JP2002318018A - Ejector cycle and gas and liquid separator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a structure capable of returning lubricating oil into a compressor, in an ejector cycle. SOLUTION: The ejector cycle is provided with a compressor, a radiator for cooling refrigerant discharged out of the compressor, an evaporator for evaporating the refrigerant to absorb the heat of the same, an ejector 400, reducing the pressure to expand the refrigerant flowing out of the radiator and sucking gas phase refrigerant evaporated in the evaporator to convert an expansion energy into a pressure energy and increase the suction pressure of the compressor, a gas and liquid separator 500, storing the refrigerant by separating the gas and liquid two-phase refrigerant from the ejector 400 and supplying the gas-phase refrigerant to the suction side of the compressor, while supplying the liquid phase refrigerant to the evaporator, and an oil returning hole 543, installed in the gas and liquid separator 500 for guiding the lubricating oil in the gas and liquid separator 500 into the compressor 100. According to this method, the lubricating oil can be returned into the compressor.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a method for reducing the pressure of a refrigerant, expanding the refrigerant, and sucking a vapor-phase refrigerant evaporated in an evaporator.
An ejector cycle having an ejector for converting expansion energy (kinetic energy discarded by a decompressor such as an expansion valve in a normal vapor compression refrigeration cycle) into pressure energy to increase a suction pressure of a compressor, and an ejector cycle. The present invention relates to a gas-liquid separator.

[0002]

SUMMARY OF THE INVENTION The present invention is directed to returning lubricating oil to a compressor as described in a seventh embodiment described below, and as described in the 24th and 25th embodiments described below.
It is to achieve at least one of improving the installation (mounting) of the ejector cycle.

[0003]

According to the present invention, in order to achieve the above object, according to the first aspect of the present invention, a compressor (100) for sucking and compressing a refrigerant and a compressor discharged from the compressor (100) are provided. A radiator (200) for cooling the refrigerant, an evaporator (300) for evaporating the refrigerant and absorbing heat, and a radiator (200)
Ejector (400) that decompresses and expands the refrigerant flowing out of the evaporator to suction the vapor-phase refrigerant evaporated in the evaporator (300), and converts expansion energy into pressure energy to increase the suction pressure of the compressor (100). And separating the gas-liquid two-phase refrigerant from the ejector (400) into a gas-phase refrigerant and a liquid-phase refrigerant to store the refrigerant, and supplying the gas-phase refrigerant to the suction side of the compressor (100). The evaporator (30
0) a gas-liquid separator (500) to be supplied to the gas-liquid separator (500); (5
43).

[0004] Thus, lubricating oil can be returned to the compressor.

[0005] According to the second aspect of the present invention, the ejector increases the suction pressure of the compressor by decompressing and expanding the refrigerant to suck the vapor-phase refrigerant evaporated in the evaporator, and converting the expansion energy into pressure energy. (400) applied to an ejector cycle having an ejector (400)
The gas-liquid two-phase refrigerant is separated into a gas-phase refrigerant and a liquid-phase refrigerant, and the liquid-phase refrigerant is stored in the tank unit (551), and the gas-phase refrigerant is supplied to the suction side of the compressor (100). A gas-liquid separator (500) for supplying a phase refrigerant to an evaporator (300), wherein an ejector (4) is provided in a tank (551).
00), the ejector (400) is arranged so that the refrigerant flowing from the upper side to the lower side flows, and a part (552, 553) of the tank section (551) is formed by a diffuser (400) of the ejector (400). 430).

[0006] Thus, a diffuser (430) having a refrigerant passage having a sufficient size can be formed as compared with a case where the diffuser (430) is formed only by the ejector (400).

In addition, since the space inside the gas-liquid separator (500) is used to constitute the diffuser (430) having a sufficiently large refrigerant passage, the performance of the ejector (400) is improved while improving the performance of the ejector (400). 400) can be reduced, and the installation (mounting) of the ejector cycle can be improved.

According to the third aspect of the present invention, the ejector increases the suction pressure of the compressor by reducing the pressure of the refrigerant and expanding the refrigerant to suck the vapor-phase refrigerant evaporated by the evaporator, and converting the expansion energy into pressure energy. (400) applied to an ejector cycle having an ejector (400)
The gas-liquid two-phase refrigerant is separated into a gas-phase refrigerant and a liquid-phase refrigerant, and the liquid-phase refrigerant is stored in the tank unit (551), and the gas-phase refrigerant is supplied to the suction side of the compressor (100). A gas-liquid separator (500) for supplying a phase refrigerant to an evaporator (300), wherein an ejector (4) is provided in a tank (551).
00), the ejector (400) is arranged so that the refrigerant flowing from the upper side to the lower side flows, and the refrigerant flows downstream from the refrigerant outlet of the diffuser (430) of the ejector (400). Is characterized in that the flow direction is changed from a downward direction to an upward direction.

Accordingly, the present invention is an ejector-integrated gas-liquid separator, so that the pace for mounting the ejector (400) can be reduced and the installation (mounting) of the ejector cycle can be improved.

[0010] Incidentally, the reference numerals in parentheses of the above means are examples showing the correspondence with specific means described in the embodiments described later.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment)
The ejector cycle according to the present invention is applied to a vehicle air conditioner using carbon dioxide as a refrigerant, and FIG. 1 is a schematic view of an ejector cycle according to the present embodiment.

Reference numeral 100 denotes a compressor for obtaining a driving force from a driving source (not shown) such as a running engine to suck and compress the refrigerant, and 200 for heat exchange between the refrigerant discharged from the compressor 100 and outdoor air. Radiator (gas cooler) that cools the refrigerant
It is.

Reference numeral 300 denotes an evaporator which exhibits a refrigerating ability by exchanging heat between air blown into a room and a liquid-phase refrigerant to evaporate the liquid-phase refrigerant, and 400 decompresses and expands the refrigerant flowing out of the radiator 200. This is an ejector that sucks the vapor-phase refrigerant evaporated by the evaporator 300 and converts expansion energy into pressure energy to increase the suction pressure of the compressor 100.

The ejector 400 is provided with the radiator 200
Energy (pressure head) of high-pressure refrigerant flowing out of
410 that converts pressure into velocity energy (velocity head) to decompress and expand the refrigerant, and a mixing section 420 that suctions a vapor-phase refrigerant evaporated in the evaporator 300 by a high-velocity refrigerant flow (jet flow) injected from the nozzle 410. And a diffuser 430 for converting the velocity energy into pressure energy and increasing the pressure of the refrigerant while mixing the refrigerant injected from the nozzle 410 and the refrigerant sucked from the evaporator 300.
Etc.

Reference numeral 500 denotes a gas-liquid separator for storing the refrigerant into which the refrigerant flowing out of the ejector 400 flows, separates the refrigerant into the gaseous refrigerant and the liquid-phase refrigerant, and stores the refrigerant.
The separated gas-phase refrigerant is drawn into the compressor 100, and the separated liquid-phase refrigerant is drawn into the evaporator 300.

Reference numeral 600 denotes a first decompressor (throttling means) for decompressing the liquid-phase refrigerant sucked from the gas-liquid separator 500 to the evaporator 300 side. Pressure (evaporation pressure) is surely reduced.

Next, the general operation of the ejector cycle will be described.

When the compressor 100 starts, the gas-liquid separator 5
From 00, the gas-phase refrigerant is sucked into the compressor 100, and the compressed refrigerant is discharged to the radiator 200. And radiator 2
The refrigerant cooled in 00 is decompressed and expanded in the nozzle 410 of the ejector 400 and sucks the refrigerant in the evaporator 300.

Next, while the refrigerant sucked from the evaporator 300 and the refrigerant blown out from the nozzle 410 are mixed in the mixing section 420, the dynamic pressure thereof is converted to static pressure by the diffuser 430, and the gas-liquid separator 500 Return to

On the other hand, the evaporator 300 is
Since the refrigerant inside is sucked, the liquid-phase refrigerant flows into the evaporator 300 from the gas-liquid separator 500, and the refrigerant flowing into the evaporator 300 is
It absorbs heat from the air that blows into the room and evaporates.

FIG. 2 is a ph diagram showing the operation of the ejector cycle according to the present embodiment, and the numbers shown in FIG. 2 indicate the state of the refrigerant at the positions indicated by the numbers in FIG.

At this time, the suction pressure increase Δ
P is a refrigerant inlet (point 2 shown in FIG. 2) of the nozzle 410 and a refrigerant outlet (point 3 shown in FIG. 2) of the nozzle 410, although its absolute value changes depending on the efficiency in the mixing section 420 and the diffuser 430. The larger the specific enthalpy difference (adiabatic heat drop) in the above, the larger the difference.

Next, the operation and effect of this embodiment will be described.

In this embodiment, since carbon dioxide is used as the refrigerant, as shown in FIG.
The pressure of the refrigerant before being depressurized by the (nozzle 410) is increased by the compressor 100 to a value higher than the critical pressure of the refrigerant (supercritical region), and then the pressure is expanded under reduced pressure.

Therefore, since the pressure difference at the time of decompression and expansion increases, the specific enthalpy difference between the refrigerant inlet of the nozzle 410 (point indicated by 2 in FIG. 2) and the refrigerant outlet of the nozzle 410 (point indicated by 3 in FIG. 2). (Adiabatic heat drop) can be increased. As a result, the expansion energy generated at the time of pressure reduction can be more reliably recovered, so that the suction pressure increase ΔP can be increased, and the coefficient of performance (efficiency) of the ejector cycle can be increased.
Can be improved.

By the way, in the supercritical region, the gas-phase refrigerant also has a density substantially equal to that of the liquid-phase state, so that the refrigerant depressurized and expanded by the ejector 400 (nozzle 410) is not a liquid-phase refrigerant. It is accelerated to approximately the same speed as the phase refrigerant. For this reason, the energy conversion efficiency in the ejector 400 (nozzle 410) is increased (about twice as much as Freon), so that the expansion energy generated at the time of decompression can be more reliably recovered. Therefore, since the suction pressure increase ΔP can be increased, the coefficient of performance (efficiency) of the ejector cycle can be improved.

Also, the isentropic line of carbon dioxide on the saturated liquid line side from the critical point has a change in specific enthalpy (Δh) with respect to a change in pressure (ΔP) as compared with Freon.
Is large (= Δh / ΔP), the ejector 400
When the pressure is expanded under reduced pressure, the specific enthalpy difference (adiabatic heat drop) between the refrigerant inlet of the nozzle 410 and the refrigerant inlet of the diffuser 430 can be increased as compared with an ejector cycle using Freon as a refrigerant.

As described above, according to the present embodiment, the coefficient of performance (efficiency) of the ejector cycle can be improved while eliminating the use of chlorofluorocarbon as the refrigerant using carbon dioxide.

FIG. 3 shows the coefficient of performance (COP), refrigeration capacity (cooling capacity) and high-pressure side pressure (ejector 400 (nozzle 410)) of the ejector cycle according to this embodiment.
As shown in FIG. 3, as the high pressure side pressure is increased, the refrigeration capacity is increased, but the high pressure side pressure is excessively increased. And the coefficient of performance deteriorates, so that the ejector 40 is controlled to maintain the high pressure side pressure at which the coefficient of performance is maximized.
0 (nozzle 410) shape and size, and compressor 1
It is desirable to control and adjust the discharge flow rate of 00 and the like.

(Embodiment 2) In the ejector cycle, as described above, the expansion energy is recovered by the ejector 400 and the suction pressure of the compressor 100 is increased to reduce the driving force of the compressor 100. However, since the refrigerant pressure on the high pressure side is as high as supercritical or higher, the diffuser 43
There is a possibility that the refrigerant pressure at the outlet side of 0 may be higher than the critical pressure.

When the refrigerant pressure at the outlet side of the diffuser 430 becomes equal to or higher than the critical pressure, the pressure in the gas-liquid separator 500 also becomes equal to or higher than the critical pressure. Since the liquid-phase refrigerant cannot be separated from the refrigerant, the liquid-phase refrigerant cannot be supplied to the evaporator 300.

Therefore, in the present embodiment, as shown in FIG. 4, a second decompressor (pressure adjusting means) 710 for decompressing the refrigerant pressurized by the ejector 400 is disposed downstream of the ejector 400 in the refrigerant flow. At the same time, the pressure of the refrigerant after being pressurized by the ejector 400 in the pressure reducer 710 is adjusted to a pressure lower than the critical pressure (gas-liquid two-phase region).

(Third Embodiment) In the second embodiment, a second decompressor (pressure adjusting means) 710 is provided downstream of the flow of the refrigerant in the ejector 400, and the pressure of the refrigerant after the pressure in the ejector 400 is increased. Although the pressure was adjusted to be lower than the critical pressure, in the present embodiment, as shown in FIG.
A third decompressor (pressure adjusting means) 72 is provided upstream of the refrigerant flow 0.
0, and the ejector 40
The pressure of the refrigerant after being pressurized at 0 is adjusted to a pressure lower than the critical pressure (gas-liquid two-phase region).

By the way, the third pressure reducer 7 according to the present embodiment
20 and the second decompressor 710 according to the second embodiment both adjust the refrigerant pressure after being pressurized by the ejector 400 so as to be lower than the critical pressure. However, the refrigerant pressure on the high pressure side and the ejector 400 Depending on the efficiency of
Even if the refrigerant is not decompressed by the decompressors 710 and 720, the pressure of the refrigerant after the pressure is increased by the ejector 400 may be lower than the critical pressure.

In such a case, as in the second embodiment, the second decompressor 7 is disposed downstream of the refrigerant flow of the ejector 400.
When 10 is provided, the second decompressor 710 becomes a flow resistance (pressure loss) of the refrigerant, which is a factor of reducing the cycle efficiency.

On the other hand, if the third decompressor 720 is provided upstream of the refrigerant flow of the ejector 400 as in the present embodiment, the pressure is necessarily reduced in the supercritical region. It is possible to prevent an increase in the flow resistance (pressure loss) of the refrigerant while adjusting the pressure of the refrigerant after the pressure is increased to a value lower than the critical pressure.

(Fourth Embodiment) In the first to third embodiments,
After flowing out of the ejector 400 (the diffuser 430)
) Is separated into a gas-phase refrigerant and a liquid-phase refrigerant by the gas-liquid separator 500, the gas-phase refrigerant flows out to the suction side of the compressor 100, and the liquid-phase refrigerant is discharged to the evaporator 300 side However, in the present embodiment, as shown in FIG.
00 at the refrigerant outlet of the mixing section 420,
The liquid-phase refrigerant is separated and extracted from the refrigerant before flowing out of the ejector 400, and the separated and extracted liquid-phase refrigerant is supplied to the evaporator 300.
And the gas-phase refrigerant is supplied to the suction side of the compressor 100.

Next, the operation and effect of this embodiment will be described.

FIG. 7A is a numerical simulation result showing the relationship between the ejector efficiency ηe and the refrigerating capacity Qe (= Ge × Δh) generated in the evaporator 300, and FIG. 7B is a graph showing the relationship between the ejector efficiency ηe and the ejector efficiency ηe. The suction pressure increase ΔP of the compressor 100
7C is a numerical simulation result showing a relationship between a specific enthalpy difference Δh between the refrigerant inlet side and the refrigerant outlet side of the evaporator 300, and FIG. 7C shows the ejector efficiency ηe and the mass flow rate of the refrigerant sucked into the compressor 100. 9 is a numerical simulation result showing a relationship between Gr and the mass flow rate Ge of the refrigerant flowing in the evaporator 300.

As is clear from FIG. 7, when the ejector efficiency ηe increases, the suction pressure increase ΔP increases, and the work of the compressor 100 can be reduced. , Gas-liquid separator 5
Since the pressure inside 00 increases, the specific enthalpy of the refrigerant when flowing into the evaporator 300 increases, as shown by the broken line in FIG. Therefore, the evaporator 300
Enthalpy difference Δh between the refrigerant inlet side and the outlet side becomes smaller, and the refrigerating capacity Qe generated in the evaporator 300 also becomes smaller.

Incidentally, the ejector efficiency ηe is the mass flow rate G of the refrigerant flowing through the radiator 200 (high pressure side heat exchanger).
The product of n and the enthalpy difference Δie between the inlet and the outlet of the nozzle 410 is used as a denominator, and the numerator includes a refrigerant flow rate Gn indicating how much energy is recovered as the work of the compressor 100 and an evaporator 300 (low pressure side heat exchanger). Is defined with the sum of the mass flow rate Ge of the refrigerant flowing through and the pressure recovery ΔP at the ejector 400. Specifically, the ejector 400
Considering the velocity energy of the suction refrigerant before being sucked into
It was defined by the following Equation 1.

[0042]

(Equation 1)

On the other hand, in the present embodiment, the liquid-phase refrigerant is separated and extracted from the refrigerant before flowing out of the ejector 400, and the separated and extracted liquid-phase refrigerant is supplied to the evaporator 300 side. As shown by the solid line, even if the suction pressure increase ΔP increases, the pressure increase ΔPe of the liquid-phase refrigerant flowing out of the gas-liquid separator 500 can be made smaller than the suction pressure increase ΔP.

Therefore, it is possible to prevent the specific enthalpy of the refrigerant from flowing into the evaporator 300 from becoming large, so that the specific enthalpy difference Δhe between the refrigerant inlet side and the refrigerant outlet side of the evaporator 300 can be increased. , Evaporator 30
The refrigeration capacity Qe generated at 0 can be increased.

FIG. 9 is a numerical curve showing the relationship between the radial position from the refrigerant outlet of the nozzle 410 to the refrigerant outlet of the diffuser 430 with reference to the center of the cross section of the refrigerant passage of the ejector 400 and the flow rate of the refrigerant. This is the result of the translation.

In the numerical simulation,
It is assumed that the nozzle 410, the mixing unit 420, and the diffuser 430 have a rotationally symmetric shape, and the flow velocity distribution is symmetrically distributed with respect to the central part (reference). Further, the refrigerant flow velocity (gas velocity) indicates a magnitude when the velocity at the nozzle 410 outlet is set to 1.

As apparent from FIG. 9, the jet flow (driving gas) flowing out of the nozzle 410 decreases its flow velocity while accelerating the suction of the refrigerant from the evaporator 300. At this time, mixing is performed so that the flow rate of the suction gas (suction flow gas) sucked from the evaporator 300 and the flow rate of the driving flow gas are substantially equal at the refrigerant outlet of the mixing section 420 (the refrigerant inlet of the diffuser 430). The mixed refrigerant flows into the diffuser 430 and increases the pressure while decreasing the flow velocity.

That is, the refrigerant (driving gas) flowing through the ejector 400 stops sucking the suction gas at the refrigerant outlet of the mixing section 420 and its pressure is increased by the diffuser 430. As described above, if the gas-liquid separator 500 is provided at the refrigerant outlet of the mixing section 420 and the separated and extracted liquid-phase refrigerant is supplied to the evaporator 300 side, the suction pressure increase ΔP is secured and the high ejector efficiency ηe is maintained. In addition, it is possible to prevent the specific enthalpy of the refrigerant when flowing into the evaporator 300 from increasing, and to increase the refrigeration capacity Qe.

(Fifth Embodiment) In the present embodiment, as shown in FIG. 10, the liquid-phase refrigerant is separated from the refrigerant flowing through the ejector 400 at the refrigerant outlet side of the mixing section 420 as in the fourth embodiment. The extracted, separated and extracted liquid-phase refrigerant flows out to the evaporator 300 side, and is added to a gas-liquid separator 500 (hereinafter, referred to as a first gas-liquid separator 500).
The refrigerant flowing out of the (diffuser 430) is separated into a gas-phase refrigerant and a liquid-phase refrigerant, and the separated liquid-phase refrigerant is supplied to the evaporator 3
A second gas-liquid separator 510 is provided to supply the gaseous refrigerant to the suction side of the compressor 100 while supplying the gaseous refrigerant to the suction side of the compressor 100.

As a result, if the first gas-liquid separator 500
Even if it is not possible to separate and extract a sufficient amount of the liquid-phase refrigerant at, the second gas-liquid separator 510 separates the refrigerant flowing out of the ejector 400 into a gas-phase refrigerant and a liquid-phase refrigerant, Since the refrigerant is supplied to the evaporator 300, a sufficient amount of the liquid-phase refrigerant can be supplied to the evaporator 300.

The pressure in the second gas-liquid separator 500 is
Since the pressure becomes the pressure before the pressure is increased by the diffuser 430, in the present embodiment, the first gas-liquid separator 500 and the evaporator 3
No decompressor is provided in the refrigerant passage connecting to 00. On the other hand, the pressure in the second gas-liquid separator 510 becomes a pressure increased by the diffuser 510, so that the pressure reducing device 6 is provided in the refrigerant passage connecting the second gas-liquid separator 510 and the evaporator 300.
FIG. 11 shows the position of the refrigerant in the radial direction with respect to the center of the cross section of the refrigerant passage of the ejector 400 and the ratio of the liquid-phase refrigerant in the refrigerant. This is a numerical simulation result showing the relationship with (liquid volume ratio). As is clear from FIG. 11, the liquid volume ratio is the largest at the center of the cross section of the refrigerant passage. The calculation conditions are the same as in the fourth embodiment. In FIG. 11, the solid line indicates the vicinity of the exit of the nozzle 410, the broken line indicates the vicinity of the exit of the mixing unit 420, and the one-dot chain line indicates the diffuser 4
It shows the vicinity of exit 30.

Therefore, in the present embodiment, the introduction opening 50 of the refrigerant introduction pipe 501 for guiding the refrigerant to the first gas-liquid separator 500.
2 is arranged at the center of the cross section of the refrigerant passage of the ejector 400 (on the refrigerant outlet side of the mixing section 420),
Liquid phase refrigerant is efficiently separated and extracted.

(Sixth Embodiment) In the present embodiment, the first gas-liquid separator 500 and the second gas-liquid separator 5 in the fifth embodiment are used.
10 is integrated into one gas-liquid separator 520 to improve the size and mountability (installability).

More specifically, as shown in FIG. 12, a casing 521 is vertically divided by a partition member 523 having a plurality of orifices (small holes) 522 such as punched metal, and a refrigerant introduction pipe 501 is partitioned. The space 524 formed below the member 523 is communicated, and the refrigerant outlet side of the ejector 400 (diffuser 530) is communicated with the space 525 formed below the partition member 523.

Then, the space 525 is communicated with the suction side of the compressor 100 so that the gas-phase refrigerant is sucked by the compressor 100.
The liquid-phase refrigerant accumulated in the space 524 is supplied to the evaporator 300 side. At this time, the orifice 522 decompresses the refrigerant flowing from the space 525 to the space 524 to reduce the pressure of the refrigerant.
Functioning as a pressure reducing means (throttling means) for suppressing the pressure increase on the side of the ejector 40 together with the partition member 523.
It functions as a disturbance prevention means for preventing the liquid-phase refrigerant in the gas-liquid separator 520 from being disturbed by the refrigerant flowing out from the zero (diffuser 530).

(Seventh Embodiment) In the present embodiment, as shown in FIG. 13, an ejector 400, a gas-liquid separator 500 and a decompressor (throttling means) 600 are integrated. State.

In FIG. 13, reference numeral 540 denotes a metal tank portion (tank main body) for separating the refrigerant ejected from the ejector 400 (diffuser 430) into a gas-phase refrigerant and a liquid-phase refrigerant and storing the separated liquid-phase refrigerant. ) And the ejector 40
0 means that the refrigerant flowing in the ejector 400 flows vertically from the lower side to the upper side in the tank section 540, and the refrigerant flowing in the ejector 400 (the diffuser 43)
The refrigerant outlet part 431 of (0) is built in the tank part 540 so as to be located above the refrigerant liquid level LS in the dunk part 540 and open upward.

At this time, the mixing section 420 is
The refrigerant passage extending to the diffuser 430 through the nozzle is substantially linear so that unnecessary pressure loss does not occur in the refrigerant, and the nozzle 410 is located outside the tank portion 540 and exposed to the atmosphere. I have.

A collision wall (jam plate) 541 against which the refrigerant flowing from the refrigerant outlet 431 collides is provided on the refrigerant outlet 431 side of the ejector 400 (diffuser 430).
Are joined to the inner wall of the tank section 540.

Incidentally, reference numeral 542 denotes a gas-phase refrigerant outlet pipe for discharging the gas-phase refrigerant accumulated above the tank section 540 to the suction side of the compressor 100.
Is formed in a U-shape by bending at approximately 180 ° in the liquid-phase refrigerant accumulated below the tank portion 540.

A bent portion 542a of the gas-phase refrigerant outflow pipe 542 located in the liquid-phase refrigerant is provided with lubricating oil mixed in the liquid-phase refrigerant (refrigeration for lubricating sliding parts in the compressor 100). An oil return hole 543 for sucking (machine oil) is provided. Note that the lubricating oil sucked from the oil return hole 543 is actually a liquid refrigerant containing a large amount of lubricating oil.

Reference numeral 543 denotes a liquid-phase refrigerant outlet pipe for discharging the liquid-phase refrigerant collected below the tank section 540 to the evaporator 300 side. A vessel 600 (in this embodiment, an orifice such as a fixed throttle having a fixed opening) is provided.

Next, the operation and effect of the ejector-integrated gas-liquid separator according to this embodiment will be described.

The refrigerant flowing out (spouting out) from the ejector 400 collides with the collision wall 541 and scatters. The liquid-phase refrigerant having a higher density and viscosity than the gas-phase refrigerant collides with the collision wall 541 and sticks. Alternatively, the liquid-phase refrigerant and the gas-phase refrigerant can be efficiently separated because they are not greatly scattered as compared with the gas-phase refrigerant. Note that the liquid-phase refrigerant that has adhered to the collision wall 541 falls down due to its own weight.

The ejector 400 (diffuser 4)
Since the refrigerant outlet portion 431 of (30) is located above the refrigerant liquid level LS in the dunk portion 540 and is open, the refrigerant flowing out (spouting) from the ejector 400 (diffuser 430) causes the inside of the tank portion 540 to be opened. Since the refrigerant can be prevented from being agitated, it is possible to prevent the refrigerant that has been gas-liquid separated from being mixed.

Further, since the refrigerant outlet 431 is open upward, the ejector 400 (the diffuser 43)
The liquid refrigerant having a high density is easily separated and extracted from the refrigerant flowing out (spouting) from 0).

When the ejector 400 is built in the gas-liquid separator 500 (tank section 540), as shown on the right side of FIG. 14, the refrigerant flowing through the ejector 400 is directed downward from the upper side. That the refrigerant outlet 431 of the ejector 400 (diffuser 430) is positioned above the refrigerant liquid level LS in the dunk part 540 (hereinafter, this means is referred to as an upper built-in type). Although it is conceivable, this upper built-in type
For the reasons described below, the vertical dimension H of the gas-liquid separator 500 (tank portion 540) is rather large.

In other words, the refrigerant outlet portion is used for both the upper built-in gas-liquid separator and the gas-liquid separator according to the present embodiment (hereinafter referred to as the lower built-in gas-liquid separator). 431 needs to be positioned above the refrigerant liquid level LS in the dunk portion 540, so that the liquid level height h1 and the nozzle 4
Assuming that the dimensions from 10 to the refrigerant outlet 431 are the same for the upper built-in type and the lower built-in type, the upper built-in type gas-liquid separator sets the size c2 above the refrigerant liquid level LS to the nozzle 410.
Needs to be larger than the size from to the refrigerant outlet 431.

On the other hand, in the lower built-in type gas-liquid separator, most of the part (mixing part 420) from the nozzle 410 to the refrigerant outlet 431 can be immersed in the liquid-phase refrigerant. The vertical dimension H of the vessel 500 (tank section 540) can be made smaller than that of the upper built-in gas-liquid separator.

By the way, from the nozzle 410 to the refrigerant outlet 43
If the dimension up to 1 is sufficiently small, the vertical dimension H of the upper built-in gas-liquid separator can be reduced to the same degree as the vertical dimension H of the lower built-in gas-liquid separator.
If the dimension from the nozzle 410 to the refrigerant outlet 431 is small, there is a high possibility that the refrigerant cannot be sufficiently sucked from the evaporator 300 and the refrigerant cannot be sufficiently pressurized by the diffuser 430.

By the way, the nozzle 410 has the radiator 20
0, the refrigerant having a relatively high temperature flows into the ejector 400, including the nozzle 410.
When the whole is built in the tank unit 540, the liquid-phase refrigerant in the tank unit 540 evaporates with the high-temperature refrigerant before being decompressed and expanded, so that a sufficient amount of the liquid-phase refrigerant is supplied to the evaporator 300. May not be possible.

On the other hand, in the present embodiment, at least the nozzle 410 of the ejector 400 is connected to the tank 5.
40, the refrigerant flowing through the tank 540 out of the refrigerant flowing through the ejector 400 is
The low-temperature refrigerant is reduced in pressure and expanded by the nozzle 410. Therefore, it is possible to prevent the liquid-phase refrigerant in the tank unit 540 from evaporating, so that a sufficient amount of the liquid-phase refrigerant can be supplied to the evaporator 300.

In this embodiment, the ejector 400 is built into the gas-liquid separator 500 so that the refrigerant flowing in the ejector 400 flows vertically from the lower side to the upper side in the tank section 540. However, the present embodiment is not limited to this, and, for example, the refrigerant flowing in the ejector 400 may flow upward from the lower side in a state inclined with respect to the horizontal plane. .

Further, in this embodiment, only the nozzle 410 is located outside the tank section 540, but in this embodiment,
For example, the mixing section 420 may be located outside the tank section 540.

In the present embodiment, the refrigerant passage from the nozzle 410 to the diffuser 430 via the mixing section 420 is substantially straight, but in the present embodiment, at least the refrigerant passage from the nozzle 410 to the mixing section 420 The diffuser 430 may be bent since the passage may be substantially straight.

It should be noted that the "coolant passage is substantially straight" here.
The term does not mean strictly on a straight line, but includes a bending that does not cause a manufacturing error or a large pressure loss.

(Eighth Embodiment) In the seventh embodiment, the refrigerant outlet 43 of the ejector 400 (diffuser 430) is used.
The refrigerant flowing out from the first side collided with the collision wall 541,
In the present embodiment, as shown in FIGS. 15 and 16, in a state where the refrigerant outlet 431 is positioned above the refrigerant liquid level LS,
The ejector 400 is moved to the tank 54 so that the refrigerant ejected from the refrigerant outlet 431 collides with the inner wall of the tank 540.
0.

Thus, the collision wall 541 can be eliminated, so that the production cost of the gas-liquid separator 500 can be reduced and the liquid-phase refrigerant and the gas-phase refrigerant can be efficiently separated.

In this embodiment, the nozzle 41
0 is located outside the tank section 540, so that the liquid-phase refrigerant in the tank section 540 can be prevented from evaporating as in the seventh embodiment, and a sufficient amount of the liquid-phase refrigerant is supplied to the evaporator 300. Can be supplied.

In this embodiment, the ejector 40
Although the longitudinal direction of the ejector 400 is set to be substantially horizontal so that the refrigerant flowing in the inner space 0 flows in a substantially horizontal direction, the present embodiment is not limited to this.
The refrigerant circulating inside 00 may flow from the lower side to the upper side in a state inclined with respect to the horizontal plane.

(Ninth Embodiment) In this embodiment, as shown in FIG. 17, heat is exchanged between refrigerant and hot water in a high-pressure side heat exchanger (radiator 200) of an ejector cycle using carbon dioxide as refrigerant. The present invention relates to an ejector cycle water heater (hereinafter, abbreviated as a water heater) for heating hot water.

Then, the evaporator 30 is removed from the gas-liquid separator 500.
An electric flow control valve (variable throttle) 730 capable of adjusting the flow rate is provided in a refrigerant passage through which the liquid-phase refrigerant supplied to 0 flows, and the gas-liquid flow control valve 730 is provided on the outlet side of the ejector 400 (diffuser 430). A first refrigerant temperature sensor 741 for detecting the temperature of the refrigerant before flowing into the separator 500 and a second refrigerant temperature sensor 742 for detecting the temperature of the refrigerant flowing into the evaporator 300 at the outlet side of the flow control valve 730 are provided. The valve opening of the flow control valve (variable throttle) 730 is controlled (adjusted) based on the temperatures detected by the temperature sensors 741 and 742.
I do.

The radiator 200 (water-refrigerant heat exchanger)
Is configured such that heat exchange is performed in a state where the refrigerant and the hot water flow in opposite directions (including a direct opposite flow). In the compressor 100, the flow rate of the refrigerant flowing into the ejector 400 becomes a predetermined value. Motor M that drives the compressor 100
The rotation speed is controlled by o.

Incidentally, reference numeral 750 denotes a hot water storage tank for keeping hot water heated by the radiator 200 in a heated state, and reference numeral 751 denotes an electric pump for circulating hot water between the hot water storage tank 750 and the radiator 200. , 743 is a hot water storage tank 75
A hot water temperature sensor for detecting the temperature of hot water within 0 is provided. Reference numeral 740 denotes an electronic control unit (ECU) that controls the valve opening of the flow control valve 730, the electric motor Mo (compressor 100), and the pump 751. .

Next, the schematic operation and features of the water heater according to the present embodiment will be described.

Hot water (hot water) stored in the hot water storage tank 750 is heated according to a request from a user of the hot water heater (user), and the amount of hot water in the hot water storage tank 750 is less than a predetermined amount. Sometimes tap water is stored in a hot water storage tank 750
Supplied to

On the other hand, when the temperature of the hot water in the hot water storage tank 750 becomes equal to or lower than the predetermined temperature, the valve opening of the flow control valve 730 is controlled to maintain a high ejector efficiency ηe, and the pump 151 and the compressor 100 Is operated to heat the hot water in the hot water storage tank 750. Here, “controlling the valve opening degree of the flow control valve 730 to maintain a high ejector efficiency ηe” is specifically performed as follows.

That is, as described above, the ejector efficiency ηe is the ratio of the pressure energy recovered (boosted) by the diffuser 430 to the expansion energy generated by the ejector 400 (nozzle 410). The increased pressure energy increases the coefficient of performance of the cycle.

As is well known, the cycle coefficient of performance is the cycle output (in this case, the amount of heat radiated from the radiator 200) with respect to the energy input to the cycle (in this case, the power consumption of the compressor 100). Say the ratio.

On the other hand, the ejector efficiency ηe is, as is clear from the above equation 1, the refrigerant flow Ge flowing through the evaporator 300 with respect to the refrigerant flow Gn flowing through the radiator 200.
Flow rate ratio α (= Ge / Gn), pressure recovery (pressure rise) ΔP at the ejector 400 (diffuser 430), enthalpy difference Δie between the entrance and exit of the nozzle 410, and the evaporator 3
From 00, it becomes a function of the flow velocity Ue of the refrigerant sucked into the ejector 400, but the flow velocity Ue (Ge · Ue2 /
The value of 2) is negligibly small and ΔP / (ρg
.DELTA.ie) decreases as the flow rate ratio .alpha. Increases, and decreases. Therefore, if the relationship between the ejector efficiency .eta.e and the flow rate ratio .alpha. Is determined using .DELTA.P / (. Rho.g. The characteristic has a maximum value as shown in FIG.

The parameter β (n) and the parameter β (n + 1) do not indicate that the parameter β (n + 1) is larger than the parameter β (n). Parameter β (n + 1)
Is different from the value of.

Therefore, with the change of the parameter β, the ejector efficiency ηe at that time at the parameter β
By controlling the valve opening of the flow control valve 730 such that the maximum value and the flow ratio α are satisfied, the ejector cycle can be operated while maintaining a high ejector efficiency ηe.

As described above, since the ejector cycle has the refrigerant flow on the high pressure side (before the pressure is reduced by the ejector 400) and the refrigerant flow on the low pressure side (the evaporator 300 side), the parameter β is set as follows. , At least the state of the high-pressure side refrigerant (enthalpy) and the function of the low-pressure side refrigerant (enthalpy).

Therefore, in the present embodiment, the ejector cycle (water heater) is controlled by determining the parameter β based on the detected temperatures of the two refrigerant temperature sensors 741 and 742 and controlling the valve opening of the flow control valve 730. Driving efficiently.

In the present embodiment, the flow control valve 7
The ejector efficiency control means for controlling the energy conversion efficiency by adjusting the depressurized amount (flow rate) of the refrigerant before flowing into the evaporator 300 is constituted by the flow control valve 7.
When the opening degree of the valve 30 is changed, the pressure and temperature in the evaporator 300 and the ejector 400 (the diffuser 43) are changed.
0), the pressure increase amount also changes, so the flow control valve (ejector efficiency control means) 730 adjusts any one of the flow ratio α, the pressure and temperature in the evaporator 300, and the pressure increase amount by the ejector 400 (diffuser 430). Thus, it can be said that the ejector efficiency ηe is adjusted.

In the present embodiment, the parameter β is determined on the basis of the temperature of the high-pressure side refrigerant and the temperature of the low-pressure side refrigerant. However, since the refrigerant state (enthalpy) can be specified also from the pressure, the refrigerant temperature Alternatively, the parameter β may be determined based on the pressure of the high-pressure side refrigerant and the pressure of the low-pressure side refrigerant.

In determining the parameter β, factors that vary depending on the environment in which the ejector cycle is operated, such as the outside air temperature, may be considered in addition to the temperature or pressure of the refrigerant.

The detection positions of sensors (detection means) for detecting the state (enthalpy) of the high-pressure side refrigerant and the state (enthalpy) of the low-pressure side refrigerant are limited to the positions shown in FIG. Instead, for example, the ejector 400
The state (enthalpy) of the high-pressure side refrigerant may be detected at the refrigerant inlet side of the refrigerant, and the state (enthalpy) of the low-pressure side refrigerant may be detected at the refrigerant outlet side of the evaporator 300.

(Tenth Embodiment) This embodiment is different from the embodiment shown in FIG.
As shown in the figure, a flow control valve 730 is disposed on the refrigerant inlet side of the ejector 400 and both refrigerant temperature sensors 74
The controller determines the parameter β based on the detected temperatures of 1, 742 and controls the valve opening of the flow control valve 730 so as to maintain a high ejector efficiency ηe.

In the present embodiment, the flow control valve 7
When the opening degree of the valve 30 is adjusted, the refrigerant pressure on the high pressure side also changes, so that the flow control valve (ejector efficiency control means) 7
30 can be said to adjust the ejector efficiency ηe by adjusting either the flow ratio α or the refrigerant pressure on the high pressure side.

(Eleventh Embodiment) In the ninth and tenth embodiments, the flow rate control valve 730 is provided in the ejector cycle to control the cycle so as to increase the ejector efficiency ηe. As shown, the flow rate control valve 730 is eliminated, and both refrigerant temperature sensors 741,
By controlling the pump 751 based on the detected temperature of 742 and controlling the flow rate of hot water for heat exchange with the high-pressure refrigerant in the radiator 200, the ejector 400 adjusts the temperature of hot water after heat exchange. In this case, the energy conversion efficiency (ejector efficiency ηe) is increased.

(Twelfth Embodiment) This embodiment is different from the twelfth embodiment shown in FIG.
, A third refrigerant temperature sensor 744 for detecting the temperature of the refrigerant flowing out of the radiator 200, and the radiator 200
Hot water temperature sensor 7 for detecting the temperature of hot water flowing into the water
45, and both refrigerant temperature sensors 741, 74
By controlling the pump 751 based on the detected temperature of No. 2 and adjusting the difference between the temperature of the refrigerant flowing through the radiator 200 and the temperature of the hot water, the energy conversion efficiency (ejector efficiency ηe) of the ejector 400 is increased. It is to become.

(Thirteenth Embodiment) This embodiment is different from the thirteenth embodiment shown in FIG.
As shown in FIG. 5, a heat exchanger (heating means) 800 for exchanging heat between the refrigerant flowing out of the radiator 200 and the refrigerant drawn into the compressor 100 is provided so that the refrigerant drawn into the compressor 100 is heated. It is composed.

Next, the operation and effect of this embodiment will be described.

In the ejector cycle, since the refrigerant pressurized by the ejector 400 (diffuser 430) is sucked into the compressor 100, the refrigerant is sucked into the compressor as compared with a normal vapor compression refrigeration cycle not using the ejector 400. (Saturated gas) refrigerant has a low enthalpy. For this reason, if the discharge pressure of the compressor in the ejector cycle is the same as the discharge pressure of the compressor in the normal vapor compression refrigeration cycle, the temperature of the refrigerant discharged from the compressor 100 is reduced by the normal vapor compression. The ejector cycle is lower than the refrigeration cycle.

On the other hand, in the present embodiment, the radiator 2
Heat exchange between the refrigerant flowing out of the compressor 00 and the refrigerant drawn into the compressor 100 is performed to heat the refrigerant drawn into the compressor 100. Therefore, the temperature of the refrigerant drawn into the compressor 100 can be increased. Therefore, the temperature of the refrigerant discharged from the compressor 100 increases, and the heating capacity (hot water supply capacity) of the radiator 200 and the coefficient of performance of the cycle can be improved.

(Fourteenth Embodiment) The fourteenth embodiment corresponds to FIG.
, An electric motor Mo for driving the compressor 100
(Drive source) and a heat exchanger (heating means) 810 for exchanging heat between the refrigerant drawn into the compressor 100 and the compressor 100
Is configured to heat the refrigerant to be sucked.

(Fifteenth Embodiment) This embodiment is different from the embodiment shown in FIG.
As shown in FIG. 8, the heat exchanger 8 heats the refrigerant drawn into the compressor 100 by the hot water stored in the hot water storage tank 750.
20 are provided.

As a result, the temperature of the refrigerant sucked into the compressor 100 gradually increases, so that the heating power of the radiator 200 is improved, the power consumption of the compressor 100 is reduced, and the coefficient of performance of the cycle is reduced. Can be improved.

(Sixteenth Embodiment) In the sixteenth embodiment, the ejector cycle according to the present invention is applied to a heat management (heat management) system for an entire building such as a home or a building including a water heater. Specifically, as shown in FIG.
In addition to providing a heat exchanger (heating means) 830 for collecting waste heat generated in the building (in the present embodiment, remaining hot water of a bath) and exchanging heat with refrigerant drawn into the compressor 100,
A second evaporator 310 is provided between the ejector 400 and the gas-liquid separator 500.

As a result, the waste heat absorbs heat while improving the heating capacity (hot water supply capacity) of the radiator 200 and the coefficient of performance of the cycle while cooling the room (air conditioning) with the evaporator 300. Heat absorbed and second evaporator 310
The hot water may be heated by the heat absorbed in the step.

In the present embodiment, the room is cooled (air-conditioned) by the evaporator 300. However, the present embodiment is not limited to this, and the room is cooled by the second evaporator 310. Cooling may be performed. Also, two evaporators 3000,
At 310, indoor cooling may be performed.

Further, the present embodiment is not limited to the configuration shown in FIG. 25, and hot water storage tank 750 may be used as a hot air exchanger for (floor) heating.

Further, the present embodiment is not limited to the configuration shown in FIG. 25. For example, as shown in FIG. May be supplied.

As a result, the heat supplied to the hot water from the ejector cycle can be efficiently used, and the hot water utilization equipment 7 that does not require the hot water storage tank 750 can be used.
Heat can be supplied in one ejector cycle to 53 and a water heater that requires a hot water storage tank 750 such as a water heater.

(Seventeenth Embodiment) This embodiment is different from the embodiment shown in FIG.
As shown in (5), a control valve 731 that changes the opening degree based on the degree of heating of the refrigerant at the refrigerant outlet side of the evaporator 300 is provided in the refrigerant passage between the radiator 200 and the ejector 400.

The control valve 731 according to the present embodiment is
A so-called external pressure equalizing type temperature expansion valve that mechanically senses the refrigerant temperature at the refrigerant outlet side of the evaporator 300 to maintain the degree of heating of the refrigerant at a predetermined constant value. And 731b is an equalizing (outer equalizing) tube.

Next, the operation and effect of this embodiment will be described.

When the degree of heating at the refrigerant outlet side of the evaporator 300 increases, the flow rate Ge of the refrigerant flowing into the evaporator 300 increases.
Becomes larger. On the other hand, since the pump work in the ejector 400 is constant, when the refrigerant flow rate Ge increases and the flow rate α increases, the ejector 40 responds accordingly.
The step-up ΔP at 0 decreases. Therefore, as shown in FIG. 28, there is a heating degree at which the ejector efficiency ηe is maximized.

Therefore, in the present embodiment, the control valve 731 is controlled so as to maintain the heating degree at which the ejector efficiency ηe is maximized.
To control the ejector cycle while maintaining a high ejector efficiency ηe.

In the present embodiment, the heating degree is controlled so as to be substantially constant. However, the present embodiment is not limited to this. For example, the control valve 731 may be electrically operated.
The control target heating degree may be changed according to the operation state of the ejector cycle.

(Eighteenth Embodiment) This embodiment is different from the embodiment shown in FIG.
As shown in (1), before the pressure is reduced by the ejector 400 in the refrigerant passage between the radiator 200 and the ejector 400 (in this embodiment, before the pressure is reduced by flowing out of the radiator 200).
Control valve 73 for controlling the high-pressure side pressure based on the refrigerant temperature of
2 is provided. Here, the high pressure side pressure means the refrigerant pressure before the pressure is reduced by the control valve 732 and the ejector 400 (nozzle 410).

Note that the control valve 732 according to this embodiment is
The refrigerant temperature at the refrigerant outlet side of the radiator 200 is mechanically sensed, and the high-pressure side pressure is controlled according to the sensed refrigerant temperature. Reference numeral 732a is a temperature sensing unit that senses the refrigerant temperature.

Next, the operation and effect of this embodiment will be described.

When the high-pressure side pressure increases, the radiator 200
, The flow rate Gn of the refrigerant flowing therethrough decreases. On the other hand, since the pump work in the ejector 400 is constant, when the refrigerant flow rate Gn decreases and the flow rate ratio α increases, the pressure increase ΔP in the ejector 400 decreases accordingly. For this reason, as shown in FIG.
There is a high pressure side at which e is maximum.

Therefore, in the present embodiment, the control valve 7 is controlled so as to maintain the high pressure side pressure at which the ejector efficiency ηe is maximized.
32, the ejector cycle is operated while maintaining a high ejector efficiency ηe.

In the present embodiment, the mechanical control valve 7
Although 32 is used, the present embodiment is not limited to this, and an electric control valve may be used.

(Nineteenth Embodiment) This embodiment is different from the nineteenth embodiment shown in FIG.
As shown in the figure, a control valve 733 whose valve opening is controlled based on the pressure in the evaporator 300 (heat load on the evaporator 300) is provided in the refrigerant passage between the radiator 200 and the ejector 400.
Is provided.

Note that the control valve 733 according to this embodiment is
733a has a structure similar to a so-called internal pressure equalization type temperature expansion valve in which the pressure in the evaporator 300 is mechanically sensed and the valve opening changes in accordance with the sensed pressure.
Is a pressure equalizing pipe for guiding the pressure in the evaporator 300 to the control valve 733.

For this reason, when the pressure in the evaporator 300 (heat load in the evaporator 300) increases, the opening of the control valve 733 increases, and conversely, the pressure in the evaporator 300 (evaporator 3) increases.
When the heat load at 00 is low, the opening of the control valve 733 decreases.

Next, the operation and effect of this embodiment will be described.

According to the present embodiment, since the valve opening is controlled based on the pressure in the evaporator 300 (heat load in the evaporator 300), the pressure in the evaporator 300 (heat load in the evaporator 300) is controlled. ) Varies, the ejector efficiency ηe can be kept high by controlling the opening according to the variation.

In this embodiment, when the pressure in the evaporator 300 (heat load in the evaporator 300) increases, the opening degree of the control valve 733 increases, and conversely, the pressure (evaporation) in the evaporator 300 increases. When the heat load in the evaporator 300 decreases, the opening of the control valve 733 is controlled so as to decrease, so that the ejector efficiency ηe is maintained high while the flow rate of the refrigerant flowing into the evaporator 300 is set to an appropriate flow rate. It is possible to

(Twentieth Embodiment) In the seventeenth embodiment,
The control valve 731 is provided in the refrigerant passage between the radiator 200 and the ejector 400, and the opening degree of the control valve 731 is controlled based on the refrigerant heating degree at the refrigerant outlet side of the evaporator 300. As shown in FIG. 32, the gas-liquid separator 5
A control valve 731 is provided in the refrigerant passage between the fuel cell 00 and the evaporator 300, and controls the opening of the control valve 731 based on the degree of heating of the refrigerant at the refrigerant outlet side of the evaporator 300.

Thus, the pressure acting on the control valve 731 can be made smaller than that in the seventeenth embodiment, so that the size of the control valve 731 can be reduced and the manufacturing cost can be reduced.

(Twenty-First Embodiment) In the nineteenth embodiment,
Although the control valve 733 is provided in the refrigerant passage between the radiator 200 and the ejector 400, in the present embodiment, as shown in FIG. 33, the control valve 733 is provided in the refrigerant passage between the gas-liquid separator 500 and the evaporator 300. A valve 733 is provided to control the valve opening based on the pressure in the evaporator 300 (heat load on the evaporator 300).

(Twenty-second Embodiment) This embodiment is different from the one shown in FIG.
38, a heat exchanger (internal heat exchanger) 800 for exchanging heat between the refrigerant flowing out of the radiator 200 and the refrigerant drawn into the compressor 100 is provided.

As a result, the refrigerant flowing into the control valves 731 to 733 is cooled, so that the expansion energy in the nozzle 410 decreases, the flow velocity of the refrigerant flowing out of the nozzle 410 decreases, and the dryness of the refrigerant in the outlet of the nozzle 410 decreases. Degree decreases.

For this reason, the ejector 4
Since the flow rate of the suction refrigerant sucked at 00 increases and the flow rate of the suction refrigerant increases, the speed difference between the flow rate of the driving refrigerant blown out from the nozzle 410 and the flow rate of the suction refrigerant decreases. Therefore, the loss (vortex loss) associated with the vortex generated when the suction refrigerant and the driving refrigerant are mixed is reduced, and the ejector efficiency ηe is improved.

FIG. 34 is an example in which a heat exchanger 800 is provided in the ejector cycle according to the seventeenth embodiment, and FIG. 35 is an example in which the heat exchanger 800 is provided in the ejector cycle according to the eighteenth embodiment. 36 shows an example in which a heat exchanger 800 is provided in the ejector cycle according to the nineteenth embodiment. FIG. 37 shows an example in which the heat exchanger 800 is provided in the ejector cycle according to the twentieth embodiment. Second
In the ejector cycle according to one embodiment, the heat exchanger 800
This is an example in which is provided.

(Twenty-third Embodiment) This embodiment is different from the one shown in FIG.
As shown in, the ejector 400 and the control valves 731 to 733 are integrated by integrating the nozzles 410 with the control valves 731 to 733 provided in the refrigerant passage between the ejector 400 and the radiator 200. Things.

By the way, the refrigerant passing through the nozzle 410 is decompressed across the saturated liquid line, so that the refrigerant enters a gas-liquid two-phase state in the middle of the nozzle 410 and
The refrigerant boils near the wall surface of the throat portion 0 (the portion where the cross-sectional area is the smallest in the nozzle 410 (see FIG. 6)). On the other hand, in the central portion distant from the inner wall of the nozzle 410, the refrigerant is difficult to boil, so that it is difficult to atomize the droplets of the refrigerant, which causes a decrease in the ejector efficiency ηe.

On the other hand, in the present embodiment and the seventeenth to tenth embodiments,
In the ninth embodiment, the refrigerant is supplied to the control valves 731 to 733.
The pressure is reduced (squeezed) in the two stages of the nozzle and the nozzle 410, so that the first stage nozzle (in this example, the control valve 73
1 to 733), the refrigerant is once boiled, and the refrigerant is expanded at the inlet of the second stage nozzle (nozzle 410 in this example) to recover the pressure, so that the boiling nuclei are generated. It can be boiled by the stage nozzle 410.

Therefore, the boiling of the refrigerant in the second stage nozzle 410 can be promoted, so that the nozzle 41
The refrigerant can be boiled even in a central portion away from the inner wall of the zero. Consequently, since the droplets of the refrigerant can be atomized, the ejector efficiency ηe can be improved.

(Twenty-fourth Embodiment) In the present embodiment, a heat exchanger (internal heat exchanger) 800 for exchanging heat between the refrigerant flowing out of the radiator 200 and the refrigerant drawn into the compressor 100, the ejector 400, A liquid separator 500 and a decompressor (throttling means) 600 are integrated (an ejector-integrated gas-liquid separator).
45 will be described.

FIG. 40 is an axial sectional view of the ejector-integrated gas-liquid separator, and FIG.
42 is an axial cross-sectional view seen from a direction shifted by an angle, FIG. 42 is a top view of FIG. 40, FIG. 43 is a cross-sectional view taken along AA of FIG. 40, FIG. 44 is a perspective view of the diffuser 430, FIG. 45A is a perspective view of the heat exchanger 800, and FIG.
(B) is a sectional view of a tube constituting the heat exchanger 800.

[0147] The gas-liquid separator 500 is similar to that shown in Figs.
As shown in FIG. 1, a lower body (tank main body) 551 having a cylindrical shape whose one end is closed and an upper body 552 closing the other end are welded to each other. The refrigerant flowing through the ejector 400 is fixed to the upper body 552 (upper side) such that the refrigerant flows vertically from the upper side to the lower side.

At this time, the diffuser 430 is
As shown at 1, 42 and 45, a trumpet-shaped (horn-shaped) first horn portion 431 and a lower end portion 552 of a lower body 551 are formed so that the cross-sectional area thereof gradually increases downward from the mixing portion 420. And a second horn part 432 that constitutes the diffuser 430 together with a part of the side wall part 553.

Then, the second horn part 432 is connected to the side wall part 5.
A substantially cylindrical portion 4 having a predetermined gap of 53 and opposed to each other.
32a, the first horn portion 431, and the curved portion 432b that smoothly connects the cylindrical portion 432a. In the present embodiment, the first horn portion 431 and the second horn 43
2 is integrally formed.

The cylindrical portion 432a has a side wall portion 553.
A positioning projection 433 for positioning the diffuser 430 with respect to the lower body 551 in contact therewith is provided.

The heat exchanger 800 is similar to that shown in FIGS.
As shown in (a), a flat first tube 840 through which a high-pressure refrigerant before being depressurized by the ejector 400 flows.
And a flat second tube 850, through which the low-pressure refrigerant sucked into the compressor 100 flows, being spirally wound in a state where the flat tube is in contact with the flat second tube 850.
850 is a multi-hole tube in which a number of refrigerant passages are formed in one tube, as shown in FIG. 45 (b).

Headers 841, 842, 851, 852 communicating with the refrigerant passages in the tubes 840, 850 are joined to both longitudinal ends of the tubes 840, 850, respectively. The headers 842 and 852 collect and collect the refrigerant flowing out of the respective refrigerant passages after completing the heat exchange.

Next, the operation (refrigerant flow) of the ejector-integrated gas-liquid separator according to this embodiment will be described.

The high-temperature and high-pressure refrigerant flowing out of the radiator 200 flows into the gas-liquid separator 500 from the first inlet 554 (see FIGS. 41 and 42), and flows into the header 841, the first tube 840, and the header 842. The communication port 555 is circulated in order.
Ejector 400 (nozzle 4) via (see FIG. 40)
10).

The ejector 400 (nozzle 41)
0) flows into the evaporator 300 in the mixing section 420.
After the pressure is increased by the diffuser 430 while sucking the refrigerant evaporated in the above, the cylindrical portion 432a and the side wall 5
Through the gap with 53 (a part of the diffuser 430), it flows out above the lower body 551 (upper space in the gas-liquid separator 500). Note that the refrigerant evaporated in the evaporator 300 is sucked into the mixing section 420 from the second inlet 558 (see FIG. 42).

The gas-phase refrigerant (low-pressure refrigerant) existing above the lower body 551 (upper space in the gas-liquid separator 500) is disposed below the lower body 551 (in the gas-liquid separator 500). Is sucked into the U-shaped tube 556 from the upper end side opening 556a of the U-shaped U-shaped tube 556 bent in the U-shaped tube and flows into the second tube 850 from the header 851.
After performing heat exchange with the high-pressure side refrigerant (refrigerant flowing in the first tube 840), the refrigerant flows out from the first outlet 557 (see FIG. 41) and is sucked into the compressor 100.

The lower bent portion of the U-shaped tube 556 includes
An oil return hole 556b (see FIG. 45) for taking in refrigerating machine oil (lubricating oil) separated from the refrigerant is provided, and the refrigerating machine oil taken in from the oil return hole 556b flows through the second tube 850 together with the low-pressure side refrigerant. And compressor 1
Sucked at 00.

On the other hand, the liquid refrigerant present below the lower body 551 (the space below the gas-liquid separator 500)
Suction pipe 55 arranged coaxially with ejector 400
8 is sucked from the lower end side opening 558a of the second outlet 5
From 59 (see FIG. 40), it flows toward the evaporator 300. In addition, the second outlet 559 extends from the lower end side opening 558a.
By generating a predetermined pressure loss in the refrigerant passage leading to, a pressure reducing device (throttling means) 600 is configured.

Next, the features of this embodiment will be described.

In this embodiment, a part of the diffuser 430 is constituted by a part of the gas-liquid separator 500 (a part of the lower end 552 of the lower body 551 and a part of the side wall 553). Compared to the case where the diffuser 430 is constituted by only one horn portion 431), the diffuser 430 having a sufficiently large refrigerant passage can be constituted.

Furthermore, the diffuser 43 having a sufficiently large refrigerant passage utilizing the space in the gas-liquid separator 500 is used.
Since 0 is configured, it is possible to improve the performance of the ejector 400, reduce the pace for mounting the ejector 400, and improve the installation (mounting) of the ejector cycle.

(Twenty-Fifth Embodiment) This embodiment also relates to a gas-liquid separator integrated with an ejector. In particular,
As shown in FIG. 46, the ejector 400 is disposed in the gas-liquid separator 500 such that the refrigerant flowing in the ejector 400 flows vertically from the upper side to the lower side, and the refrigerant outlet of the diffuser 430 On the downstream side of the flow of the refrigerant from (the position where the cross-sectional area of the refrigerant passage is the largest), the flow direction of the refrigerant is changed by approximately 180 degrees from the downward direction to the upward direction.

Thus, it is possible to concentrate the inlet and outlet of the refrigerant on the upper side of the gas-liquid separator 500 while minimizing the pressure loss in the ejector 400 (in particular, the diffuser 430).

Incidentally, reference numeral 560 denotes a gas-phase refrigerant (low-pressure side refrigerant) which is bent in a U-shape in the lower space in the gas-liquid separator 500 and exists in the upper space in the gas-liquid separator 500. A pipe 570 is a suction pipe for sucking a liquid-phase refrigerant existing in a lower space in the gas-liquid separator 500, and a refrigerating machine oil is provided at a bent portion at a lower end side of the U-shaped pipe 560. An oil return hole 561 for taking in oil is formed.

(Other Embodiments) In the above embodiment, carbon dioxide is used as the refrigerant. However, the present invention is not limited to this, and may be, for example, ethylene, ethane, nitrogen oxide, or the like.

Further, decompressors 710 and 720 may be provided on both the upstream side and the downstream side of the refrigerant flow of the ejector 400.

The first pressure reducer 600 may be omitted by providing a pressure loss applicable to the refrigerant passage itself.

In the first to third embodiments, the first to third decompressors 600, 710, and 720 are constituted by fixed apertures or capillary tubes having fixed openings, but the present invention is not limited to this. Instead, a variable opening valve that can variably control the opening may be used.

In the second embodiment, the second decompressor 710 is a variable-opening valve, and when the refrigerant pressure after being raised by the ejector 400 is lower than the critical pressure, the valve opening is increased. When the pressure loss is reduced and the refrigerant pressure after being boosted by the ejector 400 is equal to or higher than the critical pressure, the valve opening may be adjusted so that the refrigerant pressure at the inlet of the gas-liquid separator 500 is lower than the critical pressure. For example, similarly to the third embodiment, it is possible to prevent the flow resistance (pressure loss) of the refrigerant from increasing while adjusting the refrigerant pressure after being boosted by the ejector 400 so as to be surely lower than the critical pressure. .

Also, in the first to third embodiments, the second, third,
Although the pressure of the refrigerant after being pressurized by the ejector 400 in the pressure reducers 710 and 720 is reduced to a pressure lower than the critical pressure (gas-liquid two-phase region), the present invention is not limited to this. By adjusting the flow rate of the refrigerant discharged from the compressor by means such as adjusting the rotational speed or the theoretical discharge amount of the compressor, the refrigerant pressure after being boosted by the ejector 400 is lower than the critical pressure (gas-liquid two-phase region). You may comprise the pressure adjustment means which adjusts to pressure reduction.

In the fourth to sixth embodiments, the mixing section 42
The liquid refrigerant was separated and extracted near the outlet of 0.
The present invention is not limited to this.
During the pressure increase of 00 (between the entrance of the mixing unit 420 and the exit of the diffuser 430), the pressure may be anywhere.

In the ninth to sixteenth embodiments, the ejector cycle according to the present invention is applied to a water heater, but the present invention is not limited to this, and can be applied to, for example, an air conditioner. .

Further, in the ninth to sixteenth embodiments, the flow rate of the refrigerant discharged from the compressor 100 is controlled by the electric motor Mo. However, the present invention is not limited to this. May control the flow rate of the refrigerant discharged from the compressor 100.

In the ninth to sixteenth embodiments, the compressor 1
Although the flow rate of the refrigerant discharged from 00 is controlled, the present invention is not limited to this. For example, the flow rate of the refrigerant discharged from the compressor (the number of revolutions of the compressor) may be a constant value.

Further, the present invention is limited to only the above-described embodiments, and at least two of the first to sixteenth embodiments may be combined.

In the above-described embodiment, the ejector 4
00 shape (inlet diameter of nozzle 410, throat diameter of nozzle 410, outlet diameter of nozzle 410, diameter of mixing section 420,
The dimensions of the ejector such as the dimension from the nozzle inlet to the nozzle throat, the dimension from the nozzle throat to the nozzle outlet, the length of the mixing section 420, and the spread angle of the diffuser 430) are fixed. Is not limited to this, and the shape of the ejector 400 may be changed according to the operation state of the cycle. Thus, the cycle can be operated while maintaining high ejector efficiency regardless of the operating state of the ejector cycle.

The definition formula of the ejector efficiency ηe is not limited to the above formula 1, but may be any formula that accurately indicates the energy conversion efficiency when converting expansion energy into pressure energy.

In the gas-liquid separators according to the sixth and seventh embodiments and the ejector cycles according to the eighth to twenty-fifth embodiments, the high pressure side using carbon dioxide as the refrigerant is equal to or higher than the critical pressure of the refrigerant. However, these embodiments are not limited to this, and can be applied to those in which the high pressure side pressure is lower than the critical pressure of the refrigerant.

In the above embodiment, the mixing section 420
And the diffuser 430 are clearly distinguished, but the present invention is not limited to this, and the functions of the mixing unit 420 and the function of the diffuser 430 are not clearly distinguished from the mixing unit 420 and the diffuser 430. The ejector 400 may be configured by the boosting unit having the combination of the above and the nozzle 410.

In the above embodiment, the nozzle 410
Although the (ejector 400) is a one-stage throttle, the present invention is not limited to this, and the nozzle 410 (the ejector 400) may have a multi-stage throttle structure.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of an ejector cycle according to a first embodiment of the present invention.

FIG. 2 is a ph (Mollier) diagram of an ejector cycle according to the first embodiment of the present invention.

FIG. 3 is a graph showing the relationship between the high-pressure side pressure, the coefficient of performance, and the cooling capacity in the ejector cycle according to the first embodiment of the present invention.

FIG. 4 is a schematic view of an ejector cycle according to a second embodiment of the present invention.

FIG. 5 is a schematic view of an ejector cycle according to a third embodiment of the present invention.

FIG. 6 is an enlarged schematic view of an ejector and a gas-liquid separator of an ejector cycle according to a fourth embodiment of the present invention.

7A is a graph showing a relationship between an ejector efficiency ηe and a refrigerating capacity Qe generated in an evaporator, and FIG. 7B is a graph showing an ejector efficiency ηe, a suction pressure increase ΔP of a compressor, and an evaporator refrigerant inlet. (C) is a graph showing the relationship between the specific enthalpy difference Δh between the outlet side and the outlet side, and (c) shows the ejector efficiency ηe, the mass flow rate Gr of the refrigerant drawn into the compressor, and the mass flow rate Ge of the refrigerant flowing through the evaporator. 6 is a graph showing a relationship with the graph.

FIG. 8 is a ph (Mollier) diagram of an ejector cycle according to a fourth embodiment of the present invention.

FIG. 9 is a three-dimensional characteristic diagram showing a relationship between a position in a radial direction with respect to a center portion of a cross section of a refrigerant passage of an ejector and a flow velocity of the refrigerant from a refrigerant outlet of a nozzle to a refrigerant outlet of a diffuser.

FIG. 10 is an enlarged schematic view of an ejector and a gas-liquid separator of an ejector cycle according to a fifth embodiment of the present invention.

FIG. 11 is a graph showing a relationship between a position in a radial direction based on a center portion of a cross section of a refrigerant passage of an ejector and a ratio (liquid volume ratio) of a liquid-phase refrigerant in the refrigerant.

FIG. 12 is an enlarged schematic view of an ejector and a gas-liquid separator of an ejector cycle according to a sixth embodiment of the present invention.

FIG. 13 is a schematic diagram of a gas-liquid separator applied to an ejector cycle according to a seventh embodiment of the present invention.

FIG. 14 is an explanatory diagram for explaining features of a gas-liquid separator applied to an ejector cycle according to a seventh embodiment of the present invention.

FIG. 15 is a schematic diagram of a gas-liquid separator applied to an ejector cycle according to an eighth embodiment of the present invention.

16 is a sectional view taken along line AA of FIG.

FIG. 17 is a schematic view of an ejector cycle according to a ninth embodiment of the present invention.

FIG. 18 is a graph showing the relationship between ejector efficiency and flow ratio.

FIG. 19 is a schematic view of an ejector cycle according to a tenth embodiment of the present invention.

FIG. 20 is a schematic diagram of an ejector cycle according to an eleventh embodiment of the present invention.

FIG. 21 is a schematic view of an ejector cycle according to a twelfth embodiment of the present invention.

FIG. 22 is a schematic view of an ejector cycle according to a thirteenth embodiment of the present invention.

FIG. 23 is a schematic view of an ejector cycle according to a fourteenth embodiment of the present invention.

FIG. 24 is a schematic view of an ejector cycle according to a fifteenth embodiment of the present invention.

FIG. 25 is a schematic view of an ejector cycle according to a sixteenth embodiment of the present invention.

FIG. 26 is a schematic view according to a modification of the ejector cycle according to the sixteenth embodiment of the present invention.

FIG. 27 is a schematic view of an ejector cycle according to a seventeenth embodiment of the present invention.

FIG. 28 is a graph showing the relationship between the degree of heating and the flow rate ratio α, the pressure increase ΔP in the ejector 400, and the ejector efficiency ηe.

FIG. 29 is a schematic view of an ejector cycle according to an eighteenth embodiment of the present invention.

FIG. 30 is a graph showing the relationship between the high-pressure side pressure and the flow rate ratio α, the pressure increase ΔP in the ejector 400, and the ejector efficiency ηe.

FIG. 31 is a schematic view of an ejector cycle according to a nineteenth embodiment of the present invention.

FIG. 32 is a schematic view of an ejector cycle according to a twentieth embodiment of the present invention.

FIG. 33 is a schematic view of an ejector cycle according to a twenty-first embodiment of the present invention.

FIG. 34 is a schematic view of an ejector cycle according to a twenty-second embodiment of the present invention.

FIG. 35 is a schematic view according to a modification of the ejector cycle according to the twenty-second embodiment of the present invention.

FIG. 36 is a schematic view according to a modification of the ejector cycle according to the twenty-second embodiment of the present invention.

FIG. 37 is a schematic view according to a modification of the ejector cycle according to the twenty-second embodiment of the present invention.

FIG. 38 is a schematic view according to a modification of the ejector cycle according to the twenty-second embodiment of the present invention.

FIG. 39 is an enlarged schematic diagram of an ejector applied to an ejector cycle according to a twenty-third embodiment of the present invention.

FIG. 40 is an axial sectional view of an ejector-integrated gas-liquid separator according to a twenty-fourth embodiment of the present invention.

FIG. 41 is an axial cross-sectional view seen from a direction shifted by approximately 90 degrees from FIG. 40;

FIG. 42 is a top view of FIG. 40.

FIG. 43 is a sectional view taken along line AA of FIG. 40;

FIG. 44 is a perspective view of a diffuser 430.

FIG. 45 (a) is a perspective view of a heat exchanger, and FIG. 45 (b) is a cross-sectional view of a tube constituting the heat exchanger.

FIG. 46 is an axial sectional view of an ejector-integrated gas-liquid separator according to a twenty-fifth embodiment of the present invention.

[Explanation of symbols]

400: ejector, 500: gas-liquid separator, 543: oil return hole.

 ──────────────────────────────────────────────────続 き Continued on the front page (31) Priority claim number Japanese Patent Application No. 2001-5196 (P2001-5196) (32) Priority date January 12, 2001 (2001.1.12) (33) Priority claim country Japan (JP) (31) Priority claim number Japanese Patent Application No. 2001-40496 (P2001-40496) (32) Priority date February 16, 2001 (2001.2.16) (33) Priority claim country Japan (JP) (72) Inventor Hiroshi Ishikawa 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Kunio Iriya 1-1-1, Showa-cho, Kariya City, Aichi Prefecture Inside Denso Corporation (72) Inventor Satoshi Nomura 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Hisasuke Sakakibara 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Makoto Ikegami Kariya, Aichi Prefecture 1-1-1, Showa-cho, Yokohama-shi DENSO Corporation (72) Inventor Masayuki Takeuchi 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Koji Yamanaka 1-1-1, Showa-cho, Kariya City, Aichi Prefecture Inside Denso Corporation

Claims (3)

[Claims] 1. A compressor (100) for sucking and compressing a refrigerant.
A radiator (200) for cooling the refrigerant discharged from the compressor (100); an evaporator (300) for evaporating the refrigerant to absorb heat; and reducing and expanding the refrigerant flowing out of the radiator (200). An ejector (400) for sucking the vapor-phase refrigerant evaporated in the evaporator (300) and converting expansion energy into pressure energy to increase the suction pressure of the compressor (100); ) Is separated into a gas-phase refrigerant and a liquid-phase refrigerant to store the refrigerant, and the gas-phase refrigerant is supplied to the suction side of the compressor (100), and the liquid-phase refrigerant is supplied to the evaporator. Gas-liquid separator (50)
0), and an oil return hole (543) installed in the gas-liquid separator (500) for guiding the lubricating oil in the gas-liquid separator (500) to the compressor (100). Ejector cycle. 2. An ejector cycle having an ejector (400) for decompressing and expanding a refrigerant and sucking a vapor-phase refrigerant evaporated in an evaporator, and converting expansion energy into pressure energy to increase a suction pressure of a compressor. The gas-liquid two-phase refrigerant from the ejector (400) is separated into a gas-phase refrigerant and a liquid-phase refrigerant, and the liquid-phase refrigerant is supplied to the tank unit (55).
1) and the gas-phase refrigerant is stored in the compressor (10).
0) and supplies the liquid-phase refrigerant to the evaporator (30).
0) to supply the refrigerant flowing in the ejector (400) from the upper side to the lower side in the tank section (551). (400) and a part (552, 5) of the tank part (551).
53) is a diffuser (4) of the ejector (400).
30. A gas-liquid separator characterized by constituting a part of 30). 3. An ejector cycle having an ejector (400) for decompressing and expanding a refrigerant, sucking a vapor-phase refrigerant evaporated in an evaporator, and converting expansion energy into pressure energy to increase a suction pressure of a compressor. The gas-liquid two-phase refrigerant from the ejector (400) is separated into a gas-phase refrigerant and a liquid-phase refrigerant, and the liquid-phase refrigerant is supplied to the tank unit (55).
1) and the gas-phase refrigerant is stored in the compressor (10).
0) and supplies the liquid-phase refrigerant to the evaporator (30).
0) to supply the refrigerant flowing in the ejector (400) from the upper side to the lower side in the tank section (551). (400) is arranged, and at the downstream side of the refrigerant flow from the refrigerant outlet of the diffuser (430) of the ejector (400), the flow direction of the refrigerant is changed from the downward direction to the upward direction. A gas-liquid separator characterized by comprising.