JP2003090635A - Ejector cycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform defrosting operation in an ejector cycle. SOLUTION: An ejector 400 is provided with a bypass passage 406a for causing a hot gas flowing out of a radiator to bypass a nozzle and guiding the gas to an evaporator. A valve 405 for opening and closing the bypass passage 406a is driven by an actuator 412 driving a needle valve 411 regulating the opening area of the nozzle 410.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an ejector cycle.

[0002]

2. Description of the Related Art An ejector cycle is, for example, as described in Japanese Patent Laid-Open No. 6-1197 / 1994, a gas phase refrigerant vaporized by an evaporator by decompressing and expanding the refrigerant by an ejector. It is a refrigeration cycle that sucks and converts the expansion energy into pressure energy to raise the suction pressure of the compressor.

By the way, in a refrigerating cycle (hereinafter referred to as an expansion valve cycle) in which a refrigerant is isenthalpically decompressed by a decompression means such as an expansion valve, the refrigerant flowing out of the expansion valve flows into an evaporator. In the ejector cycle,
The refrigerant flowing out of the ejector flows into the gas-liquid separator, the liquid-phase refrigerant separated by the gas-liquid separator is supplied to the evaporator, and the gas-phase refrigerant separated by the gas-liquid separator is sucked into the compressor. To be done.

That is, in the expansion valve cycle, the refrigerant circulates in the order of compressor → radiator → expansion valve → evaporator → compressor 1.
On the other hand, in the ejector cycle, a refrigerant flow circulates in the order of compressor → radiator → ejector → gas-liquid separator → compressor (hereinafter, this flow is referred to as a driving flow) and gas. There exists a refrigerant flow (hereinafter, this flow is referred to as a suction flow) that circulates in the order of liquid separator → evaporator → ejector → gas liquid separator.

Therefore, in the expansion valve cycle, the expansion valve is fully opened to allow a high-temperature refrigerant to flow into the evaporator to remove (defrost) the frost on the evaporator, but the ejector cycle Then, since the high-temperature refrigerant (driving flow) flowing through the radiator and the suction flow flowing through the evaporator are different flows, and the driving flow cannot be supplied to the evaporator, the defrosting operation cannot be performed. It should be noted that there is no specific description or suggestion of the defrosting method of the evaporator in the above publication.

In view of the above points, it is an object of the present invention to provide a defrosting operation method suitable for an ejector cycle.

[0007]

In order to achieve the above object, the present invention provides a compressor (100) for sucking and compressing a refrigerant and a compressor (100) for discharging the refrigerant. A radiator (200) for cooling the refrigerant, an evaporator (300) for evaporating the refrigerant, and a nozzle (410) for converting pressure energy of the high-pressure refrigerant flowing out of the radiator (200) into velocity energy to expand the refrigerant under reduced pressure. ), The gas-phase refrigerant evaporated in the evaporator (300) is sucked by the high-speed refrigerant flow injected from the nozzle (410), and the nozzle (4
A pressure increasing unit (42) for increasing the pressure of the refrigerant by converting the velocity energy into pressure energy while mixing the refrigerant injected from 10) with the refrigerant sucked from the evaporator (300).
0, 430) and an ejector (40) having a bypass passage (406a) for guiding the refrigerant flowing out of the radiator (200) to the evaporator (300) by bypassing the nozzle (410).
0) and a gas-liquid separator (500) that stores the refrigerant by separating the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant, and an evaporator (30
In the normal operation of evaporating the refrigerant at 0), the radiator (2
00), the refrigerant flows macroscopically from the upper side to the lower side in the evaporator (300) while allowing the refrigerant to flow into the nozzle (410).
Radiator (200) for defrosting to remove the frost adhering to the
It is characterized in that the refrigerant flowing out from the refrigerant is circulated to the bypass passage (406a) and the refrigerant is allowed to flow from the lower side to the upper side in the evaporator (300).

By the way, in order to secure the lubrication and the sealing property of the sliding portion of the compressor (100), generally, in a refrigeration cycle (ejector cycle, expansion valve cycle, etc.), a lubricating oil (refrigerator) is used as a refrigerant. In the ejector cycle, the drive flow flows through the compressor (100), but the suction flow does not flow through the compressor (100). Therefore, the lubricating oil that has flowed into the evaporator (300) together with the suction flow is There is a high possibility that the lubricating oil staying in the evaporator (300) and returning to the compressor (100) will run short.

In order to solve this problem, it is conceivable to consider the amount of lubricating oil staying in the evaporator (300) and mix a large amount of lubricating oil with the refrigerant, but the amount of lubricating oil in the refrigerant is Increasing, radiator (200) and evaporator (300)
In this case, the heat exchange efficiency of the refrigerant is reduced.

However, in the present invention, during normal operation, the refrigerant is evaporated from the upper side to the lower side in the evaporator (300).
Since the oil is circulated inside, the lubricating oil accumulated in the evaporator (300) can be discharged from the evaporator (300) by utilizing the flow of the refrigerant and gravity.

Therefore, the compressor (10) is not mixed with a large amount of lubricating oil in the refrigerant (the heat exchange efficiency of the refrigerant in the radiator (200) and the evaporator (300) is reduced).
It is possible to prevent a shortage of the lubricating oil returning to 0).

Further, if the refrigerant is circulated in the evaporator (300) from the upper side to the lower side in the defrosting operation as in the normal operation, the temperature of the refrigerant is lowered toward the lower side. Therefore, the frost (melted water) thawed on the upper side where the refrigerant temperature is high may flow downward due to gravity, and may be solidified (frozen) again on the lower side where the refrigerant temperature is low.

On the other hand, in the present invention, during the defrosting operation, the refrigerant is circulated in the evaporator (300) from the lower side to the upper side, which is the reverse of the normal operation. (Melted water) will flow to the lower side where the refrigerant temperature is high. Therefore, the melted water solidifies (freezes) again
Since this can be prevented, the defrosting operation can be completed efficiently (in a short time).

According to the second aspect of the invention, the compressor (100) for sucking and compressing the refrigerant, the radiator (200) for cooling the refrigerant discharged from the compressor (100), and the evaporator (for evaporating the refrigerant ( 300), a nozzle (410) for converting the pressure energy of the high-pressure refrigerant flowing out from the radiator (200) into velocity energy to decompress and expand the refrigerant, and an evaporator with a high-velocity refrigerant flow injected from the nozzle (410). The vapor phase refrigerant evaporated at (300) is sucked in, and the nozzle (4
A pressure increasing unit (42) for increasing the pressure of the refrigerant by converting the velocity energy into pressure energy while mixing the refrigerant injected from 10) with the refrigerant sucked from the evaporator (300).
0, 430) and an ejector (400), and a gas-liquid separator (500) that stores the refrigerant by separating the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant, and removes the frost adhering to the evaporator (300). At the time of defrosting for removal, the refrigerant is made to flow from the lower side to the upper side in the evaporator (300).

As a result, similarly to the first aspect of the invention, the thawed frost (melting water) flows to the lower side where the refrigerant temperature is high, so that the melting water solidifies again (freezes). ) It can be prevented. As a result, the defrosting operation can be completed efficiently (in a short time).

In a third aspect of the present invention, a compressor (100) for sucking and compressing the refrigerant, a radiator (200) for cooling the refrigerant discharged from the compressor (100), and an evaporator (for evaporating the refrigerant ( 300) and a gas-liquid separator (500) for separating the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant and storing the refrigerant, the pressure energy of the high-pressure refrigerant flowing out from the radiator (200). (410) for converting the energy into velocity energy to expand the refrigerant under reduced pressure, and the high-velocity refrigerant flow injected from the nozzle (410) sucks the vapor-phase refrigerant evaporated in the evaporator (300), and the nozzle (410 ) And a refrigerant sucked from the evaporator (300) are mixed with each other to convert velocity energy into pressure energy to increase the pressure of the refrigerant (420, 430). A ejector having, in the housing (401) of the ejector (400), a first connection port connected to the radiator (200) side (402),
The second connection port (40) connected to the evaporator (300) side
3) and a third connection port (404) connected to the gas-liquid separator (500) side, and further, in the ejector (400), the refrigerant flowing from the first connection port (402) is nozzled. Valve means (40) for opening and closing a bypass passage (406a) that bypasses (410) and flows to the second connection port (403) and a bypass passage (406a).
5) is provided.

As a result, the bypass passage (406
The defrosting operation can be performed without providing a pipe for a).

In the invention according to claim 4, the nozzle (41
0) is a variable nozzle whose throttle cross-sectional area can be changed by a needle valve (411), and both the valve means (405) and the needle valve (411) are driven by the same actuator (412). It is characterized by

As a result, the number of parts constituting the ejector can be reduced, so that the manufacturing cost of the ejector can be reduced.

In a fifth aspect of the invention, a compressor (100) for sucking and compressing the refrigerant, a radiator (200) for cooling the refrigerant discharged from the compressor (100), and an evaporator (for evaporating the refrigerant ( 300), the ejector (400) according to claim 3 or 4, and a gas-liquid separator (500) that stores the refrigerant by separating the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant, and an evaporator (300). ) During normal operation in which the refrigerant is evaporated,
Refrigerant flowing out from the radiator (200) uses the nozzle (410)
In the evaporator (300), the refrigerant flows macroscopically from the upper side to the lower side while flowing into the evaporator (300) to remove the frost adhering to the evaporator (300) during defrosting. ), The refrigerant flowing out from the
It is characterized in that the refrigerant flows in a) and the refrigerant flows from the lower side to the upper side in the evaporator (300).

As a result, it is possible to complete the defrosting operation efficiently (in a short time) while preventing the lubricating oil returning to the compressor (100) from becoming insufficient, and to separately provide the bypass passage. The defrosting operation can be performed without providing a pipe for (406a).

Incidentally, the reference numerals in parentheses of the above-mentioned means are examples showing the correspondence with the concrete means described in the embodiments described later.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION In this embodiment, the ejector cycle according to the present invention is applied to a heat pump type water heater using carbon dioxide as a refrigerant, and FIG. 1 is a schematic view of the ejector cycle according to this embodiment. Is.

Reference numeral 100 denotes a compressor for obtaining a driving force from a drive source (not shown) such as an electric motor to suck and compress the refrigerant, and 200 denotes a high temperature / high pressure refrigerant discharged from the compressor 100 and hot water. A water-refrigerant heat exchanger (hereinafter referred to as a radiator) that heat-exchanges to heat the hot water and cools the refrigerant.
Is.

Numeral 300 is an evaporator which exchanges heat between outdoor air and liquid-phase refrigerant to evaporate the liquid-phase refrigerant, thereby removing heat from the outside air, and numeral 400 evaporates the refrigerant flowing out from the radiator 200 by decompressing and expanding it. It is an ejector that sucks the vapor-phase refrigerant evaporated in the container 300 and converts the expansion energy into pressure energy to raise the suction pressure of the compressor 100. The detailed structure of the ejector 400 will be described later.

Incidentally, although a serpentine-shaped evaporator 300 is illustrated in FIG. 1, this is a schematic illustration of a heat exchanger, and the evaporator 300 is limited to a serpentine type heat exchanger. Instead, the heat exchanger may be a so-called multi-flow type heat exchanger including a large number of tubes and a tank.

Further, reference numeral 500 denotes a gas-liquid separator which stores the refrigerant by separating the inflowing refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant while the refrigerant outflowing from the ejector 400 flows in. The refrigerant is sucked into the compressor 100,
The separated liquid-phase refrigerant is sucked toward the evaporator 300 side.

Incidentally, the gas-liquid separator 500 and the evaporator 300
The refrigerant passage connecting to and reduces the pressure of the refrigerant sucked into the evaporator 300 to surely lower the pressure (evaporation pressure) in the evaporator 300. It is set to generate a predetermined pressure loss.

In order to secure the lubrication and the sealing property of the sliding portion of the compressor 100, the refrigerant is mixed with the lubricating oil (refrigerator), but the lubricating oil (P
AG) is separated from the refrigerant in the gas-liquid separator 500 and accumulates in the lowermost layer of the gas-liquid separator 500, so that the oil provided at the bottom of the U-shaped gas-phase refrigerant discharge pipe 510 is Lubricating oil (liquid-phase refrigerant containing a large amount) is sucked from the return hole 511 and supplied to the compressor 100 together with the gas-phase refrigerant.

Next, the ejector 400 will be described.

FIG. 2 shows an ejector 400 according to this embodiment.
2 is a cross-sectional view of FIG. 2, and 410 is a nozzle that converts pressure energy (pressure head) of the high-pressure refrigerant flowing out from the radiator 200 into velocity energy (velocity head) to decompress and expand the refrigerant. Then, in the middle of the passage, the divergent nozzle (d
evergent Nozzle, de Laval
Nozzle) is adopted.

Reference numeral 411 denotes a needle valve that variably controls the opening area of the nozzle 410 by displacing it in the axial direction. Of the axial ends of the needle valve 411, the nozzle 410 side faces the nozzle 410 side. It is formed in a conical taper shape so that the cross-sectional area is reduced further, and the opposite side is fixed to an electric actuator 412.

In this embodiment, the actuator 4
A stepping motor is adopted as 12, and the needle valve 411 is an actuator (stepping motor) 4
Twelve magnet rotors 412a are screwed together.
Therefore, when the magnet rotor 412a rotates, the needle valve 411 is axially displaced by an amount proportional to the product of the rotation angle of the rotor 412a and the screw lead. Incidentally, 412b is an exciting coil for generating a magnetic field.

Reference numeral 420 denotes a mixing section 420 for sucking the vapor phase refrigerant evaporated in the evaporator 300 by the high-speed refrigerant flow (jet flow) injected from the nozzle 410.
30 is an evaporator 30 and the refrigerant injected from the nozzle 410
The diffuser 430 converts the velocity energy into pressure energy while increasing the pressure of the refrigerant while mixing with the refrigerant sucked from 0.

Incidentally, the diffuser 430 and the mixing section 4
20 is formed by a housing 401 that houses the nozzle 410, and the nozzle 410 is fixed to the housing 401 by press fitting. Incidentally, the nozzle 410 and the housing 401 are made of stainless steel.

In the mixing section 420, as shown in FIG. 3, the driving flow and the suction flow are mixed so that the sum of the momentum of the driving flow and the momentum of the suction flow is preserved. Also, the refrigerant pressure (static pressure) increases.
On the other hand, in the diffuser 430, as described above,
Since the velocity energy (dynamic pressure) of the refrigerant is converted into pressure energy (static pressure) by gradually increasing the passage cross-sectional area, the refrigerant pressure is increased by both the mixing section 420 and the diffuser 430 in the ejector 400. To do. Therefore, the mixing section 420 and the diffuser 430 are collectively referred to as a boosting section.

That is, in the ideal ejector 400, the refrigerant pressure increases so that the sum of the momentum of the driving flow and the momentum of the suction flow refrigerant is stored in the mixing section 420, and the energy is stored in the diffuser 430. It is desirable that the refrigerant pressure increases. Therefore, in the present embodiment, the opening area of the nozzle 410 is variably controlled by displacing the needle valve 411 according to the heat load required by the radiator 200.

In FIG. 3, the gas velocity is the nozzle 4
10 is the size when the speed of the refrigerant injected from 10 is 1, the axial dimension is the dimension with respect to the refrigerant outlet of the nozzle 410, and the radial dimension is the center of the ejector 400 from the center line thereof as a rotationally symmetric body. Shows dimensions.

As shown in FIG. 2, the housing 401 has the first connection port 4 connected to the radiator 200 side.
02, a second connection port 403 connected to the evaporator (300) side, and a third connection port 404 connected to the gas-liquid separator 500 side are provided.
A valve 405 controls the communication state between the devices 404.

Here, the valve 405 has a disk-shaped first valve portion 405b and a first valve portion 405b from which the needle valve 411 penetrates in the central portion and a communication hole 405a which also serves as a refrigerant passage is formed. And a flange-shaped second valve portion 405d that protrudes outward in the radial direction over the entire circumference at the tip of the cylindrical portion 405c. In the form, it is integrally molded with stainless steel).

At this time, the first valve portion 405b causes the refrigerant flowing from the first connection port 402 to bypass the nozzle 410 and flow to the second connection port 403.
The second valve portion 405d opens and closes the suction flow passage 406b for flowing the refrigerant flowing from the second connection port 402 to the mixing portion 420.

Both valve portions 405b and 405d are provided with a suction flow passage 406b when the bypass passage 406a is closed.
On the other hand, when the bypass passage 406a is opened, the suction flow passage 406b is closed.

Further, in the needle valve 411, at least a portion penetrating the communication hole 405a, the stepped portion 4 whose diameter on the conical taper side is larger than the diameter of the communication hole 405a.
By providing 11a, as shown in FIG.
When the needle valve 411 is displaced by a predetermined amount or more, the first valve portion 405b is locked to the stepped portion 411a and the valve 40
5 and the needle valve 411 are mechanically interlocked and displaced.

Next, the general operation of the heat pump type water heater (ejector cycle) will be described.

1. When hot water is generated (during normal operation), the valve 405 in the ejector 400 is operated to close the bypass passage 406a as shown in FIG. 4 (a).
At the same time, the suction flow passage 406b is opened.

As a result, when the compressor 100 starts up,
As shown in FIG. 5, the gas-phase refrigerant is sucked into the compressor 100 from the gas-liquid separator 500, and the compressed refrigerant is discharged into the radiator 200.
Is discharged. Then, the refrigerant that has heated the hot water supplied by the radiator 200 is decompressed and expanded by the nozzles 410 of the ejector 400 to suck the refrigerant in the evaporator 300.

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

On the other hand, the ejector 400 is used for the evaporator 300.
Since the refrigerant in the inside is sucked, the liquid-phase refrigerant flows into the evaporator 300 from the gas-liquid separator 500, and the inflowing refrigerant is
Macroscopically, the inside of the evaporator 300 absorbs heat from the outdoor air and evaporates while flowing from the upper side to the lower side.

During normal operation, the first valve section 4
Since the pressure on the first connection port 402 side is higher than the pressure on the second connection port 403 side across 05b, the valve 405 closes the bypass passage 406a due to this pressure difference, and
The suction flow passage 406b is opened.

Therefore, during normal operation, a range in which the stepped portion 411a of the needle valve 411 does not interfere with the first valve portion 405b (hereinafter, this range is referred to as a normal control range).
Then, the needle valve 411 is operated according to the heat load (flow rate of the driving flow) of the radiator (water-refrigerant heat exchanger) 200 (nozzle 41).
0 opening area) is controlled.

Incidentally, FIG. 6 is a ph diagram showing the operation of the ejector cycle according to the present embodiment, and the numbers shown in FIG. 6 show the state of the refrigerant at the positions of the numbers shown in FIG.

2. When removing frost adhering to the evaporator 300 (during defrosting operation) During defrosting operation, the nozzle 41 is used until the normal control range is exceeded.
The needle valve 411 is displaced so that the opening area of 0 becomes large, and as shown in FIG.
6a is opened and the suction flow passage 406b is closed, and a pump (not shown) for supplying hot water to the radiator (water-refrigerant heat exchanger) 200 is stopped to supply the refrigerant and hot water to the radiator 200. Substantially stop the heat exchange of.

As a result, the high-temperature refrigerant (hot gas) discharged from the compressor 100 flows through the bypass passage 406a in the ejector 400 into the evaporator 300 as shown in FIG. The refrigerant defrosts the frost adhering to the evaporator 300 while flowing in the inside of the evaporator 300 from the lower side to the upper side macroscopically as opposed to the time of normal operation.

Next, the features (effects) of this embodiment will be described.

According to the present embodiment, when the defrosting operation is performed, the high temperature refrigerant (hot gas) discharged from the compressor 100 using the bypass passage 406a provided in the ejector 400 is used for the evaporator 300. Will be supplied to
The configuration of the water heater (ejector cycle) can be simplified as compared with the case where the pipe for the bypass passage 406a is provided.

Further, since the valve 405 for opening / closing the bypass passage 406a and the needle valve 411 for variably controlling the opening area of the nozzle 410 are driven by the same actuator (stepping motor) 412, the ejector 400 (ejector cycle) It is possible to reduce the number of parts that compose the above) and reduce the manufacturing cost of the ejector 400 (ejector cycle).

By the way, in order to secure the lubrication and the sealing property of the sliding portion of the compressor 100, generally, in the refrigeration cycle (ejector cycle, expansion valve cycle, etc.),
Lubricating oil (refrigerator) is mixed with the refrigerant, but in the ejector cycle, although the drive flow flows through the compressor 100,
Since the suction flow does not flow through the compressor 100, there is a high possibility that the lubricating oil that has flowed into the evaporator 300 together with the suction flow will stay in the evaporator 300 and the lubricating oil that returns to the compressor 100 will run short.

In order to solve this, it is possible to consider the amount of lubricating oil staying in the evaporator 300 and mix a large amount of lubricating oil into the refrigerant, but if the amount of lubricating oil in the refrigerant increases. The heat exchange efficiency of the refrigerant in the radiator 200 and the evaporator 300 is reduced.

Therefore, in the present embodiment, during normal operation, the refrigerant is evaporated from the upper side to the lower side of the evaporator 300.
By circulating the refrigerant inside the evaporator 300, the lubricating oil accumulated in the evaporator 300 is discharged from the evaporator 300 by utilizing the flow of the refrigerant and the gravity.

Therefore, in the present embodiment, the lubricating oil returned to the compressor 100 is returned without mixing a large amount of lubricating oil in the refrigerant (the heat exchange efficiency of the refrigerant in the radiator 200 and the evaporator 300 is reduced). It can prevent running out of oil.

Further, even during the defrosting operation, the refrigerant is evaporated from the upper side to the lower side in the same manner as in the normal operation.
When it is circulated in 00, the refrigerant temperature decreases toward the lower side, so frost (molten water) thawed on the upper side where the refrigerant temperature is high flows downward due to gravity, and the lower frost temperature is lower. There is a risk that it will solidify (freeze) again.

On the other hand, in the present embodiment, in the defrosting operation, the refrigerant is circulated in the evaporator 300 from the lower side to the upper side, which is the reverse of the normal operation. Molten water) flows to the lower side where the refrigerant temperature is high. Therefore, the melted water solidifies (freezes) again
Since this can be prevented, the defrosting operation can be completed efficiently (in a short time).

(Other Embodiments) In the above-described embodiments, the present invention is applied to the water heater, but the present invention is not limited to this, and other ejector cycles such as refrigerators, freezers and air conditioners can be used. It can also be applied to the heat engine used.

Further, in the above embodiment, the supercritical ejector cycle in which the refrigerant pressure is carbon dioxide and the high pressure side refrigerant pressure (compressor discharge pressure) is equal to or higher than the critical pressure of the refrigerant has been described, but the present invention is not limited to this. Instead, it may be a critical ejector cycle in which the refrigerant pressure on the high-pressure side is less than the critical pressure of the refrigerant, such as an ejector cycle using chlorofluorocarbon as a refrigerant.

Further, in the above-mentioned embodiment, the stepping motor is adopted as the actuator 412, but the present invention is not limited to this, and other types such as a linear motor may be used.

[Brief description of drawings]

FIG. 1 is a schematic diagram of an ejector cycle (water heater) according to an embodiment of the present invention.

FIG. 2 is a schematic diagram of an ejector according to an embodiment of the present invention.

FIG. 3 is a three-dimensional characteristic diagram showing the relationship between the refrigerant flow velocity and the radial position from the refrigerant outlet of the nozzle to the refrigerant outlet of the diffuser with respect to the central portion of the refrigerant passage cross section of the ejector.

FIG. 4 is a schematic diagram showing the operation of the ejector according to the embodiment of the present invention.

FIG. 5 is an explanatory diagram showing a refrigerant flow during normal operation of the ejector cycle (water heater) according to the embodiment of the present invention.

FIG. 6 is a ph diagram at the time of normal operation of the ejector cycle (water heater) according to the embodiment of the present invention.

FIG. 7 is an explanatory diagram showing a refrigerant flow during a defrosting operation of the ejector cycle (water heater) according to the embodiment of the present invention.

[Explanation of symbols]

400 ... Ejector, 401 ... Housing, 402 ... First connection port, 403 ... Second connection port, 404 ... Third
Connection port, 405 ... Valve, 406a ... Bypass passage, 406b ... Suction flow passage, 410 ... Nozzle, 411 ...
Needle valve, 412 ... Actuator (stepping motor), 420 ... Mixing section, 430 ... Diffuser.

Claims (5)

[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, and pressure energy of the high-pressure refrigerant flowing out of the radiator (200) as velocity energy. A nozzle (410) for converting the refrigerant into a refrigerant and decompressing and expanding the refrigerant, and sucking the vapor-phase refrigerant evaporated in the evaporator (300) by a high-speed refrigerant flow injected from the nozzle (410), and the nozzle (410). A pressure increasing unit (420, 43) for increasing the pressure of the refrigerant by converting the velocity energy into pressure energy while mixing the refrigerant injected from the evaporator and the refrigerant sucked from the evaporator (300).
0) and the refrigerant flowing out of the radiator (200) bypassing the nozzle (410), and the evaporator (300).
An ejector (400) having a bypass passage (406a) leading to the refrigerant, and a gas-liquid separator (500) for storing the refrigerant by separating the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant. During normal operation in which the refrigerant is evaporated, the refrigerant that has flowed out of the radiator (200) is allowed to flow into the nozzle (410) while the evaporator (300) is being discharged.
Macroscopically, when the refrigerant is defrosted by flowing the refrigerant from the upper side toward the lower side to remove the frost adhering to the evaporator (300), the refrigerant flowing out from the radiator (200) is bypassed. An ejector cycle, characterized in that the refrigerant is caused to flow from the lower side to the upper side in the evaporator (300) while being circulated in the passage (406a). 2. 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, and pressure energy of the high-pressure refrigerant flowing out of the radiator (200) as velocity energy. A nozzle (410) for converting the refrigerant into a gas to expand the refrigerant under reduced pressure, and a high-velocity refrigerant flow injected from the nozzle (410) to suck the vapor-phase refrigerant evaporated in the evaporator (300), and the nozzle (410). ) And a refrigerant sucked from the evaporator (300) are mixed with each other to convert velocity energy into pressure energy to raise the pressure of the refrigerant (420, 4).
An ejector (400) having 30), and a gas-liquid separator (500) that stores the refrigerant by separating the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant, and removes frost adhering to the evaporator (300). An ejector cycle characterized in that, during defrosting, the refrigerant flows from the lower side toward the upper side in the evaporator (300). 3. A compressor (100) for sucking and compressing a refrigerant.
A radiator (200) that cools the refrigerant discharged from the compressor (100); an evaporator (300) that evaporates the refrigerant; and a refrigerant that stores the refrigerant by separating it into a gas-phase refrigerant and a liquid-phase refrigerant. A nozzle (410), which is applied to an ejector cycle including a gas-liquid separator (500), converts pressure energy of high-pressure refrigerant flowing out from the radiator (200) into velocity energy to expand the refrigerant under reduced pressure, and the nozzle. (4) The vapor-phase refrigerant evaporated in the evaporator (300) is sucked by the high-speed refrigerant flow injected from (410), and the refrigerant injected from the nozzle (410) and the refrigerant sucked from the evaporator (300). A pressure increasing unit (420, 4) for converting velocity energy into pressure energy while mixing
30) having a first connection port (402) connected to the radiator (200) side and a housing (401) of the ejector (400) connected to the evaporator (300) side. Second connection port (403) and the gas-liquid separator (50)
The third connection port (404) connected to the (0) side is provided, and the refrigerant introduced from the first connection port (402) is introduced into the ejector (400) inside the nozzle (4).
An ejector characterized in that a bypass passage (406a) that bypasses 10) and flows to the second connection port (403) and valve means (405) that opens and closes the bypass passage (406a) are provided. 4. The nozzle (410) is a variable nozzle whose throttle cross-sectional area can be changed by a needle valve (411), and the valve means (405) and the needle valve (411) are both The ejector according to claim 3, characterized in that it is driven by the same actuator (412). 5. 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; an ejector (400) according to claim 3 or 4; A gas-liquid separator (500) that stores a refrigerant by separating it into a phase refrigerant and a liquid refrigerant is provided, and flows out from the radiator (200) during a normal operation of evaporating the refrigerant in the evaporator (300). While allowing a refrigerant to flow into the nozzle (410), the evaporator (300)
Macroscopically, when the refrigerant is defrosted by flowing the refrigerant from the upper side toward the lower side to remove the frost adhering to the evaporator (300), the refrigerant flowing out from the radiator (200) is bypassed. An ejector cycle, characterized in that the refrigerant is caused to flow from the lower side to the upper side in the evaporator (300) while being circulated in the passage (406a).