heard by the ear is about 1.25.
KHz, and found that this flow noise was particularly generated in the process of flowing from the inlet to the inflow passage. As a result of intensive research on the most effective measures to absorb the flow noise, the present invention was completed. Reached.

That is, in the heat exchanger accommodating structure according to the present invention, a large number of tube elements are stacked in a tank portion so as to be able to communicate with each other, fins are interposed between the tube elements, and an inflow port through which a refrigerant flows is provided. An outlet for discharging the refrigerant is provided at a stacking end, and an inflow passage and an outflow passage extending along the longitudinal direction of the tube element from the inflow and outflow are provided at the stacking end. Communicating with the tank part on the side,
A heat exchanger that communicates the outflow passage with the tank portion on the downstream side, and a vibration damping material that covers the passage along a longitudinal direction of the tube element from near the inflow port and the outflow port; The heat exchanger is housed in an air-conditioning case via a vibration material (claim 1).

In particular, when the tank portion is provided below the heat exchanger, and the inflow passage and the outflow passage provided at the lamination end are formed downward from the inlet and the outlet,
The damping material may be provided from the vicinity of the inlet and the outlet to the lower part of the heat exchanger (claim 2).

Here, if the damping material is provided also on the outer peripheral portion other than the passage of the heat exchanger, a more effective damping effect can be obtained. As the vibration damping material, butyl rubber is preferably used (claim 4). In particular, the specific gravity is larger than the specific gravity of butyl rubber containing no filler, and the absolute value of the loss coefficient is 0 at the vibration frequency in the audible range. .05
It is preferable to use butyl rubber having a characteristic of about 0.2 in order to reduce the flow noise of the above-mentioned predetermined frequency (claim 5).

Therefore, the refrigerant flowing from the inlet of the heat exchanger is sent to the upstream tank through the inflow passage, and the refrigerant is supplied to the lamination end which is considered to be a source of the flow noise. Since it is covered with the vibration damping material, the noise level caused by the flow noise of the refrigerant is attenuated as shown in FIGS. 7 (a) and 8 (a) to FIGS. 7 (b) and 8 (b). Can be done.

Further, in order to suppress the odor peculiar to the vibration damping material and obtain the heat insulating effect, the heat insulating material is provided outside the vibration damping material so as to cover the heat insulating material, and the heat exchanger is interposed through the vibration damping material and the heat insulating material. (Claim 6).

[0013]

Embodiments of the present invention will be described below with reference to the drawings. In FIG. 1, the vehicle air conditioner includes:
An intake device 2 is provided at the most upstream side of the air conditioning case 1, and a blower 3 is housed below the intake device 2. This air-conditioning case 1 is configured by integrally forming a blower unit 1a and a cooling unit 1b.
An evaporator 4 is accommodated in a portion constituting the cooling unit 1b, and is connected to an air conditioning case constituting a downstream heater unit (not shown).

The evaporator 4 includes a variable capacity compressor 5 that changes the discharge capacity of the refrigerant in accordance with the heat load and the like, a condenser 6 that radiates the high-temperature and high-pressure refrigerant compressed by the variable capacity compressor 5, and a condenser 6. Receiver tank 7 for gas-liquid separation of cooled refrigerant
The cooling tank 9 is connected to an expansion valve 8 for reducing the pressure of the liquid-phase refrigerant separated by the receiver tank 7 to form a cooling cycle 9 for cooling air sent from the blower 3.

Here, in the above-described cooling cycle 9, since the variable displacement compressor 5 is used as the compressor, the valve opening pressure of the expansion valve 8 is smaller than that in the case where the fixed displacement compressor is used. I have. This is different from the fixed displacement compressor in the variable displacement compressor 5 in that the oil charged in the cooling cycle 9 must be circulated together with the refrigerant and must be actively supplied. In the cooling cycle 9 using the compressor 5, the compressor 5 continues to be operated in a state where the discharge capacity is suppressed even at the time of a low heat load. Therefore, even when the refrigerant flow rate at the time of the low heat load becomes small, the oil is sufficiently supplied to the compressor. To avoid burning of the compressor.

As shown in FIGS. 2 and 3, the evaporator 4 forms a core body by alternately stacking the fins 11 and the tube elements 12 in a plurality of stages, and forms one end of the tube element 12 in the stacking direction. Refrigerant inlet 14
And a lamination type heat exchanger of, for example, a four-pass type provided with an outlet 15, and the tube element 12 is a face-to-face joint of two formed plates formed by pressing an aluminum alloy clad with a brazing material. It is configured.

The tube element 12 has a pair of tank portions 16 at one end and a folded passage portion 17 connecting the other tank portion to the other tank portion at the other end. The portion 16 is formed so as to protrude larger than the folded passage portion 17. Further, between the tank portions of each tube element 12, a tube element 12c having tube elements 12a, 12b at both ends and an enlarged tank portion 16a described later.
Except for the above, a pipe mounting recess 19 for mounting the communication pipe 18 is formed.

Tube elements 12 at both ends in the stacking direction
a, 12b, the outer forming plate is constituted by a flat plate 13 having a flat plate shape, and one of the tube elements 1
An end plate 20 is joined to 2a via a fin 11, and a bowl-shaped inlet / outlet plate 21 having an inlet 14 and an outlet 15 is joined to the other tube element 12b. In addition, the expanded tank portion 16
The tube element 12c having a is provided closer to the end plate 20 than the center, and is enlarged so that one tank portion 16a approaches the other tank portion.

As shown in FIG. 3, the evaporator 4 has a structure in which adjacent tube elements are abutted in a tank portion, and a series of the abutted tank portions makes a first direction in a laminating direction (a direction orthogonal to the ventilation direction). And the second two
The first tank group 22 including the enlarged tank portion 16a has a through-hole formed in the tank portion except for the tube element 12d located substantially at the center in the stacking direction. Is communicated through.

That is, the first tank group 22 is expanded by the tube element 12d so that the expanded tank portion 16a
Is divided into a first tank block α including the remaining tank portion and a second tank block β including the remaining tank portion. In the second tank group 23, all the tank portions are communicated without being partitioned and the third tank block γ is formed. Is composed.

The inlet / outlet plate 21 is formed with first and second overhangs 25 and 26 by press working or the like, and the inflow port 14 is provided at one end of the first overhang 25 with a flow. The outlets 15 are formed at the same side end of the second overhang portion 26, respectively. This doorway plate 2
1 and the flat plate 13 are joined to form an inflow passage 27 communicating with the inflow port 14 and an outflow passage 28 communicating with the outflow port 15 between the plates, and the inflow passage 27 is formed at one end of the enlarged tank portion 16a. Communication pipe 1 to which is connected
8 is connected via the flat plate 13, and the outflow passage 28 communicates with the second tank block β via the flat plate 13. A joint 30 for fixing the expansion valve 8 is joined to the inflow port 14 and the outflow port 15.

Therefore, the refrigerant flowing in from the inlet 14 enters the enlarged tank portion 16a through the inflow passage 28 and the communication pipe 18, and is dispersed throughout the first tank block α. Flows away from the tank portion through the turn-back passage portion 17 of the tube element (first pass). Then, it flows through the turn-back passage 17 in a U-turn (second pass) to reach the tank group on the opposite side (third tank block γ). Then, it moves in parallel with the remaining tube elements constituting the third tank block γ, and flows through the turn-back passage 17 of the remaining tube elements away from the tank portion again (third tank element).
path). Then, it flows in a U-turn along the turn-back passage (fourth pass), is guided to the tank part forming the second tank block β, and then flows out of the outlet 15 through the outlet passage 28. For this reason, the heat of the refrigerant is transmitted to the fins 11 and exchanges heat with the air passing between the fins in the process of flowing through the return passage 17 forming the first to fourth paths.

The above-described evaporator 4 is used with the tank portion down, and is housed in the air-conditioning case 1 via a vibration damping material 31 and a heat insulating material 32 described below. The damping material 31
As shown in FIGS. 4 and 5, the evaporator 4 is provided so as to cover the entrance plate 21 from the vicinity of the inflow port 14 and the outflow port 15 to the lower end portion of the evaporator 4, that is, the tank portion, and as shown in FIG. This entrance plate 21
Is provided so as not to block the ventilation section from above the entire upper surface and the opposite side surface of the evaporator 4, for example,
It is directly attached by double-sided tape or adhesive.

Here, the damping material 31 is made of butyl rubber, and its specific gravity is adjusted to the specific gravity of ordinary butyl rubber in which a filler (an inorganic filler such as silicon or manganese oxide called talc) is mixed and the filler is not mixed. (About 1.0)
The absolute value of the loss coefficient is 0.05 to 0.2 at the vibration frequency in the audible range.

For example, it is conceivable to use butyl rubber having any of the characteristics shown in FIG.
The butyl rubber indicated by A has a specific gravity of 1.9 and a hardness approximately equal to that of ordinary rubber (about 50 in Shore hardness). The absolute value of the loss coefficient increases with an increase in the audible vibration frequency. It has the characteristic of increasing, and the product name “Calmflex RP” manufactured by Inoac Corporation corresponds to this. The butyl rubber indicated by B has a specific gravity of 2.3 and has a product name of “Calmflex R”.
The butyl rubbers represented by "Y" and "C" correspond to the product name "Calmflex RC" made by the company with a specific gravity of 1.6, and have a characteristic that the loss coefficient is almost constant in the audible range.

On the other hand, as the heat insulating material 32, a known heat insulating material made of urethane foam or the like is used. The heat insulating material 32 is directly attached to the outside of the vibration damping material 31 with a double-sided tape or an adhesive. It is provided so that it is hardly exposed.

In the above configuration, if the compressor 5 stops for some reason, such as stopping the air conditioner, the valve opening pressure of the expansion valve 8 is set to a small value. The refrigerant in the high pressure line continues to flow to the low pressure line. The flow noise of the refrigerant generated at this time is mainly generated from the vicinity of the entrance / exit plate 21 because the evaporator 4 is disposed with the tank portion down and the refrigerant flows so as to fall from the inflow port 14. Is covered with the damping material 31 from the vicinity of the inflow port 14 to the tank, so that the flow noise of the refrigerant is absorbed by the damping material 31 and is less likely to be transmitted to the vehicle interior.

The damping material 31 is provided on the entrance / exit plate 21.
In addition, since it is also provided on the outer peripheral surface excluding the lower surface, the vibration during the flow of the refrigerant transmitted from the vicinity of the inlet of the evaporator 4 to the whole can be further reduced, and a further vibration damping effect can be achieved. The noise level in the cabin can be reduced.

Further, in the above configuration, the heat insulating material 32
Is provided so as to cover almost the entirety of the damping material 31, the odor of the damping material 31 itself can be contained, and the generation of an unusual odor due to the provision of the damping material 31 can be suppressed.

7 and 8, the case where the damping material 31 is not attached to the evaporator 4 at all ((a) in the figure)
) And the case where butyl rubber having the above-mentioned characteristic A is used as the damping material 31 and the damping material 31 is attached so as to cover the entrance plate 21 (shown by (b) in the figure). The result of actual measurement of the noise level is shown. FIG.
FIG. 8 shows the change in the noise level in the vehicle interior after the compressor 5 was stopped after 30 seconds from the start of the measurement. FIG. 8 shows the case where the compressor 5 is operating and the case where the compressor 5 is stopped. 10sec, 30sec,
FIG. 9 shows changes in the noise level with respect to the frequency when 60 seconds and 90 seconds have elapsed.

From these results, even when the damping material 31 is attached only to the entrance / exit plate 21, the noise level in the vehicle cabin when the compressor is driven can be reduced as compared with the evaporator without the damping material. The noise level after stopping the compressor 5 is also about 70 seconds after the compressor reaches the steady state (about 100 seconds from the start of the measurement).
It was confirmed that the noise level could be reduced in the period up to c), and in particular, the vibration sound of about 1.25 KHz which was annoying was effectively absorbed by the damping material 31.

[0032]

As described above, according to the present invention,
In the heat exchanger, an inlet and an outlet are provided at the stacking end, and at the stacking end, a passage for inflow and outflow of the refrigerant extends from the inlet and the outlet along the longitudinal direction of the tube element. Damping material is installed so as to cover the passage for inflow and outflow from the vicinity of the inflow port and outflow port, and the heat exchanger is housed in the air-conditioning case, so that the flow noise of the heat exchange medium can be reduced. Can be.

That is, the provision of the damping material can reduce the noise level as a whole irrespective of whether the cooling cycle is in operation or stopped, and is particularly easy to hear after the cooling cycle is stopped. Discomfort can be suppressed by effectively reducing the flow noise of the refrigerant. In addition, the specific gravity of about 2., in which the loss coefficient increases as the vibration frequency increases.
Butyl rubber of about 1.25K
Hz flowing noise can be effectively suppressed.

Further, if a heat insulating material is provided outside the vibration damping material and the heat exchanger is housed in the air conditioning case via the vibration damping material and the heat insulating material, the heat insulating effect as well as the vibration damping effect can be obtained. In addition, the odor peculiar to the damping material such as butyl rubber can be suppressed by the heat insulating material.

[Brief description of the drawings]

FIG. 1 is a diagram showing a part of an air conditioner to which a heat exchanger according to the present invention is attached.

FIG. 2 is a front view showing a configuration example of a heat exchanger according to the present invention.

3 (a) is a view of the heat exchanger shown in FIG. 2 as viewed from below, and FIG. 3 (b) is a view of the heat exchanger shown in FIG. 2 in which an inlet and an outlet are provided. It is the figure seen from the side.

FIG. 4 is a diagram showing a state where a vibration damping material and a heat insulating material are attached to the heat exchanger shown in FIG. 1;

5 is a view showing the vicinity of an inlet and an outlet of the heat exchanger shown in FIG. 4, (a) is a front view of a partly cutaway portion thereof, and (b) is It is a perspective view of a part.

FIG. 6 is a characteristic diagram showing a relationship between a loss coefficient and a vibration frequency of a vibration damping material used in the present invention.

FIG. 7 is an actual measurement diagram showing a temporal change of a vehicle interior noise level before and after the compressor is stopped, and FIG.
(B) shows a case where a damping material is not attached to a heat exchanger, and (b) shows a case where a damping material is attached to a side surface provided with an inlet and an outlet.

FIG. 8 is an actual measurement diagram showing a relationship between a vehicle interior noise level and a frequency during and after driving of a compressor, and FIG. 8 (a) is a case where a damping material is not attached to a heat exchanger. (B) shows the case where the damping material is attached to the side surface where the inflow port and the outflow port are provided.

[Explanation of symbols]

REFERENCE SIGNS LIST 1 air conditioning case 4 evaporator 11 fins 12, 12a, 12b, 12c, 12d tube element 13 flat plate 14 inflow port 15 outflow port 16 tank section 21 inlet / outlet plate 27 inflow passageway 28 outflow passageway 31 damping material 32 heat insulating material

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[Procedure amendment]

[Submission date] July 12, 1999 (1999.7.1)
2)

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] Full text

[Correction method] Change

[Correction contents]

[Document Name] Statement

[Title of the Invention] Storage structure of heat exchanger

[Claims]

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a storage structure for a heat exchanger used in a vehicle air conditioner or the like.

[0002]

2. Description of the Related Art Japanese Patent Application Laid-Open No. Hei 9-145290 discloses one of the heat exchangers which have been researched and developed by the present applicant.
And Japanese Unexamined Patent Application Publication No. 9-166394 are known. This is because, in a heat exchanger in which fins and tube elements are alternately stacked, each tube element has a pair of tank portions at one end in the longitudinal direction and a return passage communicating the paired tank portions. It is formed and formed by abutting adjacent tube elements so that they can communicate with each other in the tank.
A plate formed in a bowl shape is joined to the flat plate at the lamination end, and an inflow passage facing the inflow port of the refrigerant and an outflow passage facing the outflow port are formed so as to extend in the longitudinal direction of the flat plate. The inflow passage communicates with the upstream tank portion, and the outflow passage communicates with the downstream tank portion.

[0003]

However, the above-described heat exchanger is housed in an air-conditioning case with the tank portion down, and at least a variable capacity compressor, a condenser,
It has been pointed out that when a cooling cycle is configured together with an expansion valve, the inconvenience that refrigerant flow noise is generated even after the compressor is stopped.

In a cooling cycle using a variable displacement compressor, unlike a fixed displacement compressor, it is necessary to supply oil required for sliding portions of the compressor to the compressor together with the refrigerant. In order to improve the durability of the compressor, it is necessary to increase the flow rate of the refrigerant and supply a sufficient amount of oil. To achieve this, the opening pressure of the expansion valve is reduced and the flow rate of the refrigerant is increased as much as possible. Means have been taken to do so. Therefore, even when the compressor is stopped, the expansion valve does not close completely, and the refrigerant in the high-pressure line passes through the expansion valve and enters the heat exchanger from the inlet, and the refrigerant flows so as to fall from the inlet into the inflow passage. Therefore, it is thought that flowing noise is generated.

As a countermeasure to reduce such a flow noise, it is conceivable to change the arrangement of the heat exchanger such that the refrigerant falls from the inlet, but it is necessary to change the design of the air conditioning case itself. Therefore, it is not a good idea to change the arrangement because the heat exchanger is designed to be able to fully exhibit its performance with the tank part down, with large scale measures.

Accordingly, in the present invention, the flow noise of the refrigerant in the heat exchanger is reduced without improving the storage case. In particular, in the cycle using the variable capacity compressor, the flow noise after stopping the compressor is reduced. An object of the present invention is to provide a heat exchanger storage structure that is reduced.

[0007]

In order to achieve the above object, the present inventor has proposed that the frequency of a flowing sound that can be heard by the ear is about 1.25.
KHz, and found that this flow noise was particularly generated in the process of flowing from the inlet to the inflow passage. As a result of intensive research on the most effective measures to absorb the flow noise, the present invention was completed. Reached.

That is, in the heat exchanger accommodating structure according to the present invention, a large number of tube elements are stacked in a tank portion so as to be able to communicate with each other, fins are interposed between the tube elements, and an inflow port through which a refrigerant flows is provided. An outlet for discharging the refrigerant is provided at a stacking end, and an inflow passage and an outflow passage extending along the longitudinal direction of the tube element from the inflow and outflow are provided at the stacking end. Communicating with the tank part on the side,
A heat exchanger that communicates the outflow passage with the tank portion on the downstream side, wherein the tank portion is provided at a lower portion of the heat exchanger.
And an inflow passage and an outflow passage provided at the lamination end.
Is formed downward from the inlet and the outlet.
From at least the vicinity of the inflow port and the outflow port.
Covering the passage along the longitudinal direction of the tube element,
A vibration damping material is provided over the lower part of the heat exchanger, and
A heat insulating material is provided so as to cover the outside of the damping material,
And the heat exchanger is housed in the air-conditioning case via heat insulating material.
It is characterized by having been delivered (claim 1).

Therefore, the refrigerant flowing from the inlet of the heat exchanger is sent to the upstream tank through the inflow passage, but the passage provided at the lamination end which is considered to be a source of the flow noise is provided. Since it is covered with the vibration damping material, the noise level caused by the flow noise of the refrigerant is attenuated as shown in FIGS. 7 (a) and 8 (a) to FIGS. 7 (b) and 8 (b). Insulation can also be applied to the outside of the damping material
Air-conditioning cabinet via a vibration-damping material and heat-insulating material.
The odor characteristic of the damping material is suppressed and cut off.
A thermal effect can be obtained.

[0010]

Embodiments of the present invention will be described below with reference to the drawings. In FIG. 1, the vehicle air conditioner includes:
An intake device 2 is provided at the most upstream side of the air conditioning case 1, and a blower 3 is housed below the intake device 2. This air-conditioning case 1 is configured by integrally forming a blower unit 1a and a cooling unit 1b.
An evaporator 4 is accommodated in a portion constituting the cooling unit 1b, and is connected to an air conditioning case constituting a downstream heater unit (not shown).

The evaporator 4 includes a variable capacity compressor 5 for changing the discharge capacity of the refrigerant in accordance with the heat load and the like, a condenser 6 for radiating the high-temperature and high-pressure refrigerant compressed by the variable capacity compressor 5, and a condenser 6. Receiver tank 7 for gas-liquid separation of cooled refrigerant
The cooling tank 9 is connected to an expansion valve 8 for reducing the pressure of the liquid-phase refrigerant separated by the receiver tank 7 to form a cooling cycle 9 for cooling air sent from the blower 3.

Here, in the above-described cooling cycle 9, since the variable displacement compressor 5 is used as the compressor, the valve opening pressure of the expansion valve 8 is smaller than that in the case where the fixed displacement compressor is used. I have. This is different from the fixed displacement compressor in the variable displacement compressor 5 in that the oil charged in the cooling cycle 9 must be circulated together with the refrigerant and must be actively supplied. In the cooling cycle 9 using the compressor 5, the compressor 5 continues to be operated in a state where the discharge capacity is suppressed even at the time of a low heat load. Therefore, even when the refrigerant flow rate at the time of the low heat load becomes small, the oil is sufficiently supplied to the compressor. To avoid burning of the compressor.

As shown in FIGS. 2 and 3, the evaporator 4 forms a core body by alternately stacking the fins 11 and the tube elements 12 in a plurality of stages, and forms one end of the tube element 12 in the stacking direction. Refrigerant inlet 14
And a lamination type heat exchanger of, for example, a four-pass type provided with an outlet 15, and the tube element 12 is a face-to-face joint of two formed plates formed by pressing an aluminum alloy clad with a brazing material. It is configured.

The tube element 12 has a pair of tank portions 16 at one end and a folded passage portion 17 connecting the other tank portion to the other tank portion at the other end. The portion 16 is formed so as to protrude larger than the folded passage portion 17. Further, between the tank portions of each tube element 12, a tube element 12c having tube elements 12a, 12b at both ends and an enlarged tank portion 16a described later.
Except for the above, a pipe mounting recess 19 for mounting the communication pipe 18 is formed.

Tube elements 12 at both ends in the stacking direction
a, 12b, the outer forming plate is constituted by a flat plate 13 having a flat plate shape, and one of the tube elements 1
An end plate 20 is joined to 2a via a fin 11, and a bowl-shaped inlet / outlet plate 21 having an inlet 14 and an outlet 15 is joined to the other tube element 12b. In addition, the expanded tank portion 16
The tube element 12c having a is provided closer to the end plate 20 than the center, and is enlarged so that one tank portion 16a approaches the other tank portion.

As shown in FIG. 3, the evaporator 4 has a structure in which adjacent tube elements are abutted by a tank portion, and a series of abutted tank portions make the first in the stacking direction (a direction orthogonal to the ventilation direction). And the second two
The first tank group 22 including the enlarged tank portion 16a has a through-hole formed in the tank portion except for the tube element 12d located substantially at the center in the stacking direction. Is communicated through.

That is, the first tank group 22 is expanded by the tube element 12d so that the expanded tank portion 16a
Is divided into a first tank block α including the remaining tank portion and a second tank block β including the remaining tank portion. In the second tank group 23, all the tank portions are communicated without being partitioned and the third tank block γ is formed. Is composed.

The inlet / outlet plate 21 is formed with first and second overhangs 25 and 26 by press working or the like, and the inflow port 14 is provided at one end of the first overhang 25 with a flow. The outlets 15 are formed at the same side end of the second overhang portion 26, respectively. This doorway plate 2
1 and the flat plate 13 are joined to form an inflow passage 27 communicating with the inflow port 14 and an outflow passage 28 communicating with the outflow port 15 between the plates, and the inflow passage 27 is formed at one end of the enlarged tank portion 16a. Communication pipe 1 to which is connected
8 is connected via the flat plate 13, and the outflow passage 28 communicates with the second tank block β via the flat plate 13. A joint 30 for fixing the expansion valve 8 is joined to the inflow port 14 and the outflow port 15.

Therefore, the refrigerant flowing in from the inflow port 14 enters the enlarged tank portion 16a through the inflow passage 28 and the communication pipe 18, and is dispersed throughout the first tank block α. Flows away from the tank portion through the turn-back passage portion 17 of the tube element (first pass). Then, it flows through the turn-back passage 17 in a U-turn (second pass) to reach the tank group on the opposite side (third tank block γ). Then, it moves in parallel with the remaining tube elements constituting the third tank block γ, and flows through the turn-back passage 17 of the remaining tube elements away from the tank portion again (third tank element).
path). Then, it flows in a U-turn along the turn-back passage (fourth pass), is guided to the tank part forming the second tank block β, and then flows out of the outlet 15 through the outlet passage 28. For this reason, the heat of the refrigerant is transmitted to the fins 11 and exchanges heat with the air passing between the fins in the process of flowing through the return passage 17 forming the first to fourth paths.

The above-described evaporator 4 is used with the tank portion down, and is housed in the air-conditioning case 1 via a vibration damping material 31 and a heat insulating material 32 described below. The damping material 31
As shown in FIGS. 4 and 5, the evaporator 4 is provided so as to cover the entrance plate 21 from the vicinity of the inflow port 14 and the outflow port 15 to the lower end portion of the evaporator 4, that is, the tank portion, and as shown in FIG. This entrance plate 21
Is provided so as not to block the ventilation section from above the entire upper surface and the opposite side surface of the evaporator 4, for example,
It is directly attached by double-sided tape or adhesive.

Here, the damping material 31 is made of butyl rubber, and its specific gravity is adjusted to the specific gravity of ordinary butyl rubber in which a filler (an inorganic filler such as silicon or manganese oxide called talc) is mixed and the filler is not mixed. (About 1.0)
Larger than the absolute value of the loss factor in the oscillation frequency of the audible range are used is made 0.05 to 0.2 0.

For example, it is conceivable to use butyl rubber having any of the characteristics shown in FIG.
The butyl rubber indicated by A has a specific gravity of 1.9 and a hardness approximately equal to that of ordinary rubber (about 50 in Shore hardness). The absolute value of the loss coefficient increases with an increase in the audible vibration frequency. It has the characteristic of increasing, and the product name “Calmflex RP” manufactured by Inoac Corporation corresponds to this. The butyl rubber indicated by B has a specific gravity of 2.3 and has a product name of “Calmflex R”.
The butyl rubbers represented by "Y" and "C" correspond to the product name "Calmflex RC" made by the company with a specific gravity of 1.6, and have a characteristic that the loss coefficient is almost constant in the audible range.

On the other hand, as the heat insulating material 32, a known heat insulating material made of urethane foam or the like is used. The heat insulating material 32 is directly attached to the outside of the vibration damping material 31 with a double-sided tape or an adhesive. It is provided so that it is hardly exposed.

In the above configuration, if the compressor 5 stops for some reason such as stopping the air conditioner, the valve opening pressure of the expansion valve 8 is set to a small value. The refrigerant in the high pressure line continues to flow to the low pressure line. The flow noise of the refrigerant generated at this time is mainly generated from the vicinity of the entrance / exit plate 21 because the evaporator 4 is disposed with the tank part down and the refrigerant flows so as to fall from the inflow port 14. Is covered with the damping material 31 from the vicinity of the inflow port 14 to the tank, so that the flow noise of the refrigerant is absorbed by the damping material 31 and is less likely to be transmitted to the vehicle interior.

The damping material 31 is provided on the entrance / exit plate 21.
In addition, since it is also provided on the outer peripheral surface excluding the lower surface, the vibration during the flow of the refrigerant transmitted from the vicinity of the inlet of the evaporator 4 to the whole can be further reduced, and a further vibration damping effect can be achieved. The noise level in the cabin can be reduced.

Further, in the above configuration, the heat insulating material 32
Is provided so as to cover almost the entirety of the damping material 31, the odor of the damping material 31 itself can be contained, and the generation of an unusual odor due to the provision of the damping material 31 can be suppressed.

7 and 8, the case where the damping material 31 is not attached to the evaporator 4 at all ((a) in the figure)
) And the case where butyl rubber having the above-mentioned characteristic A is used as the damping material 31 and the damping material 31 is attached so as to cover the entrance plate 21 (shown by (b) in the figure). The result of actual measurement of the noise level is shown. FIG.
FIG. 8 shows the change in the noise level in the vehicle interior after the compressor 5 was stopped after 30 seconds from the start of the measurement. FIG. 8 shows the case where the compressor 5 is operating and the case where the compressor 5 is stopped. 10sec, 30sec,
FIG. 9 shows changes in the noise level with respect to the frequency when 60 seconds and 90 seconds have elapsed.

From this result, even when the damping material 31 is attached only to the entrance / exit plate 21, the noise level in the vehicle cabin when the compressor is driven can be reduced as compared with the evaporator without the damping material. The noise level after stopping the compressor 5 is also about 70 seconds after the compressor reaches the steady state (about 100 seconds from the start of the measurement).
It was confirmed that the noise level could be reduced in the period up to c), and in particular, the vibration sound of about 1.25 KHz which was annoying was effectively absorbed by the damping material 31.

[0029]

As described above, according to the present invention,
In the heat exchanger, an inlet and an outlet are provided at the stacking end, and at the stacking end, a passage for inflow and outflow of the refrigerant extends from the inlet and the outlet along the longitudinal direction of the tube element. Damping material is installed so as to cover the passage for inflow and outflow from the vicinity of the inflow port and outflow port, and the heat exchanger is housed in the air-conditioning case, so that the flow noise of the heat exchange medium can be reduced. Can be.

In other words, the provision of the damping material can reduce the noise level as a whole regardless of the operation of the cooling cycle and whether or not it is stopped. Discomfort can be suppressed by effectively reducing the flow noise of the refrigerant.

Further, a heat insulating material is provided outside the vibration damping material, and the heat exchanger is housed in the air conditioning case via the vibration damping material and the heat insulating material .
As a result, the heat insulating effect can be obtained together with the vibration damping effect, and the odor peculiar to the vibration damping material such as butyl rubber can be suppressed by the heat insulating material.

[Brief description of the drawings]

FIG. 1 is a diagram showing a part of an air conditioner to which a heat exchanger according to the present invention is attached.

FIG. 2 is a front view showing a configuration example of a heat exchanger according to the present invention.

3 (a) is a view of the heat exchanger shown in FIG. 2 as viewed from below, and FIG. 3 (b) is a view of the heat exchanger shown in FIG. 2 in which an inlet and an outlet are provided. It is the figure seen from the side.

FIG. 4 is a diagram showing a state where a vibration damping material and a heat insulating material are attached to the heat exchanger shown in FIG. 1;

5 is a view showing the vicinity of an inlet and an outlet of the heat exchanger shown in FIG. 4, (a) is a front view of a partly cutaway portion thereof, and (b) is It is a perspective view of a part.

FIG. 6 is a characteristic diagram showing a relationship between a loss coefficient and a vibration frequency of a vibration damping material used in the present invention.

FIG. 7 is an actual measurement diagram showing a temporal change of a vehicle interior noise level before and after the compressor is stopped, and FIG.
(B) shows a case where a damping material is not attached to a heat exchanger, and (b) shows a case where a damping material is attached to a side surface provided with an inlet and an outlet.

FIG. 8 is an actual measurement diagram showing a relationship between a vehicle interior noise level and a frequency during and after driving of a compressor, and FIG. 8 (a) is a case where a damping material is not attached to a heat exchanger. (B) shows the case where the damping material is attached to the side surface where the inflow port and the outflow port are provided.

[Description of Signs] 1 Air-conditioning case 4 Evaporator 11 Fin 12, 12a, 12b, 12c, 12d Tube element 13 Flat plate 14 Inlet 15 Outlet 16 Tank part 21 Inlet / outlet plate 27 Inflow passageway 28 Outflow passageway 31 Damping material 32 Thermal insulation Lumber

Claims (6)

[Claims] 1. A large number of tube elements are stacked in a tank portion so as to be able to communicate with each other, and a fin is interposed between the tube elements. An inlet for flowing in a refrigerant and an outlet for discharging the refrigerant are stacked. And an inflow passage and an outflow passage extending along the longitudinal direction of the tube element from the inflow port and the outflow port at the lamination end, and communicating the inflow passage with the tank section on the upstream side, In the heat exchanger communicating with the tank portion on the downstream side, a damping material that covers the passage along the longitudinal direction of the tube element from near the inflow port and the outflow port is provided. Characterized in that the heat exchanger is housed in an air-conditioning case via the heat exchanger. 2. The damping member is provided at a lower portion of a heat exchanger, and an inflow passage and an outflow passage provided at the lamination end are formed downward from the inflow port and the outflow port. The storage structure for a heat exchanger according to claim 1, wherein: is provided from near the inflow port and the outflow port to a lower portion of the heat exchanger. 3. The heat exchanger storage structure according to claim 1, wherein said damping material is also provided on an outer peripheral portion of said heat exchanger other than said passage. 4. The heat exchanger storage structure according to claim 1, wherein said damping material is butyl rubber. 5. The butyl rubber has a characteristic that the specific gravity is larger than that of butyl rubber containing no filler, and the absolute value of a loss coefficient is 0.05 to 0.2 at an audible vibration frequency. The storage structure for a heat exchanger according to claim 4, wherein: 6. The air conditioner according to claim 1, wherein a heat insulating material is provided outside the damping material so as to cover the heat insulating material, and the heat exchanger is housed in the air conditioning case via the damping material and the heat insulating material. 2
Or the storage structure of the heat exchanger of 3.