DE102006038462A1 - Refrigeration cycle device with an ejector and refrigerant manifold construction therefor - Google Patents

Abstract

There is provided a branching structure upstream of an ejector (18) in a refrigerant cycle device for branching and supplying a refrigerant to a nozzle (18a) of the ejector (18) and to an evaporator (22) connected to a refrigerant suction port (18b) of the ejector (18) , For example, the branching structure is constructed with an introduction pipe part (15a) for introducing the refrigerant and at least two arm parts branching from the introduction pipe part (15a). The two arm parts are substantially symmetrical with respect to the introduction pipe part (15a) while being positioned in substantially the same state with respect to a direction of gravity.

Description

BACKGROUND OF THE INVENTION

Field of the invention

The The present invention relates to a refrigeration cycle device having a Ejector pump and a refrigerant branch construction for branching a refrigerant flow in the refrigeration cycle device.

Out Japanese Patent No. 3322263 (corresponding to U.S. Patent No. 6,477,857 and US Pat. No. 6,574,987), a refrigeration cycle device is known, which contains a memory, the one with a downstream Side of an ejector pump is connected. In this refrigeration cycle device is an outlet for a liquid phase refrigerant the accumulator connected to an inlet of an evaporator, and an outlet of the evaporator is connected to a refrigerant suction port of Ejector pump connected.

In this conventional Circle becomes the refrigerant through a nozzle the ejector with a small passage area for the refrigerant decompressed and expanded, and the refrigerant flowing out of the evaporator is by means of a by a high-speed flow of the refrigerant during decompression and sucked the expansion caused pressure drop. The speed energy of the refrigerant during expansion, the diffuser is driven by a diffuser Pressure energy, resulting in an increase in the refrigerant pressure (suction pressure a compressor) results. This can be a drive energy of the Reduce compressor, thereby improving the efficiency of the circuit becomes.

In this circle hangs however, a flow rate the refrigerant supplied to the evaporator only of a suction capacity the ejector pump. Therefore, a small difference between causes high and low pressures of the cooling circuit a sinking of the inlet of the ejector, a deterioration the absorbency of the Ejector and a decrease in the flow rate of the refrigerant of the evaporator. Accordingly, it is for the Evaporator difficult to perform its cooling performance accurately.

Therefore propose the US 2005/0178150 A1 and the US 2005/0268644 A1 a A refrigeration cycle apparatus before, which is provided with a branching path that the refrigerant flow on an upstream Side of a nozzle an ejector pump can branch to a Ejektorpumpenansaugöffnung. Further is the branch channel with a throttle mechanism for adjusting the Pressure and flow rate of the refrigerant and an evaporator provided. Since the refrigerant flow upstream of the Ejector pump branches and the branched refrigerant sucked into a refrigerant suction port is, the branch channel is connected in parallel to the ejector. This can the refrigerant through the branch channel, which not only the refrigerant suction capacity of Ejector, but also the refrigerant suction and -ausgabevermögen of the compressor, to the evaporator feed. Even if an input level the ejector is reduced and the suction capacity of the Ejector pump drops, the degree of the Waste of the flow rate of the evaporator supplied refrigerant in this cooling circuit be made smaller.

In this refrigeration cycle device the diffuser of the ejector converts the velocity energy of the refrigerant in pressure energy to increase the pressure of the refrigerant. If only a vapor phase refrigerant with a smaller density than that of the liquid-phase refrigerant into the nozzle of the ejector flows, the speed energy of the refrigerant becomes small, which makes it difficult the pressure of the refrigerant to increase through the diffuser. As a result, the drive power of the compressor does not become easy reduced, whereby the efficiency of the cooling circuit is reduced.

The upstream of the nozzle the ejector pump branched off refrigerant contains generally the liquid phase refrigerant and the vapor-phase refrigerant. These phases differ from each other in their density and are therefore subject to an influence by gravity or a kinetic energy of the refrigerant, so that they are individual in the refrigerant be mixed. Therefore, the liquid-phase refrigerant is easily branched while it deflected to the evaporator side or to the nozzle side of the ejector becomes. The state of deflection of the vapor-phase and liquid-phase refrigerant can be according to a change the operating state of the circuit can be varied. This can be too changes in the flow rate ratio of branched refrigerant to lead.

Out For this reason, the liquid-phase refrigerant becomes in a branching section upstream of the nozzle of the ejector suitable branched so as not to the evaporator side or the nozzle side the ejector pump to be deflected so that the liquid phase refrigerant reliable to the nozzle side the ejector pump is passed. In the US 2005/0178150 A1 and the However, US 2005/0268644 A1 has no disclosure, such as a branching section from the point of view of supplying the Liquid phase refrigerant to the nozzle the ejector with reliability should be adjusted.

SUMMARY OF THE INVENTION

In In view of the above problems, it is an object of the present invention Invention, a liquid phase refrigerant from a branching section upstream of a nozzle of an ejector for reliable Nozzle the Ejector pump for a refrigeration cycle device to lead.

It Another object of the present invention is an ejector pump to work stably by having an influence of a distracted State of vapor-phase and liquid-phase refrigerants in a refrigeration cycle device is prevented.

It is a still further object of the present invention, a Influence of a deflected state of vapor-phase and liquid-phase refrigerants in a refrigeration cycle device to reduce.

It Yet another object of the present invention is a refrigeration cycle device to create with an ejector, which are operated stable can, while their circuit performance is improved.

According to one Aspect of the present invention includes a branch construction for branching and feeding a refrigerant to a nozzle an ejector and to a with a refrigerant suction of the Ejector connected to an evaporator inlet pipe part for introducing the refrigerant and at least two arm parts branching from the introduction pipe part. Further, the two arm parts are with respect to the introduction pipe part substantially symmetrical, with respect to a direction of gravity are positioned substantially in the same state. Therefore, if the branch construction for a refrigeration cycle device is used with the ejector, the ejector function by Reduce the fluctuation of the distribution difference between the vapor-phase and liquid-phase refrigerants be obtained stable. For example, the two arm parts are essentially arranged in a U-shape, one end of which is connected to the inlet pipe part.

According to one Another aspect of the present invention includes a branch construction for branching and feeding a refrigerant to a nozzle an ejector and to a with a refrigerant suction of the Ejector connected to an evaporator inlet pipe part for introducing the refrigerant and at least a first and a second branching part, the branch off from the inlet pipe part. Furthermore, the runs first branch part in an extension direction of the introduction pipe part, and the second branch part is substantially perpendicular to the extension direction of the introduction pipe part. Therefore, the refrigerant can stably move to the nozzle of the ejector be initiated. For example, the introduction pipe part is so positioned to be in the direction of gravity, and / or the second branching part is positioned so that it is in one horizontal direction from an extension of the introductory part runs.

According to one Still another aspect of the present invention includes a A refrigeration cycle apparatus a condenser for cooling and condensing a cold by, a branching section for branching a refrigerant flow downstream of the capacitor into a first and a second stream, an ejector, which is a nozzle for decompressing and expanding the refrigerant of the first stream from the branching section and a refrigerant suction port, from the refrigerant through one from the nozzle expelled High-speed refrigerant flow is sucked in, contains a throttle element for decompressing and expanding the refrigerant the second stream from the branching section and an evaporator for vaporizing the refrigerant decompressed by the throttle element, with an outlet coupled to the refrigerant suction port. In the refrigeration cycle device branches the branching section, the refrigerant flow so that a Proportion of a liquid phase refrigerant in one to the nozzle flowing refrigerant approximately equal to a proportion of a liquid phase refrigerant in a to the evaporator flowing refrigerant is. Therefore it is for the ejector pump possible, to work stably while an influence of a deflected state of vapor phase and liquid phase refrigerant in the cooling circuit device is prevented. For example, a flow direction of the branch portion to the nozzle flowing Refrigerant and a flow direction the refrigerant flowing from the branching section to the evaporator arranged essentially in the same plane. Alternatively they are the flow direction the refrigerant flowing from the branching portion to the nozzle and the flow direction the refrigerant flowing from the branching section to the evaporator substantially symmetrical to a flow direction of the branching section flowing refrigerant arranged. Further, the branch portion may be formed with an introduction pipe part for introducing the refrigerant and at least two arm parts branching from the introduction pipe part, be constructed. In this case, you can the two arm parts are substantially symmetrical to the inlet tube part be substantially in the same state with respect to a Direction of gravity are positioned.

According to one In still another aspect of the present invention, the branching portion branches the refrigerant flow such that a portion of a liquid phase refrigerant in a refrigerant flowing to the nozzle equal to or greater than a proportion of a liquid phase refrigerant in the refrigerant flowing to the evaporator is. In this case, the liquid refrigerant stably divided and the nozzle supplied to the ejector become. For example, a flow direction of the into the branching section flowing refrigerant on a substantially same line as a flow direction of the refrigerant flowing from the branching section to the nozzle. Alternatively, the flow direction of the refrigerant flowing from the branching portion to the nozzle substantially be oriented in a vertical direction down. Further For example, the branching section may be provided with an introduction pipe part for introduction of the refrigerant and at least a first and a second branching part, which branch off from the inlet pipe part, be constructed. In this Case, the first branch part in an extension direction of the introduction pipe part, and the second branch part may be substantially perpendicular to the extension direction of the introduction tube part run.

According to one Still another aspect of the present invention includes a A refrigeration cycle apparatus a compressor for compressing and discharging a refrigerant, a branching section for branching one from the compressor output refrigerant flow in a vapor phase state or a vapor / liquid two-phase state near a saturated steam line into a first and a second stream, a first condensation part for cooling and condensing the refrigerant of through the branching branched first stream, a second condensation part for cooling and condensing the refrigerant the branched by the branch portion second stream, an ejector, which is a nozzle for decompressing and expanding the from the first condensation part flowing refrigerant and a refrigerant suction port, from the the refrigerant through one of the nozzle expelled High-speed refrigerant flow is sucked in, contains a throttle element for decompressing and expanding the from the second condensation part flowing Refrigerant and an evaporator for evaporating through the throttle element decompressed refrigerant, which is coupled to the refrigerant suction port is. Because the refrigerant through the branching section prior to its decompression in the first and the second condensation part is branched, the refrigerant stable and accurate in both the nozzle the ejector and the throttle element are divided. For example, the branch portion between an output opening of the Compressor and an upstream Side of the first and second condensation part in a refrigerant flow be provided. Alternatively you can the first and the second condensation part being designed that they form a capacitor, and the branching section can on a refrigerant inlet side be provided within the capacitor.

According to one Still another aspect of the present invention includes a A refrigeration cycle apparatus a condenser for cooling and condensing a refrigerant, a vapor / liquid separator for separating the refrigerant on a downstream Side of the capacitor in a vapor-phase refrigerant and a liquid-phase refrigerant and let out of the liquid phase refrigerant therefrom, a branching section for branching a stream of the liquid phase refrigerant from the steam / liquid separator in a first and a second stream, an ejector, the one Nozzle for Decompressing and expanding the liquid refrigerant of the first stream and a refrigerant suction port, from the the refrigerant through one of the nozzle expelled High-speed refrigerant flow is sucked in, contains a throttle element for decompressing and expanding the liquid refrigerant of the second stream, and an evaporator for evaporating through the throttle element decompressed refrigerant, which is coupled to the refrigerant suction port is. Accordingly, the liquid refrigerant exactly to both the nozzle the ejector and the throttle element are supplied. For example, the branching section may be in a collecting vessel of the vapor / liquid separator be provided. Alternatively, the branching section may be attached to a downstream Side of a liquid phase refrigerant outlet the vapor / liquid separator may be arranged or the branch portion may be integral with be provided the ejector.

The above terms "im Substantially equal to "or" about the same "not only mean that the proportion of the liquid phase refrigerant completely identical in the refrigerant flowing to the ejector side to that of the liquid phase refrigerant in the refrigerant flowing to the evaporator side, but also, that these proportions may be substantially equal to each other, too with a little difference.

BRIEF DESCRIPTION OF THE DRAWINGS

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

1 a circuit structure of a refrigeration cycle device according to a first embodiment of the present invention;

2 a sectional view of a three-way connection of the refrigeration cycle device of the first embodiment;

3 a circuit structure of a refrigeration cycle device according to a second embodiment of the present invention;

4 a sectional view of a three-way connection of the refrigeration cycle device of the second embodiment;

5 a circuit structure of a refrigeration cycle device according to a third embodiment of the present invention;

6 a circuit structure of a refrigeration cycle device according to a fourth embodiment of the present invention;

7 a circuit structure of a refrigeration cycle device according to a fifth embodiment of the present invention;

8th Fig. 12 is a diagram for explaining a refrigerant state in a vapor-liquid two-phase state near a saturated steam line;

9 a circuit structure of a refrigerant cycle device according to a sixth embodiment of the present invention;

10 a sectional view of an ejector in the refrigerant cycle device of the sixth embodiment; and

11 a circuit structure of a refrigeration cycle device according to a seventh embodiment of the present invention.

DETAILED DESCRIPTION THE PREFERRED EMBODIMENTS

(First embodiment)

1 shows an example in which a refrigeration cycle device according to a first embodiment is used for a refrigeration system for a vehicle. The cooling system for a vehicle in the embodiment is configured to cool the interior of a room to a very low temperature, for example, about -20 ° C.

In an in 1 shown cooling circuit device 10 is a compressor 11 designed to aspirate, compress and dispense a refrigerant. The compressor 11 is provided by an engine for driving a vehicle (not shown) via an electromagnetic clutch 11a and a belt rotatably driven. In the embodiment, the compressor used is a swash plate type variable displacement compressor that can variably control an output capacity based on a control signal from outside.

Specifically, the pressure of a swash plate chamber (not shown) is used by using an output pressure and a suction pressure of the compressor 11 controlled to change a tilt angle of the swash plate, whereby a piston stroke is changed. This varies the output volume continuously in a range of about 0% to 100%. This change in the discharge volume can adjust a refrigerant discharge performance.

This Output volume is a geometric volume of a workspace for sucking and compressing the refrigerant and corresponds to one Cylinder volume, which is between a top dead center and a bottom Dead center of the piston stroke is defined.

The control of the pressure of the swash plate chamber will now be described. The compressor 11 contains an electromagnetic volume control valve 11b comprising therein a pressure responsive mechanism (not shown) for generating a force F1 by a low pressure of the refrigerant on the suction side of the compressor 11 and an electromagnetic mechanism (not shown) for generating an electromagnetic force F2 against the force F1 generated by the refrigerant pressure Ps.

The electromagnetic force F2 of the electromagnetic mechanism is determined by a control current In, which is described later by a climate control 23 is issued. The ratio of the high-pressure refrigerant to the low-pressure refrigerant introduced into the swash plate chamber is changed by a valve body (not shown) which is displaced in accordance with the force F1 corresponding to the refrigerant low pressure Ps and the electromagnetic force F2, thereby changing the pressure of the swash plate chamber.

Furthermore, the compressor can 11 vary its output volume continuously in the range of about 0% to 100% by adjusting the pressure of the swash plate chamber. Reducing the dispensing volume to about 0% allows the compressor 11 to be essentially out of service in one state. Therefore, the compressor can 11 have a clutchless construction, in which one Rotary shaft of the compressor 11 is constantly connected to a vehicle engine via a pulley or a belt V.

The capacitor 12 is a heat exchanger connected to the discharge side of the compressor 11 connected to exchange heat between that of the compressor 11 discharged high pressure refrigerant and one by a blower 12a for the condenser blown outside air (air outside the vehicle interior) and for condensing the high-pressure refrigerant by dissipation of the heat from the refrigerant. The fan 12a for the capacitor is powered by an electromagnetic motor 12b driven to drive, which is adapted to be rotatably driven when connected to a voltage output from the climate control 23 is created.

An indoor heat exchanger 13 is with a refrigerant downstream side of the condenser 12 via a refrigerant pipe 14a connected and exchanges heat between the from the condenser 12 flowing high pressure refrigerant and into the compressor 11 sucked low pressure refrigerant off. The heat exchange between the refrigerant at the indoor heat exchanger 13 leaves the refrigerant after flowing through the refrigerant pipe 14 be cooled, and therefore, a difference of the enthalpy (cooling capacity) of the refrigerant between an inlet and an outlet of the evaporators 19 . 22 , which will be described later, are increased.

The refrigerant pipe 14 is from a refrigerant pipe 14a for connecting the capacitor 12 with the indoor heat exchanger 13 and a refrigerant pipe 14b for connecting the indoor heat exchanger 13 with the three way connection 15 built up. The three way connection 15 is a pipe joint that is the one from the refrigerant pipe 14b flowing refrigerant into a refrigerant pipe 16 for passing the refrigerant to the nozzle 18a the ejector pump 18 , as described later, branches, and a branch pipe 17 for guiding the refrigerant to the refrigerant suction port 18b ,

The details of the three way connection 15 will be referred to below with reference to 2 specified. The three way connection 15 is made of the same material (for example, aluminum) as the refrigerant pipes 14 and 16 and the branch pipe 17 made. The three-way connection consists of a Einleitungsrohrteil 15a having a substantially linear shape and a branch pipe part 15b with a substantially U-like shape.

One end of the inlet pipe part 15a is with the refrigerant pipe 14b connected, and the other end is with a connection hole 15c connected substantially at a center of a U-shaped bottom of the branch pipe part 15b is arranged. One end of the branch pipe part 15b is with the refrigerant pipe 16 connected, and the other end is with a branch pipe 17a connected. These connections are made by brazing so as to prevent leakage of the refrigerant.

That is, as in 2 shown, the three-way connection 15 is constructed to have a branch portion (branching area) A on the refrigerant downstream side of the communication hole 15c has. Further, in this embodiment, a flow direction of the branch portion A to the refrigerant pipe 16 flowing refrigerant (the direction of an arrow B in 2 ) and a flow direction of the branching section A to the branch pipe 17a flowing refrigerant (the direction of an arrow C in 2 ) substantially symmetrical with respect to a flow direction of the in the three-way connection 15 flowing refrigerant. Further, the direction of the arrow B and the direction of the arrow C are both positioned in a substantially horizontal plane.

In this embodiment, the introduction pipe part 15a a straight pipe and may be of sufficient length to direct the flow of refrigerant into a straight stream. The branch pipe part 15b provides at its center the branching section A serving as a connecting part to which the introducing pipe part 15a opened and connected. The branch pipe part 15b provides two arms leading to a tube axis of the inlet tube part 15a , ie to an axis of extension of the pipe part 15a , symmetrical.

These arm parts of the branch pipe part 15b are positioned so that the refrigerant flows to the tube axis of the inlet tube part 15a are symmetrical. Therefore, the curved shapes of the refrigerant streams are in the two arm pipes of the branch pipe part 15b in the horizontal and vertical directions symmetrical to each other. For example, the two arm pipes may be arranged in the same plane so that respective parts of both arm pipes are positioned at the same height from each other as viewed from the branching section A. For example, the two arm tubes can be arranged in the same horizontal plane.

As a result, from the viewpoint of the branching section A, the distribution of the vapor-phase refrigerant and the liquid-phase refrigerant in both arm pipes and the distribution fluctuations in both arm pipes are symmetrical. This can reduce the influences of the distribution and the fluctuations, so that the refrigerant is divided in a predetermined ratio in both arm pipes can. For example, the distribution of the vapor-phase and liquid-phase refrigerants occurs at each arm part in the same manner and is changed at each arm part in the same way even if the operating state of the circuit is changed.

Then the other end of the refrigerant pipe 16 with the ejector pump 18 connected. The ejector pump 18 serves as a decompressing means for decompressing the refrigerant, and as a refrigerant transport and circulation means for circulating the refrigerant by an aspirating action (trapping action) of the high-velocity expelled refrigerant flow.

The ejector pump 18 contains the nozzle 18a for decompressing and expanding the refrigerant isentropically by throttling a path surface of the refrigerant via the refrigerant pipe 16 flowing refrigerant to a small level, and in conjunction with a refrigerant discharge port of the nozzle 18a provided refrigerant suction port 18b , The refrigerant suction port 18b is for sucking the vapor-phase refrigerant from the second evaporator 22 provided as described later.

Downstream of the nozzle 18a and the refrigerant suction port 18b is a mixing section 18c for mixing the high-speed refrigerant flow from the nozzle 18a and the sucked refrigerant from the refrigerant suction port 18b intended. A diffuser 18d serving as a pressure increasing portion is downstream of the mixing portion 18c intended.

The diffuser 18d is formed in a shape that gradually increases the path area of the refrigerant, and has a function of braking the refrigerant flow to increase the refrigerant pressure, that is, a function for converting speed energy of the refrigerant into pressure energy.

A first evaporator 19 is with the refrigerant downstream side of the diffuser 18d the ejector pump 18 connected. The first evaporator 19 is a heat sink that is designed to transfer heat between the refrigerant and that through a blower 19a to exchange for the evaporator blown air and to show a heat absorption effect by evaporation of the refrigerant. The fan 19a for the evaporator is by an electric motor 19b driven, and the electric motor 19b is powered by rotation when the climate control 23 output voltage is applied.

With the refrigerant downstream side of the first evaporator 19 is a store 20 (Gas / liquid separator) connected. The reservoir is a vapor-liquid separator for separating the refrigerant into liquid-phase and vapor-phase refrigerants. An outlet for the vapor-phase refrigerant of the store 20 is above the indoor heat exchanger described above 13 with a suction side of the compressor 11 connected.

The branch pipe 17 is a pipe for connecting the three-way connection 15 with the refrigerant suction port 18b the ejector pump 18 , In the branch pipe 17 are a solid throttle 21 and the second evaporator 22 arranged. The branch pipe 17 is from the branch pipe 17a for connecting the three-way connection 15 and the fixed throttle 21 , a branch pipe 17b for connecting the fixed throttle 21 and the inlet of the second evaporator 22 and a branch pipe 17c for connecting the outlet of the second evaporator 22 and the refrigerant suction port 18b built up.

The fixed throttle 21 performs flow rate adjustment and decompression of the refrigerant entering the second evaporator 22 flows through, and is constructed in this embodiment, for example, from an aperture. It is obvious that the fixed throttle can also be formed from a capillary tube.

The second evaporator 22 is a heat sink for evaporating the refrigerant and exhibiting a heat absorbing effect. In this embodiment, the first evaporator 19 and the second evaporator 22 integrally connected. In particular, the components of the first evaporator 19 and the second evaporator 22 made of aluminum and soldered together integrally.

Therefore, flows through the above blower 19a for the evaporator blown air in a direction of an arrow D. First, the blower through the 19a blown air through the first evaporator 19 cooled, and then through the second evaporator in the air flow direction. That is, the same room to be cooled is through the first evaporator 19 and the second evaporator 22 cooled.

Climate control (climate ECU) 23 is composed of the known microcomputers including a CPU, a ROM and a RAM, and peripheral circuits. The climate control 23 performs various kinds of calculations and processes based on a control program stored in the ROM, thereby performing the functions of the above various devices 11a . 11b . 12b and 19b to control.

Furthermore, the climate control receives 23 Measurement signals from various sensors and various types of operation signals input to an operation panel (not shown). As a group of sensors, for example, an outside air sensor or the like for detecting a temperature of the outside air (a temperature of the air outside the vehicle) is provided. The operation panel is provided with a temperature setting switch for setting a cooling temperature of the space to be cooled and an air conditioning operation switch or the like for outputting an operation command signal of the compressor 11 Mistake.

An operation of the refrigeration cycle device having the above arrangement according to the embodiment will now be described. When an air conditioner switch is turned on, the electromagnetic clutch becomes 11a based on a control output from the climate control 23 energized and then engaged, so that a rotational driving force from an engine for driving a vehicle on the compressor 11 is transmitted.

When a control current In from the climate control 23 based on the control program to the electromagnetic volume control valve 11b is discharged, the compressor sucks 11 the vapor-phase refrigerant and compresses it to output the compressed refrigerant therefrom.

That through the compressor 11 compressed and discharged through it high temperature / high pressure vapor phase refrigerant flows into the condenser 12 , In the condenser, the high-temperature / high-pressure refrigerant is cooled by the outside air and condensed. The high-pressure refrigerant after flowing through the condenser 12 and after a heat radiation exchanges in the indoor heat exchanger 13 Heat with one from the store 20 flowing low pressure vapor phase refrigerant.

The refrigerant flow from the indoor heat exchanger 13 flows into the three-way connection 15 , That in the three way connection 15 flowing refrigerant is in the via the refrigerant pipe 16 to the ejector pump 18 directed refrigerant flow and the over the branch pipe 17a to the fixed throttle 21 divided refrigerant flow divided.

The three way connection 15 is arranged so that the flow direction of the branching section A to the refrigerant pipe 16 flowing refrigerant (the direction of arrow B in 2 ) and the flow direction of the branching section A to the branch pipe 17a flowing refrigerant (the direction of the arrow C in 2 ) are aligned on a substantially horizontal plane. That's how it gets into the three-way connection 15 flowing liquid phase refrigerant without being affected by gravity divided.

The direction of the arrow B and the direction of the arrow C are substantially symmetrical to the refrigerant flow direction from the refrigerant pipe 14b in the three way connection 15 , That in the three way connection 15 flowing refrigerant is without being affected by a kinetic energy in the flow direction of the refrigerant from the refrigerant pipe 14b to the branch portion A in the side of the refrigerant pipe 16 and the side of the branch pipe 17a divided.

In this embodiment, two arm parts of the three-way connection 15 symmetrical to the inlet pipe part 15a formed and positioned from the viewpoint of the branching section A at the same height or the like. Therefore, these arm parts are positioned in the same state from the viewpoint of the branching section A with respect to the direction of gravity. This reduces the difference in the distribution of the vapor-phase and liquid-phase refrigerants caused by gravity between the interiors of the respective arm portions respectively extending from the branch portion A, and also reduces the fluctuation of the distribution difference, so that the refrigerant in each arm at a predetermined Ratio can be divided.

Therefore, the refrigerant at the branch portion A is branched so that a proportion of a liquid-phase refrigerant in the nozzle 18a the ejector pump 18 flowing refrigerant substantially equal to that of a liquid-phase refrigerant in the side of the second evaporator 22 flowing refrigerant. As a result, the liquid-phase refrigerant can reliably enter the nozzle 18a the ejector pump 18 be directed.

That into the ejector 18 flowing refrigerant is through the nozzle 18a decompressed and stretched. In the decompression and expansion, the pressure energy of the refrigerant is converted into the velocity energy, whereby the refrigerant flows at high speed from the discharge port of the nozzle 18a is ejected. The ejector pump 18 sucks the refrigerant after flowing through the second evaporator 22 from the refrigerant suction port 18b at.

That from the nozzle 18a discharged refrigerant and into the refrigerant suction port 18b sucked refrigerants are through the mixing section 18c downstream of the nozzle 18a mixed to get into the diffuser 18d to stream. In this diffuser 18d the expansion of the refrigerant path surface converts the speed energy of the refrigerant into its pressure energy so as to increase the pressure of the refrigerant.

In the present embodiment, the liquid phase refrigerant reliably enters the nozzle of the ejector 18 so the diffuser 18d its pressure-increasing ability can show well, whereby the deterioration of the efficiency of the circuit is prevented.

That from the diffuser 18d the ejector pump 18 flowing refrigerant flows into the first evaporator 19 where the low-pressure refrigerant releases heat from the blower 19a absorbed air blown for the evaporator and then evaporated. The refrigerant after flowing through the first evaporator 19 flows into the store 20 to be separated into the vapor-phase refrigerant and the liquid-phase refrigerant.

That from the store 20 flowing vapor phase refrigerant flows into the indoor heat exchanger 13 to heat with the through the refrigerant pipe 14 replaced high-pressure refrigerant. Then this will be out of the indoor heat exchanger 13 flowing vapor phase refrigerant into the compressor 11 sucked to be compressed again.

On the other hand, that gets into the branch pipe 17 flowing refrigerant through the fixed throttle 21 to become the low-pressure refrigerant that enters the second evaporator 22 flows. In the second evaporator 22 The low pressure refrigerant passing through absorbs heat from the first evaporator 19 cooled air and then evaporated.

Then the refrigerant that is on the second evaporator 22 evaporated, from the refrigerant suction port 18b the ejector pump 18 sucked in and then with the through the nozzle 18a reaching liquid phase refrigerant at the mixing section 18c mixed to get into the first evaporator 19 to stream.

As mentioned above, in this embodiment, since the refrigerant on the downstream side of the diffuser 18d the ejector pump 18 the first evaporator 19 can be supplied and the refrigerant on the side of the branch pipe 17 the second evaporator 22 over the fixed throttle 21 can be supplied, the first evaporator 19 and the second evaporator 22 provide the cooling capacity at the same time.

Here, the refrigerant evaporation pressure of the first evaporator is 19 a pressure of the refrigerant after the pressure increase through the diffuser 18d , And the outlet of the second evaporator 22 is with the refrigerant suction port 18b the ejector pump 18 connected. Therefore, the lowest pressure after decompression through the nozzle 18d on the second evaporator 22 be applied. Thus, the refrigerant evaporation pressure (the refrigerant evaporation temperature) of the second evaporator 22 lower than that (those) of the first evaporator 19 be.

Further, since the liquid-phase refrigerant reliably flows from the branch portion A to the nozzle 18a the ejector pump 18 can be passed, the pressure increasing effect of the diffuser 18d shown and the suction pressure of the compressor 11 increase. As a result, a compression work by the compressor 11 be reduced, thereby showing an energy saving.

Second Embodiment

In the second embodiment, as in FIG 3 shown, a three-way connection 30 used, which is constructed of connecting tubes, each having a substantially straight shape. The second embodiment may be the same as the first embodiment in the components other than the above connection.

The details of the three way connection 30 be referring to 4 described. The material of the three way connection 30 is the same as that of the first embodiment, and the three-way connection 30 is from an input / output pipe part 30a having a substantially straight shape and a branch pipe part 30b constructed with a substantially straight shape. The input / output pipe part 30a extends vertically and has an upper and a lower part with respect to the branching section E. The upper part of the input / output pipe part 30a provides an inlet pipe part. The lower part of the branch pipe part 30a and the branch pipe part 30b provide branching arm parts from the introduction pipe part.

One end of the input / output pipe part 30a is with the refrigerant pipe 14b connected, and the other end of it is with the refrigerant pipe 16 connected. Further, substantially in the middle of the input / output pipe part 30a one with the branch pipe part 30b connected connection hole 30c intended. One end of the branch pipe part 30b is with the input / output pipe part 30a at the connection hole 30c connected, and the other end is branch pipe with the United 17a connected. These connections are made by soldering to prevent refrigerant leakage.

Therefore, the branch portion (branch portion) E is in the vicinity of the communication hole 30c educated. Further, in a refrigeration cycle device of this embodiment, the three-way geverbindung 30 arranged such that a flow direction of the refrigerant pipe 14b to the branching section E flowing refrigerant (the direction of an arrow F in 4 ) and a flow direction of the branching section E to the refrigerant pipe 16 flowing refrigerant (the direction of the arrow G in 4 ) are set down on the same straight line in the vertical direction.

An operation of the embodiment having the above arrangement will now be described. Similar to the first embodiment, that is from the compressor 11 discharged refrigerant through the condenser 12 cooled and condensed. The cooled refrigerant passes through the internal heat exchanger 13 and then flows into the three-way connection 30 to get into a via the refrigerant pipe 16 to the ejector pump 18 directed refrigerant flow and one via the branch pipe 17 to the fixed throttle 21 directed refrigerant flow to be shared.

The three way connection 30 is arranged such that the flow direction of the refrigerant pipe 14b to the branching section E flowing refrigerant and the flow direction of the branching section E to the refrigerant pipe 16 flowing refrigerant are oriented on the same straight line in the vertical direction downwards. Therefore, this flows out of the refrigerant pipe 14 in the three way connection 30 flowing liquid phase refrigerant due to the kinetic energy and gravity probably from the branching section E to the refrigerant pipe 16 instead of the branching section E to the refrigerant pipe 17a ,

In this way, the proportion of the liquid-phase refrigerant in the branching section E to the nozzle 18a the ejector pump 18 over the refrigerant pipe 16 flowing refrigerant substantially equal to or greater than that of the liquid-phase refrigerant in the via the branch pipe 17a to the second evaporator 22 be flowing refrigerant.

The ejector pump 18 has the suction effect and the pressure increasing effect of the branching section E to the nozzle 18a the ejector pump 18 flowing refrigerant, as in the case of the first embodiment. In addition, the first evaporator has the cooling effect of this refrigerant, which then returns to the compressor 11 is sucked. The second evaporator 22 has the cooling capacity of the branching section E to the second evaporator 22 flowing refrigerant, as in the case of the first embodiment, while the refrigerant in the refrigerant suction port 18b the ejector pump 18 is sucked.

In this embodiment, the lower part of the input / output pipe part 30a , which is one of the arm parts, as an extension from the upper part of the input / output pipe part 30a , which is an inlet pipe, extended. In addition, the branch pipe part 30b which is the other of the arm parts, extended substantially perpendicular to the extension of the introduction pipe part. The inlet pipe is positioned in the direction of gravity. The branch pipe part 30b , which is the other of the arm parts, is horizontally positioned from the extension of the inlet tube.

As mentioned above, the first evaporator 19 and the second evaporator 22 perform the cooling effect at the same time. In addition, the refrigerant evaporation pressure (the refrigerant evaporation temperature) of the second evaporator may be 22 lower than that (those) of the first evaporator 19 be made.

Furthermore, this flows from the refrigerant pipe 14b in the three way connection 30 flowing refrigerant rather to the nozzle 18a the ejector pump 18 out. For example, even if a cooling load is small, or even if a refrigerant flow rate or speed in a home-use or commercial refrigerator or the like is small, the liquid-phase refrigerant can be exactly due to the kinetic energy of the refrigerant and gravity to the nozzle 18a be directed. As a result, this embodiment can achieve the effect described in the first embodiment.

(Third Embodiment)

Although in the first embodiment, the three-way connection 15 for branching the refrigerant flow downstream of the condenser 12 is arranged, the invention is not limited thereto. In this embodiment, as in FIG 5 shown, the three-way connection described in the first embodiment 15 and the capacitor 12 not provided, instead are a capacitor 31 and a branching section H for branching the refrigerant at a position between a refrigerant discharge port of the compressor 11 and a refrigerant inlet of the condenser 31 intended. This branching section H is used to control the refrigerant flow using the same pipe connection as the three-way connection 15 branch of the first embodiment.

The capacitor 31 is a heat exchanger for exchanging heat between that of the compressor 11 discharged high pressure refrigerant and one through the blower 31a for the condenser blown outside air (ie air outside the interior of the vehicle) to the high pressure refrigerant to cool and condense. The fan 31a for the capacitor is powered by an electric motor 31b powered, which is designed to be driven when the climate control system 23 output voltage is applied.

Next contains the capacitor 31 a first condensation part 31c and a second condensation part 31d , One of the refrigerant streams branched by the branching portion H is connected to the inlet of the first condensing part 31c of the capacitor 31 connected, and the other refrigerant flow is with the inlet of the second condensation part 31d connected.

The first condensation part 31c radiates heat only from one of the branched by the branch portion H refrigerant to condense the one refrigerant, and the second condensation part 31d radiates heat only from the other of the branched by the branch portion H refrigerant to condense the other, whereby in the first condensation part 31c flowing refrigerant and that in the second condensation part 31d flowing refrigerant can not be mixed together.

In this embodiment, the first condensation part 31c and the second condensation part 31d Combined vertically via a clamp with a screw vertically. The fan 31a for the condenser is arranged so that it is the refrigerant of both the first condensation part 31c as well as the second condensation part 31d cools at the same time.

The refrigerant outlet of the first condensation part 31c is with the refrigerant pipe 16 connected and the refrigerant outlet of the second condensation part 31d is with the refrigerant pipe 17a connected. In this embodiment, the first evaporator is 19 not provided and only one evaporator 22 performs the cooling process, which builds the circuit. To simplify the system is the indoor heat exchanger 31 in the 5 not shown circle provided. However, the third embodiment may be the same as the first embodiment in the other components other than the above connection.

An operation of the third embodiment with the above arrangement will now be described. That from the compressor 11 discharged refrigerant is in the first condensation part 31c and the second condensation part 31d divided. Here, the refrigerant at the branch portion H is a from the compressor 11 discharged vapor phase refrigerant containing no liquid phase refrigerant.

Thus, the vapor-phase refrigerant at the branch portion H can be appropriately into the first condensing part without being affected by the kinetic energy and the gravity 31c and the second condensation part 31d be split. The high-temperature / high-pressure vapor-phase refrigerant is generated by the outside air at the first condensation part 31c cooled and condensed, and also, the high-temperature / high-pressure vapor-phase refrigerant by the outside air at the second condensation part 31d cooled and condensed.

That from the first condensation part 31c flowing liquid-phase refrigerant flows over the refrigerant pipe 16 in the nozzle 18a the ejector pump 18 , and the ejector pump 18 has the suction effect and the pressure increasing effect of the cold by means of what the refrigerant in the memory 20 flow and back into the compressor 11 can be sucked.

On the other hand, this will be from the second condensation part 31d flowing liquid phase refrigerant through the fixed throttle 21 over the branch pipe 17a to low pressure refrigerant to enter the evaporator 22 to stream. In the evaporator 22 The low pressure refrigerant passing through absorbs heat from the fan 19a for the evaporation blown air and then evaporates. That from the evaporator 22 flowing refrigerant is in the refrigerant suction port 18b the ejector pump 18 sucked and with the through the nozzle 18a liquid phase refrigerant passed through the mixing section 18c mixed to get into the store 20 to stream.

As mentioned above, in this embodiment, the branching portion H is between the refrigerant discharge port of the compressor 11 and the refrigerant inlet of the condenser 31 arranged so that the vapor-phase refrigerant containing no liquid-phase refrigerant can branch at the branch portion H accordingly.

Further, after the branching of the refrigerant in the condenser 31 Heat radiated so that the refrigerant in the first and second condensation part 31c . 31d condensed. This can reliably supply the liquid-phase refrigerant to the nozzle 18a the ejector pump 18 conduct. As a result, the refrigerant pressure on the diffuser 18d the ejector pump 18 increases, whereby the driving energy of the compressor is reduced, which allows an improvement in the efficiency of the circuit.

(Fourth Embodiment)

Although, in the third embodiment, the branching section H is for branching the refrigerant flow between the refrigerant discharge port of the compressor 11 and the refrigerant leave the capacitor 31 is arranged, the invention is not limited thereto. In this embodiment, as in FIG 6 shown, the branch portion H and the capacitor 31 not provided, but a capacitor 32 is planned.

The capacitor 32 is a heat exchanger for heat exchange between that of the compressor 11 discharged high-pressure refrigerant and by the blower 12a external air blown to the condenser to condense the high pressure refrigerant by dissipating the heat from the refrigerant. The fan 32a for the capacitor is powered by an electric motor 32b driven, which is adapted to be rotatably driven when the of the climate control 23 output voltage is applied.

Next is in the condenser 32 a branching section I for branching the flow of the compressor 11 output high-pressure refrigerant provided while the heat is radiated. The capacitor 32 contains a first condensation part 32c for radiating heat from one of the branched branched by the branch portion I refrigerant to condense the one refrigerant, and a second condensing part 32d for radiating heat from the other of the branched refrigerants to condense the other.

The branch portion I is on the refrigerant inlet side in the condenser 32 arranged. At the branching section I, the heat is not sufficiently radiated from the refrigerant at the branching section I, and therefore, the refrigerant is in a vapor-phase state or in a vapor-liquid two-phase state near a saturated vapor line, as in FIG 8th shown. That is, in the condenser 32 can be a heat exchanger 32e small capacity upstream of the branching section I can be arranged.

The first condensation part 32c radiates heat only from one of the branched by the branch portion I refrigerant to condense the one refrigerant, and the second condensation part 32d radiates heat only from the other of the branched by the branch portion I refrigerant to condense the other, so that in the first condensation part 32c flowing refrigerant and that in the second condensation part 32d flowing refrigerant can not be mixed together.

The first condensation part 32c and the second condensation part 32d are vertically integrally connected in the same manner as in the third embodiment.

The fan 32a for the condenser is arranged so that the refrigerant both in the first condensation part 32c as well as in the second condensation part 32d can be cooled simultaneously. Further, the refrigerant outlet of the first condensation part 32c with the refrigerant pipe 16 connected, and the refrigerant outlet of the second condensation part 32d is with the branch pipe 17a connected.

The refrigeration cycle with this arrangement of the embodiment is operated to that of the compressor 11 discharged refrigerant into the condenser 32 flow and through the branching section I in the condenser 32 in the first condensation part 32c and the second condensation part 32d to branch.

The refrigerant at the branch portion I is on the refrigerant inlet side in the condenser 32 and is therefore in the vapor phase state or in the vapor / liquid two-phase state near the saturated steam line without being sufficiently cooled. Thus, the refrigerant at the branching section I is a vapor-phase refrigerant containing no liquid-phase refrigerant or containing only a small amount of liquid-phase refrigerant.

Accordingly, the branching section I may introduce the vapor-phase refrigerant into the first condensing part 32c and the second condensation part 32d branch. At the first condensation part 32c The high-temperature / high-pressure vapor-phase refrigerant is cooled and condensed by the outside air, and that of the first condensation part 32c flowing liquid-phase refrigerant flows over the refrigerant pipe 16 in the nozzle 18a the ejector pump 18 , Thus, the liquid-phase refrigerant can reliably reach the nozzle 18a the ejector pump 18 be directed. This embodiment can achieve the same effect as the third embodiment.

(Fifth Embodiment)

In the fifth embodiment, as in FIG 7 shown, the capacitor 12 similar to the first embodiment, and a vapor / liquid separator 33 for dividing the refrigerant into a vapor phase and a liquid phase refrigerant is downstream of the condenser 12 intended.

Next are the refrigerant pipe 16 and the branch pipe 17a with a liquid-phase refrigerant outlet of the vapor-liquid separator 33 connected. Therefore, in this embodiment, a branch portion J is in a liquid-phase refrigerant storage in the vapor-liquid separator 33 intended. The fifth Embodiment may be the same as the third embodiment in the components other than the above components.

The refrigeration cycle device having the above arrangement of the embodiment is operated to be that of the compressor 11 discharged refrigerant through the condenser 12 cooled and through the vapor / liquid separator 33 be separated in vapor phase and liquid phase refrigerant. The in the steam / liquid separator 33 stored liquid-phase refrigerant becomes the side of the ejector 18 and to the side of the evaporator 22 branched. As a result, the liquid-phase refrigerant can reliably reach the nozzle 18a the ejector pump 18 be directed. This embodiment can achieve the advantages similar to those of the third embodiment.

Further, although in this embodiment, the branch portion J is disposed in the liquid-phase refrigerant receiver, the invention is not limited thereto. Alternatively, a branch portion in the pipe may be downstream of a liquid-phase refrigerant outlet of the vapor-liquid separator 33 be provided, and the refrigerant pipe 16 and the refrigerant pipe 17a can be connected to each other. Also in this case, the same effect as in the third embodiment can be achieved.

For example, a condenser having a condensation part, a vapor-liquid separation cell, and a sub-cooling part sequentially arranged along the refrigerant flow may be used as a condenser 12 be used. In addition, a branch portion may be provided downstream of the supercooling part. By this arrangement, one end of the refrigerant pipe 16 be opened into a range for the liquid-phase refrigerant of the refrigerant path, so that the liquid-phase refrigerant reliably to the ejector 18 can be directed.

As a result, even if the size and shape of each component can be the ejector 18 is set assuming that the liquid-phase refrigerant to the nozzle 18a is passed, the function of the ejector 18 be reliably provided. In another aspect, the ends of the refrigerant tube 16 and the branch pipe 17 to the liquid-phase refrigerant region of the refrigerant path, thereby reducing uneven distribution of the vapor-phase and liquid-phase refrigerants and an influence of fluctuations in the uneven distribution. This can branch the refrigerant in a predetermined ratio.

(Sixth Embodiment)

Although in the first embodiment, the refrigerant flow through the three-way connection 15 is branched, the invention is limited thereto. In this embodiment, as in FIG 9 shown, the three-way connection 15 , the refrigerant pipe 16 and the ejector pump 18 not provided, and an ejector pump 40 with a branching section therein is provided.

First, the ejector 40 with reference to 10 described. The ejector pump 40 is a variable flow rate ejector and is made from a housing 40a , a nozzle 40b , a diffuser 40c and a path surface adjustment mechanism 41 built up. The housing 40a is used to attach and hold the components of the ejector 40 , The housing 40a is with a refrigerant flow inlet 40d through which the refrigerant from the refrigerant pipe 14b into the ejector pump 40 flows, a branch refrigerant flow outlet 40e through which the inlet 40d flowing refrigerant to a branching path 17a flows, and a refrigerant suction port 40f , which in conjunction with a refrigerant jet hole 40h the nozzle is provided, as described later, and which for sucking the refrigerant from the branching path 17c is formed, provided.

Here, the refrigerant flow inlet 40d with the refrigerant pipe 14b connected, the branch refrigerant flow outlet 40e is with the branch path 17a connected, and the refrigerant suction port 14f is with the branch path 17c connected. These parts are connected by brazing so as to prevent refrigerant leakage from the joints.

The nozzle 40b is configured to isentropically decompressing and expanding the refrigerant by throttling the path area of the refrigerant to a small level, and is fixed within the housing.

As in 10 shown is the nozzle 40b with a refrigerant inflow hole 40g that the refrigerant flow inlet 40d and the inside of the nozzle 40b connects and through which the refrigerant in the nozzle 40b flows, the refrigerant jet hole 40h through which the from the refrigerant inflow hole 40g in the nozzle 40b flowing refrigerant to a mixing section 40j is discharged as described later, and a branch refrigerant outflow hole 40i that with the interior of the nozzle 40b and the branch refrigerant flow outlet 40e communicates.

This flows out of the refrigerant inflow hole 40g in the nozzle 40b flowing refrigerant from the refrigerant jet hole 40h and the branch refrigerant outflow hole 40i from the nozzle 40b out. In this embodiment, a branch portion (branch portion) K is in the vicinity of the branch refrigerant outflow hole 40i in the nozzle 40b constructed as in 10 shown.

On the refrigerant downstream side of the refrigerant jet hole 40h in the case 40a is the mixing section 40j intended. The mixing section 40j mixes this from the refrigerant jet hole 40h discharged refrigerant and that of the refrigerant suction port 40f sucked in refrigerant.

The serving as a pressure increasing section diffuser 40c is on the refrigerant downstream side of the mixing section 40j arranged. The diffuser 40c is formed in a shape that gradually increases the path area of the refrigerant, and performs a function of decelerating the refrigerant flow to increase the refrigerant pressure, that is, a function of converting the speed energy of the refrigerant into the pressure energy.

Furthermore, the diffuser contains 40c a diffuser outlet 40l through which the through the diffuser 40c reached refrigerant flows out. It should be noted that the diffuser 40c by soldering or the like, so as to prevent a refrigerant leakage. The diffuser may be integral with the housing by a cutting work or the like 40a be formed.

The path surface adjustment mechanism 41 is over the top of the nozzle 40b of the housing 40a (in the by the arrow of 10 indicated upward direction) with a screw or the like via a gasket or the like, so as to prevent the refrigerant leakage. The ejector pump 40 and the path surface adjustment mechanism 41 are integrally formed.

The path surface adjustment mechanism 41 contains a needle 41a and a drive section 41b , The needle 41a contains a slender sharp tip with a substantially similar shape to that of an inner path of the nozzle 40b as well as one with a rotor 41c connected axle part. The axis part of the needle 41a is with the rotor 41c connected with a helical connection. Therefore, the rotation of the screw-type connection allows movement of the axial part of the needle 41a in a longitudinal direction in the nozzle (in a direction indicated by the arrow in FIG 10 indicated vertical direction (top / bottom direction)).

The drive section 41b is constructed from a known stepper motor. When a control signal (pulse signal) from the climate control 23 is output, the rotor is 41c of the drive section 41b turned. If the rotor 41 turns, the helical connection rotates on the side of the rotor 41c what the needle 41a lets move. Therefore, when the needle 41a the refrigerant jet hole 40h (in a by the arrow in 10 indicated upward direction), the flow rate of the refrigerant jet hole 40h ejected refrigerant decreases. If the needle 41a but away from the refrigerant jet hole 40h (in a by the arrow in 10 indicated upward direction), the flow rate of the refrigerant jet hole becomes 40h ejected refrigerant increases.

In contrast, the branching refrigerant outflow hole is 40i arranged at such a position that, even if the needle 41a is moved, the flow rate of the branched by the branch refrigerant outflow hole 40i flowing refrigerant is not changed. Further, the ejector is 40 arranged such that in the cooling circuit device 10 This embodiment, the path surface adjustment mechanism 41 is oriented in the vertical direction upwards and the diffuser 40c aligned in the vertical direction downwards.

So are the flow direction of the refrigerant from the refrigerant pipe 14b to the branching section K (the direction of the arrow L in FIG 10 ) and the flow direction of the refrigerant from the branch portion K to the branch pipe 17a (the direction of an arrow M in 101 aligned horizontally. The flow direction of the refrigerant from the branch portion K to the refrigerant jet hole 40h (the direction of an arrow N in 10 ) is oriented downwards in the vertical direction (up / down direction).

In the sixth embodiment, the refrigerant flow direction to the nozzle means 40b a direction of the branching section K to the refrigerant jet hole 40h flowing refrigerant. The sixth embodiment may be the same as the first embodiment in the components other than the above components.

An operation of the sixth embodiment with the above arrangement will now be described. That from the compressor 11 output refrigerant is similar to the first embodiment by the capacitor 12 cooled and condensed. The condensed refrigerant passes through the internal heat exchanger 13 to get into the ejector 40 to flow, and in the branching section K to the branch pipe 17a directed refrigerant flow and in the refrigerant jet hole 40h split oriented refrigerant flow.

The climate control 23 gives the control signal to the path surface adjustment mechanism 41 so that a supercooling degree of the refrigerant on the outlet side of the condenser 12 is in a predetermined range, and then sets the flow rate of the refrigerant jet hole 40h ejected refrigerant.

Because the ejector pump 40 As mentioned above, this flows out of the refrigerant pipe 14 to the three way connection 30 Further, liquid-phase refrigerant flows toward the refrigerant jet hole due to gravity 40h from instead of the branching section E to the refrigerant pipe 17a emanate.

In this way, the proportion of the liquid-phase refrigerant in the refrigerant jet hole can be made 40a flowing refrigerant equal to or greater than that of the liquid-phase refrigerant in the via the branch pipe 17a to the second evaporator 22 be flowing refrigerant.

The ejector pump 40 has the suction function and the pressure increasing function of the refrigerant jet hole 40h flowing refrigerant, as in the case of the first embodiment. In addition, the first evaporator evaporates 19 this refrigerant to have a cooling capacity, which then returns to the compressor 11 is sucked. The second evaporator 22 evaporates from the branching section K to the second evaporator 22 flowing refrigerant as in the case of the first embodiment, while the refrigerant in the refrigerant suction port 40b the ejector pump 40 is sucked.

As mentioned above, in this embodiment, similar to the first embodiment, the first evaporator 19 and the second evaporator 22 perform the cooling functions simultaneously. Further, the refrigerant evaporation pressure of the second evaporator 22 lower than that of the first evaporator 19 be.

It also flows out of the refrigerant pipe 14b to the ejector pump 40 flowing refrigerant rather in the refrigerant jet hole 40h the ejector pump 40 , This embodiment can achieve the same effect as the first embodiment.

In this embodiment, since the branching portion K is integral with the interior of the ejector 40 is formed, it is not necessary, a branch portion for guiding the liquid-phase refrigerant to the side of the nozzle 40b (the refrigerant jet hole 40h ) of the ejector 40 in the tube of the refrigeration cycle device 10 provided. Therefore, even if the entire circuit has to be installed in a narrow space, a pipe construction of the circuit can be simplified, thereby achieving a reduction in the size of the entire circuit.

(Seventh Embodiment)

In the seventh embodiment, as in 11 shown, a vapor / liquid separator 33 provided, and an ejector 40 with integrated branching section as that of the sixth embodiment is also provided. Further, the liquid-phase refrigerant outlet is the vapor-liquid separator 33 with the refrigerant flow inlet 40d connected, the branch refrigerant flow outlet 40e is with the refrigerant pipe 17a connected, and the refrigerant suction port 40f is with the branch pipe 17c connected.

Also, the direction of the arrangement of the ejector 40 same as the sixth embodiment. The seventh embodiment may be the same as the fifth embodiment in the components other than the above components as in FIG 11 shown.

The refrigeration cycle with the above arrangement of the embodiment is operated to that of the compressor 11 discharged refrigerant through the condenser 12 cooled and through the vapor / liquid separator 33 to be separated into the vapor-phase and liquid-phase refrigerants. The in the steam / liquid separator 33 stored liquid-phase refrigerant flows into the ejector 40 and becomes the refrigerant jet hole at the branch portion K 40h and to the branch pipe 17a branched. As a result, the liquid-phase refrigerant can reliably flow to the refrigerant jet hole 40h the ejector pump 40 be supplied. This embodiment can achieve the same advantages as the fifth embodiment.

In addition, can in the seventh embodiment the pipe construction of the cooling circuit be simplified, thereby reducing the size of the entire Circle is achieved as in the case of the sixth embodiment.

(Further embodiments)

• (1) Obwohl in dem ersten, dem zweiten und dem sechsten Ausführungsbeispiel der zu kühlende Raum des ersten Verdampfapparats 19 gleich dem des zweiten Verdampfapparats 22 ist, kann der zu kühlende Raum des ersten Verdampfapparats 19 auch von dem des zweiten Verdampfapparats 22 verschieden sein. Zum Beispiel kann der erste Verdampfapparat 19 zur Klimatisierung eines Innenraums eines Fahrzeugs verwendet werden, und der zweite Verdampfapparat 22 kann für einen Kühlapparat im Innern des Fahrzeugs verwendet werden. Ferner kann analog zum dritten bis fünften und siebten Ausführungsbeispiel der erste Verdampfapparat 19 auch nicht vorgesehen sein, und nur der zweite Verdampfapparat 22 kann vorgesehen werden, um die Kühlleistung zu haben.
• (2) Obwohl im ersten und im zweiten Ausführungsbeispiel die Wärme im Innenwärmetauscher 13 zwischen dem durch das Kältemittelrohr 14 strömenden Kältemittel und dem Kältemittel auf der Ansaugseite des Kompressors 11 ausgetauscht wird, kann die Wärme auch zwischen dem durch das Kältemittelrohr 16 oder das Verzweigungsrohr 17a strömenden Kältemittel und dem angesaugten Kältemittel des Kompressors 11 ausgetauscht werden. Auch im dritten bis fünften und siebten Ausführungsbeispiel kann der Innenwärmetauscher 13 so angeordnet werden, dass er Wärme zwischen dem Kältemittel auf der stromabwärtigen Seite des Kondensators 12, 31, 32 und dem Kältemittel auf der Ansaugseite des Kompressors 11 austauscht.
• (3) In den obigen Ausführungsbeispielen ist die im Verzweigungsrohr 17 angeordnete Drosseleinrichtung die feste Drossel 21, aber ein variabler Drosselmechanismus, der die Kältemittelpfadfläche elektrisch und mechanisch verändern kann, kann ebenfalls benutzt werden. Zum Beispiel kann in der Konstruktion des ersten Ausführungsbeispiels der Unterkühlungsgrad des Kältemittels an der Auslassseite des zweiten Verdampfapparats 22 erfasst werden und der Öffnungsgrad der Kältemittelpfadfläche kann so gesteuert werden, dass der erfasste Unterkühlungsgrad in einem vorbestimmten Bereich liegt.
• (4) Obwohl in den ersten bis fünften Ausführungsbeispielen die Ejektorpumpe 18 des festen Strömungsratentyps eingesetzt wird, bei der die Kältemittelpfadfläche der Düse 18a nicht verändert wird, kann analog zum sechsten und siebten Ausführungsbeispiel auch die Ejektorpumpe mit variabler Strömungsrate eingesetzt werden, die die Kältemittelpfadfläche der Düse 18a elektrisch und mechanisch verändern kann. Zum Beispiel kann bei der Konstruktion des ersten Ausführungsbeispiels der Unterkühlungsgrad des Kältemittels am Auslass des Kondensators 12 erfasst werden und der Öffnungsgrad der Kältemittelpfadfläche der Düse kann so gesteuert werden, dass der erfasste Unterkühlungsgrad in dem vorbestimmten Bereich liegt.
• (5) Die Dreiwegeverbindung 30 des zweiten Ausführungsbeispiels ist so angeordnet, dass die Richtung des Kältemittelstroms vom Kältemittelrohr 14 zum Verzweigungsabschnitt E (die Richtung des Pfeils F in 4) und die Richtung des Kältemittelstroms vom Verzweigungsabschnitt E zum Kältemittelrohr 16 (die Richtung des Pfeils G in 4) auf der gleichen Geraden in der vertikalen Richtung nach unten orientiert sind, um das Flüssigphasenkältemittel gut vom Verzweigungsabschnitt E zum Kältemittelrohr 16 strömen zu lassen. Die Anordnungsrichtung der Dreiwegeverbindung 30 ist jedoch nicht darauf beschränkt. Selbst wenn der Kältemittelstrom vom Kältemittelrohr 14 zum Verzweigungsabschnitt E (die Richtung des Pfeils F in 4) und der Kältemittelstrom vom Verzweigungsabschnitt E zum Kältemittelrohr 16 (die Richtung des Pfeils G in 4) auf der gleichen Geraden horizontal ausgerichtet sind und wenn der Kältemittelstrom vom Verzweigungsabschnitt E zum Verzweigungsrohr 17a in der vertikalen Richtung nach oben ausgerichtet ist, kann zum Beispiel der gleiche Effekt erzielt werden. Falls die Kältemittelgeschwindigkeit gering ist und stark durch die Schwerkraft beeinflusst wird, selbst wenn nur die Richtung des Kältemittelstroms vom Verzweigungsabschnitt E des Kältemittelrohrs 16 in der vertikalen Richtung nach unten ausgerichtet ist, kann der gleiche Effekt wie beim zweiten Ausführungsbeispiel erzielt werden.
• (6) Obwohl im sechsten Ausführungsbeispiel die Anordnungsrichtung der Ejektorpumpe 40 so eingestellt ist, dass die Richtung des Kältemittelstroms in das Kältemittelstrahlloch 40h in der vertikalen Richtung nach unten ausgerichtet ist (in der Richtung des Pfeils N in 10), kann die Anordnungsrichtung verändert werden. Zum Beispiel können die Richtung des Kältemittelstroms vom Kältemittelrohr 14b zum Verzweigungsabschnitt K (die Richtung des Pfeils L in 10) und die Richtung des Kältemittelstroms vom Verzweigungsabschnitt K zum Verzweigungsrohr 17a (die Richtung des Pfeils Mutter in 10) in der vertikalen Richtung nach oben ausgerichtet werden, und die Richtung des Kältemittelstroms in das Kältemittelstrahlloch 40h (die Richtung des Pfeils N in 10) kann horizontal ausgerichtet werden. Dies macht es für das Kältemittel wegen der Schwerkraft schwierig, in der Richtung vom Verzweigungsabschnitt K zum Verzweigungsrohr 17a zu strömen, und macht es für das Kältemittel einfach, zum Kältemittelstrahlloch 40h zu strömen. Der gleiche Effekt wie beim sechsten Ausführungsbeispiel kann erzielt werden.
• (7) Mit der obigen Konstruktion der Ejektorpumpe 40 des sechsten und des siebten Ausführungsbeispiels können die Richtung des Kältemittelstroms vom Verzweigungsabschnitt K zum Verzweigungsrohr 17a und die Richtung des Kältemittelstroms in das Kältemittelstrahlloch 40h im Wesentlichen symmetrisch zum Kältemittelstrom vom Kältemittelrohr 14b zum Verzweigungsabschnitt K sein. Wenn zum Beispiel die Richtung des Kältemittelstroms vom Verzweigungsabschnitt K zum Verzweigungsrohr 17a senkrecht zur Richtung des Kältemittelstroms vom Kältemittelrohr 14b zum Verzweigungsabschnitt K und zur Richtung des Kältemittelstroms in das Kältemittelstrahlloch 40h orientiert ist (in der Vorne/Hinten-Richtung bezüglich der Zeichnungsebene von 10 orientiert), können Einflüsse durch die kinetische Energie in der Kältemittelströmungsrichtung vom Kältemittelrohr 14b zum Verzweigungsabschnitt K eliminiert werden, sodass die gleiche Wirkung wie beim ersten Ausführungsbeispiel erzielt werden kann.
• (8) Obwohl in dem obigen sechsten und siebten Ausführungsbeispiel die Ejektorpumpe 40 mit dem Verzweigungsabschnitt darin eingesetzt wird, kann diese Ejektorpumpe auch integral mit der festen Drossel 21 oder dem im Verzweigungsrohr 17 angeordneten variablen Drosselmechanismus ausgebildet werden. Dies kann die Rohrkonstruktion des Kreises weiter vereinfachen, wodurch eine Reduzierung der Größe des gesamten Kreises erreicht wird.
• (9) Obwohl in den obigen Ausführungsbeispielen der Verstellkompressor als Kompressor 11 verwendet wird, kann auch ein Kompressor mit fester Verdrängung oder ein elektrischer Kompressor benutzt werden. Ferner steuert der Kompressor mit fester Verdrängung die Kältemittelausgabeleistung durch Steuern eines Verhältnisses (Betriebsverhältnis) eines Betriebszustandes zu einem Nicht-Betriebszustand der elektromagnetischen Kupplung. Der elektrische Kompressor kann das Kältemittelausgabevolumen durch Steuern der Drehzahl steuern.
• (10) In den obigen Ausführungsbeispielen dienen der erste Verdampfapparat 19 und der zweite Verdampfapparat 22 als Innenwärmetauscher zum Kühlen des zu kühlenden Raums, und die Kondensatoren 12, 31 und 32 dienen als Außenwärmetauscher zum Abstrahlen von Wärme in die Atmosphäre. Dagegen kann die Erfindung auch auf ein Beispiel angewendet werden (Wärmepumpenkreis), bei dem der erste Verdampfapparat 19 und der zweite Verdampfapparat 22 als Außenwärmetauscher zum Absorbieren von Wärme von einer Wärmequelle, wie beispielsweise der Atmosphäre, dienen und die Kondensatoren 12, 31 und 32 als Innenwärmetauscher zum Heizen eines zu heizenden Fluids, wie beispielsweise Luft oder Wasser, dienen.

Although the present invention has been fully described in connection with the preferred embodiments thereof with reference to the accompanying drawings, it is to be noted that various modifications and variations can be made in the disclosed circuit as follows.

• (1) Although, in the first, second and sixth embodiments, the space to be cooled of the first evaporator 19 equal that of the second evaporator 22 is, the space to be cooled of the first evaporator 19 also from that of the second evaporator 22 to be different. For example, the first evaporator 19 be used for air conditioning of an interior of a vehicle, and the second evaporator 22 can be used for a refrigerator inside the vehicle. Further, similarly to the third to fifth and seventh embodiments, the first evaporator 19 also not be provided, and only the second evaporator 22 can be provided to have the cooling capacity.
• (2) Although in the first and second embodiments, the heat in the indoor heat exchanger 13 between through the refrigerant pipe 14 flowing refrigerant and the refrigerant on the suction side of the compressor 11 The heat can also be exchanged between that through the refrigerant pipe 16 or the branch pipe 17a flowing refrigerant and the drawn refrigerant of the compressor 11 be replaced. Also in the third to fifth and seventh embodiments, the indoor heat exchanger 13 be arranged to heat between the refrigerant on the downstream side of the condenser 12 . 31 . 32 and the refrigerant on the suction side of the compressor 11 exchanges.
• (3) In the above embodiments, that is in the branch pipe 17 arranged throttle device the fixed throttle 21 but a variable throttle mechanism that can electrically and mechanically change the refrigerant path area can also be used. For example, in the construction of the first embodiment, the supercooling degree of the refrigerant may be at the outlet side of the second evaporator 22 can be detected and the opening degree of the refrigerant path area can be controlled so that the detected supercooling degree is within a predetermined range.
• (4) Although in the first to fifth embodiments, the ejector 18 is used of the fixed flow rate type, wherein the refrigerant path surface of the nozzle 18a is not changed, can be used analogously to the sixth and seventh embodiments, the variable-displacement ejector, which the refrigerant path area of the nozzle 18a can change electrically and mechanically. For example, in the construction of the first embodiment, the supercooling degree of the refrigerant may be at the outlet of the condenser 12 and the opening degree of the refrigerant path area of the nozzle can be controlled so that the detected supercooling degree is within the predetermined range.
• (5) The three-way connection 30 of the second embodiment is arranged such that the direction of the refrigerant flow from the refrigerant pipe 14 to the branching section E (the direction of the arrow F in FIG 4 ) and the direction of the refrigerant flow from the branching section E to the refrigerant pipe 16 (the direction of the arrow G in 4 ) are oriented down the same straight line in the vertical direction to move the liquid-phase refrigerant well from the branching section E to the refrigerant pipe 16 to flow. The arrangement direction of the three-way connection 30 but is not limited to this. Even if the refrigerant flow from the refrigerant pipe 14 to the branching section E (the direction of the arrow F in FIG 4 ) and the refrigerant flow from the branching section E to the refrigerant pipe 16 (the direction of the arrow G in 4 ) are aligned horizontally on the same straight line and when the refrigerant flow from the branching section E to the branch pipe 17a In the vertical direction, for example, the same effect can be obtained. If the refrigerant velocity is small and heavily influenced by gravity, even if only the direction of the refrigerant flow from the branch portion E of the refrigerant tube 16 is aligned in the vertical direction downward, the same effect as in the second embodiment can be achieved.
• (6) Although in the sixth embodiment, the arrangement direction of the ejector 40 is set so that the direction of the refrigerant flow into the refrigerant jet hole 40h is oriented downward in the vertical direction (in the direction of the arrow N in FIG 10 ), the arrangement direction can be changed. For example, the direction of the refrigerant flow may be from the refrigerant tube 14b to the branching section K (the direction of the arrow L in FIG 10 ) and the direction of the refrigerant flow from the branch portion K to the branch pipe 17a (the direction of the arrow mother in 10 ) in the vertical direction, and the direction of the refrigerant flow in the refrigerant jet hole 40h (the direction of the arrow N in 10 ) can be aligned horizontally. This makes it difficult for the refrigerant due to gravity, in the direction from the branch portion K to the branch pipe 17a to flow, and makes it easy for the refrigerant to the refrigerant jet hole 40h to stream. The same effect as in the sixth embodiment can be obtained.
• (7) With the above construction of the ejector pump 40 of the sixth and seventh embodiments, the direction of the refrigerant flow from the branching section K to the Verzwei supply pipe 17a and the direction of the refrigerant flow in the refrigerant jet hole 40h substantially symmetrical to the refrigerant flow from the refrigerant pipe 14b to the branching section K. For example, when the direction of the refrigerant flow from the branch portion K to the branch pipe 17a perpendicular to the direction of the refrigerant flow from the refrigerant pipe 14b to the branch portion K and to the direction of the refrigerant flow in the refrigerant jet hole 40h is oriented (in the front / rear direction with respect to the plane of the drawing of 10 Influences can be influenced by the kinetic energy in the refrigerant flow direction from the refrigerant pipe 14b to the branch portion K are eliminated, so that the same effect as in the first embodiment can be achieved.
• (8) Although in the above sixth and seventh embodiments, the ejector 40 With the branch portion inserted therein, this ejector may also be integral with the fixed throttle 21 or in the branch pipe 17 arranged variable throttle mechanism can be formed. This can further simplify the tube construction of the circle, thereby reducing the size of the entire circle.
• (9) Although, in the above embodiments, the variable displacement compressor is a compressor 11 is used, a fixed displacement compressor or an electric compressor can also be used. Further, the fixed displacement compressor controls the refrigerant output by controlling a ratio (operating ratio) of an operating state to a non-operating state of the electromagnetic clutch. The electric compressor may control the refrigerant discharge volume by controlling the rotational speed.
• (10) In the above embodiments, the first evaporator is used 19 and the second evaporator 22 as an indoor heat exchanger for cooling the room to be cooled, and the capacitors 12 . 31 and 32 serve as outdoor heat exchanger for radiating heat into the atmosphere. In contrast, the invention can also be applied to an example (heat pump cycle) in which the first evaporator 19 and the second evaporator 22 as an outdoor heat exchanger for absorbing heat from a heat source, such as the atmosphere, serve and the capacitors 12 . 31 and 32 serve as an indoor heat exchanger for heating a fluid to be heated, such as air or water.

The Refrigerant branch construction with the branching section can for any refrigeration cycle devices be used with an ejector, even with another Circular construction as in the embodiments described above.

Further, the term "substantially equal to" described in the embodiments means not only that the proportion of the liquid-phase refrigerant in the ejector-pump side (FIG. 18 ) flowing refrigerant completely identical to that of the liquid-phase refrigerant in the side of the evaporator ( 22 ), but also that these proportions may be substantially equal to each other, even with a small difference.

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

Claims (20)

Branching construction for a refrigeration cycle device with an ejector pump ( 18 ), wherein the branch construction upstream of the ejector ( 18 ) is provided for branching and supplying a refrigerant to a nozzle ( 18a ) of the ejector pump ( 18 ) and to a with a refrigerant suction port ( 18b ) of the ejector pump ( 18 ) connected evaporator ( 22 ), wherein the branch construction comprises: an inlet pipe part ( 15a ) for introducing the refrigerant; and at least two arm parts extending from the inlet pipe part ( 15a ), wherein the two arm parts with respect to the inlet pipe part ( 15a ) are substantially symmetrical, being positioned substantially in the same state with respect to a direction of gravity. A branching structure according to claim 1, wherein the two arm parts are arranged substantially in a U-shape, wherein one end is connected to the introduction pipe part. Branching construction for a refrigeration cycle device with an ejector pump ( 18 ), wherein the branch construction upstream of the ejector ( 18 ) is provided for branching and supplying a refrigerant to a nozzle ( 18a ) of the ejector pump ( 18 ) and to a with a refrigerant suction port ( 18b ) of the ejector pump ( 18 ) connected evaporator ( 22 ), wherein the branch construction comprises: an inlet pipe part ( 30a ) for introducing the refrigerant; and at least a first and a second branching part ( 30b ) coming from the inlet pipe part ( 30a ) branch, wherein the first branch part in an extension direction of the introduction pipe part ( 30a ) and the second branch part is substantially perpendicular to the direction of extension of the introduction tube part (FIG. 30a ) runs. A branching structure according to claim 3, wherein the inlet pipe part (10) 30a ) is positioned so that it runs in the direction of gravity. A branch construction according to claim 3 or 4, wherein said second branching part is positioned so as to extend in a horizontal direction from an extension of said introduction pipe part (10). 30a ) runs. Cooling circuit device, with a condenser ( 12 ) for cooling and condensing a refrigerant; a branching section for branching a refrigerant flow upstream of the condenser (FIG. 12 ) into a first and a second stream; an ejector pump ( 18 ), which has a nozzle ( 18a ) for decompressing and expanding the refrigerant of the first stream flowing out of the branching portion and a refrigerant suction port 18b ) from which the refrigerant passes through one of the nozzles ( 18a ) is sucked in high-velocity refrigerant flow; a throttle element ( 21 ) for decompressing and expanding the refrigerant of the second stream flowing out of the branching portion; and an evaporator ( 22 ) for vaporizing the through the throttle element ( 21 ) decompressed refrigerant, wherein the evaporator ( 22 ) one with the refrigerant suction port ( 18b ), wherein the branching portion branches the refrigerant flow such that a portion of a liquid-phase refrigerant in the nozzle 18a ) flowing refrigerant about equal to a proportion of a liquid phase refrigerant in a to the evaporator 122 ) is flowing refrigerant. Cooling-circuit device according to claim 6, in which a flow direction (B) of the branching section to the nozzle ( 18a ) flowing refrigerant and a flow direction (C) of the branch portion from the evaporator ( 22 ) flowing refrigerant are arranged substantially in the same plane. Cooling-circuit device according to claim 6 or 7, in which the flow direction (B) of the branching section to the nozzle ( 18a ) flowing refrigerant and the flow direction (C) of the branching section to the evaporator ( 22 ) flowing refrigerant are arranged substantially symmetrically to a flow direction of the refrigerant flowing into the branch portion. Cooling-circuit device according to one of claims 6 to 8, wherein the branching section with an inlet pipe part ( 15a ) for introducing the refrigerant and at least two arm parts ( 15b ) coming from the inlet pipe part ( 15a ) branch off, is built up; and the two arm parts are substantially symmetrical to the inlet tube part ( 15a ), being positioned substantially in the same state with respect to a direction of gravity. Cooling circuit device, with a condenser ( 12 ) for cooling and condensing a refrigerant; a branching section for branching a flow of the refrigerant downstream of the condenser (FIG. 12 ); an ejector pump ( 18 ), which has a nozzle ( 18a ) for decompressing and expanding the refrigerant of the first stream flowing out of the branching portion and a refrigerant suction port 18b ) from which the refrigerant passes through one of the nozzles ( 18a ) is sucked in high-velocity refrigerant flow; a throttle element ( 21 ) for decompressing and expanding the refrigerant of the second stream from the branching section; and an evaporator ( 22 ) for vaporizing the through the throttle element ( 21 ) decompressed refrigerant, wherein the evaporator ( 22 ) one with the refrigerant suction port ( 18b ), wherein the branching section branches the refrigerant flow in such a way that a portion of a liquid-phase refrigerant in the direction of the nozzle ( 18a ) flowing refrigerant equal to or greater than a proportion of a liquid-phase refrigerant in the evaporator ( 22 ) is flowing refrigerant. The refrigerant cycle device according to claim 10, wherein a flow direction (F) of the refrigerant flowing into the branch portion is set to a substantially same straight line as a flow direction (G) of the branch portion to the nozzle (FIG. 18a ) flowing refrigerant is arranged. Cooling-circuit device according to claim 10 or 11, in which the flow direction (G) of the branching section to the nozzle ( 18a ) flowing refrigerant is oriented in a substantially vertical direction downwards. Cooling circuit device according to claim 10, in which the branching section with an inlet pipe part ( 30a ) for introducing the refrigerant and at least a first and a second branch part ( 30b ) coming from the inlet pipe part ( 30a ) branch off, is built up; and the first branch part in an extension direction of the introduction pipe part (FIG. 30a ) and the second branch part is substantially perpendicular to the direction of extension of the introduction tube part (FIG. 30a ) runs. Cooling circuit device, with a compressor ( 11 ) for compressing and discharging a refrigerant; a branching section (H, I) for branching one of the compressor ( 11 ) discharged in a vapor phase state or a vapor / liquid two-phase state near a saturated steam line in a first and a second stream; a first condensation part ( 31c . 32c ) for cooling and condensing the refrigerant of the first stream branched by the branching portion (H, I); a second condensation part ( 31d . 32d ) for cooling and condensing the refrigerant of the branched by the branch portion (H, I) second stream; an ejector pump ( 18 ), which has a nozzle ( 18a ) for decompressing and expanding the from the first condensation part ( 31c . 32c ) flowing refrigerant and a refrigerant suction port ( 18b ) from which the refrigerant flows through the nozzle ( 18a ) is sucked in high-velocity refrigerant flow; a throttle element ( 21 ) for decompressing and expanding the from the second condensation part ( 31d . 32d ) flowing refrigerant; and an evaporator ( 22 ) for vaporizing the through the throttle element ( 21 decompressed refrigerant, wherein the evaporator communicates with the refrigerant suction port ( 18b ) has coupled outlet. The refrigeration cycle device according to claim 14, wherein the branching portion (H) is disposed between an output port of the compressor (10). 11 ) and a refrigerant upstream side of the first and second condensing parts. The refrigeration cycle device of claim 14, wherein the first and second condensing parts are constructed to form a condenser (10). 32 ) to build; and the branching portion (I) on a refrigerant inlet side in the condenser (FIG. 32 ) is provided. Cooling circuit device, with a condenser ( 12 ) for cooling and condensing a refrigerant; a vapor / liquid separator ( 33 ) for separating the refrigerant on a downstream side of the condenser ( 12 ) into a vapor-phase refrigerant and a liquid-phase refrigerant and to discharge the liquid-phase refrigerant; a branching section for branching a flow of the liquid-phase refrigerant from the vapor-liquid separation device (FIG. 33 ) into a first and a second stream; an ejector pump ( 18 ), which has a nozzle ( 18a ) for decompressing and expanding the liquid refrigerant flowing out of the first stream and a refrigerant suction port ( 18b ), from which the refrigerant through the out of the nozzle ( 18a ) is sucked in high-velocity refrigerant flow; a throttle element ( 21 ) for decompressing and expanding the liquid refrigerant flowing out of the second stream; and an evaporator ( 22 ) for vaporizing the through the throttle element ( 21 decompressed refrigerant, wherein the evaporator has a refrigerant outlet coupled to the refrigerant suction port. A refrigeration cycle apparatus according to claim 17, wherein the vapor / liquid separation device comprises a collecting vessel for collecting of the liquid phase refrigerant contains; and the branching portion (J) is provided in the collecting vessel. A refrigeration cycle apparatus according to claim 17, wherein said branching portion is downstream of a liquid-phase refrigerant outlet of said vapor-liquid separator (10). 33 ) is arranged. A refrigeration cycle apparatus according to one of the claims 10-12 17 and 19, in which the branch portion is integral with the Ejector pump is provided.