DE102008051510B4 - Refrigeration cycle device - Google Patents

Abstract

A refrigeration cycle device comprising: a compressor (11) configured to suck, compress and discharge refrigerant; a radiator (12) configured to carry out the heat radiation of the refrigerant discharged from the compressor (11); a first one A variable decompression amount decompression section (13a, 113) configured to decompress and expand the refrigerant flowing out of the radiator (12); a first evaporator (14) arranged to communicate in the first decompression section (13a, 113) A circuit passage (10) through which the compressor (11), the radiator (12), the first decompression section (13a, 113) and the first evaporator (14) are connected in a circle, so that the refrigerant evaporated in the first evaporator (14) is sucked into the compressor (11); a branch passage (20) provided to flow from the cycle passage (10); to be branched at a position between the radiator (12) and the first decompressing portion (13a, 113), so that a part of the refrigerant flowing out of the radiator (12) bypasses the first decompressing portion (13a, 113) and merges with the first decompressing portion (13a, 113) a second decompressing portion (23) of variable decompression amount located in the branching portion (20) for decompressing the refrigerant flowing out of the radiator (12) and a second evaporator (24) located in the branch passage (20) for evaporating the refrigerant decompressed in the second decompression section (23); anda control section (100) for controlling the decompression amounts of the first decompressing section (13a, 113) and the second decompressing section (23), wherein the first evaporator (14) and the second evaporator (24) are arranged such that an external fluid after passing through the first evaporator (14) flows through the second evaporator (24), the refrigeration cycle device being characterized in that: the control section (100) determines the decompression amount of the first decompression section (13a, 113) or the second decompression section (23) based on a pressure or a temperature of the refrigerant discharged from the compressor (11) before being decompressed by the first and second decompression portions (13a, 113, 23); andthe control section (100) determines the decompression amount of the other of the first decompression section (13a, 113) and the second decompression section (23) based on a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) a physical quantity that is relevant to the pressure difference controls.

Description

The present invention relates to a vapor compression refrigerating cycle provided with a plurality of parallel refrigerant decompression portions for respectively adjusting decompression states of refrigerant supplied to a plurality of refrigerant evaporators.

As a prior art, a vapor compression refrigeration cycle device is known in JP 2007-78339A described. In the refrigeration cycle device, a first evaporator is disposed on a refrigerant downstream side of an ejector that acts as a refrigerant decompression section and a refrigerant circulating device in a refrigerant cycle passage. Another decompression portion and a second evaporator are located in a refrigerant branch passage that is branched from the refrigerant cycle passage at a downstream portion of the ejector and connected to a refrigerant suction port of the ejector. In addition, the first evaporator and the second evaporator, which are different from each other in the refrigerant evaporating temperatures, are arranged in an air flow direction.

In the refrigeration cycle device, a nozzle portion as a decompression portion of the ejector, a decompression portion provided on an upstream side of the nozzle portion, or the decompression portion provided in the branch portion, are each made of a variable decompression amount type. By setting a ratio between a refrigerant flow amount discharged from the nozzle portion and a refrigerant flow amount drawn from the refrigerant suction port, the heat capacity in both the first evaporator and the second evaporator can be effectively obtained.

The inventors of the present application have studied details regarding the refrigeration cycle device in which the plurality of decompressing portions are arranged in parallel to set respective refrigerant states supplied to the plurality of evaporators. As a result, it has been found that the circulation efficiency can be more effectively improved by appropriately setting the refrigerant state in the cycle while making both the decompression portion provided in the cycle passage and the decompression portion provided in the branch passage of the variable decompression amount type.

In view of the foregoing, it is an object of the present invention to provide a refrigerant cycle device in which a plurality of variable decompression portions are provided to control the refrigerant decompression amounts to effectively improve the cycle efficiency.

In order to achieve the above object, the refrigeration cycle device according to one aspect of the present invention includes: a compressor (11) configured to suck, compress and discharge refrigerant; a radiator (12) configured to perform the heat radiation of the refrigerant discharged from the compressor (11); a first variable decompression amount decompression portion (13a) configured to decompress and expand the refrigerant flowing out of the radiator (12); a first evaporator (14) arranged to evaporate the refrigerant decompressed in the first decompression section (13a); a circulation passage (10) through which the compressor (11), the radiator (12), the first decompression section (13a) and the first evaporator (14) are connected in a circuit so that the vaporized in the first evaporator (14) Refrigerant is sucked into the compressor (11); a branch passage (20) provided to be branched from the circulation passage (10) at a position between the radiator (12) and the first decompressing portion (13a) so that a part of the refrigerant flowing out of the radiator (12) bypassing the first decompression section (13a) and merging with the refrigerant flowing from the first decompression section (13a) toward the compressor (11); a second variable decompression amount decompression section (23) located in the branching section (20) for decompressing and expanding the refrigerant flowing out of the radiator (12); a second evaporator (24) located in the branch passage (20) for evaporating the refrigerant decompressed in the second decompression section (23); and a control section (100) for controlling the decompression amounts of the first decompression section (13a) and the second decompression section (23). The first evaporator (14) and the second evaporator (24) are arranged such that an external fluid flows through the second evaporator (24) after passing through the first evaporator (14). In addition, the control section (100) controls the decompression amount of the first decompression section (13a) or the second decompression section (23) based on a pressure or a temperature of the refrigerant discharged from the compressor (11), before being released from the first and second decompression sections (13a, 13a). 23) is decompressed, and the The control section controls the decompression amount of the other of the first decompression section and the second decompression section based on a pressure difference between the refrigerant in the first evaporator and the second evaporator based on a physical pressure Size, which is decisive for the pressure difference.

Thus, the refrigerant state discharged from the compressor (11) before being decompressed by the first and second decompression sections (13a, 23), that is, the high-pressure-side refrigerant state, can be set to a refrigerant condition in which the heat-radiation efficiency in the radiator (12) becomes optimal. In addition, the temperature difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) may be set to an appropriate temperature difference, thereby preventing the generation of frost on the first evaporator (14) and the second evaporator (24). , which are arranged in a flow direction (AA) of an external fluid, can be restricted and the heat absorption efficiency in the first and second evaporators (14, 24) is improved. Consequently, the efficiency of the refrigeration cycle device can be further improved.

For example, the refrigeration cycle device may be provided with an ejector (13) having a nozzle portion (13a) that decompresses and expands the refrigerant flowing out of the radiator (12) by converting the pressure energy of the refrigerant into its velocity energy, a refrigerant suction port (13b). from which refrigerant is sucked by a refrigerant flow discharged from the nozzle portion (13a), and a pressure increasing portion (13c, 13d) in which the pressure of the refrigerant is increased by converting the velocity energy into the pressure energy while discharging from the nozzle portion (13a) ejected refrigerant and the refrigerant sucked from the refrigerant suction port (13b) are mixed. In this case, the first decompressing portion (13a) is the nozzle portion (13a), and the branch portion (20) has a downstream end connected to the refrigerant suction port (13b), so that the refrigerant evaporated in the second evaporator (24) flows into the refrigerant suction port (13b) flows.

Thus, the pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator 24 can be appropriately adjusted by the heat transfer efficiency with the pressure increasing efficiency of the ejector (13).

The refrigeration cycle device may be provided with a pressure detecting portion (92) arranged to detect the pressure of the refrigerant discharged from the compressor (11) before being decompressed by the first and second decompression portions (13a, 23). In this case, the control section (100) controls the decompression amount of the one first decompressing section (13a) or the second decompressing section (23) based on the pressure detected by the pressure detecting section (92).

The pressure of the refrigerant discharged from the compressor (11) before being decompressed by the first and second decompression portions (13a, 23), that is, the refrigerant pressure on the high pressure side, is used as a control factor. Therefore, the refrigerant pressure can be increased to a refrigerant state in which the heat radiation efficiency in the radiator (12) can be made to fit regardless of the refrigerant state sucked into the compressor (11).

The refrigeration cycle device may be provided with an ejection refrigerant temperature detecting portion (91) arranged to detect the temperature of the refrigerant discharged from the compressor (11). In this case, the control section (100) controls the decompression amount of the first decompression section (13a) or the second decompression section (23) based on the refrigerant temperature detected by the discharge-refrigerant temperature detection section (91).

Since the refrigerant temperature at the discharge port of the compressor (11) is used as the control factor, the compressor (11) can be operated without exceeding the heat-resistant temperature of the compressor (11), thereby limiting a life reduction in the compressor (11).

The refrigeration cycle device may be provided with a first evaporator refrigerant pressure detecting portion arranged to detect the pressure of the refrigerant flowing into the first evaporator (14), and a second evaporator refrigerant pressure detecting portion arranged to regulate the pressure of the second evaporator (24). to detect flowing refrigerant. In this case, the control section (100) controls the decompression amount of the other of the first decompression section (13a) and the second decompression section (23) based on a difference between the refrigerant pressure detected by the first evaporator refrigerant pressure detecting section and the refrigerant pressure received from the second evaporator refrigerant pressure detecting section is detected.

Consequently, the refrigerant pressure in the first evaporator (14) and the refrigerant pressure in the second evaporator (24) can be directly detected, and the decompression amount of the other of the first decompression section (13a) and the second decompression section (23) can be controlled based on the actual refrigerant pressure difference ,

The refrigeration cycle device may be provided with a first evaporator refrigerant temperature detecting portion (93) arranged to detect the temperature of the refrigerant flowing into the first evaporator (14), and a second evaporator refrigerant temperature detecting portion (94) arranged to adjust the temperature of the in to detect the second evaporator (24) flowing refrigerant. In this case, the control section (100) controls the decompression amount of the other of the first decompression section (13a) and the second decompression section (23) using a difference between the refrigerant temperature detected by the first evaporator refrigerant temperature detecting section (93) and the refrigerant temperature is detected by the second evaporator refrigerant temperature detecting portion (94) as a physical quantity that is indicative of the pressure difference.

Consequently, the refrigerant temperature difference, which is relevant to the pressure difference, can be detected relatively easily, whereby the decompression amount of the other of the first decompression section (13a) and the second decompression section (23) is controlled.

The control section (100) may control the decompression amount of the other of the first decompression section (13a) and the second decompression section (23) so that a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) or a second physical quantity, which is relevant for the pressure difference, corresponds to a target value. In this case, the control section (100) changes the target value according to an environmental condition of the radiator (12) and / or the first evaporator (14) and / or the second evaporator (24).

Even if the environmental condition such as the temperature of the outer fluid of the radiator (12), the first evaporator (14) and the second evaporator (24), the freezing conditions of the first evaporator (14) and the second evaporator (24) and the like is changed, the circulation operation can be performed while the pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) can be obtained.

Alternatively, the control section (100) may change the target value according to an outer surface temperature of the first evaporator (14) and / or the second evaporator (24).

Consequently, the pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) is increased in a case where frost on the first evaporator (14) and the second evaporator (24) starts and the temperature is reduced on the outer surface of the first evaporator (14) and the second evaporator (24), that is, a case in which frost increases slightly. Consequently, the temperature difference between the two evaporators (14, 24) can be made large, so that the temperature of the first evaporator (14) is increased as compared with the second evaporator (24), thereby restricting frost.

Alternatively, at a time immediately after an operation start of the compressor (11), the control portion (100) may set the decompression amount of the first decompression portion (13a) and the decompression amount of the second decompression portion (23) based on a pressure or a temperature of the compressor (11). ejected refrigerant before decompression through the first and second decompression sections (13a, 23) control. Then, after the pressure or the temperature of the refrigerant discharged from the compressor has reached a predetermined value before being decompressed by the first and second decompression sections (13a, 23), the control section (100) can set the decompression amount of the first decompression section (13a) or of the second decompression portion (23) based on the pressure or the temperature of the refrigerant discharged from the compressor (11) before decompressing through the first and second decompression portions (13a, 23), and the control portion (100) can control the decompression amount of the other of first decompression section (13a) and second decompression section (23) based on a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) or based on a physical quantity that is relevant to the pressure difference control ,

Accordingly, until the pressure or the temperature of the refrigerant discharged from the compressor (11) has reached the predetermined value before being decompressed by the first and second decompressing sections (13a, 23), that is, the pressure or the high-pressure side temperature the increase speed of the refrigerant pressure on the high pressure side using the refrigerant pressure or the refrigerant temperature on the high pressure side as the control factor of the two decompression portions (13a, 23) is increased, and thereby it is possible to quickly put the cycle operation into the operating state with a high efficiency.

Alternatively, the control section (100) may determine the pressure or the temperature of the refrigerant discharged from the compressor (11) before decompressing by the first and second decompression sections (13a, 23) according to an environmental condition of the radiator (12) and / or the first evaporator (12). 14) and / or the second evaporator (24). Until the pressure or the temperature of the refrigerant discharged from the compressor (11) reaches a predetermined value before being decompressed by the first and second decompression sections (13a, 23), the control section (100) may in this case set the decompression amount of the first decompression section (13a ) and the decompression amount of the second decompressing portion (23) based on the pressure or the temperature of the refrigerant discharged from the compressor (11) before being decompressed by the first and second decompression portions (13a, 23). Further, after the pressure or the temperature of the refrigerant discharged from the compressor (11) has reached the predetermined value before being decompressed by the first and second decompressing sections (13a, 23), the control section (100) can determine the decompression amount of the one of the first decompression section (FIG. 13a) or the second compression portion (23) based on the pressure or the temperature of the refrigerant discharged from the compressor (11) before decompressing by the first and second decompression portions (13a, 23), and the control portion (100) can control the decompression amount the other of the first decompression section (13a) and the second decompression section (23) based on a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) or based on a physical quantity relevant to the pressure difference is, control.

Consequently, in a case where the refrigerant pressure or the refrigerant temperature on the high-pressure side is changed according to a change in the ambient condition of the radiator (12) and / or the first evaporator (14) and / or the second evaporator (24), the refrigerant pressure or the high-pressure-side refrigerant temperature is used as the control factor of the two decompressing portions (13a, 23) until the refrigerant pressure or the high-pressure-side refrigerant temperature reaches the predetermined value. Therefore, the time of a transient state can be shortened, and thereby it is possible that the cycle operation is quickly put into the operating state with high efficiency.

• 1 ist ein schematisches Diagramm, das eine Dampfkompressionskältekreislaufvorrichtung gemäß einer ersten Ausführungsform zeigt, in der die vorliegende Erfindung angewendet ist;
• 2 ist ein Flussdiagramm, das einen schematischen Steuerbetrieb einer Steuervorrichtung gemäß der ersten Ausführungsform zeigt;
• 3 ist ein Diagramm, das ein Beispiel für die Beziehung zwischen einer Außenlufttemperatur und einer Verdampfungstemperaturdifferenz zeigt; und
• 4 ist ein schematisches Diagramm, das eine Dampfkompressionskältekreislaufvorrichtung gemäß einer zweiten Ausführungsform zeigt, in der die vorliegende Erfindung angewendet ist.

Additional objects and advantages of the present invention will become more readily apparent from the following detailed description of preferred embodiments when taken in conjunction with the accompanying drawings.

• 1 Fig. 10 is a schematic diagram showing a vapor compression refrigerating cycle apparatus according to a first embodiment to which the present invention is applied;
• 2 FIG. 10 is a flowchart showing a schematic control operation of a control apparatus according to the first embodiment; FIG.
• 3 Fig. 12 is a diagram showing an example of the relationship between an outside air temperature and an evaporating temperature difference; and
• 4 Fig. 10 is a schematic diagram showing a vapor compression refrigerating cycle apparatus according to a second embodiment to which the present invention is applied.

Next, embodiments of the present invention will be described with reference to the accompanying drawings.

First Embodiment

1 FIG. 10 is a schematic structural diagram showing a vapor compression refrigerating cycle apparatus according to a first embodiment to which the present invention is applied. In the present embodiment, the refrigeration cycle device is 1 an example applied to a heat pump water heater.

In the refrigeration cycle device 1 The present invention is a radiator 12 on a refrigerant discharge side of a compressor 11 for sucking and compressing refrigerant. The spotlight 12 According to the present embodiment, a water and refrigerant heat exchanger provided with a refrigerant passage 12a in which the compressor 11 discharged high-pressure refrigerant flows, and a water passage 12b , in which water flows, is provided. The high-pressure refrigerant and water (outer fluid of the radiator) exchange in the radiator 12 Heat so that the high pressure refrigerant is cooled and water is heated to be boiled.

As the refrigerant of the refrigerant cycle device 1 For example, a conventional Freon-based refrigerant can be used. In this case, the refrigeration cycle device 1 becomes a subcritical cycle in which the refrigerant pressure on the high-pressure side is not higher than the critical pressure of the refrigerant, and thereby the radiator acts 12 as a condenser for cooling and condensing the refrigerant. On the other hand, when the refrigerant pressure on the high pressure side is higher than the critical pressure in the refrigeration cycle device 1, such as in a case where the carbon dioxide (CO2) is used as the refrigerant, the refrigeration cycle device becomes 1 a supercritical cycle, and thereby the refrigerant enters a supercritical state without being in the radiator 12 to be condensed.

An ejector 13 is in a refrigerant flow at a downstream position of the refrigerant radiator 12 arranged. The ejector 13 is used as a decompression section for decompressing the refrigerant, and is also used as a refrigerant circulation device (kinetic motion pump) for performing the refrigerant circulation using the suction (associated effect) of a refrigerant flow discharged at a high speed.

The ejector 13 is with a nozzle section 13a and a refrigerant suction port 13b. A passage sectional area of the nozzle portion 13a is throttled so that that of the radiator 12 flowing high-pressure refrigerant isentropically decompressed and expanded. In the ejector 13 is the refrigerant suction port 13b , is sucked by the gas refrigerant from the second evaporator 24, provided in the same pressure space as a refrigerant discharge port of the nozzle portion 13a ,

In the present embodiment, the nozzle portion is 13a of the ejector 13, a variable nozzle in which the nozzle opening degree is variable to set a refrigerant decompression amount. The nozzle opening degree of the nozzle section 13a can be adjusted by adjusting a needle valve or the like using a driving means such as a stepping motor or the like. The nozzle section 13a is a first decompression section in the second embodiment.

A mixing section 13c in which of the nozzle section 13a ejected high-speed refrigerant flow and the suction refrigerant of the refrigerant suction port 13b is in the ejector 13 on a downstream side of the nozzle portion 13a and the refrigerant suction port 13b provided in the refrigerant flow.

A diffuser section 13d is in the ejector 13 on a refrigerant downstream side of the mixing section 13c provided. The diffuser portion 13 d is formed to have a refrigerant passage sectional area gradually increasing so that the refrigerant flow is slowed down and pressurized, and the refrigerant speed energy in the diffuser portion 13d is converted into the pressure energy.

In the ejector 13 According to the present embodiment, the refrigerant passage sectional area of the mixing portion 13c also be designed so that it gradually increases. Therefore, in the ejector 13 In the present embodiment, a pressure increasing portion having the mixing portion 13c and the diffuser portion 13d built up.

A first evaporator 14 is with a downstream side of the diffuser portion 13d of the ejector 13 connected, and a refrigerant downstream side of the first evaporator 14 is with a refrigerant suction side of the compressor 11 connected. The compressor 11 , the radiator 12, the ejector 13 and the first evaporator 14 are connected in a circuit through a refrigerant cycle passage 10 corresponding to a circulation passage.

A refrigerant branch passage (corresponding to the branch passage) 20 is branched from a branch point ZZ formed on a refrigerant downstream side of the radiator 12 and a refrigerant upstream side of the ejector 13 is branched, and a downstream end of the refrigerant branch passage 20 is with the refrigerant suction port 13b of the ejector 13 connected.

An expansion valve 23 , which is a second decompression section, is located in the refrigerant branch passage 20 on a downstream side of the branch portion ZZ, and a second evaporator 24 is located in the refrigerant branch passage 20 on a refrigerant downstream side of the expansion valve 23 , For example, the expansion valve 23 in the present embodiment, an electronic expansion valve in which a valve opening degree is set to set a refrigerant decompressing amount.

In the present embodiment, the two evaporators 14 . 24 integrally combined, and the two evaporators 14 . 24 are integrally housed in a single outer box. Air is blown into an air passage in the outer box, as shown by the arrow AA, using an ordinary blower not shown (eg, electric blower), so that the refrigerant in the two evaporators 14 . 24 Heat from air absorbs which the two evaporators 14 . 24 passes.

Under the two evaporators 14 . 24 is the first evaporator 14 located in the refrigerant cycle passage 10 is located on a downstream side of the ejector 13, disposed upstream in the air flow AA, and the second evaporator 24 with the refrigerant suction port 13b of the ejector 13 is connected, is disposed downstream in the air flow AA.

An ejection temperature sensor 91 as an ejection refrigerant temperature detecting portion is provided in the refrigerant cycle passage 10 at a portion downstream of the compressor 11 and upstream of the radiator 12 provided to the temperature of the compressor 11 to detect discharged refrigerant. There is also a pressure sensor 92 as a pressure detecting portion in the refrigerant cycle passage 10 at a portion downstream of the radiator 12 and upstream of the ejector 13 (For example, in the present embodiment, upstream of the branch point ZZ) to a refrigerant pressure on a high-pressure side in the refrigeration cycle device 1 capture.

A first evaporator temperature sensor 93 as a first evaporator refrigerant temperature detecting portion is located in the refrigerant cycle passage 10 at a portion downstream of the ejector 13 and upstream of the first evaporator 14 (ie, a refrigerant inlet side of the first evaporator 14 ) to the temperature of the first evaporator 14 to detect flowing refrigerant. There is also a second evaporator temperature sensor 94 as a second evaporator refrigerant temperature detecting portion in the refrigerant branch passage 20 at a portion downstream of the expansion valve 23 and upstream of the second evaporator 24 (ie, a refrigerant inlet side of the second evaporator 24 ) to the temperature of the second evaporator 24 to detect flowing refrigerant.

The by the reference number 100 in 1 The displayed structure shows a control device of the heat pump device, and the control device 100 is a control section in the present embodiment.

The control device 100 is built to operate the compressor 11 , the nozzle section 13a of the ejector 13 , the expansion valve 23 , the blower and etc. based on temperature information from the respective temperature sensors 91, 93, 94, the pressure information from the pressure sensor 92 , a tap water temperature, which is a Außenfluideinströmtemperatur (temperature before the heat exchange) of the radiator 12 is, a heated temperature, the Außenfluidausströmtemperatur (temperature after the heat exchange) of the radiator 12 is, an outside air temperature, the outside fluid inflow temperature (temperature before the heat exchange) of both evaporators 14 . 24 to control signals from switches provided on a control panel (not shown).

Next, the operation of the refrigeration cycle device 1 with the above structure according to the present embodiment.

2 FIG. 10 is a flowchart showing a schematic control operation of the control device 100.

The control device 100 is built to operate the compressor 11 to start with a refrigerant discharge amount that is first determined based on an outside air temperature. Then, the opening degree (ie, the amount of compression) of the nozzle portion becomes 13a of the ejector 13 set (step 110 ), and the degree of opening (ie, the amount of decompression) of the expansion valve 23 is set (step 120 ), so that of the pressure sensor 92 detected high-pressure side refrigerant pressure approaches a target pressure value, which is determined based on a line water temperature, etc.

Then it is determined whether that of the pressure sensor 92 detected high-pressure side refrigerant pressure has reached a predetermined value (step 130 ), and the control processing returns to step 110 back when the of the pressure sensor 92 detected high-pressure side refrigerant pressure has not reached the predetermined value. For example, the predetermined value used as the determination value is 9.5 MPa, which is 95% of the pressure target value when the pressure target value 10 MPa is.

If at step 130 it is determined that of the pressure sensor 92 detected high-pressure side refrigerant pressure has reached the predetermined value, the opening degree of the nozzle portion 13a of the ejector 13 set (step 140), so that of the pressure sensor 92 detected high-pressure side refrigerant pressure approaches the pressure target value, and the opening degree of the expansion valve 23 is set (step 150 ) that a difference between one of the first evaporator refrigerant temperature sensor 93 detected refrigerant temperature and a detected by the second evaporator refrigerant temperature sensor 94 refrigerant temperature approaches a temperature difference target value, which is determined based on the outside air temperature and the like.

That is, until the high-pressure side refrigerant pressure of a time right after the start of operation of the compressor 11 reaches the predetermined value, the decompression amounts of both the nozzle portion become 13a as well as the expansion valve 23 controlled based on the high-pressure side refrigerant pressure. After the high-pressure side refrigerant pressure reaches the predetermined value, the decompression amount of the nozzle portion 13 a that is one of the two decompression portions is also controlled based on the high-pressure-side refrigerant pressure while the decompression amount of the expansion portion 23 which is the other of the two decompression sections based on the temperature difference between the refrigerant in the first evaporator 14 and the refrigerant in the second evaporator 24 is controlled. Then, the above control is continued until the compressor operation is ended.

When the refrigeration cycle device 1 is operated by the control operation of the control device 100, the gas-like refrigerant, which consists of the in 1 shown first evaporator 14 flows into the compressor 11 sucked and compressed.

The high-temperature and high-pressure refrigerant, which is compressed in and discharged from the compressor 11, flows into the radiator 12 in the radiator 12 The high-temperature and high-pressure refrigerant is cooled by the heat exchange with water. That from the spotlight 12 flowing high-pressure refrigerant is branched at the branch point ZZ, in the direction of the ejector 13 and the expansion valve 23 to flow.

Part of the radiator 12 flowing refrigerant is decompressed in the expansion valve 23 to become a low-pressure refrigerant, and the low-pressure refrigerant flows into the second evaporator 24 , In the second evaporator 24 The refrigerant is evaporated by absorbing heat from air flowing outside in the arrow direction AA.

That of the spotlight 12 into the ejector 13 flowing refrigerant is in the nozzle section 13a decompresses and expands. In this way, the pressure energy of the refrigerant at the nozzle portion becomes 13a is converted into the velocity energy of the refrigerant, and thereby the high-speed refrigerant flow is discharged from the discharge port of the nozzle portion 13a. When the high-speed refrigerant flow is discharged from the discharge port of the nozzle portion 13a, the refrigerant pressure is lowered, so that refrigerant after passing through the second evaporator 24 of the refrigerant branch passage 20 from the refrigerant suction port 13b into the ejector 13 is sucked.

That from the nozzle section 13a discharged refrigerant and that of the refrigerant suction port 13b Sucked refrigerants become in the mixing section 13c downstream of the nozzle section 13a mixed to enter the diffuser section 13d to stream. Since the passage sectional area in the diffuser portion 13d is increased, the speed energy (expansion energy) of the refrigerant is converted into its pressure energy, whereby the pressure of the refrigerant in the diffuser portion 13d is increased.

That from the diffuser section 13d of the ejector 13 flowing refrigerant flows into the first evaporator 14 , Low-temperature and low-pressure refrigerant in the first evaporator 14 is vaporized by absorbing heat from air flowing in the arrow direction AA. Gas refrigerant will, after it is in the first evaporator 14 evaporated, back into the compressor 11 sucked and compressed.

Since the refrigerant pressure in the pressure increasing portion of the ejector 13 is pressurized, the refrigerant evaporation pressure (the refrigerant evaporation temperature) in the second evaporator 24 lower than the refrigerant evaporation pressure (the refrigerant evaporation temperature) in the first evaporator 14 be made.

The first evaporator 14 with a relatively high refrigerant evaporation temperature is in the flow direction AA of blown air on an upstream side, and the second evaporator 24 with a relatively low refrigerant evaporation temperature, there is AA of blown air on a downstream side in the flow direction. Therefore, both the temperature difference between the refrigerant evaporation temperature and air in the first evaporator 14 and the temperature difference between the refrigerant evaporation temperature and air in the second evaporator can be achieved.

Therefore, the heat absorption performance in both the first and second evaporators 14 and 24 be achieved effectively. In addition, the suction pressure of the compressor 11 by the pressure increasing effect in the mixing section 13c and the diffuser section 13d be increased, reducing the drive power in the compressor 11 is reduced.

According to the above structure and operation, the control device 100 controls the decompression amount of the nozzle portion 13a the ejector 13 based on the high-pressure side Refrigerant pressure and controls the decompression amount of the expansion valve 23 based on the temperature difference between the refrigerant of the first evaporator 14 and the refrigerant of the second evaporator 24 After the operation of the compressor 11 starts, and the high-pressure side refrigerant pressure has reached the predetermined pressure.

Consequently, the refrigerant chase such as the pressure of the refrigerant or the temperature of the refrigerant or the like discharged from the compressor 11, but before the decompression in the nozzle portion 13a and the expansion valve can be 23 that is, the high-pressure side refrigerant state (eg, the refrigerant temperature at the discharge port of the compressor 11 , the refrigerant pressure downstream of the radiator 12 ) are set to a refrigerant state in which the heat radiation efficiency of the radiator 12 can be set to an optimal value. In addition, the temperature difference between the refrigerant in the first evaporator 14 and the refrigerant in the second evaporator 24 can be set to a suitable temperature difference so that frost on the first evaporator 14 and the second evaporator 24 , which are arranged in the air flow direction AA, can be restricted, and the heat absorption capacity for absorbing heat from the outer fluid in both the first evaporator 14 as well as the second evaporator 24 can be effectively fulfilled. In addition, the pressure difference between the refrigerant in the first evaporator 14 and the refrigerant in the second evaporator 24 are set so that the heat transfer efficiency due to the pressure increasing effect of the ejector 13 can be made optimum.

In the refrigeration cycle device 1 In the present embodiment, the suction pressure of the compressor 11 on one to the first evaporator 14 similar level when the ejector 13 is used. Therefore, the load of the compressor 11 be reduced to the operating efficiency of the compressor 11 improve, while the heat capacity of the first and second evaporators 14 . 24 can be maintained.

The pressure of the ejector 13 pressurized refrigerant flow, that is, the pressure increasing amount in the ejector 13 , According to the flow rate of the drive current of the ejector 13 (ie, the refrigerant flow amount, which is the nozzle portion 13a passes through) and / or according to the refrigerant condition entering the refrigerant suction port 13b is sucked, changed.

In a state where the evaporation temperature is high, that is, in a state where the temperature of air flowing into the second evaporator 24 is high, the refrigerant becomes at the refrigerant outlet of the second evaporator 24 completely to steam, and thereby the density of the refrigerant at the refrigerant outlet of the second evaporator 24 smaller, and the pressure increasing amount in the ejector 13 becomes, relatively high. On the other hand, in a state where the evaporation temperature is low, that is, in a state where the temperature of air flowing into the second evaporator 24 flows, is low, the refrigerant comes at the refrigerant outlet of the second evaporator 24 in a wet-out state (ie, a state containing liquid refrigerant), and thereby the density of the refrigerant at the refrigerant outlet of the second evaporator becomes 24 greater, and the pressure increase amount in the ejector 13 becomes relatively small. In this way, the pressure increase amount due to the ejector 13 be adjusted based on the various conditions, so that the circulation operation comes in a state with the highest efficiency.

Since the evaporation temperature difference between the first evaporator 14 and the second evaporator 24 in the in 1 For example, as shown in FIG. 1, the circulating structure is approximately proportional to the pressurizing amount, an optimum pressurizing amount can be obtained by adjusting the evaporator temperature difference.

Then, according to the present embodiment, the high-pressure side refrigerant state becomes the control factor of the opening degree control of the nozzle portion 13a of the ejector 13 is used, and the evaporator temperature difference is used as the control factor for the opening degree of the expansion valve 23 used. Therefore, the high-pressure side refrigerant state (eg, the refrigerant temperature at the discharge port of the compressor, the refrigerant pressure downstream of the radiator) can be set so that the heat radiating power of the radiator 12 can be maximally increased effectively, and the evaporator temperature levels of the first and second evaporators 14 . 24 can be set to a desired state. That is, the pressure-increasing effect of the ejector 13 can be set to a state to have the highest efficiency. As a result, the efficiency of the refrigeration cycle device 1 can be effectively improved.

When the control processing at step 150 In the above-described first embodiment, the target value of the evaporator temperature difference may be set according to the operating environment condition, for example, according to the operating environment condition of the radiator 12 and / or the first evaporator 14 and / or the second evaporator 24 changed become. For example, the target value of the evaporator temperature difference may be changed according to the outside air temperature (ie, the temperature of an external fluid flowing into the first and second evaporators) or the tap water temperature (ie, the temperature of an external fluid flowing into the radiator) or the like. 3 FIG. 15 shows an example in which the target evaporator temperature difference (ie, the target value of the evaporator temperature difference) is changed according to the outside air temperature.

According to the example of 2 For example, the cycle may be operated while the temperature difference between the refrigerant in the first evaporator 14 and the refrigerant in the second evaporator 24 can be achieved, even if the environmental condition, such as the temperatures of external fluids of the radiator 12 , the first evaporator 14 and the second evaporator 24, or the environmental condition such as freezing conditions of the first evaporator 14 and the second evaporator 24 to be changed

The target value of the evaporator temperature difference may correspond to an outer surface temperature of the first evaporator 14 and / or the second evaporator 24 be changed. If in this case the formation of frost on the first evaporator 14 or the second evaporator 24 that is, when the ambient condition is the condition in which the frost is easily caused, the refrigerant temperature difference between the first evaporator 14 and the second evaporator 24 be enlarged, and thereby the temperature difference between the two evaporators 14 . 24 made bigger, so the temperature of the first evaporator 14 higher than the second evaporator 24 becomes. Consequently, the effect of frost on the evaporators 14, 24 can be restricted.

The control device 100 leads the steps 110 and 120 until the high-pressure side refrigerant pressure has reached the predetermined pressure after the start of the cycle operation, so that the decompression amount of the nozzle portion 13a of the ejector and the decompression amount of the expansion valve 23 can be controlled based on the high-pressure side refrigerant pressure. Consequently, until the high-pressure side refrigerant pressure reaches the predetermined value, the pressure of the high-pressure side refrigerant becomes the control factor for both decompression sections 13a . 23 is used, so that the increasing speed of the high-pressure side refrigerant pressure can be promoted, and thereby it is for the circulation operation due to the control operation of the steps 140 . 150 possible to quickly switch to the highly efficient operating state.

The rate of change of the refrigerant state on the evaporator side is later than the rate of change of the refrigerant state on the high pressure side. Accordingly, in a case where the high-pressure-side refrigerant state has to be greatly changed, the evaporator temperature difference is used as the control factor, the change ratio of the opening degree of the expansion valve comes 23 later, and the increase of the refrigerant pressure on the high pressure side is restricted. Therefore, it takes a long time until the opening degree of the expansion valve 23 reaches the opening degree in a stable state.

During the operation control of both decompression portions from the operation start to a state where the refrigerant pressure on the high pressure side reaches the predetermined pressure, the refrigerant pressure on the high pressure side can be used as a main control factor, and an evaporator temperature difference or the like can be added to the control factor without limited only to the refrigerant pressure on the high pressure side as the control factor.

As described above, in the present embodiment, at the operation start time, the operation control of both decompression sections based on the refrigerant pressure on the high pressure side is used. In a case where the refrigerant pressure or the refrigerant temperature on the high-pressure side corresponding to the changes in the environmental condition of the radiator 12 and or of the first evaporator 14 and / or the second evaporator 24 is changed, that is, in a transition state of the operating state change, similar to the operation start time, the operation control of both decompression sections based on the refrigerant pressure on the high pressure side can be used. Even in a case where the operating state of the refrigeration cycle device 1 For example, by changing the water inflow temperature (inflow temperature of the outer fluid of the radiator 12 ) and / or the heated temperature (outflow temperature of the outer fluid of the radiator 12 ) and / or the outside air temperature (inflow temperature of the outer fluid of the first and second, evaporators 14 . 24 ) and / or the outside air humidity (inflow moisture of the outer fluid of the first and second evaporators 14 . 24 ), similar to the operation start time, the operation control of both decompression sections may be used based on the refrigerant pressure on the high pressure side.

Accordingly, in a case where the refrigerant pressure or the refrigerant temperature on the high pressure side corresponding to a change in the ambient condition of the radiator 12 and / or the first evaporator 14 and / or the second evaporator 24 is changed, the refrigerant pressure or the refrigerant temperature on the high pressure side as the control factor of the decompression 13a, 23 used. Accordingly, the time of the transient state can be shortened, whereby the shift to the high-efficiency operation state is quick.

The control device 100 controls the decompression amount of the nozzle portion 13a based on that of the pressure sensor 92 detected high pressure side refrigerant pressure. As described above, since the refrigerant pressure on the high pressure side is used as the control factor, the refrigerant pressure can be increased to the refrigerant state in which the heat radiation due to the radiator 12 regardless of the compressor 11 sucked refrigerant condition is optimal.

Then the control device controls 100 the decompression amount of the expansion valve 23 based on the difference between that of the first evaporator refrigerant temperature sensor 93 detected refrigerant temperature and that of the second evaporator refrigerant temperature sensor 94 detected refrigerant temperature. Accordingly, the refrigerant temperature difference of the first and second evaporators 14 . 24 be detected using relatively inexpensive facilities.

Second Embodiment

Next, a second embodiment will be described with reference to FIG 4 described.

In the second embodiment, the two decompression portions are expansion valves, and the downstream connection portion of the refrigerant branch passage is a point downstream of the first evaporator as compared with the first embodiment described above. Here, the portions similar to those of the first embodiment described above are indicated by the same reference numerals, and their detailed explanation is omitted.

As in 4 12, in the present embodiment, a refrigerant branch passage 20A (corresponding to the branch passage) is formed such that a downstream end of the refrigerant branch passage 20A flows in a refrigerant flow at a position downstream of the first evaporator 14 and upstream of the compressor 11 with the refrigeration cycle passage 10 is united. An expansion valve 113 is located as a first decompression portion in the refrigerant cycle passage 10 , The expansion valve 113 is also an electronic expansion valve, and a refrigerant decompression amount of the expansion valve 113 can be adjusted by adjusting its opening degree.

A control device is in 4 omitted. However, similar to the first embodiment, the control device controls the decompression amount of the expansion valve 113 and the decompression amount of the expansion valve 23 based on the refrigerant pressure on the high pressure side. Then, after the refrigerant pressure on the high pressure side after the start of operation has reached the predetermined pressure, the decompression amount of the expansion valve becomes 113 controlled based on the refrigerant pressure on the high pressure side, and the decompression amount of the expansion valve 23 is based on the temperature difference between the refrigerant in the first evaporator 14 and the refrigerant in the second evaporator 24 controlled.

Consequently, until the high-pressure side refrigerant pressure reaches the predetermined value, the refrigerant pressure on the high-pressure side becomes the control factor of both decompression sections 113 . 23 is used, so that the increase speed of the high-pressure side refrigerant pressure can be promoted, and thereby it is possible that the cycle operation quickly goes into the high-efficiency operating state. In addition, after the refrigerant pressure on the high pressure side has reached the predetermined pressure, the refrigerant state such as that of the compressor may be increased 11 discharged refrigerant pressure or the refrigerant temperature, but before decompression, through the expansion valve 113 and the expansion valve 23 be set to a refrigerant state in which the heat radiation efficiency in the radiator 12 becomes optimal. That is, after the refrigerant pressure on the high pressure side has reached the predetermined pressure, the refrigerant state on the high pressure side (eg, the refrigerant temperature at the discharge port of the compressor 11 , the refrigerant pressure on the downstream side of the radiator 12 ) are set to the refrigerant state in which the heat radiation efficiency in the radiator 12 becomes optimal.

In addition, the temperature difference between the refrigerant in the first evaporator 14 and the refrigerant in the second evaporator 24 be set to a suitable temperature difference, allowing frost of the first evaporator 4 and the second evaporator 24 , which are arranged in the air flow direction AA, limited and the heat-absorbing effect of the outer fluid in the first evaporator 14 and the second evaporator 24 can be effectively improved.

In the refrigeration cycle device with the in 4 As shown, the two evaporators are arranged independently downstream of the respective decompression portions. Therefore, by adjusting the opening areas of the respective decompression portions, the refrigerant evaporation temperatures in the respective evaporators can be freely set. For example, the refrigerant evaporation temperature on the upstream air side is made higher, and the refrigerant evaporation temperature on the downstream air side is made lower. In this case, it is possible for the frost to be evenly distributed on each of the evaporators, thereby reducing the frequency of defrosting times.

In the present embodiment, the high-pressure side refrigerant state becomes from the discharge port of the compressor 11 to the expansion valves 113, 23 as the control factor of one of the two variable expansion valves 113, 23, and the evaporator temperature difference is used as the control factor for the other of the two variable expansion valves 113 . 23 used. Therefore, the high-pressure side refrigerant state can be adjusted so that the heat radiation performance of the radiator 12 can be maximally increased and the evaporator temperature level of the first and second evaporators 14 . 24 can be set to a desired state. For example, the refrigerant evaporation temperature on the upstream air side may be made higher under a light freezing condition, and the refrigerant evaporation temperature on the downstream air side may be made lower.

In the refrigeration cycle device of the present embodiment, throttle means such as constriction, etc., may be set at a position in the refrigeration cycle passage 10 between the refrigerant downstream side of the first evaporator 14 and the downstream connection portion of the refrigerant branch passage 20A, so that the temperature difference, that is , the pressure difference between the refrigerant in the first evaporator 14 and the refrigerant in the second evaporator 24 can be determined.

Other Embodiments

While the present invention has been described in conjunction with the preferred embodiments thereof with reference to the accompanying drawings, it is to be noted that various changes and modifications will become apparent to those skilled in the art.

For example, in the above-described embodiments, after the refrigerant pressure on the high-pressure side has reached the predetermined pressure, the nozzle portion becomes 13a or the expansion valve 113 controlled based on the refrigerant pressure on the high pressure side, and the expansion valve 23 is based on the refrigerant temperature difference between the first evaporator 14 and the second evaporator 24 controlled. However, the tax factor can be set vice versa.

In the embodiments described above, the nozzle portion 13a or the expansion valve 113 controlled as the control factor using the refrigerant pressure on the high pressure side. The nozzle portion 13a or the expansion valve 113 However, it can be controlled using the refrigerant temperature on the high pressure side as the control factor. For example, the decompression amount of the nozzle portion may be 13a or the expansion valve 113 based on the refrigerant temperature detected by the discharge temperature sensor 91, which is a discharge refrigerant detecting portion configured to be the temperature of the refrigerant discharged from the compressor 11 To detect discharged refrigerant to be controlled.

As the refrigerant temperature at the discharge port of the compressor 11 In this case, as the control factor, it is possible that the compressor 11 is operated under a condition without the heat-resistant temperature of the compressor 11 to exceed, and thereby it is possible to limit the life reduction in the compressor.

In the above-described embodiments, the refrigerant pressure on the high pressure side is rapidly changed by using the refrigerant pressure on the high pressure side as the control factor for the two decompression portions until the refrigerant pressure on the high pressure side has reached the predetermined value. However, the refrigerant pressure on the high-pressure side may be quickly changed by using the refrigerant pressure or the refrigerant temperature on the high-pressure side as the control factors of the two decompression portions until the refrigerant temperature on the high-pressure side has reached the predetermined value. In addition, the switching of the control operation may be determined based on a predetermined time set in consideration of the change of the refrigerant pressure or the refrigerant temperature on the high-pressure side without being limited to the high-pressure side refrigerant pressure or the high-pressure side refrigerant temperature directly detected.

In the embodiments described above, the refrigerant temperature in the first evaporator 14 from the temperature sensor 93 detected on the refrigerant inlet side of the first evaporator 14 and the refrigerant temperature in the second evaporator 24 is from the temperature sensor 94 detected on the refrigerant inlet side of the second evaporator 24 located. The temperature sensors for detecting the refrigerant temperatures in the first evaporator 14 and in the second evaporator 24, however, in each case in the refrigerant passages of the first and second evaporators 14 . 24 or at refrigerant outlet sides of the first and second evaporators 14 . 24 to be ordered. Alternatively, the temperature sensor may be disposed on the surface of a refrigerant passage member such as a refrigerant piping in the first or second evaporator 14 . 24 may be arranged or may be disposed inside the refrigerant passage member to directly detect the refrigerant temperature in the refrigerant piping.

In the above-described embodiments, the expansion valve 23 becomes based on the refrigerant temperature difference between the two evaporators 14 and 24 controlled. The expansion valve 23 however, can be controlled based on a physical quantity representative of the refrigerant pressure difference between the two evaporators 14 . 24 is decisive. The refrigerant temperature difference between the two evaporators 14 and 24 is a physical quantity that governs the refrigerant pressure difference between the two evaporators 14 and 24.

For example, a first evaporator refrigerant pressure detection section configured to increase the pressure of the first evaporator 14 to detect a flowing refrigerant, and a second evaporator refrigerant pressure detecting portion, which is constructed to the pressure of the second evaporator 14 be detected flowing refrigerant to be provided. In this case, the pressure decompression amount of the expansion valve 23 are controlled based on a difference between the refrigerant pressure detected by the first evaporator refrigerant pressure detecting portion and the refrigerant pressure detected by the second evaporator refrigerant pressure detecting portion. Accordingly, the refrigerant pressure in the first evaporator 14 and the refrigerant pressure in the second evaporator 24 are detected directly, and the decompression amount of the expansion valve 23 can be controlled based on the actual refrigerant pressure difference.

In the above-described respective embodiments, the decompression portion is disposed in each of the two branched refrigerant passages, that is, the two decompression portions are arranged one by one for the two branched refrigerant passages. However, the decompression portion may be disposed in each of three or more than three branched refrigerant passages, and the present invention may be applied to at least two of the three or more branched refrigerant passages.

In the embodiments described above, the present invention is applied to the refrigeration cycle device for water heating, but it can be applied to a refrigeration cycle device for the other use.

In the above-described embodiments, any types of refrigerants may be used for the refrigeration cycle device. Any supercritical refrigerant cycle or subcritical refrigerant cycle refrigerant such as freon based refrigerant, HC based CFC substitute, carbon dioxide (CO2) or the like may be used.

Here Freon is a generic term for organic chemicals that consist of carbon, fluorine, chlorine and hydrogen. The Freon based refrigerant includes HCFC-based refrigerant and HFC-based refrigerant, which is commonly used as a CFC substitute without ozone reduction.

In addition, the HC (carbon-hydrogen) based refrigerant is a natural refrigerant containing hydrogen and carbon. For example, the HC-based refrigerant is R600a (isobutene), R290 (propane) or the like.

It should be understood that such changes and modifications are within the scope of the present invention as defined by the appended claims.

Claims (11)

A refrigeration cycle device, comprising: a compressor (11) configured to suck, compress and expel refrigerant; a radiator (12) configured to perform the heat radiation of the refrigerant discharged from the compressor (11); a first decompression amount decompression portion (13a, 113) configured to decompress and expand the refrigerant flowing out of the radiator (12); a first evaporator (14) arranged to evaporate the refrigerant decompressed in the first decompression section (13a, 113); a circulation passage (10) through which the compressor (11), the radiator (12), the first decompression section (13a, 113) and the first evaporator (14) are connected in a circuit so that the refrigerant evaporated in the first evaporator (14) is sucked into the compressor (11); a branch passage (20) provided to be branched from the circulation passage (10) at a position between the radiator (12) and the first decompression portion (13a, 113), so that a part of the radiator (12) flowing refrigerant bypasses the first decompression portion (13a, 113) and merges with the refrigerant flowing out of the first decompression portion (13a, 113) toward the compressor (11); a second variable decompression amount decompression section (23) located in the branching section (20) for decompressing and expanding the refrigerant flowing out of the radiator (12); a second evaporator (24) located in the branch passage (20) for evaporating the refrigerant decompressed in the second decompression section (23); and a control section (100) for controlling the decompression amounts of the first decompressing section (13a, 113) and the second decompressing section (23), wherein the first evaporator (14) and the second evaporator (24) are arranged so that an external fluid flows after the first decompressing section Passing through the first evaporator (14) through the second evaporator (24), the refrigeration cycle device being characterized in that: the control section (100) determines the decompression amount of the first decompression section (13a, 113) or the second decompression section (23) based on a decompression amount Pressure or a temperature of the refrigerant discharged from the compressor (11) before being decompressed by the first and second decompression portions (13a, 113, 23); and the control section (100) determines the decompression amount of the other of the first decompression section (13a, 113) and the second decompression section (23) based on a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) on a physical quantity, which is relevant for the pressure difference controls. Refrigeration cycle device according to Claim 1 fuel injector comprising: an ejector (13) having a nozzle portion (13a) that decompresses and expands the refrigerant flowing out of the radiator (12) by converting the pressure energy of the refrigerant into its velocity energy, a refrigerant suction port (13b) from the refrigerant is sucked by a refrigerant flow discharged from the nozzle portion (13a), and a pressure increasing portion (13c, 13d) in which the pressure of the refrigerant is increased by converting the velocity energy into the pressure energy, while the refrigerant discharged from the nozzle portion (13a) and refrigerant sucked from the refrigerant suction port (13b), wherein the first decompressing portion (13a) is the nozzle portion (13a), and the branch portion (20) has a downstream end connected to the refrigerant suction port (13b), so that the in the second evaporator (24) evaporated refrigerant in the Kältemittelsaugöff (13b) flows. Refrigeration cycle device according to Claim 1 or Claim 2 further comprising: a pressure detecting section (92) arranged to detect the pressure of the refrigerant discharged from the compressor (11) before being decompressed by the first and second decompression sections (13a, 113, 23), the control section (13) 100) controls the decompression amount of the one first decompressing portion (13a, 113) or the second decompressing portion (23) based on the pressure detected by the pressure detecting portion (92). Refrigeration cycle device according to Claim 1 or Claim 2 , which further comprises: an ejection refrigerant temperature detecting portion (91) arranged to detect the temperature of the refrigerant discharged from the compressor (11), the control portion (100) determining the decompression amount of the first decompression portion (13a, 113) or second decompression portion (23) controls based on the refrigerant temperature detected by the ejection refrigerant temperature detecting portion (91). Refrigeration cycle device according to any one of Claims 1 to 4 semiconductor device comprising: a first evaporator refrigerant pressure detecting section arranged to detect the pressure of the refrigerant flowing into the first evaporator (14); and a second evaporator refrigerant pressure detection section arranged to detect the pressure of the refrigerant flowing into the second evaporator (24), the control section (100) based on the decompression amount of the other of the first decompression section (13a, 113) and the second decompression section (23) on a difference between the refrigerant pressure detected by the first evaporator refrigerant pressure detecting portion and the refrigerant pressure detected by the second evaporator refrigerant pressure detecting portion. Refrigeration cycle device according to any one of Claims 1 to 4 semiconductor device comprising: a first evaporator refrigerant temperature detecting section (93) arranged to detect the temperature of the refrigerant flowing into the first evaporator (14); and a second evaporator refrigerant temperature detecting portion (94) arranged to detect the temperature of the refrigerant flowing into the second evaporator (24), the control portion (100) determining the decompression amount of the other of the first decompressing portion (13a, 113) and the second decompressing portion (13). 23) using a difference between the refrigerant temperature detected by the first evaporator refrigerant temperature detecting portion (93) and the refrigerant temperature detected by the second evaporator refrigerant temperature detecting portion (94) as a physical quantity that is indicative of the pressure difference. Refrigeration cycle device according to any one of Claims 1 to 6 wherein the control section (100) controls the decompression amount of the other of the first decompression section (13a, 113) and the second decompression section (23) so that a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24 ) or a physical quantity relevant to the pressure difference corresponds to a target value, and the control section (100) sets the target value according to an environmental condition of the radiator (12) and / or the first evaporator (14) and / or the second evaporator (24 ) changes. Refrigeration cycle device according to any one of Claims 1 to 7 wherein the control section (100) controls the decompression amount of the other of the first decompression section (13a, 113) and the second decompression section (23) so that a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24 ) or a physical quantity relevant to the pressure difference corresponds to a target value, and the control section (100) changes the target value according to an outer surface temperature of the first evaporator (14) and / or the second evaporator (24). Refrigeration cycle device according to any one of Claims 1 to 8th wherein the control section (100) at a time immediately after an operation start of the compressor (11) the decompression amount of the first decompression section (13a, 113) and the decompression amount of the second decompression section (23) based on a pressure or a temperature of the compressor ( 11) before being decompressed by the first and second decompression sections (13a, 113, 23), and the control section (100) after the pressure or temperature of the refrigerant discharged from the compressor (11) is decompressed by the first and second decompression portions (13a, 113, 23) has reached a predetermined value, the decompression amount of the one first decompression portion (13a, 113) or the second decompression portion (23) based on the pressure or the temperature of the refrigerant discharged from the compressor (11) before decompressing by the first and second decompression tabs sections (13a, 113, 23) and the control section (100) controls the decompression amount of the other of the first decompressing section (13a, 113) and the second one Decompression section (23) based on a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) or based on a physical quantity that is decisive for the pressure difference controls. Refrigeration cycle device according to any one of Claims 1 to 8th wherein the control section (100) determines the pressure or the temperature of the refrigerant discharged from the compressor (11) before decompressing by the first and second decompression sections (13a, 113, 23) according to an ambient condition of the radiator (12) and / or the first The evaporator (14) and / or the second evaporator (24) changes, the control section (100) until the pressure or the temperature of the expelled refrigerant from the compressor (11) before decompression by the first and second decompression sections (13a, 113, 23) reaches a predetermined value, the decompression amount of the first decompression portion (13a, 113) and the decompression amount of the second decompression portion (23) based on the pressure or the temperature of the refrigerant discharged from the compressor (11) before being decompressed by the first and second Decompression sections (13a, 113, 23) controls, the control section (100) after the pressure or the temperature ur of the refrigerant discharged from the compressor (11) has reached the predetermined value before being decompressed by the first and second decompression sections (13a, 113, 23), the decompression amount of either one of the first decompression section (13a, 113) or the second compression section (23 ) based on the pressure or the temperature of the refrigerant discharged from the compressor (11) before being decompressed by the first and second decompression sections (13a, 113, 23), and the control section (100) determines the decompression amount of the other of the first decompression section (13a , 113) and second decompressing section (23) based on a pressure difference between the refrigerant in the first evaporator (14) and the refrigerant in the second evaporator (24) or based on a physical quantity that governs the pressure difference controls. Refrigeration cycle device according to Claim 1 wherein each of the first and second decompressing sections (113, 23) is an expansion valve (113, 23).

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