DE102007002720A1 - Heat exchanger and cooling circuit device with this - Google Patents

Abstract

A heat exchanger includes a plurality of fluid channels (21) through which a heat exchange fluid passes with a liquid phase fluid, a container (18b) disposed above inlet portions (21a) of the fluid channels for distributing a flow of the heat exchange fluid to the fluid channels and a retainer (75, 77, 80) disposed above the inlet portions in the container for temporarily storing therein the liquid phase fluid flowing into the container. The retaining member (75, 77, 80) is constructed so that the liquid phase fluid passing from the retaining member falls to the inlet part. Accordingly, the heat exchange fluid from the container can be evenly distributed in the fluid channels. For example, the heat exchanger may be used as an evaporator (18) for a refrigeration cycle device having an ejector (14).

Description

FIELD OF THE INVENTION

The The present invention relates to a heat exchanger having a plurality of fluid channels, the suitably, for example, as an evaporator for a refrigeration cycle device used with an ejector pump. In particular, the The present invention provides a liquid fluid retaining portion provided in a container of the heat exchanger.

BACKGROUND THE INVENTION

It is an ejector-type refrigerant cycle device known which contains an ejector, which as a refrigerant decompression device and refrigerant circulation means serves. The ejector refrigerant cycle device is for example for a vehicle air conditioning or a vehicle cooling system for Cool and freezing of cargoes on a vehicle or the like useful. The cooling circuit is also for a fixed cooling system, such as an air conditioner, a refrigerator or a freezer. This type of ejector refrigerant cycle device is disclosed, for example, in JP-B2-3322263 (corresponding to U.S. Patents Nos. 6,477,857 and 6,574,987).

The JP-A-2005-308384 (corresponding to US 2005/0268644 A1) proposes a Ejector refrigerant cycle device before, which arranged one on an outlet side of an ejector first evaporator, wherein an outlet side of the first evaporator is connected to a suction side of a compressor, one of an upstream one Part of the ejector branched off the refrigerant side channel, and a downstream in the refrigerant side channel arranged second evaporator, wherein an outlet side of the second evaporator with a refrigerant suction port of the ejector is connected contains.

Further is in the ejector refrigerant cycle device JP-A-2005-308384 a container, in the through the refrigerant side channel reaching refrigerant flows, arranged on the upper side of the second evaporator. Of the container is designed to handle the refrigerant on several refrigerant channels (pipes) of the second evaporator to distribute. This can be a simple one Construction for distributing the refrigerant to the several Reach pipes of the second evaporator. In particular, the diverted flows refrigerant in the refrigerant side channel in the container of the second evaporator. That is, only part of the refrigerant circuit circulating refrigerant flows in the container the second evaporator, resulting in a small flow rate in the container flowing refrigerant results.

Therefore reaches the refrigerant directly one of the rooms in the container near an inlet for the refrigerant, but does not easily reach another room directly from the refrigerant inlet, causing an insufficient uniformity in the distribution of the refrigerant on the several tubes is effected.

When As a result, it is difficult to have an endothermic (cooling) effect of the multiple tubes to make even which disadvantageously results in insufficient uniformity in the temperature distribution of the second evaporator flowing Air is effected.

Also in another heat exchanger with a container for distributing a heat exchange fluid (for example, hot Water or the like) on several inner channels creates the same problem, if a flow rate the heat exchange fluid is small.

SUMMARY THE INVENTION

In In view of the above problems, it is an object of the present invention Invention, a heat exchanger to provide a fluid evenly distributed to a plurality of fluid channels can, even if a flow rate the fluid is small. It is another task of the present Invention, a refrigeration cycle device with an evaporator to provide a refrigerant evenly in several Distribute refrigerant channels can.

According to one Aspect of the present invention includes a heat exchanger several tubes, the fluid channels define, through which a heat exchange fluid including at least one liquid phase fluid flows, one over an inlet part of the plurality of fluid channels arranged container for distributing a stream of the heat exchange fluid on the fluid channels, and an over the inlet part in the container arranged retaining element to the temporary Save the in the container flowing Liquid-phase fluid in this. In the heat exchanger is the retaining element so constructed that over the retaining element trespassing Liquid phase fluid falls to the inlet part. Accordingly, the in the container flowing Liquid phase refrigerant in the retaining element saved, and that over the retaining element trespassing Liquid phase fluid flows in the fluid channels. Therefore, it may simply be a direct flow of liquid phase fluid into a part the fluid channels restrict, making it the liquid-phase refrigerant evenly in all fluid channels can initiate, even if a flow rate of the in the heat exchanger entering fluid is small.

For example, the retaining element has a mountain section projecting from a horizontal surface. In this case, the mountain portion and an inner wall surface of the container extending in a vertical direction define a recessed retaining portion in which the liquid phase fluid is temporarily stored, and the mountain portion of the retaining member includes a vertex portion having a hole through which the liquid phase fluid stored in the retaining portion is flooded falls to the inlet part. Here, an arc angle (θ) of the mountain portion may be in a range of 30 ° to 170 °, and the hole may be provided overlying the inlet portion in the mountain portion.

alternative contains the retaining element one in the tank a tilting plate inclined in a horizontal direction. In this case The inclination plate has a lower part which, together with an inner wall surface of the container a retention section forms, in which the liquid phase fluid temporarily is stored; and an upper part with a hole through which that in the retention section stored liquid phase fluid because of transgressing falls to the inlet part. Alternative contains the retaining element a plate member having a recessed part for defining a Retaining portion, in which the liquid phase fluid temporarily is stored. In this case, the plate member of a Inner wall of the container separated to form the hole through which the in the retention section stored liquid phase fluid through the trespassing falls to the inlet part.

Of the heat exchangers can be used as an evaporator in a refrigeration cycle device become. For example, contains the refrigeration cycle device a compressor for compressing a refrigerant, a radiator for Cool of the refrigerant from the compressor, an ejector pump that decompresses a nozzle part of the refrigerant from the cooler and a refrigerant suction port, from which the refrigerant through one of a jet opening of the nozzle part ejected high-velocity refrigerant stream is sucked in, and the one evaporator, in the that into the refrigerant suction port too Sucking refrigerant evaporates becomes. In this case contains one evaporator several pipes that define refrigerant channels through which the refrigerant including flows at least one liquid-phase refrigerant, and one over an inlet part of the plurality of refrigerant channels arranged container for distributing a flow of the refrigerant on the refrigerant channels. Further is a retaining element in the container above the Einlasssteil for temporary storage in the container flowing Liquid phase refrigerant arranged therein, and the retaining element is intended to form a hole through which the out of the Retaining element exceeded Liquid phase refrigerant falls to the inlet part. Accordingly, the refrigerant evenly in the Refrigerant channels in the be distributed an evaporator.

To the Example, the cooling circuit device with another evaporator for evaporating the refrigerant be provided. In this case, the further evaporator one Refrigerant inlet, with a refrigerant outlet the ejector is coupled, and a refrigerant outlet, with a refrigerant suction the compressor is coupled, and the one evaporator and the other evaporator can be combined with the ejector. The ejector pump can with at least be combined with the one evaporator. In this Case, the ejector in the container of the one evaporator be arranged or can with the one evaporator outside of the one evaporator combined.

Further can the other components, such as a decompression element, a Gas / liquid separator and the other evaporator, with the exception of the ejector pump be combined with an evaporator.

SUMMARY THE TERMS

Above and other objects, features and advantages of the present invention will become apparent from the following detailed description of exemplary embodiments better understood together with the accompanying drawings. Show:

1 a cooling circuit diagram of an ejector-type refrigeration cycle device for a vehicle according to a first embodiment of the invention;

2 an exploded perspective view of a schematic structure of an integrated unit in the first embodiment;

3 a schematic cross-sectional view of an evaporator tank in the integrated unit of 2 ;

4 a longitudinal sectional view of an evaporator tank in the integrated units of 2 ;

5 an enlarged sectional view taken along the line VV of 4 ;

6 a perspective view of a terminal block and an intermediate plate in the integrated unit of 2 ;

7 a perspective view of an ejector mounting plate in the integrated unit of 2 ;

8th a perspective view of an upper and a lower partition plate in the integrated unit of 2 ;

9 a perspective view of a spacer in the integrated unit of 2 ;

10 a perspective view of a refrigerant retaining plate in the integrated unit of 2 ;

11 a schematic cross-sectional view of a lower space in an evaporator tank of the integrated unit of 2 ;

12 a schematic perspective view of an entire refrigerant flow path in the integrated unit of 2 ;

13 a perspective view of a structure of an integrated unit in an example 1 of the first embodiment;

14 a schematic cross-sectional view of an evaporator tank of the integrated unit of 13 ;

15 a side view of the evaporator tank of 14 ;

16 a perspective view of a schematic structure of an integrated unit in an example 2;

17 a schematic cross-sectional view of an evaporator tank of the integrated unit of 16 ;

18 a side view of the evaporator tank of 17 ;

19 a perspective view of a schematic structure of an integrated unit in an example 3;

20 a schematic longitudinal sectional view of an evaporator tank of the integrated unit of 19 ;

21 a cross-sectional view of the evaporator tank of the integrated unit of 19 ;

22 a perspective view of a schematic structure of an integrated unit in an example 4;

23 a schematic longitudinal sectional view of an evaporator tank of the integrated unit of 22 ;

24 a side view of the evaporator tank of 23 ;

25 5 is a perspective view of a schematic structure of an integrated unit in Example 5, together with a sectional view of an external cartridge;

26 a perspective view of a schematic structure of an integrated unit in an example 6, together with a sectional view of an external cassette;

27 a perspective view of a refrigerant retaining plate according to a second embodiment of the present invention;

28 a schematic cross-sectional view of a lower space of an evaporator tank of an integrated unit according to the second embodiment;

29 a perspective view of a refrigerant retaining plate according to a third embodiment of the present invention;

30 a cross-sectional view of a lower space of an evaporator tank of an integrated unit according to the third embodiment;

31 FIG. 12 is a cross-sectional view of a lower space of an evaporator tank of an integrated unit according to a fourth embodiment of the present invention; FIG.

32 a longitudinal sectional view of an evaporator tank of an integrated unit according to a fifth embodiment of the present invention;

33 a longitudinal sectional view of an evaporator tank of an integrated unit according to a sixth embodiment of the present invention;

34 1 is a refrigerant circuit diagram of an ejector refrigerant cycle device for a vehicle according to a seventh embodiment of the present invention;

35 1 is a refrigerant circuit diagram of an ejector refrigerant cycle device for a vehicle according to an eighth embodiment of the present invention;

36 1 is a refrigerant circuit diagram of an ejector refrigerant cycle device for a vehicle according to a ninth embodiment of the present invention;

37 FIG. 10 is a refrigerant circuit diagram of an ejector-type refrigerant cycle device for a vehicle according to a tenth embodiment of the present invention; FIG.

38 1 is a refrigerant circuit diagram of an ejector refrigerant cycle device for a vehicle according to an eleventh embodiment of the present invention; and

39 12 is a refrigerant circuit diagram of an ejector refrigerant cycle device for a vehicle according to a twelfth embodiment of the present invention.

DETAILED DESCRIPTION THE PREFERRED EMBODIMENTS

(First embodiment)

A first embodiment of the present invention will now be described with reference to FIG 1 to 12 described. In the embodiment, a heat exchanger of the present invention is typically used for a refrigeration cycle of an ejector refrigerant cycle device. A unit for the refrigeration cycle is a heat exchange unit such as an evaporator unit or, for example, an evaporator unit equipped with an ejector.

These Unity is over a pipeline with other components of the cooling circuit, including one Condenser, a compressor and the like, connected to a A refrigeration cycle apparatus to form with an ejector. The unit of the embodiment is for an application on an indoor unit (Evaporator) for cooling Air used. The unit may also be referred to in other embodiments as a Outdoor unit used become.

In an in 1 illustrated ejector refrigerant cycle device 10 becomes a compressor 11 for sucking and compressing a refrigerant by a motor for a vehicle drive (not shown) via an electromagnetic clutch 11a , a belt or the like driven.

As a compressor 11 For example, either a variable displacement compressor that can adjust a refrigerant discharge capacity by changing the discharge capacity, or a fixed displacement compressor that supplies a refrigerant discharge capacity by changing a duty ratio of the compressor by coupling and decoupling an electromagnetic clutch 11a can be used. If an electric compressor as a compressor 11 is used, the refrigerant discharge capacity can be adjusted or regulated by adjusting the rotational speed of an electric motor.

A cooler 12 is on a refrigerant discharge side of the compressor 11 arranged. The cooler 12 exchanges heat between that of the compressor 11 discharged high-pressure refrigerant and a blown by a cooling fan (not shown) outside air (air outside a space of a vehicle), thereby to cool the high-pressure refrigerant.

As a refrigerant for the ejector refrigerant cycle device 10 For example, in the embodiment, a refrigerant whose high pressure does not exceed a critical pressure, for example, a flon-based refrigerant or an HC-based refrigerant, so as to form a subcritical vapor compression cycle, is used. Therefore, the cooler is used 12 as a condenser for cooling and condensing the refrigerant.

A liquid receiver 12a is on a refrigerant outlet side of the radiator 12 intended. The liquid receiver 12a has an elongated container-like shape, as is known in the art, and forms a vapor / liquid separator for separating the refrigerant into a vapor and a liquid phase to store therein excess liquid refrigerant of the refrigeration cycle. At a refrigerant outlet of the liquid receiver 12a the liquid refrigerant is discharged from the lower part of the inside in the container-like shape. In the embodiment, the liquid collecting vessel 12a integral with the radiator 12 educated.

The cooler 12 may have a known construction, which is a first heat exchanger for condensation, which is positioned on the refrigerant upstream side, the Flüssigkeitsauftanggefäß 12a for introducing the refrigerant from the first heat exchanger for condensation and for separating the refrigerant in the vapor and liquid phase, and a second heat exchanger for subcooling the saturated liquid refrigerant from the liquid collecting vessel 12a contains.

A thermal expansion valve 13 is on an outlet side of the liquid receiver 12a arranged. The thermal expansion valve 13 is a decompression unit for decompressing the liquid refrigerant from the liquid receiver 12a and includes a in a refrigerant suction passage of the compressor 11 is arrange tes temperature measuring part 13a ,

The thermal expansion valve 13 detects a degree of superheat of the refrigerant on the compressor suction side based on the temperature and the pressure of the suction side refrigerant of the compressor 11 and adjusts an opening degree of the valve (a refrigerant flow rate) so that the superheat degree of the refrigerant on the compressor suction side becomes a predetermined value that is preset, as is known in the art.

An ejector pump 14 is on a refrigerant outlet side of the thermal expansion valve 13 arranged. The ejector pump 14 is a decompression device for decompressing the refrigerant, and a refrigerant circulation device (kinetic vacuum pump) for circulating the refrigerant by a suction effect (entrainment effect) of the high-velocity expelled refrigerant flow.

The ejector pump 14 contains a nozzle part 14a for further decompressing and expanding the refrigerant (the medium-pressure refrigerant) by restricting a path area through the expansion valve 13 reached refrigerant to a low level, and a refrigerant suction port 14b in the same space as a refrigerant jet port of the nozzle part 14a is arranged, for sucking the vapor-phase refrigerant from a later-described second evaporator 18 ,

A mixer 14c is on the refrigerant downstream side of the nozzle part 14a and the refrigerant suction port 14b for mixing a high-speed refrigerant flow from the nozzle part 14a and a suctioned refrigerant from the refrigerant suction port 14b intended. A diffuser serving as a pressure increasing section 14b is on the refrigerant downstream side of the nozzle part 14c intended. The diffuser 14d is formed in such a manner that a path surface of the refrigerant downstream of the mixer 14c generally gets bigger. The diffuser 14d serves to increase the refrigerant pressure by braking the refrigerant flow, that is, converting the speed energy of the refrigerant into pressure energy.

A first evaporator 15 is with an outlet 14e (the tip of the diffuser 14d ) of the ejector 14 connected. The outlet side of the first evaporator 15 is with a suction side of the compressor 11 connected.

On the other hand, a secondary refrigerant channel 16 provided from an inlet side of the ejector 14 branches. That is, the refrigerant side channel 16 branches at a position between the refrigerant outlet of the thermal expansion valve 13 and the refrigerant inlet of the nozzle part 14a the ejector pump 14 from. The downstream side of the refrigerant side channel 16 is with the refrigerant suction port 14b the ejector pump 14 connected. A point Z indicates a branch point of the refrigerant subchannel 16 at.

In the refrigerant side channel 16 is a throttle 17 arranged. On the refrigerant downstream side of the throttle 17 is a second evaporator 18 arranged. The throttle 17 serves as a decompression unit having a function of setting a refrigerant flow rate in the second evaporator 18 performs. In particular, the throttle 17 be constructed of a fixed throttle, such as a capillary tube or an opening.

In the first embodiment, two evaporators 15 and 18 integrated into an integrated construction with a later described arrangement. These two evaporators 15 and 18 are housed in a housing, not shown, and the air (air to be cooled) is through a common electric fan 19 is blown through an air passage formed in the housing in the direction of an arrow "A", so that the blown air through the two evaporators 15 and 18 is cooled.

The through the two evaporators 15 and 18 cooled air is supplied to a common space to be cooled (not shown). This causes the two evaporators 15 and 18 cool the common room to be cooled. Of these two evaporators 15 and 18 is the first evaporator 15 with a main flow path on the downstream side of the ejector 14 is connected, disposed on the upstream side of the air flow A, while with the refrigerant suction port 14b the ejector pump 14 connected second evaporator 18 is arranged on the downstream side of the air flow A.

When the ejector refrigerant cycle device 10 of the embodiment is used as a refrigeration cycle for a vehicle air conditioner, the space in the vehicle compartment is a space to be cooled. When the ejector refrigerant cycle device 10 is used in the embodiment of a refrigeration cycle of a freezer vehicle, the space in the freezer compartment and refrigerator of the freezer vehicle is the space to be cooled.

In the embodiment, the ejector 14 , the first and second evaporators 15 and 18 and the throttle 17 in an integrated unit 20 combined. It will now be referred on 2 to 11 specific examples of the integrated unit 20 described in detail.

2 FIG. 13 is an exploded perspective view of the schematic overall construction of the first and second evaporators. FIG 15 and 18 , 3 FIG. 12 is a cross-sectional view of upper tanks for the first and second evaporators. FIG 15 and 18 . 4 is a schematic longitudinal sectional view of the upper container of the second evaporator 18 , and 5 is an enlarged sectional view taken along the line VV of 4 ,

First, reference will now be made 2 an example of the integrated design with the two evaporators 15 and 18 explained. In the embodiment of 2 can the two evaporators 15 and 18 be integrally formed in a completely individual evaporator construction. So forms the first evaporator 15 an upstream portion of the one evaporator structure in the direction of the air flow A, while the second evaporator 18 a downstream portion forming an evaporator structure in the direction of the air flow A.

The first evaporator 15 and the second evaporator 18 have the same basic structure and contain heat exchange cores 15a and 18a and on both the upper and lower sides of the heat exchange cores 15a respectively. 18a positioned containers 15b . 15c . 18b and 18c ,

The heat exchange cores 15a and 18a each contain several tubes 21 in a tube longitudinal direction (eg vertically in 2 ). The pipe 21 corresponds to a heat source fluid passage in which a heat source fluid for performing heat exchange with a heat exchange medium flows. One or more channels for passing a heat exchange medium, in particular air to be cooled in this embodiment, are between these tubes 21 educated.

Between these pipes 21 are ribs 22 so arranged that the pipes 21 with the ribs 22 can be connected. Each of the heat exchange cores 15a and 18a is from a layer structure of the pipes 21 and the ribs 22 built up. These pipes 21 and ribs 22 are in a transverse direction of the heat exchange cores 15a and 18a layered alternately. In other embodiments or examples, another suitable construction without the ribs may also be used 22 in the cores 15a and 18a be used.

In 2 are just a few of the ribs 22 shown, but in fact are the ribs 22 over the entire areas of the heat exchange cores 15a and 18a arranged, and the layer structure with the pipes 21 and the ribs 22 is over the entire areas of the heat exchange cores 15a and 18a arranged. The blown air through the electric fan 19 can get through free spaces in the layer structure.

The pipe 21 forms the refrigerant passage through which a refrigerant flows, and is made of a flat tube having a flat cross-sectional shape in the air flow direction A. The rib 22 is a corrugated fin made by bending a thin plate in a wave-like shape, and having a flat outer surface of the tube 21 connected to expand a heat exchange area of the air side.

The pipes 21 of the heat exchange core 15a and the pipes 21 of the heat exchange core 18a independently form the respective refrigerant channels. The containers 15b and 15c on the top and bottom of the first evaporator 15 and the containers 18b and 18c on the upper and lower sides of the second evaporator 18 independently form the respective refrigerant channel spaces.

As in 5 represented, have the containers 15b and 15c on the top and bottom of the first evaporator 15 Pipe fitting holes 15d (not shown), in which upper and lower ends of the tube 21 of the heat exchange core 15a Inserted and fastened so that the upper and lower ends of the tube 21 with the interior of the containers 15b respectively. 15c keep in touch.

Analog have the containers 18b and 18c on the upper and lower sides of the second evaporator 18 Pipe fitting holes 18d (not shown), in which upper and lower ends of the tube 21 of the heat exchange core 18a Inserted and fastened so that the upper and lower ends of the tube 21 both with the interior of the container 18b respectively. 18c keep in touch.

Thus, the containers arranged on the upper and lower sides serve 15b . 15c . 18b and 18c distributing the refrigerant flows to the respective tubes 21 the heat exchange cores 15a and 18a and collecting the refrigerant flows from these tubes 21 ,

In 5 are just the pipe fitting holes on the side of the upper tank 15b and 18b from the pipe fitting holes 15d and 18d the container 15b . 15c . 18b and 18c shown on the top and bottom. Because the pipe fitting holes on the side of the lower tank 15c and 18c the same construction as the pipe fitting holes on the side of the upper tanks 15b and 18b have, on the other hand is the representation the pipe fitting holes on the side of the lower tanks 15c and 18c omitted.

Because the two upper containers 15b and 18b next to each other, the two upper containers 15b and 18b be molded integrally. The same can be done for the two lower containers 15c and 18c be valid. It is obvious that the two upper containers 15b and 18b can be independently formed as an independent component and that same for the two lower tanks 15c and 18c can apply.

In the embodiment, as in 2 and 5 shown, the two upper containers 15b and 18b by division into a lower half element 60 (first element), an upper half element 61 (second element) and a lid 62 shaped.

In particular, the lower half element has 60 a substantially W-shaped section obtained by integrally molding respective lower halves of the upper containers 15b and 18b receives. The upper half element 61 has a substantially M-shaped section, which is formed by integrally molding respective upper halves of the two upper containers 15b and 18b receives.

In the central region of the substantially W-shaped section of the lower half-element 60 is a flat surface part 60a educated. In the central region of the substantially M-shaped section of the upper half-element 61 is a flat surface part 61a educated. Combine the lower half element 60 with the upper half element 61 brings the flat surface part 60a in contact with the flat surface part 61a to form two cylindrical shapes. The one ends of the two cylindrical shapes (right end of 2 ) in the longitudinal direction are with the lid 62 closed, bringing the two upper containers 15b and 18b be formed.

One for the evaporator components, such as the pipe 21 , the rib 22 , the container 15b . 15c . 18b and 18c For example, suitable material may be aluminum, which is a metal having excellent heat conductivity and excellent soldering property. By molding each component of the aluminum material, the overall constructions of the first and second evaporators 15 and 18 be assembled integrally with soldering.

In this embodiment, a capillary tube 17a or the like, which is the throttle 17 forms, and one in 2 illustrated terminal block 23 with soldering integral with the first and second evaporators 15 and 18 assembled.

On the other hand, the ejector has 14 the nozzle part 14a in which a fine channel is formed with high accuracy. A soldering of the ejector pump 14 can be a hot deformation of the nozzle part 14a at the high temperature during brazing (at a brazing temperature of aluminum of about 600 ° C) cause. This unfavorably results in the fact that the shape and the dimension or the like of the channel of the nozzle part 14a can not be kept according to a predetermined construction.

Therefore, the ejector 14 assembled with the evaporator side after the first and the second evaporator 15 and 18 , the connection block 23 and the capillary tube 17a and the like are soldered integrally.

It now becomes more accurate an assembly design with the ejector 14 , the capillary tube 17a , the terminal block 23 and the like explained. The capillary tube 17a and the terminal block 23 are made of the same aluminum material as the evaporator components.

Referring to 5 is the capillary tube 17a in a valley-like part 61b (Depression part between the containers 15b . 18b ), on the flat surface part 61a of the upper half element 61 the upper container 15b and 18b is formed, arranged in sandwich construction.

The connection block 23 is one with one side (the left side in 2 ) each of the upper containers 15b and 18b in the tank longitudinal direction of the first and the second evaporator 15 and 18 soldered and fastened element. The connection block 23 contains a refrigerant inlet 25 the in 1 illustrated integrated unit 20 , a refrigerant outlet 26 and an ejector inlet part 63 for mounting the ejector pump 14 on the evaporator side.

As in 3 and 6 shown, the refrigerant inlet branches 25 in a middle of the terminal block 23 in the thickness direction in a main channel 25a as one to the inlet of the ejector 14 directed first channel serves, and a secondary channel 16 acting as an inlet to the capillary tube 17a directed second channel is used. This part of the side channel 16 corresponds to an inlet part of the in 1 shown secondary channels 16 , Thus, a branch point Z of 1 within the terminal block 23 intended.

The refrigerant outlet 26 consists of a simple through hole (round hole or the like), which is the terminal block 23 penetrates in the thickness direction, as in 2 and 6 shown.

The connection block 23 is with the side of the upper container 15b and 18b over an intermediate plate 64 soldered and fastened. The intermediate plate 24 serves to make the main channel 25a and the secondary channel 16 as described above, by being integral with the terminal block 23 is attached, and fixing the ejector 14 in the longitudinal direction.

In the formed of the aluminum material intermediate plate 64 are a main channel side opening 64a in conjunction with the main channel 25a of the terminal block 23 , a side channel opening 24b in conjunction with the secondary channel 16 of the terminal block 23 and a refrigerant outlet side opening 64c in conjunction with the refrigerant outlet 26 of the terminal block 23 educated.

A cylindrical part 64d is at a peripheral part of the main-channel-side opening 64a designed to fit in the upper container 18b to be used. An annular flange 64e in the inner diameter direction of the cylindrical part 64d protrudes, is at the top of the cylindrical part 64d educated.

A first nose 64f (Claw section) coming from the intermediate plate 64 to the evaporator side is with the upper containers 15b and 18b caulked and attached to them so that the intermediate plate 64 can be provisionally fixed to the evaporator side. Furthermore, a second nose 64g (Claw section) coming from the intermediate plate 64 to the connection block 23 protrudes, with the terminal block 23 caulked and attached to it so that the terminal block 23 can be provisionally fixed to the evaporator side.

The side channel side opening 64b the intermediate plate 64 is at the upstream end (the left end in FIG 2 ) of the capillary tube 17a soldered and tightly connected.

With such an arrangement of the terminal block 23 and the intermediate plate 64 is the refrigerant outlet 26 of the terminal block 23 via the refrigerant outlet side opening 64c the intermediate plate 64 with a left room 31 of the upper container 15b in connection, and the main channel 25a of the terminal block 23 is above the main channel side opening 64a the intermediate plate 64 with a left room 27 of the upper container 18b in connection. Further, the terminal block 23 and the intermediate plate 64 with the front sides of the upper container 15b and 18b soldered, with the secondary channel 16 of the terminal block 63 with the upstream end 17c of the capillary tube 17a over the side channel opening 64b the intermediate plate 64 communicates.

An ejector mounting plate 65 is an element that fixes the diffuser 14d the ejector pump 14 serves, the interior of the upper container 18b in the left room 27 and a right-space 28 is disconnected, as in 2 to 4 shown. The left room 27 of the upper container 18b works as a sump for collecting through multiple pipes 21 in the second evaporator 18 streamed refrigerant.

The ejector mounting plate 65 is in a substantially central portion in the longitudinal direction of the interior of the upper container 18b of the second evaporator 18 arranged and with the inner wall surface of the upper container 18b soldered.

As in 7 is shown, the Ejektorpumpenbefestigungsplatte 65 made of aluminum material and contains a flat plate part 65a that the upper container 18b in the transverse direction of 7 separates, a cylindrical part 65b that from the flat plate part 65a in the longitudinal direction of the upper container 18b protrudes and a nose 65c from the top of the flat plate part 65a sticks up.

Inside the cylindrical part 65b a through hole is formed, which is the ejector mounting plate 65 penetrates laterally. The nose 65c penetrates a slot-like hole 66 at the top of the upper container 18b , and she is with the upper container 18b caulked and attached to it, as in 4 shown. This may be the ejector mounting plate 65 provisionally on the upper container 18b fix.

Back to 4 is the downstream end (the right end) 17d of the capillary tube 17a in the layering direction of the tubes 21 (across in 4 ) in the upper container 18b used. In particular, the downstream end 18d of the capillary tube 17a in a through hole 62a of the lid 62 of the upper container 18b used to be within the right space 28 to open. A sealing connection is between the outer peripheral surface of the capillary tube 17a and the through hole 62a of the lid 62 trained with soldering.

An up / down partition plate 67 is in a substantially central area in the vertical direction of the right space 28 of the upper container 18b arranged. The top / bottom separator plate 67 serves the separation of the right space 28 in two rooms in the up / down direction, ie in an upper room 69 and a lower room 70 , which serves as a distribution container for distributing the refrigerant to the plurality of tubes 21 of the second evaporator 18 serves.

The top / bottom separator plate 67 is made of an aluminum material and with the inner wall surface of the upper container 18b soldered. The partition plate 67 has a plate shape extending in the longitudinal direction of the upper container 18b extends, as in 8th shown.

In particular, the top / bottom separator plate contains 67 a flat plate surface 67a extending in the longitudinal direction of the upper container 18b extends, and a first and a second bent part 67b and 67c at right angles in directions against each other at two ends of the flat plate surface 67a bent in the longitudinal direction.

This first curved part 67b is from one end of the flat plate surface 67a closer to the downstream end 17d of the capillary tube 17a is (on the right side of 4 ), bent upwards while the second curved part 67c from the other end of the flat plate surface 67a bent down.

As in 5 shown is the flat plate surface 67a so inclined that they are from the side of the first evaporator 15 to the side of the second evaporator 18 is lowered. At the foot of the first bent part 67b is integrally a rib 67d formed in a triangular shape to the flat plate surface 67a protrudes. The rib 67d increases the rigidity of the first bent part 67b , whereby a bending angle of the first bent part 67b held at right angles.

As in 4 represented, penetrates a nose 67e coming from the top (the upper end) of the first bent part 67b towers up, the slot-like hole 68 at the top of the upper container 18b and is so with the upper container 18b caulked and attached to it. Therefore, the top / bottom separator plate 67 provisionally on the upper container 18b be attached.

By forming the first bent part 67b in the top / bottom partition plate 67 is the lower room 70 at the downstream end 17d of the capillary tube 17a (on the right side of 4 ) extended further upwards than at the first bent part 67b , That is, in the room on the side of the downstream end 17d of the capillary tube 17a in the right room 28 is the upper room 69 not trained, and the lower room 70 is over the entire vertical area of the right space 28 educated.

As in 8th is shown at one end of the flat plate surface 67a the top / bottom separator plate 67 on the side of the second bent part 67c (on the left in 8th ) a recess 67f formed to the side of the lower room 70 is deepened. The depression 67f contains a cylindrical recess part 67g and a conical depression part 67h ,

The cylindrical recess part 67g has a shape that extends in the longitudinal direction in the flat plate surface 67a at one end of the flat plate surface 67a on the side of the second bent part 67c (on the left in 8th ). The conical depression part 67h is successively in connection with the cylindrical recess part 67g closer to the side of the first bent part 67b (on the right in 8th ) as the cylindrical recess part 67g educated. The conical depression part 67h has such a shape that the side of the cylindrical recess part 67g the depression part 67h is deep and that the deepening part 67h the flatter the further it is from the cylindrical recess part 67g away.

The ejector pump 14 is made of a metallic material such as copper or aluminum. Alternatively, the ejector 14 made of synthetic resin (non-metallic material). After a step of integrally soldering and assembling the first and second evaporators 15 and 18 or the like (a step of soldering) becomes the ejector 14 through holes including the ejector inlet 63 of the terminal block 23 and the main channel side opening 64a the intermediate plate 64 in the upper container 18b used.

The summit 14e the ejector pump 14 in the in 3 shown longitudinal direction corresponds to the outlet part 14e the in 1 shown ejector 14 , This ejector tip 14e gets into the cylindrical part 65b the ejector mounting plate 65 used to by means of an O-ring 29a sealed and fastened.

As in 4 shown is the ejector tip 14e arranged at such a position that they the flat plate surface 67a the top / bottom separator plate 67 crosses in the vertical direction. The depression 67f is in the top / bottom separator plate 67 formed, and the outer peripheral surface of the diffuser 14d the ejector pump 14 is in and on the cylindrical recess part 67g the depression 67f arranged. This leaves the entire top 14e the ejector pump in the upper room 69 of the right room 28 in the upper container 18b be open. The refrigerant suction port 15b the ejector pump 14 stands with the left room 27 of the upper container 18b of the second evaporator 18 in connection.

As in 3 is shown at a substantially center in the tank longitudinal direction of the interior of the upper tank 15b of the first Ver steam system troubles 15 a left / right partition plate 30 arranged the the interior of the upper container 15b in the tank longitudinal direction in two rooms, ie the left room 31 and a right-space 32 separates.

The left room 31 serves as a collection container for collecting the through the multiple tubes 21 of the evaporator 15 arrived refrigerant. The right room 32 serves as a distribution tank for distributing the refrigerant to the multiple pipes 21 of the first evaporator 15 ,

As in 4 and 5 is shown on the flat plate surface 61a of the upper half element 61 the upper container 15b and 18b a deepening part 61c at one in the upper room 69 of the right room 28 in the upper container 18b formed positioned part.

Several depression parts 61c are in the layering direction of the tubes 21 (across in 4 ) arranged. Several connection holes 71 are formed by spaces that are from these depression parts 61c and the flat plate surface 60a of the lower half element 60 the upper container 15b and 18b are included.

The upper room 69 of the right room 28 in the upper container 18b and the right room 32 of the upper container 15b of the first evaporator 15 stand together over the multiple communication holes 71 in connection.

The several depression parts 61c may be formed in such a form that they are connected in a body, whereby the communication holes 71 across the entire area in the upper room 69 in the transverse direction (in the layering direction of the tubes 21 ) are formed.

The left end of the ejector pump 14 (left end of 3 ) in the longitudinal direction corresponds to the inlet part of the nozzle part 14a from 1 , This left end is in the inner peripheral surface of the cylindrical part 64d the intermediate plate 64 using an O-ring 29b fitted and tightly fastened.

In the embodiment, the ejector is 14 attached in the longitudinal direction as follows. First, after inserting the ejector 14 from the ejector inlet part 63 of the terminal block 23 in the upper container 18b the spacer 72 into the ejector inlet part 63 inserted, and then grip external threads on the outer peripheral surface of a columnar plug 73 with internal threads on the inner peripheral surface of the Ejektorpumpeneinlassteils 63 each other. In the embodiment, the spacers 72 and the stopper 73 each made of aluminum material.

As in 9 shown, contains the spacer 72 an annular part 72a and one of a part of the annular part 72a protruding part projecting in an axial direction 72b , So pushes when the stopper 73 with the ejector inlet part 63 is engaged, the projection part 72b of the spacer 72 the left end of the ejector pump 14 in the direction of insertion of the ejector 14 ,

On the other hand, at the left end of the ejector 14 an annular part 74 formed, whose diameter is larger than the ejector itself. Therefore, when the projection part 72b of the spacer 72 against the left end of the ejector 14 in the insertion direction of the ejector 14 is pressed, the annular part 74 the ejector pump 14 against the flange 64e the intermediate plate 64 pressed. This can be the ejector pump 14 in the longitudinal direction of the ejector 14 fix.

If the projection part 72b is formed so that it is from the total circumference of the annular part 72a of the spacer 72 so as to project the spacer 72 in a simple cylindrical shape, would make the main channel 25a of the terminal block 23 through the spacer 72 getting closed.

In contrast, since in the embodiment, the projection part 72b of the spacer 72 is designed so that it is only part of the annular part 72a of the spacer 72 protrudes, the ejector 14 be fixed in the longitudinal direction, without the main channel 25a of the terminal block 23 to close.

The outer peripheral surface of the cylindrical plug 23 becomes in the inner peripheral surface of the Ejektorpumpeneinlassteils 63 of the terminal block 23 using the O-ring 29c fitted and tightly attached.

As in 4 and 5 is a refrigerant retention plate 75 in the lower room 70 of the right room 28 in the upper container 18b arranged. The refrigerant retention plate 75 is an element that allows the even distribution of the refrigerant to the multiple tubes 21 of the second evaporator 18 serves, and it corresponds to a retaining element of the invention.

The refrigerant retention plate 75 of the embodiment is made of aluminum material and has a plate-like shape with a mountain-like cut, in the layering direction of the tubes 21 (across in 4 ) runs. The mountainous section protrudes from a horizontal area in the Käl temittelrückhalteplatte 75 in front.

Referring to 10 are several holes 75a at the upper part of the refrigerant retention plate 75 with the mountainous section in the layering direction of the tubes 21 educated. Between these holes 75a is a connecting part 75b formed with a mountainous cut. The connecting part 75b can the rigidity of the refrigerant retention plate 75 ensure even if the holes 75a in the refrigerant retention plate 75 are formed.

As in 10 pictured, has the hole 75a a shape that is completely in the layering direction of the tubes 21 extends. As reflected in the layering direction of the tubes 21 extending edge of the hole 75a has a wave-like shape, the edge has several vertices 75c that are deformed outwards. In contrast, has another edge of the hole 75a extending in a direction perpendicular to the laminating direction of the tubes 21 extends, a linear shape, as in 11 shown.

In the embodiment, the wave-like shape is at the edge of the hole 75a formed by distorting and deforming the linear shape. Alternatively, the wave-like shape at the edge of the hole 75a be formed in a gently curved shape.

As in 5 represented, is an end 75e on the side of a floor 75d with a mountainous section of the refrigerant retention plate 75 at the upper end face of the pipe 21 placed and with the running in the vertical direction inner wall surface 60b of the lower half element 60 of the upper container 18b soldered. This creates a valley-like retention section 76 between the ground 75d the refrigerant retention plate 75 and the inner wall surface of the upper container 18b ,

In the embodiment, as in FIG 11 shown, a distance P between the wave-like vertices 75c of the hole 75a at the same distance between the pipes 21 set, and therefore is the vertex 75c the inlet part 21a of the pipe 21 superimposed.

Referring to 3 . 4 and 12 Now, in the above construction, the refrigerant flow paths of the entire integrated unit will be described in more detail 20 described. 12 FIG. 12 is a schematic perspective view of the entire refrigerant flow paths in the integrated unit. FIG 20 ,

The refrigerant inlet 25 of the terminal block 23 is in the main channel 25a and the side channel 16 branched. The refrigerant in the main channel 25a passes through the main channel side opening 64a in the intermediate plate 64 and then through the ejector 14 (the nozzle part 14a → the mixer 14c → the diffuser 14d ) decompressed. The decompressed low-pressure refrigerant flows into the right-hand room 32 of the upper container 15b of the first evaporator 15 over the upper room 69 of the right room 28 in the upper container 18b and over several communication holes 71 in the direction of the arrow "a".

The refrigerant in the right room 32 moves into the on the right side of the heat exchange core 15a positioned pipes 21 in the direction of the arrow "b" down to the right part of the lower container 15c to stream. In the lower container 15c If no partition plate is provided, and therefore, the refrigerant moves in the direction of the arrow "c" from the right side of the lower tank 15c to his left side.

The refrigerant on the left side of the lower tank 15c moves into the on the left side of the heat exchange core 15a positioned pipes 21 in the direction of the arrow "d" up to the left room 31 of the upper container 15b to stream. The refrigerant continues to flow in the direction of the arrow "e" to the refrigerant outlet 26 of the terminal block 23 ,

In contrast, the refrigerant is in the secondary channel 16 of the terminal block 23 first through the capillary tube 17a decompresses, and then the decompressed low-pressure refrigerant (liquid / vapor two-phase refrigerant) flows in the direction of the arrow "f" in the lower space 70 of the right room 28 of the upper container 18b of the second evaporator 18 ,

That in the lower room 70 flowing refrigerant moves to the right side of the heat exchange core 18a positioned pipes 21 in the direction of the arrow "g" to enter the right part of the lower container 18c to stream. In the lower container 18c If there is no right / left partition plate, and therefore, the refrigerant moves in the direction of an arrow "h" from the right side of the lower tank 18c to his left side.

The refrigerant on the left side of the lower tank 18c moves in the direction of the arrow "i" in the left side of the heat exchange core 18a positioned pipes 21 up to the left room 27 of the upper container 18c to stream. Because the refrigerant suction port 14b the ejector pump 14 with the left room 27 communicates, the refrigerant is in the left room 27 from the refrigerant suction port 14b into the ejector pump 14 sucked.

The integrated unit 20 has the structure of the refrigerant channel described above. Only the one refrigerant inlet 25 must be on the terminal block 23 be provided, and only the one refrigerant outlet 26 must be on the terminal block 23 in the integrated unit 20 be provided.

An operation of the first embodiment will now be described. When the compressor 11 driven by a vehicle engine, flows through the compressor 11 compressed and discharged from him high temperature and high pressure refrigerant into the cooler 12 where the high-temperature refrigerant is cooled and condensed by the outside air. That from the radiator 12 flowing high pressure refrigerant flows into the liquid receiver 12a in which the refrigerant is separated into a liquid and a vapor phase. The liquid refrigerant is removed from the liquid receiver 12a derived and passes through the expansion valve 13 ,

The expansion valve 13 Sets the opening degree of the valve (the refrigerant flow rate) so that the superheat degree of the refrigerant at the outlet of the first evaporator 15 (ie, the refrigerant sucked by the compressor) becomes a predetermined value, and the high-pressure refrigerant is decompressed. That through the expansion valve 13 reached refrigerant (medium-pressure refrigerant) flows into one in the terminal block 23 the integrated unit 20 provided refrigerant inlet 25 ,

At this time, the refrigerant flow is in the main channel 25a of the terminal block 23 to the nozzle part 14a the ejector pump 14 directed refrigerant flow and that of the refrigerant side channel 16 of the terminal block 23 to the capillary tube 17a divided refrigerant flow divided.

The refrigerant flow into the ejector 14 is through the nozzle part 14a decompressed and stretched. Thus, the pressure energy of the refrigerant at the nozzle part becomes 14a converted into the pressure energy, and the refrigerant is from the jet opening of the nozzle part 14a ejected at high speed. At this time, the pressure drop of the refrigerant sucks from the refrigerant suction port 14b that through the second evaporator 18 in the refrigerant side channel 16 reached refrigerant (vapor-phase refrigerant).

That from the nozzle part 14a discharged refrigerant and into the refrigerant suction port 14b sucked refrigerants are through the mixer 14c downstream of the nozzle part 14a combined to get into the diffuser 14d to stream. In the diffuser 14d For example, the speed energy (expansion energy) of the refrigerant is converted into pressure energy by increasing the path area, resulting in increased pressure of the refrigerant.

That from the diffuser 14d the ejector pump 14 flowing refrigerant flows through the through the arrows "a" to "e" in 12 indicated refrigerant flow paths in the first evaporator 15 , During this time absorbed in the heat exchange core 15a of the first evaporator 15 the low-temperature and low-pressure refrigerant heat from the air blown in the direction of an arrow "A" so as to vaporize.The vaporized vapor-phase refrigerant is discharged from the one refrigerant outlet 26 in the compressor 11 sucked and compressed again.

The refrigerant flow into the secondary refrigerant channel 16 is through the capillary tube 17a decompressed to become a low pressure refrigerant (liquid / vapor two phase refrigerant). The low-pressure refrigerant flows through the through the arrows "f" to "i" of 12 indicated refrigerant flow paths in the second evaporator 18 , During this time, the low-temperature and low-pressure refrigerant absorbs in the heat exchange core 18a of the second evaporator 18 Heat out through the first evaporator 15 arrived blown air to evaporate. The vaporized vapor-phase refrigerant is discharged from the refrigerant suction port 14b into the ejector pump 14 sucked.

As mentioned above, according to the embodiment, the refrigerant on the downstream side of the diffuser 14d the ejector pump 14 the first evaporator 15 be fed, and the refrigerant on the side of the secondary channel 16 can the second evaporator 18 via a capillary tube (throttle) 17a be supplied, so that the first and the second evaporator 15 and 18 show cooling effects at the same time. Thus, that by both the first and the second evaporator 15 and 18 cooled air is blown into a room to be cooled, whereby the space to be cooled is cooled.

Here, the refrigerant evaporation pressure of the first evaporator is 15 the pressure of the refrigerant passing through the diffuser 14d has been increased. In contrast, since the outlet side of the second evaporator 18 with the refrigerant suction port 14b the ejector pump 14 is connected, the lowest pressure of the refrigerant at the nozzle part 14a has been decompressed on the second evaporator 18 Act.

Therefore, the refrigerant evaporation pressure (the refrigerant evaporation temperature) of the second evaporator 18 lower than the refrigerant evaporation pressure (the refrigerant evaporation Funging temperature) of the first evaporator 15 be. With respect to the flow direction A of the blown air, the first evaporator is 15 , whose refrigerant evaporation temperature is high, disposed on the upstream side, and the second evaporator 18 whose refrigerant evaporation temperature is low is disposed on the downstream side. Both a difference between the refrigerant evaporation temperature of the first evaporator 15 and the temperature of the blown air and a difference between the refrigerant evaporation temperature of the second evaporator 18 and the temperature of the blown air can be secured.

Therefore, both cooling capacities of the first and second evaporators can 15 and 18 be shown effectively. Thus, the cooling performance of the common space to be cooled in the combination of the first and the second evaporator 15 and 18 be effectively improved. Further, the effect of increasing the pressure through the diffuser increases 14d the pressure of the suction refrigerant of the compressor 11 , which reduces the drive energy of the compressor 11 is reduced.

The refrigerant flow rate on the side of the second evaporator 18 can through the capillary tube (the throttle) 17 be set independently, without the function of the ejector 14 depend, and the refrigerant flow rate in the first evaporator 15 can by a throttle characteristic of the ejector 14 be set. Thus, the refrigerant flow rates in the first and the second evaporator 15 and 18 corresponding to the respective heat loads of the first and second evaporators 15 and 18 easy to set.

For a small heat load of the circuit, the difference between high and low pressures in the circuit becomes small, as well as the input power of the ejector 14 gets small. In the circle disclosed in JP-B2-3322263, it hangs through the second evaporator 18 reaching refrigerant flow rate only from the refrigerant suction capacity of the ejector 14 from. This results in a reduced input power of the ejector 14 , a deterioration of the refrigerant suction capacity of the ejector 14 and a drop in the refrigerant flow rate of the second evaporator 18 , which makes it difficult to control the cooling performance of the second evaporator 18 to secure.

In contrast, in this embodiment, by the expansion valve 13 reached refrigerant upstream of the nozzle part 14a the ejector pump 14 branches, and the branched refrigerant is through the refrigerant side channel 16 into the refrigerant suction port 14b sucked so that the refrigerant side channel 16 parallel to the ejector pump 14 is switched.

So the refrigerant can the refrigerant side channel 16 not only by means of the refrigerant suction capacity of the ejector 14 but also the refrigerant suction and discharge capacity of the compressor 11 be supplied. This may be the degree of decrease of the refrigerant flow rate on the side of the second evaporator 18 in comparison to that in the patent document 1 disclosed circuit even when a phenomenon such as the drop in the input power of the ejector 14 and the deterioration of the refrigerant suction capacity of the ejector 14 to reduce. Accordingly, even at a low heat load, the cooling performance of the second evaporator 18 just be secured.

In the ejector-type refrigerant cycle device of the embodiment, this is achieved by the expansion valve 13 arrived vapor / liquid two-phase refrigerant (medium-pressure refrigerant) in the main channel 25a of the terminal block 23 to the nozzle part 14a the ejector pump 14 directed refrigerant flow and that of the refrigerant side channel 16 of the terminal block 23 to the capillary tube 17a divided refrigerant flow divided.

As the flow rate of the capillary tube 17a in the lower room 70 of the right room 28 of the upper container 18b in the second evaporator 18 flowing refrigerant (as indicated by the arrow "f") becomes small, the refrigerant does not easily reach that from the downstream end 17d of the capillary tube 17a distant side in the lower room 70 (the distribution tank).

As a result, the distribution of the refrigerant on the multiple tubes 21 in the lower room 70 (Distribution tank) become uneven, resulting in uneven temperature distribution by the second evaporator 18 cooled air leads.

For this reason, in the embodiment, as indicated by the arrow "j" of FIG 5 indicated, the liquid refrigerant from that of the capillary tube 17a in the lower room 70 flowing liquid / vapor two-phase refrigerant temporarily in the bottom 75d the refrigerant retention plate 75 trained talar-like retention section 76 saved. Then, a part of the liquid refrigerant falling from the valley-like retention portion falls 76 breaks, out of the holes 75a the refrigerant retention plate 75 in the pipes 21 ,

This allows the liquid refrigerant to be from the downstream end 17d of the capillary tube 17a distant side in the lower room 70 (Distribution tank) are directed so that the distribution of the refrigerant to the in the lower room 70 inserted pipes 21 can be made more uniform. Therefore, the temperature distribution of the second evaporator can 18 be made evenly cooled air.

Through detailed studies, the inventors have found that when a bending angle θ of the mountainous section of the refrigerant retention plate 75 (please refer 5 ) is set to a range of 30 ° to 170 °, the retention and fall of the liquid refrigerant through the refrigerant retention plate 75 can be suitably performed, which makes the refrigerant more uniform on the multiple tubes 21 is distributed.

Likewise, through the detailed studies, the inventors further found that the straight edge of the hole 75a the refrigerant retention plate 75 a relatively large drop of the liquid refrigerant due to one at the edge of the hole 75a can produce surface tension that comes from the hole 75a to the pipes 21 or the like, thereby reducing the effect of uniform distribution of the refrigerant.

As in the embodiment, as in 11 represented the edge of the hole 75a the refrigerant retention plate 75 which edge is in the layering direction of the tubes 21 extends, is in the wave-like shape, a relatively large drop of the liquid refrigerant due to the surface tension from the hole 75a fall before it grows even bigger.

That is, because the liquid refrigerant out of the hole 75a in the pipe 21 can fall in the smallest droplet state, the effect of a uniform distribution of the refrigerant can be well shown.

It should be noted that in the retention section 76 stored refrigerant from the vertex 75a passes and falls at the lowest position from the edges of the hole 75a is positioned. In the embodiment, as in FIG 11 shown, the distance P between the wave-like vertices 75c at the same distance between the pipes 21 set, eliminating the wavy vertex 75c the inlet part 21a of the pipe 21 is superimposed. That is, the wavy vertices 75c overlap each with the inlet parts 21a the pipes 21 , This leaves that from the crests 75c leaking and falling liquid refrigerant directly into the pipes 21 flow, causing the liquid refrigerant effectively into the pipes 21 can flow.

13 to 15 show an example 1, to which the invention is applied to a modified integrated unit 20 of the present embodiment. That is, Example 1 is a modification of the first embodiment described above. 13 Figure 3 is a schematic perspective view of the overall structure of the integrated unit 20 in Example 1, 14 FIG. 12 is a schematic cross-sectional view of an upper tank of the first and second evaporators. FIG 15 and 18 in Example 1, and 15 is a sectional view of the upper container of the second evaporator 18 in Example 1.

In Example 1, the capillary tube 17a in the upper container 18b arranged. That is, the downstream end 17d of the capillary tube 17a is in the right room 28 of the upper container 18b open, being a support hole 24a a second terminal block 24 is permeated, as in 14 shown. In Example 1, the refrigerant retention plate 75 not in the right room 28 arranged.

The connection block 23 in Example 1 of 14 corresponds to a combined body of the terminal block 23 and the intermediate plate 24 according to the embodiment described above. In Example 1, the ejector inlet part is 63 not trained, and the ejector 14 is from the refrigerant inlet 25 in the upper container 18 of the second evaporator 18 used. Therefore, in this example, the spacer 72 and the stopper 73 of the embodiment not necessary.

Instead of the ejector mounting plate 65 of the embodiment is the second terminal block 24 in the middle region of the upper container 18b arranged in the container longitudinal direction. This second connection block 24 separates the interior of the upper container 18b in a left and a right room.

Because the top / bottom separator plate 67 of the above-described embodiment is not provided in this example 1, the right space is used 28 in the upper container 18b of the second evaporator 18 as a room without going into the upper room 69 and the lower room 70 to be separated.

Instead of the connection hole 71 of the embodiment is a connection hole 24c of the second terminal block 24 with the right room 32 of the upper container 15b of the first evaporator 15 over a through hole 33a an intermediate wall 23 between both upper containers 15b and 18b in connection So that flows from the diffuser 14d the ejector pump 14 discharged low pressure refrigerant through the communication hole 24c of the second terminal block 24 and the passage hole 32a the partition 33 in the direction of the arrow "a" in 14 in the right room 32 of the upper container 15b of the first evaporator 15 ,

In this example 1, the refrigerant retaining plate described in the embodiment 75 in the right room 28 to be ordered. In this case, the refrigerant retention plate 75 that from the downstream end 17d of the capillary tube 17a in the right room 28 flowing refrigerant on the several tubes 21 to distribute.

16 to 18 correspond to a modified example 2 of the first embodiment described above. In the embodiment described above, the capillary tube 17a between the secondary channel 16 of the first terminal block 23 the integrated unit 20 and the inlet side of the second evaporator 18 arranged, and the refrigerant at the inlet of the second evaporator 18 is through the capillary tube 17a decompressed. In the in 16 to 18 Example 2 shown is the capillary tube 17a not as a decompression device of the second evaporator 18 used, and instead is a fixed throttle hole 17b , For example, an opening, for throttling a path surface to a predetermined level in the secondary channel 16 of the first terminal block 23 provided, and together with it is a connecting pipe 160 whose channel diameter is larger than that of the capillary tube 17a is at an arrangement position of the capillary tube 17a of the first embodiment arranged.

Example 2 has the same refrigerant channels as in 13 to 15 Example 1, except that by the fixed throttle hole 17b in the side channel 16 of the first terminal block 23 is formed, decompressed low-pressure refrigerant through the connecting pipe 160 in the right room 28 of the upper container 18b of the second evaporator 18 is initiated.

19 to 21 correspond to a modified example 3 of the first embodiment described above. Although in the in 13 to 15 Example 1 shown, the ejector 14 and the capillary tube 17a in a common container, ie in the upper container 18b of the second evaporator 18 , is in the in 19 to 21 Example 3 shown only the capillary tube 17a in the upper container 18b of the second evaporator, while the ejector 14 in another special container 34 is arranged.

Along with removing the ejector pump 14 from the upper container 18b of the second evaporator 18 will also be in the in 13 to 15 Example 1 used second terminal block 24 away. Instead, it is a partition plate 35 in a central region of the upper container 18b arranged in the longitudinal direction and for separating the interior of the upper container 18b formed in the left and right spaces. The downstream end 17d of the capillary tube 17a is formed to the partition plate 35 to penetrate, so with the right space 28 of the upper container 18b to communicate.

The above other container 34 is in intermediate position between the upper tank 15b of the first evaporator 15 and the upper container 18b of the second evaporator 18 arranged as in 18 shown. The container 34 has a cylindrical shape that extends in the longitudinal direction of both containers 15b and 18b extends. In this example, the other container 34 integral with the upper containers 15b and 18b educated.

The ejector pump 14 and the cylindrical further container 34 run up to that of the partition plates 30 and 35 for both containers 15b and 18b removed floor (right side), as in 20 shown. The outlet part of the ejector pump 14 (Outlet part of the diffuser 14d ) stands with the right space 32 of the upper container 15b of the first evaporator 15 through the through hole (cross hole) 34a in conjunction, which is the peripheral wall of the container 34 penetrates.

The refrigerant inlet opening is analogous 14b the ejector pump 14 with the left room 27 of the upper container 18b of the second evaporator 18 through the through hole (cross hole) 34b in conjunction, which is the peripheral wall of the container 34 penetrates.

Also in the in 19 to 21 Example 3 would be in the right room 28 the downstream end 17d of the capillary tube 17a flowing low-pressure refrigerant (liquid / vapor two-phase refrigerant) directly into the multiple tubes 21 on the right side of the heat exchange core 18a flow, resulting in uneven distribution of the liquid refrigerant to the multiple tubes 21 would lead.

For this reason, in the in 19 to 21 Example 3 shown, the refrigerant retaining plate described in the first embodiment 25 in the right room 28 to be ordered. In this case, the refrigerant retention plate 75 the refrigerant evenly into the several tubes 21 distribute, as in the case of the first embodiment.

An in 22 to 24 Example 4 is obtained by modifying the in 19 to 21 Example 3 shown, wherein the capillary tube 17a of in 19 to 21 Example 3 is omitted and instead the fixed throttle hole 17b and the connection pipe 160 used in Example 2.

That is, in the in 22 to 24 Example 4 shown is the fixed throttle hole serving as a decompression unit 17b in the secondary channel 16 of the first terminal block 23 formed, and the downstream side of the fixed throttle hole 17b stands with the right space 28 of the upper container 18b of the second evaporator 19 through the connecting pipe 160 in connection.

Although in each of the first embodiment and the example 1 to 4, the ejector 14 in the upper container 18b of the second evaporator 18 or in the other container 34 next to the upper container 18b is arranged in an in 25 Example 5 shown the ejector 14 in an external cassette 36 (Housing member) disposed outside of the first and second evaporator 15 and 18 is arranged. 25 is a schematic representation in which a part of the integrated unit is shown in cross section.

This cassette 36 is an external element attached to the outside of the first and second evaporators 15 and 18 is attached and mainly the ejector 14 , one in the ejector part 14 receiving lower housing part 37 and an upper housing part 38 contains.

The main body of the ejector pump 14 (ie the part where the nozzle part 14a is formed) is formed in a columnar shape extending vertically along the one side of each of the first and the second evaporator 15 and 18 in an in 25 example shown extends. The main body of the ejector pump 14 can be made of any element of metal, such as aluminum, and synthetic resin.

On the outer peripheral wall of the main body of the ejector 14 Seal elements S1 and S2 are arranged from O-rings. Note that the main body of the ejector 14 may also be formed in a different form than the columnar shape, for example in a rectangular parallelepiped.

The lower case 37 is provisionally at the end faces of the first and second evaporator 15 and 18 fixed. In particular, the lower housing 37 a rectangular parallelepiped with a closed bottom and an open top. Note that the material for the lower case 37 may be any of metal, for example aluminum, and synthetic resin. The lower case 37 becomes on the sides of the first and the second evaporator 15 and 18 attached with screwing or the like.

The ejector body of the ejector 14 comes from an opening at the top of the lower case 37 in the lower case 37 used. An upper part of the ejector pump 14 ie, an upper part (an inlet side part of the nozzle 14a ) from the refrigerant suction port 14b the ejector pump 14 protrudes above the lower housing 37 ,

Then the upper protruding part of the ejector 14 in the upper case 38 fitted while the upper case 38 as a cover on the opening at the top of the lower housing 37 is placed. The upper case 38 and the lower case 37 be integrally clamped with the screw or another fastener.

This can be the body of the ejector 14 in the lower case 37 and in the upper case 38 hold and fix. Because in 25 the air flow direction A opposite to that of 2 is, are the first and the second evaporator 15 and 18 in 25 across from 2 transposed in the transverse direction.

The upper case 38 is integral with the first terminal block 23 formed in Examples 1 to 4. That is, in the upper case 38 are the refrigerant inlet 25 and the refrigerant outlet 26 arranged side by side and parallel to each other. The refrigerant inlet 25 Branches in a center of the channel in the inlet side of the nozzle part 14a the ejector pump 14 directed main channel and the secondary channel 16 , The fixed throttle hole serving as a decompression device 17b is in the side channel 16 educated. The fixed throttle hole 17b of this example is the same as that in each of Comparative Example 3 or Example 4.

The main channel 25a is from the direction of the channel of the refrigerant inlet 25 bent in an L-shape to the longitudinal direction (vertical direction) of the ejector 14 to get lost. In the main channel 25a are from the upper part to the lower part of the nozzle 14a , the mixer 14c and the diffuser 14d the ejector pump 14 formed in this order.

The outlet part of the ejector pump 14 (Outlet part of the diffuser 14d ) is positioned in the longitudinal direction near the other end (lower end) of the ejector. The outlet part of the ejector pump 14 is with one end of a connecting pipe 39 over the connection hole 37a of the lower case 37 connected. The other end of the connecting pipe 39 is with the right space 32 of the upper container 15b of the first evaporator 15 connected.

The channel of the refrigerant outlet 26 of the upper case 38 is with the left room 31 of the upper container 15b of the first evaporator 15 connected.

The refrigerant suction port 14b the ejector pump 14 is designed to be the wall of the main body of the ejector 14 penetrates in the radial direction, and it communicates with the downstream part of the nozzle part 14a the ejector pump 14 in connection. The refrigerant suction port 14b is with one end of a connecting pipe 40 over a connection hole 38a of the upper case 38 connected, and the other end of the connecting pipe 40 is with the left room 27 of the upper container 18b connected to the second evaporator.

The outlet side of the fixed throttle hole 17b of the secondary channel 16 is over the connecting pipe 41 with the right room 28 of the upper container 18b of the second evaporator 18 connected.

By connecting the channel of the external cassette 36 with the four left and right spaces 27 . 28 . 31 and 32 the upper container 15b and 18b the first and the second evaporator 15 and 19 As described above, this flows through the ejector 14 reached refrigerant after flowing through the connecting pipe 39 through the flow path of the first evaporator 15 indicated by the arrows "a" to "e", and then flows from the refrigerant outlet 26 the external cassette 36 in the external flow path (to the suction side of the compressor), as in 25 shown.

The at the refrigerant inlet 25 in the secondary channel 16 branched and through the fixed throttle hole 17b decompressed refrigerant flows after flowing through the connecting pipe 41 through the flow path of the second evaporator 18 indicated by the arrows "f" to "i" and reaches the left space 27 of the upper container 18b , The refrigerant is through the connecting pipe 40 from the left room 27 into the refrigerant suction port 14b the ejector pump 14 sucked.

Although in example 5 of 25 a the first terminal block 23 corresponding part integral with the upper housing part 38 the external cassette 36 is formed, is in an example 6 of 6 the first connection block 23 from the external cassette 36 separated and is used as an independent component.

In example 6 of 26 is on one side (eg, the right side) from both sides of the first and second evaporators 15 and 18 the first connection block 23 arranged, and on the other side is the external cassette 36 arranged.

The external cassette 36 has such a construction that it has the ejector part 14 in the lower case 37 and in the upper case 38 in the same way as example 5 of 25 holds and fixes. Note that in Example 6 of 26 not the lower case 37 but the upper case 38 provisionally on one side of the first and second evaporators 15 and 18 is fixed.

In example 6 of 26 becomes the ejector 14 from a lower opening of the upper housing 38 in the upper case 38 inserted, and then the lower case 37 as a cover over the lower opening of the upper housing 38 placed. The upper and the lower case 37 and 38 Both are clamped integrally with the screw or the like.

In this example, the arrangement direction of the ejector is 14 contrary to that in Example 5 of 25 , The ejector pump 14 is mounted so that the nozzle part 14a (Inlet side) is placed at the lower position while the diffuser 14d (Outlet side) is placed at the upper position.

The refrigerant suction port 14b the ejector pump 14 is with the left side of the lower container 18c of the second evaporator 18 over a connection hole 37b of the lower case 37 connected. The diffuser 14d is with the left room 31 of the upper container 15b of the first evaporator 15 over a connection hole 38b of the upper case 38 connected.

On the other hand, the refrigerant inlet branches 25 of the first terminal block 23 in the main channel 25a and the side channel 16 , The main channel 25a is with the connection hole 37c of the lower case 37 the external cassette 36 through the connecting pipe 42 connected. The connection hole 37c stands with an inlet part 43 of the nozzle part 14a the ejector pump 14 in connection.

The secondary channel 16 is with the right side of the lower container 18c of the second evaporator 18 via the capillary tube serving as a decompression device 17a connected.

In the second evaporator 18 Example 6 of 26 is the partition plate of the upper container described above 18b omitted, and instead is another partition plate 35a in the central region of the lower container 18c arranged in the longitudinal direction. This partition plate 35a is for separating the interior of the lower container 18c formed in the left and right spaces.

This is how it gets through the capillary tube 17a reached low-pressure refrigerant through the indicated by the arrows "f" to "i" refrigerant flow path of the second evaporator 18 and then from the left side of the lower container 18c over the connection hole 37b into the refrigerant suction port 14b the ejector pump 14 sucked.

The refrigerant in the main channel 25a of the refrigerant inlet 25 passes through the connecting pipe 42 , flows over the connection hole 37c in the inlet 43 the ejector pump 14 the external cassette 36 and gets through the nozzle part 14a decompressed and stretched. The low-pressure refrigerant from the outlet of the ejector pump 14 flows over the connection hole 38b of the upper case 38 in the left room 31 of the upper container 15b of the first evaporator 15 ,

Thereafter, the low-pressure refrigerant flows through the refrigerant flow path of the first evaporator indicated by the arrows "a" to "d" 15 to the refrigerant outlet 26 of the first terminal block 23 ,

In In the above-described Examples 1 to 6, the other parts may be similar to those of Figs corresponding parts indicated by the same reference numerals are made of the first embodiment described above, and their detailed description is omitted.

Second Embodiment

In the first embodiment described above, the edge of the hole 75a the refrigerant retention plate 75 , which are in the layering direction of the tubes 21 extends, formed in the wave-like shape. In the second embodiment, however, as in FIG 27 and 28 represented, an edge of the hole 75a the refrigerant retention plate 75 , which are in the layering direction of the tubes 21 extends, rectilinear and the hole 75a itself is in one in the stratification direction of the tubes 21 extending rectangular shape formed.

Also in the second embodiment, the liquid refrigerant from that of the capillary tube 17a in the lower room 70 flowing liquid / vapor two-phase refrigerant temporarily in the retaining portion 76 stored, and some liquid refrigerant from the retention section 76 breaks, falls out of the holes 75a the refrigerant retention plate 75 in the pipes 21 , This allows the even distribution of the liquid refrigerant to the multiple tubes 21 , In the second embodiment, the other parts may be made similar to those of the first embodiment described above.

In addition, the construction of the refrigerant retention plate 75 of the second embodiment may be used for any of the modified examples 1 to 6 of the first embodiment.

(Third Embodiment)

In the second embodiment described above, the hole 75a the refrigerant retention plate 75 formed approximately in a rectangular shape, which is in the layering direction of the tubes 21 extends. However, in the third embodiment, as in FIG 29 and 30 represented the hole 75a the refrigerant retention plate 75 formed in an elliptical shape, this is in the layering direction of the tubes 21 extends.

Also in the third embodiment, the liquid refrigerant from the capillary tube 17a in the lower room 70 flowing liquid / vapor two-phase refrigerant temporarily in the retention section 76 stored, and some liquid refrigerant from the retention section 76 breaks, falls out of the holes 75a the refrigerant retention plate 75 in the pipes 21 , This allows the even distribution of the liquid refrigerant to the multiple tubes 21 ,

In the third embodiment, the other parts may be made similar to those of the first embodiment described above. In addition, the construction of the refrigerant retention plate 75 of the third embodiment may be used for any of the modified examples 1 to 6 of the first embodiment.

(Fourth Embodiment)

In the third embodiment, each hole overlaps 75a the refrigerant retention plate 75 with the inlet parts 21a the several pipes 21 , However, in the fourth embodiment, as in FIG 31 represented, every hole 75a the refrigerant retention plate 75 only with the inlet part 21a a pipe 21 superimposed. That is, a hole 75a the refrigerant retention plate 75 overlaps only with the inlet part 21a a pipe 21 ,

In the fourth embodiment, the diameter of the hole 75a in the longitudinal direction of the tube 21 reduced in size compared to the third embodiment, and instead, the number of holes 75a elevated.

In particular, the distance between the holes 75a identical to those between the pipes 21 , and every hole 75a is above the inlet part 21a of the pipe 21 positioned.

In the fourth embodiment, the liquid refrigerant, that of the retaining portion 76 goes over to the holes 75a in the pipe 21 to fall, directly into the pipes 21 stream.

Therefore, the distribution of the liquid refrigerant to the plurality of tubes 21 be brought in an even manner. In the fourth embodiment, the other parts may be made similar to those of the first embodiment described above.

In addition, the construction of the refrigerant retention plate 75 of the fourth embodiment may be used for any of the modified examples 1 to 6 of the first embodiment.

(Fifth Embodiment)

In the respective embodiments described above, the refrigerant retaining plate 75 designed so that they have the mountainous cut in the ground 75d from which the retention section 76 is formed. However, in the fifth embodiment, as in FIG 32 represented, a depression part 77a with a U-shaped cut in a refrigerant retention plate 77 formed, and the recess part 77a forms the retention part 78 ,

As in 32 shown, has the refrigerant retention plate 77 a flat surface part 77b from both ends of the depression 77a with the U-shaped section to the running in the vertical direction inner wall surface 60b of the lower half element 60 of the upper container 18b is formed running. A top surface 77c of the flat surface part 77b bumps against the inner wall surface 60b of the lower half element 60 ,

One to the inner wall surface 60b of the lower half element 60 directed notch 77d is in the flat surface part 77b educated. One by the score 77d and the inner wall surface 60b of the lower half element 60 enclosed space forms a hole 79 to temporarily transfer the liquid refrigerant into the retention section 78 of the depression part 77a to be able to store in the tube side 21 to fall.

In the fifth embodiment, the liquid refrigerant from that of the capillary tube 17a in the lower room 70 flowing liquid / vapor two-phase refrigerant temporarily in the retaining portion 78 the refrigerant retention plate 77 stored, and some liquid refrigerant from the refrigerant retention section 78 breaks, falls from the hole 79 in the tube side 21 as indicated by an arrow "k".

This allows the even distribution of the liquid refrigerant to the multiple tubes 21 in the same manner as in the above-described embodiments.

In the fifth embodiment, the other parts may be made similar to those of the first embodiment described above. In addition, the retention section 78 the refrigerant retention plate 77 of the fifth embodiment may be used for any of the modified examples 1 to 6 of the first embodiment.

(Sixth Embodiment)

In the above first to fourth embodiments and their modified examples 1 to 6, the refrigerant retaining plate has 75 the mountainous cut, at the bottom 75d the retention section 76 is trained. In the sixth embodiment, however, as in 33 shown, a refrigerant retaining plate 80 formed in a flat plate shape with an oblique cut and at the bottom of the slope of the refrigerant retention plate 80 is a retention section 81 educated.

As in 33 pictured, bump two ends 80a the section of the refrigerant retention plate 80 against the inner wall surface 60b of the lower half element 60 , To form the oblique bottom of the refrigerant retention plate 80 and the inner wall surface 60b the bottom half-element 60 the retention section 81 for temporarily storing the liquid refrigerant therein.

At the sloping top of the refrigerant retention plate 80 is a score 80b formed to the inner wall surface 60b the bottom half-element 60 is directed. A space through the notch 80b and the inner wall surface 60b the bottom half-element 60 enclosed forms a hole 62 to temporarily transfer the liquid refrigerant into the retention section 81 to be able to store in the tube side 21 to fall.

In the sixth embodiment, the liquid refrigerant from the capillary tube 17a in the lower room 70 flowing liquid / vapor two-phase refrigerant temporarily in the retention section 81 stored, and some liquid refrigerant from the retention section 81 breaks, falls from the hole 82 to the pipe side 21 as indicated by the arrow "m" of 33 specified.

This allows the even distribution of the liquid refrigerant to the multiple tubes 21 as in the case of the embodiments described above.

In the sixth embodiment, the other parts may be made similar to those of the first embodiment described above. In addition, the construction of the refrigerant retention plate 80 of the sixth embodiment may be used for any one of Modified Examples 1 to 6 of the first embodiment.

(Seventh Embodiment)

In the first embodiment, the circuit of the expansion valve type includes the liquid receiver 12a on the outlet side of the radiator 12 , and that on the outlet side of the liquid collecting vessel 12a arranged expansion valve 13 is used. In a seventh embodiment, however, as in 34 represented, a memory 50 serving as a liquid-vapor separator for separating the refrigerant into a liquid and a vapor phase on the outlet side of the first evaporator 15 and for storing the excess refrigerant in the form of the liquid. The vapor-phase refrigerant is removed from the store 50 into the suction side of the compressor 15 derived.

In the memory circle of the 34 is a liquid / vapor interface between the vapor-phase refrigerant and the liquid-phase refrigerant in the reservoir 50 formed, and therefore it is not necessary, the superheat degree of the refrigerant at the outlet of the first evaporator 15 through the expansion valve 13 as in the first embodiment to control.

Since the liquid receiver 12a and the expansion valve 13 are omitted in the storage circuit, the refrigerant inlet 25 the integrated unit 20 directly to the outlet side of the radiator 12 get connected. The refrigerant outlet 26 the integrated unit 20 can with the inlet side of the store 50 connected, and the outlet side of the memory 50 Can directly with the suction side of the compressor 11 get connected.

In the seventh embodiment, any construction of the above-described refrigerant retention plates 75 . 77 . 80 for the integrated unit 20 of the cooling circuit (storage circuit) of 34 be used.

(Eighth Embodiment)

The eighth embodiment is a modification of the seventh embodiment. As in 35 represented is the memory 50 as an element integral in the integrated unit 20 integrated. The outlet part of the store 50 forms the refrigerant outlet 26 the entire integrated unit 20 , In the eighth embodiment, the other parts may be made similar to the seventh embodiment described above.

Ninth Embodiment

In each of the first to eighth embodiments described above, the one on the inlet side of the ejector 14 branching side channel 16 with the refrigerant suction port 14b the ejector pump 14 connected, and the throttle 17 and the second evaporator 18 are in the side channel 16 arranged. In the ninth embodiment, however, as in 36 represented, serving as a liquid / vapor separator memory 50 on the outlet side of the first evaporator 15 arranged, the side channel 16 is for connecting the liquid-phase refrigerant Auslassteilils 50a of the memory 50 with the refrigerant suction port 14b the ejector pump 14 provided, and the throttle 17 and the second evaporator 18 are in the side channel 16 arranged.

In the ninth embodiment form the ejector 14 , the first and second evaporators 15 and 18 , the throttle 17 and the memory 50 an integrated unit 20 , In the whole integrated unit 20 is a refrigerant inlet 25 at the inlet of the ejector pump 14 provided with the outlet of the radiator 12 connected is.

In the whole integrated unit 20 is a refrigerant outlet 26 at the vapor phase refrigerant outlet of the store 50 provided and with the suction side of the compressor 11 connected.

In the ninth embodiment, any construction of the above-described refrigerant retaining plates 75 . 77 . 80 for the integrated unit 20 of the cooling circuit of 36 be used.

(Tenth embodiment)

Each of the first to ninth embodiments includes that with the exhaust side of the ejector 14 connected first evaporator 15 and with the refrigerant suction port 14b the ejector pump 14 connected second evaporator 18 , In the tenth embodiment, however, as in 37 represented, an integrated unit 20 in the ejector refrigerant cycle device 10 with only one evaporator 18 constructed with the refrigerant suction port 14b the ejector pump 14 connected is.

The integrated unit of the tenth embodiment is the ejector 14 , the evaporator 18 , the throttle 17 and the memory 50 built up. The integrated unit has a total of one refrigerant inlet 25 and a refrigerant let 26 , That is, the tenth embodiment corresponds to the unit of the ninth embodiment in which the first evaporator 15 is not provided.

Also in the tenth embodiment, any construction of the above-described refrigerant retaining plates 75 . 77 . 80 for the integrated unit 20 the ejector refrigerant cycle device 10 from 37 be used.

Eleventh Embodiment

In each of the first to ninth embodiments described, the throttle is 17 the integrated unit 20 integrated. In the eleventh embodiment, however, as in 38 represented, the integrated unit 20 from the first and second evaporators 15 and 18 and the ejector pump 14 built, and the throttle 17 is separate from the integrated unit 20 independently provided.

Also in the eleventh embodiment, the liquid / vapor separator is disposed neither on the high pressure side nor on the low pressure side of the circle as in FIG 38 shown.

(Twelfth embodiment)

39 shows the twelfth embodiment, in which the serving as a liquid / vapor separator memory 50 relative to the eleventh embodiment on the outlet side of the first evaporator 15 provided and in the integrated unit 20 is integrally integrated. That is, in the twelfth embodiment, the ejector form 14 , the first and second evaporators 15 and 18 and the memory 50 the integrated unit 20 , and the throttle 17 is separate from the integrated unit 20 independently provided.

In the twelfth embodiment, any structure of the above-described refrigerant retaining plates 75 . 77 . 80 for the integrated unit 20 the ejector refrigerant cycle device of 39 be used.

(Further embodiments)

• (1) Im ersten Ausführungsbeispiel werden beim integralen Zusammenbauen jeder Komponente der integrierten Einheit 20 die Komponenten außer der Ejektorpumpe 4, d.h. der erste Verdampfapparat 15, der zweite Verdampfapparat 18, der Anschlussblock 23, das Kapillarrohr 17a und dergleichen integral miteinander verlötet. Der integrale Zusammenbau dieser Komponenten kann auch durch verschiedene Befestigungseinrichtungen außer Löten, einschließlich Verschrauben, Verstemmen, Schweißen, Verkleben und dergleichen, durchgeführt werden. Obwohl im ersten Ausführungsbeispiel die beispielhafte Befestigungseinrichtung der Ejektorpumpe 14 das Verschrauben ist, kann irgendeine Befestigungseinrichtung außer dem Verschrauben verwendet werden, sofern die Befestigungseinrichtung keine thermische Verformung bewirkt. Insbesondere kann die Befestigungseinrichtung wie beispielsweise Verstemmen oder Verkleben benutzt werden, um die Ejektorpumpe 14 zu befestigen.
• (2) Obwohl in den obigen jeweiligen Ausführungsbeispielen der unterkritische Dampfkompressionskühlkreis beschrieben worden ist, bei dem das Kältemittel eines auf Flon-Basis, eines auf HC-Basis oder dergleichen ist, dessen Hochdruck den kritischen Druck nicht übersteigt, kann die Erfindung auch auf einen überkritischen Dampfkompressionskühlkreis angewendet werden, der ein Kältemittel wie beispielsweise Kohlendioxid (CO₂) verwendet, dessen Hochdruck den kritischen Druck übersteigt. Es ist zu beachten, dass im überkritischen Kreis nur das durch den Kompressor ausgegebenen Kältemittel Wärme im überkritischen Zustand am Kühler 12 abstrahlt und daher nicht kondensiert. Daher kann das auf der Hochdruckseite angeordnete Flüssigkeitsauffanggefäß 12a keine Flüssigkeit/Dampf-Trennwirkung des Kältemittels und keine Rückhaltewirkung des überschüssigen flüssigen Kältemittels zeigen. Wie in 34 bis 39 dargestellt, kann der überkritische Kreis eine Konstruktion mit dem Speicher 50 am Auslass des ersten Verdampfapparats 15 als Niederdruck-Flüssigkeit/Dampf-Trennvorrichtung haben.
• (3) Obwohl in den obigen Ausführungsbeispielen die Drossel 17 aus dem festen Drosselloch 17a wie beispielsweise dem Kapillarrohr 17a oder der Öffnung aufgebaut ist, kann die Drossel 17 auch durch ein elektrisches Regelventil gebildet werden, dessen Ventilöffnung (ein Öffnungsgrad einer Kanalverengung) durch den elektrischen Stellantrieb einstellbar ist. Die Drossel 17 kann aus einer Kombination der festen Drossel wie beispielsweise dem Kapillarrohr 17a und dem festen Drosselloch 17b sowie einem elektromagnetischen Ventil gebildet werden.
• (4) Obwohl in den obigen jeweiligen Ausführungsbeispielen die beispielhafte Ejektorpumpe 14 eine feste Ejektorpumpe mit dem Düsenteil 14a mit der bestimmten Pfadfläche ist, kann die Ejektorpumpe 14 in der Praxis auch eine variable Ejektorpumpe mit einem variablen Drosselteil sein, dessen Pfadfläche einstellbar ist. Zum Beispiel kann das variable Drosselteil ein Mechanismus sein, der ausgebildet ist, um die Pfadfläche durch Steuern der Position einer in einen Kanal des variablen Drosselteils eingesetzten Nadel unter Verwendung des elektrischen Stellantriebs einzustellen.
• (5) Obwohl im ersten Ausführungsbeispiel und dergleichen die Erfindung auf die Kühlkreisvorrichtung zum Kühlen des Innenraums des Fahrzeugs und für den Tiefkühlraum und den Kühlraum angewendet ist, können sowohl der erste Verdampfapparat 15, dessen Kältemittelverdampfungstemperatur hoch ist, als auch der zweite Verdampfapparat 18, dessen Kältemittelverdampfungstemperatur niedrig ist, auch zum Kühlen verschiedener Bereiche innerhalb des Raums des Fahrzeugs verwendet werden (zum Beispiel einen Bereich auf einer Vordersitzseite im Raum des Fahrzeugs und einen Bereich auf einer Rücksitzseite darin). Alternativ oder zusätzlich können sowohl der erste Verdampfapparat 15, dessen Kältemittelverdampfungstemperatur hoch ist, als auch der zweite Verdampfapparat 18, dessen Kältemittelverdampfungstemperatur niedrig ist, zum Kühlen des Tiefkühlraums und des Kühlraums verwendet werden. Das heißt, eine Kühlkammer des Tiefkühlraums und des Kühlraums kann durch den ersten Verdampfapparat 15, dessen Kältemittelverdampfungstemperatur hoch ist, gekühlt werden, während eine Tiefkühlkammer des Tiefkühlraums und des Kühlraums durch den zweiten Verdampfapparat 18 gekühlt werden kann, dessen Kältemittelverdampfungstemperatur niedrig ist.
• (6) Obwohl im ersten Ausführungsbeispiel und dergleichen das thermische Expansionsventil 13 und das Temperaturmessteil 13a separat von der Einheit für die Ejektorpumpen-Kühlkreisvorrichtung vorgesehen sind, können das thermische Expansionsventil 13 und das Temperaturmessteil 13a auch integral in der Einheit für die Ejektorpumpen-Kühlkreisvorrichtung integriert sein. Zum Beispiel kann ein Mechanismus zum Aufnehmen des thermischen Expansionsventils 13 und des Temperaturmessteils 13a im Anschlussblock 23 der integrierten Einheit 20 eingesetzt werden. In diesem Fall ist der Kältemitteleinlass 25 zwischen dem Flüssigkeitsauffanggefäß 12a und dem thermischen Expansionsventil 13 positioniert, und der Kältemittelauslass 26 ist zwischen dem Kompressor 11 und einem Kanalteil, an dem das Temperaturmessteil 13a installiert ist, positioniert.
• (7) Es ist offensichtlich, dass, obwohl in den obigen jeweiligen Ausführungsbeispielen die Kühlkreisvorrichtung für das Fahrzeug beschrieben worden ist, die Erfindung nicht nur auf das Fahrzeug, sondern auch auf einen festen Kühlkreis oder dergleichen in der gleichen Weise angewendet werden kann.
• (8) Obwohl im oben beschriebenen ersten Ausführungsbeispiel das stromabwärtige Ende 17d des Kapillarrohrs 17a horizontal in den oberen Behälter 18b eingesetzt ist, kann das stromabwärtige Ende 17d des Kapillarrohrs 17a auch vertikal in den oberen Behälter 18b eingesetzt werden.
• (9) In den obigen jeweiligen Ausführungsbeispielen sind die Behälter 15b, 15c, 18b und 18c des ersten Verdampfapparats 15 und des zweiten Verdampfapparats 18 auf sowohl der oberen Seite als auch der unteren Seite des ersten Verdampfapparats 15 angeordnet, d.h. der erste Verdampfapparat 15 und der zweite Verdampfapparat 18 sind vertikal angeordnet. Alternativ können der erste Verdampfapparat 15 und der zweite Verdampfapparat 18 auch in einer geneigten Weise bezüglich der vertikalen Richtung angeordnet werden. In diesem Fall würde, falls die Kältemittelrückhalteplatten 75, 77 und 80 zusammen mit dem ersten und dem zweiten Verdampfapparat 15 und 18 geneigt werden, dann das flüssige Kältemittel dazu neigen, von den Rückhalteabschnitten 76, 78 und 81 überzutreten, was in einem verringerten Effekt des Speicherns des flüssigen Kältemittels resultiert. Daher sind die Kältemittelrückhalteplatten 75, 77 und 80 nicht geneigt und können bevorzugt im gleichen Winkel wie in den obigen jeweiligen Ausführungsbeispielen angeordnet werden.
• (10) Obwohl in den obigen jeweiligen Ausführungsbeispielen die Erfindung auf den als Wärmetauscher auf der Wärmeabsorptionsseite des Kühlkreises dienenden Verdampfapparat 18 angewendet ist, kann die Erfindung auch auf verschiedene Anwendungen von Wärmetauschern angewendet werden.

It goes without saying that the invention is not limited to the above embodiments, and various modifications can be made to the embodiments as follows.

• (1) In the first embodiment, in integrally assembling each component of the integrated unit 20 the components except the ejector pump 4 ie the first evaporator 15 , the second evaporator 18 , the connection block 23 , the capillary tube 17a and the like are brazed integrally with each other. The integral assembly of these components can also be accomplished by various fasteners other than brazing, including bolting, caulking, welding, bonding, and the like. Although in the first embodiment, the exemplary attachment means of the ejector 14 screwing, any fastening means other than screwing may be used, as long as the fastening means does not cause thermal deformation. In particular, the attachment means such as caulking or gluing may be used to the ejector 14 to fix.
• (2) Although in the above respective embodiments, the subcritical vapor compression refrigerating cycle in which the refrigerant is a Flon-based, HC-based or the like whose high pressure does not exceed the critical pressure has been described, the invention can also be applied to a supercritical one Steam compression refrigeration cycle can be applied, which uses a refrigerant such as carbon dioxide (CO ₂ ), whose high pressure exceeds the critical pressure. It should be noted that in the supercritical circuit, only the refrigerant discharged through the compressor is heat in the supercritical state at the radiator 12 radiates and therefore not condensed. Therefore, the liquid receiver arranged on the high pressure side 12a show no liquid / vapor separation effect of the refrigerant and no retention effect of the excess liquid refrigerant. As in 34 to 39 shown, the supercritical circle can be a construction with the memory 50 at the outlet of the first evaporator 15 as a low pressure liquid / vapor separator.
• (3) Although in the above embodiments, the throttle 17 from the fixed throttle hole 17a such as the capillary tube 17a or the opening is constructed, the throttle can 17 also be formed by an electric control valve whose valve opening (an opening degree of a channel constriction) is adjustable by the electric actuator. The throttle 17 may be a combination of the fixed throttle such as the capillary tube 17a and the fixed throttle hole 17b and an electromagnetic valve are formed.
• (4) Although in the above respective embodiments, the exemplary ejector 14 a solid ejector with the nozzle part 14a with the particular path surface is, the ejector can 14 in practice also be a variable ejector with a variable throttle part, the path surface is adjustable. For example, the variable throttle portion may be a mechanism configured to adjust the path area by controlling the position of a needle inserted into a passage of the variable throttle portion using the electric actuator.
• (5) Although in the first embodiment and the like the invention is applied to the refrigeration cycle apparatus for cooling the interior of the vehicle and the freezing room and the refrigerating room, both the first evaporator 15 whose refrigerant evaporation temperature is high, as well as the second evaporator 18 , whose refrigerant evaporation temperature is low, can also be used for cooling various areas within the space of the vehicle (for example, an area on a front seat side in the space of the vehicle and an area on a rear seat side therein). Alternatively or additionally, both the first evaporator 15 whose refrigerant evaporation temperature is high, as well as the second evaporator 18 , whose refrigerant evaporation temperature is low, used for cooling the freezer compartment and the refrigerator. That is, a cooling chamber of the freezing room and the refrigerating room can pass through the first evaporator 15 Whose refrigerant evaporation temperature is high, are cooled, while a freezing chamber of the freezing space and the cooling space by the second evaporator 18 can be cooled, the refrigerant evaporation temperature is low.
• (6) Although in the first embodiment and the like, the thermal expansion valve 13 and the temperature measuring part 13a are provided separately from the unit for the ejector refrigerant cycle device, the thermal expansion valve 13 and the temperature measuring part 13a also integrally integrated in the unit for the ejector-type refrigeration cycle device. For example, a mechanism for accommodating the thermal expansion valve 13 and the temperature measuring part 13a in the connection block 23 the integrated unit 20 be used. In this case, the refrigerant inlet 25 between the liquid receiver 12a and the thermal expansion valve 13 positioned, and the refrigerant outlet 26 is between the compressor 11 and a channel part to which the temperature measuring part 13a is installed, positioned.
• (7) It is obvious that although in the above respective embodiments, the refrigeration cycle device for the vehicle has been described, the invention can be applied not only to the vehicle but also to a fixed refrigeration cycle or the like in the same manner.
• (8) Although in the first embodiment described above, the downstream end 17d of the capillary tube 17a horizontally in the upper container 18b can be used, the downstream end 17d of the capillary tube 17a also vertically in the upper container 18b be used.
• (9) In the above respective embodiments, the containers are 15b . 15c . 18b and 18c of the first evaporator 15 and the second evaporator 18 on both the upper side and the lower side of the first evaporator 15 arranged, ie the first evaporator 15 and the second evaporator 18 are arranged vertically. Alternatively, the first evaporator 15 and the second evaporator 18 also be arranged in an inclined manner with respect to the vertical direction. In this case, if the refrigerant retention plates 75 . 77 and 80 together with the first and second evaporators 15 and 18 be inclined, then the liquid refrigerant tend to from the retention sections 76 . 78 and 81 to pass, resulting in a reduced effect of storing the liquid refrigerant. Therefore, the refrigerant retention plates are 75 . 77 and 80 not inclined and may preferably be arranged at the same angle as in the above respective embodiments.
• (10) Although in the above respective embodiments, the invention is applied to the evaporator serving as a heat exchanger on the heat absorption side of the refrigerant cycle 18 is applied, the invention can also be applied to various applications of heat exchangers.

For example, the invention can be applied to a condenser or the like which serves as a heat exchanger on the heat radiation side of the refrigeration cycle. Likewise, the invention can be applied to the heat exchanger, through which the hot water in the inner channel (in the fluid channel corresponding to the pipe 21 in each embodiment described above) such as a hot water radiator for heating or a radiator for engine cooling.

The Invention can also be applied to the heat exchanger be applied through the oil or the like enters the inner channel, such as a Engine oil cooler, or the heat exchanger or the like, by the cold water in the inner channel in the same Way flows.

Such changes and modifications are of course within the scope of the present invention as defined by the appended claims is.

Claims (20)

Heat exchanger, with several pipes ( 21 ) defining fluid passages through which a heat exchange fluid flows with at least one liquid phase fluid; one above an inlet part ( 21a ) of the plurality of fluid channels arranged container ( 18b ) for distributing a flow of the heat exchange fluid to the fluid passages; and a retaining element arranged in the container above the inlet part ( 75 . 77 . 80 ) for temporarily storing the liquid phase fluid flowing into the container therein, wherein the retaining member is constructed so that the liquid phase fluid passing from the retaining member falls to the inlet part. Heat exchanger according to claim 1, in which the retaining element has a section (9) protruding from a horizontal surface ( 75 ) having; the downcut and an inner wall surface of the container extending in a vertical direction have a recessed retaining portion (FIG. 76 ), in which the liquid phase fluid is temporarily stored; and the mountain section of the retaining element has a vertex area with a hole ( 75a ) through which the liquid phase fluid stored in the retention section falls to the inlet part by crossing. heat exchangers according to claim 2, wherein a bending angle (θ) of the mountain section in a range from 30 ° to 170 °. Heat exchanger according to claim 2 or 3, in which the hole ( 75a ) is provided in the mountain section superimposed on the inlet part. heat exchangers according to one of the claims 2 to 4, wherein an edge of the hole is formed in a waveform is. heat exchangers according to claim 2 or 3, in which an edge of the hole in a waveform is formed; and a vertex of the waveform, which to the outside the hole is recessed, the inlet part is superimposed. A heat exchanger according to claim 1, wherein the retaining member comprises a tilt plate (14) inclined in the container with respect to a horizontal direction. 80 ) contains; and the tilt plate comprises: a lower part ( 80a ) forming, together with an inner wall surface of the container, a retaining portion in which the liquid phase fluid is temporarily stored; and an upper part ( 80b ) with a hole ( 82 ) through which the liquid phase fluid stored in the retaining portion falls to the inlet part by crossing. Heat exchanger according to claim 1, in which the retaining element is a plate element ( 77 ) with a recessed part ( 77a ) for defining a retention section in which the liquid phase fluid is temporarily stored; and the plate member is separated from an inner wall of the container to a hole ( 79 ), through which the liquid phase fluid stored in the retention section falls through the passage to the inlet part. Heat exchanger according to claim 1, wherein the retaining element comprises a plurality of holes ( 75a ) each overlapping at least one of the inlet portions of the tubes. Cooling circuit device, with a compressor ( 11 ) for compressing a refrigerant; a cooler ( 12 ) for cooling the refrigerant from the compressor; an ejector pump ( 14 ), which has a nozzle part ( 14a ) for decompressing the refrigerant from the radiator and a refrigerant suction port ( 14b ), from which a refrigerant is sucked by a high-speed refrigerant flow discharged from a jet port of the nozzle part; an evaporator ( 18 ), in which the refrigerant to be sucked into the refrigerant suction port is evaporated, the one evaporator having a plurality of tubes (FIG. 21 ) defining refrigerant passages through which a refrigerant passes with at least one liquid-phase refrigerant, and a container disposed above an inlet part of the plurality of refrigerant passages 18b for distributing a flow of the refrigerant to the refrigerant passages; and a retaining element disposed in the container above the inlet part ( 75 . 77 . 80 ) for temporarily storing the liquid-phase refrigerant flowing into the container therein, wherein the retaining element is provided to form a hole (Fig. 75a . 79 . 82 ), through which the liquid phase refrigerant passing from the retaining element falls to the inlet part. Cooling circuit device according to claim 10, further comprising a further evaporator ( 15 ) for vaporizing a refrigerant, wherein the another evaporator includes a refrigerant inlet connected to a refrigerant outlet of the ejector and a refrigerant outlet connected to a refrigerant suction side of the compressor; and one evaporator and the other evaporator apparatus are combined with the ejector. A refrigeration cycle apparatus according to claim 10 or 11, wherein the ejector with at least the an evaporator is combined. A refrigeration cycle apparatus according to claim 12, wherein the ejector in the container of the an evaporator is arranged. A refrigeration cycle apparatus according to claim 12, wherein the ejector with the one evaporator outside the one evaporator is combined. Cooling circuit device according to one of claims 10 to 14, further comprising a decompression element ( 17a ) combined with the one evaporator for decompressing the refrigerant flowing into the one evaporator. A refrigeration cycle device according to any one of claims 10 to 15, further comprising a gas / liquid separation device combined with said one evaporator ( 50 ) for separating the refrigerant after flowing the tubes of the one evaporator into a gas-phase refrigerant and the liquid-phase refrigerant. Cooling circuit device according to one of claims 10 to 16, wherein the retaining element comprises a mountain section projecting from a horizontal surface ( 75 ) having; the downcut and an inner wall surface of the container extending in a vertical direction have a recessed retaining portion (FIG. 76 ) in which the liquid-phase refrigerant is temporarily stored; and the mountain section of the retaining element a vertex area with the hole ( 75a ), through which the liquid-phase refrigerant stored in the retention section falls through the passage to the inlet part. A refrigeration cycle device according to any one of claims 10 to 16, wherein the retaining member comprises a tilt plate (14) inclined in the container with respect to a horizontal direction (Fig. 80 ) contains; and the tilt plate comprises: a lower part ( 80a ) forming, together with an inner wall surface of the container, a retaining portion in which the liquid-phase refrigerant is temporarily stored; and an upper part ( 80b ) with the hole ( 82 ), through which the liquid-phase refrigerant stored in the retention section falls to the inlet part by crossing over. Cooling circuit device according to one of claims 10 to 16, in which the retaining element is a plate element ( 77 ) with a recessed part ( 77a ) for defining a retention section in which the liquid-phase refrigerant is temporarily stored; and the plate member is separated from an inner wall of the container to the hole ( 79 ), through which the liquid-phase refrigerant stored in the retention section falls through the passage to the inlet part. A refrigeration cycle apparatus according to claim 15, wherein the decompression element and the Ejector pump with an evaporator are combined.