JP3218734B2 - Refrigerant supply device for evaporator - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention provides a plurality of refrigerant flow paths through which a gas-liquid mixed-phase refrigerant flows and a plurality of cooling fluid flow paths through which a cooling fluid flows. The present invention relates to a refrigerant supply device for an evaporator that supplies the refrigerant to an evaporator that performs heat exchange. The evaporator refrigerant supply device and the evaporator are used in a cooling device for cooling members (electronic devices and the like) that need to be mounted and mounted on vehicles such as aircraft, vehicles, and ships. A gas or a liquid is used as the cooling fluid cooled by the refrigerant in the evaporator. The cooling fluid cooled by the refrigerant in the evaporator is transferred to a place where members (such as electronic devices) requiring cooling are arranged, and cools those members.

[0002]

2. Description of the Related Art A cooling device of the type described above is provided with a cooling fluid such as the cooling liquid and cooling air and a refrigerant such as chlorofluorocarbon (that is, condensed and liquefied from a gaseous state, and deprives the object to be cooled of heat. (A refrigerant that repeatedly vaporizes from a liquid state) so as to conduct heat exchange by heat conduction, thereby cooling the cooling fluid. In such a cooling device, usually, a refrigerant vaporized by heat exchange with the cooling fluid in the evaporator is compressed by a compressor, and is condensed and liquefied by a condenser for the cooling device.

[0003] The refrigerant liquefied in the cooling device condenser is transferred to a cooling device receiver on the downstream side. The cooling device receiver temporarily stores the refrigerant in a gas-liquid mixed phase state,
The downstream side has a function of transferring only the liquid refrigerant. The liquid refrigerant discharged from the cooling device receiver is transferred to an expansion valve. The opening of the expansion valve is appropriately adjusted to adjust the ratio of the gas phase and the liquid phase of the refrigerant. The adjusted gas-liquid mixed-phase refrigerant is transferred to the evaporator, where the heat exchange is performed with the cooling fluid. Due to this heat exchange, the ratio of the liquid in the gas-liquid mixed-phase refrigerant decreases. 12 and 13 are explanatory views of this type of evaporator.
2 shows a state in which the gas-liquid mixed-phase refrigerant is evenly distributed to the plurality of refrigerant flow paths of the evaporator, and FIG. 13 shows a state in which the refrigerant is unevenly distributed. In FIG. 12, the evaporator 01
Are a plurality of refrigerant channels 02 and a plurality of cooling fluid channels 03
Is provided. A refrigerant such as a mixed gas and liquid phase refrigerant flows through the refrigerant flow path 02, and a cooling fluid such as water or air flows through the cooling fluid flow path 03. Water cooled in this evaporator,
A cooling fluid such as air is used to cool a member requiring cooling such as an electronic device.

[0004]

When the vehicle is an aircraft, for example, a sudden acceleration or deceleration occurs in the aircraft due to a change in the attitude of the aircraft or a turn. When rapid acceleration or deceleration occurs not only in an aircraft but also in a vehicle, an inertial force acts on the liquid refrigerant in the evaporator 01. When the liquid refrigerant in the evaporator is biased in the evaporator due to the inertial force, the refrigerant may not flow through the refrigerant flow path 02 as shown in FIG. In this case, the heat exchange area decreases, and the performance of the evaporator 01 decreases.

[0005] The above-mentioned inconvenience frequently occurs particularly on a high-mobility aircraft having large changes in acceleration and attitude. The present invention has been made in view of the above circumstances, and has an object of the following content (O01). (O01) Even when acceleration or deceleration occurs in the vehicle, the refrigerant must flow uniformly in the refrigerant flow path of the evaporator.

[0006]

Next, the configuration of the present invention devised to solve the above-mentioned problem will be described. The components of the present invention correspond to the components of the embodiments described later. For the sake of simplicity, the reference numerals of the components of the embodiment are enclosed in parentheses. The reason why the present invention is described in correspondence with the reference numerals of the embodiments described below is to facilitate understanding of the present invention, and not to limit the scope of the present invention to the embodiments.

[0007] In order to solve the above problems, the first of the present application
The refrigerant supply device for an evaporator (12) of the invention is provided with a plurality of refrigerant flow paths (14a) through which a gas-liquid mixed-phase refrigerant flows and a plurality of cooling fluid flow paths (14b) through which a cooling fluid flows.
An evaporator (1) for exchanging heat between the refrigerant and the cooling fluid.
4), an evaporator refrigerant supply device (1) for supplying the refrigerant.
(A01) An annular refrigerant distribution formed by a cylindrical small-diameter inner wall (21a) and a large-diameter inner wall (22a), which is characterized by having the following components (A01) to (A05). Room (23), (A02) The small-diameter inner wall (21)
a) a plurality of refrigerant inlets (21b) which are provided along the circumferential direction of a) and allow the gas-liquid mixed-phase refrigerant to flow into the annular refrigerant distribution chamber (23) in a swirling manner; A plurality of refrigerant outlets (22b) provided along the circumferential direction of the inner wall (22a) to allow the refrigerant in the annular refrigerant distribution chamber (23) to flow out, (A04) the plurality of refrigerant inlets (21b) For supplying a gas-liquid mixed-phase refrigerant to the tank (A05)
The plurality of refrigerant outlets (22b) are connected to the evaporator (14).
A plurality of refrigerant connection paths (13) respectively connected to the predetermined refrigerant flow path (14a).

Further, the refrigerant supply device for an evaporator (32) of the second invention of the present application comprises a plurality of refrigerant flow paths (14a) through which a gas-liquid mixed-phase refrigerant flows and a plurality of cooling fluid flows through which a cooling fluid flows. And a refrigerant supply device (32) for supplying the refrigerant to an evaporator (14) which is provided with a passage (14b) and exchanges heat between the refrigerant and the cooling fluid. (A06), characterized in that the liquid refrigerant supply member (33) and the gas-liquid multiphase refrigerant outflow member (34, 36) are relatively rotatable in a state where their contact surfaces are in surface contact with each other. ), (A07) a plurality of liquid refrigerant supply ports (33c) formed along the circumference on the contact surface of the liquid refrigerant supply member (33), (A08) the gas-liquid mixed phase refrigerant outflow member (34). The contact surface corresponds to the plurality of liquid refrigerant supply ports (33c). Made a plurality of refrigerant inlet (34b, 36a), (A09) the plurality of liquid coolant supply port device for supplying a liquid coolant to (33c), (A010) of the plurality of refrigerant inlet (34b, 36
a) a plurality of refrigerant connection paths (13) for respectively connecting the a) to predetermined refrigerant flow paths (14a) of the evaporator (14).

[0009]

Next, the operation of the present invention having the above-mentioned features will be described. In the refrigerant supply device (12) for an evaporator according to the first invention of the present application having the above-described features, the cylindrical small-diameter inner wall (21) is provided.
a) and a plurality of refrigerant inlets (21b) provided along the circumferential direction of the small-diameter inner wall (21a) of the annular refrigerant distribution chamber (23) formed by the large-diameter inner wall (22a). A multi-phase refrigerant is supplied. The gas-liquid mixed-phase refrigerant flows from the refrigerant inlet (21b) to the annular refrigerant distribution chamber (2).
3) Introduce while turning. The swirling gas-liquid mixed phase refrigerant moves toward the large-diameter inner wall (22a) by centrifugal force in the annular refrigerant distribution chamber (23). The gas-liquid mixed-phase refrigerant swirling in the annular refrigerant distribution chamber (23) flows out from a plurality of refrigerant outlets (22b) provided along the circumferential direction of the large-diameter inner wall (22a). . Since the swirling gas-liquid mixed phase refrigerant moves toward the large-diameter inner wall (22a) by centrifugal force while swirling, even if acceleration or deceleration in a certain direction occurs in the vehicle, the plurality of refrigerant outlets ( 22b) flows out uniformly. That is, the swirling refrigerant does not flow out of the refrigerant outlet (22b) in a specific region among the plurality of refrigerant outlets (22b).

The gas-liquid mixed-phase refrigerant uniformly flowing out of the plurality of refrigerant outlets (22b) flows through the plurality of refrigerant connection paths (13) to a predetermined refrigerant flow path (14a) of the evaporator (14). ). Therefore, even if acceleration occurs in the vehicle, the refrigerant in the gas-liquid mixed phase causes the evaporator (14).
Are uniformly supplied to the plurality of refrigerant flow paths (14a). In the evaporator (14), heat flows between the gas-liquid mixed-phase refrigerant flowing uniformly through the plurality of refrigerant flow paths (14a) and the cooling fluid when flowing through the plurality of cooling fluid flow paths (14b). An exchange takes place. As described above, the gas-liquid mixed-phase refrigerant is uniformly supplied to the plurality of refrigerant flow paths (14a) of the evaporator (14) even when acceleration or the like occurs in the vehicle.
4) It is possible to prevent a decrease in the efficiency of heat exchange.

In the refrigerant supply device (32) for an evaporator according to the second invention of the present application having the above-described features, a circle is formed on the contact surface of the liquid refrigerant supply member (33) with the gas-liquid mixed-phase refrigerant outflow member (34). A plurality of liquid coolant supply ports (3) formed along the circumference
In 3c), a liquid refrigerant is supplied. Each of the liquid refrigerant supply ports (33c) of the liquid refrigerant supply member (33) and a plurality of refrigerant receiving ports (34b, 36a) formed in the gas-liquid mixed-phase refrigerant outflow member (34) corresponding thereto. The area of the connection part (that is, the connection area or the communication area) is
The liquid refrigerant supply member (33) and the gas-liquid multi-phase refrigerant outflow member (34) can be adjusted by relatively rotating the members in a state where their contact surfaces are in surface contact. Liquid refrigerant supplied from the plurality of liquid refrigerant supply ports (33c) to the plurality of refrigerant receiving ports (34b, 36a) respectively flows into the plurality of refrigerant connection paths (13). At this time, the liquid refrigerant supply port (33c) and the refrigerant receiving port (3
4b, 36a), the liquid refrigerant supplied to the liquid refrigerant supply port (33c) passes through the refrigerant receiving port (34b, 36a), and the liquid refrigerant is supplied to the liquid refrigerant supply port (33c). When entering the connection path (13) side, it adiabatically expands to become a gas-liquid mixed phase refrigerant.

The refrigerant is supplied to the plurality of liquid refrigerant supply ports (33).
Since c) is supplied in a liquid state without gas,
The liquid refrigerant is uniformly supplied to the plurality of liquid refrigerant supply ports (33c).
The refrigerant flowing from the plurality of liquid refrigerant supply ports (33c) to the respective refrigerant connection paths (13) through the corresponding refrigerant reception ports (34b, 36a) becomes a gas-liquid mixed phase refrigerant. Since each of the refrigerant connection paths (13) is connected to a predetermined refrigerant flow path (14a) of the evaporator (14), the refrigerant in the gas-liquid mixed phase can maintain the evaporator even if acceleration occurs in the vehicle. (14) The refrigerant is uniformly supplied to the plurality of refrigerant channels (14a). In the evaporator (14), a gas-liquid mixed-phase refrigerant uniformly flowing through the plurality of refrigerant channels (14a);
When flowing through the plurality of cooling fluid channels (14b), heat exchange is performed with the cooling fluid. As described above, the gas-liquid mixed phase refrigerant is uniformly supplied to the plurality of refrigerant flow paths (14a) of the evaporator (14) even when acceleration or the like occurs in the vehicle. A decrease in the efficiency of heat exchange can be prevented.

[0013]

Next, embodiments of the present invention will be described with reference to the drawings, but the present invention is not limited to the following embodiments. FIG. 1 is an explanatory diagram of a cooling device U having a refrigerant supply device for an evaporator according to an embodiment of the present invention. This cooling device U
Is on board the aircraft. The cooling device U mounted on the aircraft has a controller C and a motor driver D driven by a power supply B. The Freon compressor 2 is connected to the output shaft of the motor 1 driven by the motor driver D. The Freon compressor 2 has a function of compressing Freon, which is a refrigerant, and transferring it to the condenser 3. The condenser 3 is a heat exchanger that exchanges heat between Freon (refrigerant) flowing from the Freon compressor 2 and a condensing coolant such as external air or fuel supplied from a condensing coolant supply source 4. It is configured.

The condenser 3 has a function of condensing a gaseous refrigerant supplied from the CFC 2 and converting it into a liquid, and has a refrigerant flow path 4. In addition, the condenser 3 has a condensing coolant flow path 5 disposed in contact with the refrigerant flow path 4. The condensing coolant flow path 5 is supplied with a condensing coolant such as external air or fuel from the condensing coolant supply source 4 (see FIG. 1). The refrigerant removes heat from the gaseous refrigerant flowing through the flow path 4 to liquefy the refrigerant.

The condenser 3 is connected to a cooling device receiver 7 via a liquid refrigerant transfer pipe 6 for transferring refrigerant liquefied by heat exchange (ie, liquid refrigerant). The cooling device receiver 7 includes the liquid refrigerant transfer pipe 6.
Has the function of temporarily storing the refrigerant transferred by the above. The cooling device receiver 7 is connected to the expansion valve 9 by a liquid refrigerant transfer pipe 8. The expansion valve 9 connected to the liquid refrigerant transfer pipe 8 is configured so that the opening thereof is controlled by the controller C.

The refrigerant that has been expanded by the expansion valve 9 into a gas-liquid mixed phase state is connected to a refrigerant supply device 12 for an evaporator by a gas-liquid mixed phase flow transfer pipe 11. Evaporator refrigerant supply device 1
2 has a function of uniformly distributing the gas-liquid mixed-phase refrigerant supplied by the gas-liquid mixed-phase flow transfer pipe 11 to the plurality of refrigerant connection paths 13 as will be described in detail later. Each of the plurality of refrigerant connection paths 13 is provided with a number of refrigerant flow paths 14 of the evaporator 14.
a of the plurality of refrigerant channels 14a. The evaporator 14 has a large number of cooling fluid passages 14b disposed in contact with the large number of coolant passages 14a, and flows from the coolant connection passage 13 into the coolant passage 14a.
And a heat exchanger for exchanging heat between the refrigerant flowing through the cooling fluid and the antifreeze coolant flowing through the cooling fluid flow path 14b. The antifreezing coolant flowing through the cooling fluid flow path 14b is deprived of heat by the evaporator 14 and its temperature decreases, and is transferred to a member such as an electronic device that needs to be cooled (a member requiring cooling). At this time, the cooling member 15 is cooled and then returns to the evaporator 14 again.

In the evaporator 14, the refrigerant removes heat of vaporization from the antifreeze coolant and vaporizes. The refrigerant that has passed through the evaporator 14 flows through a connection pipe 16 that connects the evaporator 14 and the CFC 2 and returns to the CFC 2. The connection pipe 1
6 is provided with a sensor 17 for detecting the pressure and temperature of the refrigerant flowing therethrough. The detection signal of the sensor 17 is input to the controller C. The controller C
Has a function of controlling the opening of the expansion valve 9 based on the detection signal of the sensor 17 so that the pressure and temperature of the refrigerant flowing through the connection pipe 16 are maintained at predetermined values.

Next, the evaporator refrigerant supply device 12 will be described in detail with reference to FIGS. 2 is a detailed explanatory view of the gas-liquid multiphase flow transfer pipe 11, the evaporator refrigerant supply device 12, the refrigerant connection path 13, and the evaporator 14 shown in FIG. 1, and FIG. 3 is a cross-sectional view taken along the line III-III of FIG. FIG. 2 and 3,
The evaporator refrigerant supply device 12 includes a small-diameter cylindrical member 21 and a bottomed cylindrical member 22. Bottomed cylindrical member 22
An annular groove is formed on the inner surface of the small-diameter cylindrical member 22. The small-diameter cylindrical member 21 is inserted and fixed inside the bottomed cylindrical member 22. An annular refrigerant distribution chamber 23 is formed by the outer surface of the small-diameter cylindrical member 21, that is, the small-diameter inner wall 21 a, and the inner surface of the annular concave groove of the bottomed cylindrical member 22, that is, the large-diameter inner wall 22 a. The small diameter inner wall 2
A plurality of refrigerant inlets 21b are formed in 1a along the circumferential direction. The small-diameter cylindrical member 21 includes a refrigerant inflow passage 21c connected to the gas-liquid multiphase flow transfer pipe 11, and a plurality of refrigerants through which the gas-liquid multiphase refrigerant flows from the refrigerant inflow passage 21c to the plurality of refrigerant inflow ports 21b. A communication hole 21d (see FIG. 3) is formed. The refrigerant communication hole 21d and the refrigerant inflow port 21b are formed so as to face in a direction such that the gas-liquid mixed-phase refrigerant flowing into the annular refrigerant distribution chamber 23 swirls.

Large-diameter inner wall 22a of the bottomed cylindrical member 22
Is provided with a plurality of refrigerant outlets 22b along its circumferential direction. Each of the refrigerant outlets 22b is for allowing a gas-liquid mixed-phase refrigerant to flow out of the annular refrigerant distribution chamber 23. Each of the refrigerant outlets 22b communicates with the external refrigerant connection path 13 through a refrigerant communication hole 22c.
The refrigerant inflow side of the evaporator 14 is divided into a plurality of sections by a partition wall 14c (see FIG. 2), and a predetermined plurality of refrigerant flow paths 14a communicate with each section. The plurality of refrigerant connection paths 13 are respectively connected to a plurality of predetermined refrigerant flow paths 14a communicating with each section separated by the partition wall 14c. The refrigerant flow path 14a separated by the partition wall 14c on the refrigerant inflow side of the evaporator 14 merges on the refrigerant outflow side of the evaporator 14 and is connected to the connection pipe 16 (see FIGS. 1 and 2). ing.

(Operation of the First Embodiment) Next, the operation of the first embodiment having the above-described configuration will be described. Refrigerant (Freon) vaporized by removing heat of the antifreeze coolant in the evaporator 14
Pass through the connection pipe 16. The temperature and pressure of the refrigerant passing through the connection pipe 16 are input to the controller C,
Controls the opening degree of the expansion valve 9 based on the detection signal of the sensor 17 so that the pressure and temperature of the refrigerant flowing through the connection pipe 16 are maintained at predetermined values. The refrigerant which has been compressed by the Freon compressor 2 and has its temperature raised and its pressure increased is transferred to the condenser 3. Heat exchange is performed between the refrigerant and the condensing coolant in the condenser 3, and the refrigerant is condensed and liquefied.

The refrigerant liquefied in the condenser 3, ie, the liquid refrigerant, is transferred by the refrigerant transfer pipe 6 and flows into the cooling device receiver 7. The liquid refrigerant once stored in the cooling device receiver 7 is transferred from the liquid refrigerant transfer pipe 8 to the expansion valve 9.
Is transferred to The liquid refrigerant is adiabatically expanded by the expansion valve 9 and passes through the gas-liquid multiphase flow transfer pipe 11 in a state where the ratio between the liquid phase portion and the gas phase portion of the refrigerant is controlled to a predetermined value. The refrigerant flows into the refrigerant supply device 12 (see FIGS. 1 and 2). 2 and 3, the gas-liquid mixed-phase refrigerant flowing into the evaporator refrigerant supply device 12 flows into the annular refrigerant distribution chamber 23 from the refrigerant inlet 21b of the small-diameter cylindrical member 21 and swirls. The swirling gas-liquid mixed phase refrigerant moves toward the large-diameter inner wall 22a of the bottomed cylindrical member 22 by centrifugal force. And
The refrigerant is uniformly distributed to the plurality of refrigerant outlets 22b formed on the large-diameter inner wall 22a. Even if the acceleration in the horizontal direction (Y1-Y2 direction) occurs in FIG. 2, the refrigerant of the gas-liquid mixed phase swirling in the refrigerant distribution chamber 23 is not biased to one side and the plurality of refrigerant outlets 22b is evenly distributed.

The gas-liquid mixed-phase refrigerant flowing out of each of the refrigerant outlets 22b is supplied to the refrigerant communication hole 22c and the external refrigerant connection path 1c.
3 and flows into the evaporator 14. As can be seen from FIG. 2, since each refrigerant connection path 13 is connected to a partition partitioned by the partition wall 14c, the gas-liquid mixed-phase refrigerant is uniformly distributed to each partition. Assuming that the horizontal direction (Y1-
Even if an acceleration in the Y2 direction occurs, the gas-liquid mixed-phase refrigerant uniformly distributed to each section partitioned by the partition wall 14c is:
Even when the refrigerant flows in the predetermined plurality of refrigerant flow paths 14a communicating with the respective sections, the flow is biased to one side (see FIG. 4), but does not entirely bias to one side in the evaporator 14 (see FIG. 13). Therefore, a plurality of predetermined refrigerant flow paths 14a communicating with each section are provided.
Since the gas-liquid mixed phase refrigerant can flow uniformly every time, it is possible to mitigate a decrease in the heat exchange rate due to acceleration. Then, the refrigerant (Freon) vaporized by heat exchange with the antifreeze coolant in the evaporator 14 flows through the connection pipe 16 again into the Freon compressor 2.

(Embodiment 2) Next, Embodiment 2 of the present invention will be described with reference to FIG. FIG. 5 is a view corresponding to FIG. 2 of the first embodiment. In the description of the second embodiment, components corresponding to the components of the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted. The second embodiment differs from the first embodiment in that a refrigerant connection path 13 for connecting the evaporator refrigerant supply device 12 and the evaporator 14 is formed inside the connection path forming plate P. In other respects, the second embodiment is the same as the first embodiment. In FIG. 5, the refrigerant connection path 13 is formed by perforating a connection path forming plate P. The upper surface of the connection path forming plate P is coupled to the lower surface of the evaporator refrigerant supply device 12, and the lower surface of the connection path forming plate P is coupled to the upper surface of the evaporator 14. In addition,
Gaskets (not shown) are arranged on the connection surfaces. The refrigerant communication port 22c of the bottomed cylindrical member 22 and each part of the evaporator 14 partitioned by the partition wall 14c are connected by a refrigerant connection path 13 formed in the connection path forming plate P. I have. By using the connection path forming plate P, the work of assembling the cooling device is facilitated. The second embodiment also has the same operation as the first embodiment. ,

Third Embodiment Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 6 is a view corresponding to FIG. 1 of the first embodiment. In the description of the third embodiment, components corresponding to the components of the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted. In the third embodiment, instead of the expansion valve 9, the gas-liquid multi-phase flow transfer pipe 11, and the evaporator refrigerant supply device 12 shown in FIG. 1 of the first embodiment, the evaporator refrigerant supply device 32 having the function of an expansion valve is provided. Is different from the first embodiment in that the first embodiment is used. In other respects, the second embodiment is the same as the first embodiment. FIG.
, The cooling device receiver 7 for temporarily storing the refrigerant transferred by the liquid refrigerant transfer pipe 6 is provided with a liquid refrigerant transfer pipe 8.
It is connected to the evaporator refrigerant supply device 32 by the.
The evaporator refrigerant supply device 32 connected to the liquid refrigerant transfer pipe 8 has the function of an expansion valve, and the controller C
The opening degree of the expansion valve is controlled by the control valve.

The refrigerant supply device 32 for the evaporator, which functions as an expansion valve, expands the liquid refrigerant transferred from the liquid refrigerant transfer pipe 8 into a gas-liquid mixed state, and then converts the gas-liquid mixed phase refrigerant into a plurality of liquid refrigerants. It has a function of uniformly distributing the refrigerant to the refrigerant connection path 13. Each of the plurality of refrigerant connection paths 13 is connected to a predetermined one of the plurality of refrigerant flow paths 14a of the plurality of refrigerant flow paths 14a of the evaporator 14, similarly to the first embodiment.

Next, the evaporator refrigerant supply device 32 will be described in detail with reference to FIGS. 7 is a detailed explanatory diagram of the liquid refrigerant transfer pipe 8, the evaporator refrigerant supply device 32, the refrigerant connection path 13, and the evaporator 14 shown in FIG. 6, and FIG. 8 is a detailed explanatory diagram of the evaporator refrigerant supply device 32. 8A is a sectional view taken along the line VIIIA-VIIIA of FIG. 7, and FIG. 8B is a sectional view taken along the line VII of FIG.
FIG. 7 is a sectional view taken along line IB-VIIIB. 7 and 8, the evaporator refrigerant supply device 32 has a small-diameter cylindrical member 33 and a large-diameter cylindrical member 34. The small-diameter cylindrical member 33 is inserted into the inner surface of the large-diameter cylindrical member 34. The small-diameter cylindrical member 33 is held inside the large-diameter cylindrical member 34 by an upper cover 35 and a lower cover 36 fixed above and below the large-diameter cylindrical member 34. The small-diameter cylindrical member 33 is rotatable inside the large-diameter cylindrical member 34 by bearings 38 and 39, and a coil 41
Can control the rotational position. In the third embodiment, the small-diameter cylindrical member 33 has a function as a liquid refrigerant supply member of the present invention, and the large-diameter cylindrical member 34 has a function as a gas-liquid mixed-phase refrigerant outflow member of the present invention. ing.

An annular concave groove is formed on the outer surface of the small-diameter cylindrical member 33, and an annular refrigerant distribution chamber 4 is formed by the inner surface of the annular concave groove and the inner surface of the large-diameter cylindrical member 34.
2 are formed. A plurality of refrigerant inlets 33a are formed on the bottom surface of the concave groove of the small-diameter cylindrical member 33 along the circumferential direction. One end of a refrigerant communication hole 33b is connected to each of the plurality of refrigerant inlets 33a, and the other end of the refrigerant communication hole 33b is connected to an outer surface of the small-diameter cylindrical member 33 (that is, an inner surface of the large-diameter cylindrical member 34). (A contact surface) is connected to a liquid refrigerant supply port 33c arranged along the circumference.

On the outer wall of the large-diameter cylindrical member 34, there is formed a through hole 34a for connecting the external liquid refrigerant transfer pipe 8 and the internal annular refrigerant distribution chamber 42.
A plurality of refrigerant receiving ports 34b are formed on the inner surface of the outer wall of the large-diameter cylindrical member 34 in correspondence with the plurality of liquid refrigerant supply ports 33c. Each of the refrigerant receiving ports 34b
Are respectively connected to the external refrigerant connection path 13 through the refrigerant communication holes 34c. The communication area between the liquid refrigerant supply port 33c and the refrigerant receiving port 34b can be adjusted by rotating the small-diameter cylindrical member 33. When the communication area between the liquid refrigerant supply port 33c and the refrigerant receiving port 34b is narrowed, the refrigerant flowing into the refrigerant communication hole 34c through the part becomes a gas-liquid mixed phase refrigerant by adiabatic expansion. . Therefore, the liquid refrigerant supply port 33
c, the refrigerant receiving port 34b, and the refrigerant communication hole 34c,
The function of the expansion valve is realized. The degree of opening of the valve that functions as the expansion valve can be controlled by adjusting the rotational position of the small-diameter cylindrical member 33 by the coil 41 operated by the controller C.

The refrigerant inflow side of the evaporator 14 is
The partition is divided into a plurality of sections by c, and a plurality of predetermined refrigerant flow paths 14a communicate with each section. The plurality of refrigerant connection paths 13 are respectively connected to a plurality of predetermined refrigerant flow paths 14a communicating with each section separated by the partition wall 14c. The refrigerant flow path 14a separated by the partition wall 14c on the refrigerant inflow side of the evaporator 14 merges on the refrigerant outflow side of the evaporator 14 and is connected to the connection pipe 16 (see FIGS. 6 and 7). ing. The evaporator refrigerant supply device 32 of the third embodiment described above is used instead of the expansion valve 9, the gas-liquid multi-phase flow transfer pipe 11, and the evaporator refrigerant supply device 12 of the first embodiment shown in FIG. And other configurations are the same as those of the first embodiment.
Is the same as

(Operation of Third Embodiment) Next, the operation of the third embodiment having the above-described configuration will be described. Refrigerant (Freon) vaporized by removing heat of the antifreeze coolant in the evaporator 14
Pass through the connection pipe 16. The temperature and pressure of the refrigerant passing through the connection pipe 16 are input to the controller C,
The small-diameter cylindrical member 3 of the evaporator refrigerant supply device 32 is configured to maintain the pressure and temperature of the refrigerant flowing through the connection pipe 16 at predetermined values based on the detection signal of the sensor 17.
3, the size of the communication area between the liquid refrigerant supply port 33c and the refrigerant receiving port 34b is adjusted. The refrigerant which has been compressed by the Freon compressor 2 and has its temperature raised and its pressure increased is transferred to the condenser 3. Heat exchange is performed between the refrigerant and the condensing coolant in the condenser 3, and the refrigerant is condensed and liquefied.

The refrigerant liquefied in the condenser 3, that is, the liquid refrigerant is transferred by the refrigerant transfer pipe 6 and flows into the cooling device receiver 7. The liquid refrigerant once stored in the cooling device receiver 7 is transferred from the liquid refrigerant transfer pipe 8 to the evaporator refrigerant supply device 32. The liquid refrigerant flows to the liquid refrigerant supply port 33c through the through hole 34a, the refrigerant distribution chamber 42, the plurality of refrigerant inlets 33a, and the refrigerant communication holes 33b of the evaporator refrigerant supply device 32 in this order. When the liquid refrigerant flows into the refrigerant communication hole 34c through the narrowed communication area between the liquid refrigerant supply port 33c and the refrigerant receiving port 34b,
When flowing into the third side, the refrigerant becomes a gas-liquid mixed phase refrigerant due to adiabatic expansion. The liquid refrigerant supply port 33c and the refrigerant receiving port 34b
The communication area between them is controlled by the rotational position of the small-diameter cylindrical member 33, whereby the ratio between the liquid phase portion and the gas phase portion of the refrigerant adiabatically expanded in the communication area portion is controlled to a predetermined value. Is done. The gas-liquid mixed-phase refrigerant whose state is controlled in this way flows into the evaporator 14 through the refrigerant communication hole 34c and the refrigerant connection path 13.

As can be seen from FIG. 7, each refrigerant connection path 13
Is connected to the sections partitioned by the partition wall 14c, so that the gas-liquid mixed-phase refrigerant is uniformly distributed to each section. Then, the refrigerant (Freon) vaporized by heat exchange with the antifreeze coolant in the evaporator 14 flows through the connection pipe 16 again into the Freon compressor 2. In the third embodiment, similarly to the first embodiment, a gas-liquid mixed-phase refrigerant can flow uniformly in each of a plurality of predetermined refrigerant flow paths 14a communicating with each section, so that a decrease in the heat exchange rate due to acceleration is mitigated. be able to.

Embodiment 4 Next, Embodiment 4 of the present invention will be described with reference to FIG. FIG. 9 is a view corresponding to FIG. 7 of the third embodiment. In the description of the fourth embodiment, the same reference numerals are given to components corresponding to the components of the third embodiment, and a detailed description thereof will be omitted. The fourth embodiment differs from the third embodiment in the structure of the evaporator refrigerant supply device 32, but is otherwise the same as the third embodiment. In the fourth embodiment, the small-diameter cylindrical member 3
3 has a function as a liquid refrigerant supply member of the present invention, and the lower cover 36 has a function as a gas-liquid mixed phase refrigerant outflow member of the present invention. In FIG. 9, an annular concave groove is formed on the outer surface of the small-diameter cylindrical member 33,
An annular refrigerant distribution chamber 42 is formed by the inner surface of the annular groove and the inner surface of the large-diameter cylindrical member 34. A plurality of refrigerant inlets 33a are formed on the bottom surface of the concave groove of the small-diameter cylindrical member 33 along the circumferential direction. One end of a refrigerant communication hole 33b is connected to each of the plurality of refrigerant inlets 33a, and the other end of the refrigerant communication hole 33b is formed on the outer bottom surface of the small-diameter cylindrical member 33 (contact surface with the inner bottom surface of the lower cover 36). It is connected to the liquid refrigerant supply port 33c arranged along the circumference. The fourth embodiment is different from the third embodiment in that the liquid refrigerant supply hole 33c is formed on the bottom surface of the small-diameter cylindrical member 33 on the outer peripheral surface.

On the inner bottom surface of the lower cover 36 (that is, the contact surface with the outer bottom surface of the small-diameter cylindrical member 33), a plurality of refrigerant receiving ports 36a are formed corresponding to the plurality of liquid refrigerant supply ports 33c. ing. Each refrigerant receiving port 3
6a are each connected with the external refrigerant connection path 13 by the refrigerant communication hole 36b. The communication area between the liquid refrigerant supply port 33c and the refrigerant receiving port 36a can be adjusted by rotating the small-diameter cylindrical member 33. When the communication area between the liquid refrigerant supply port 33c and the refrigerant receiving port 36a is narrowed, the refrigerant that has flowed into the refrigerant communication hole 36b through that part becomes a gas-liquid mixed phase refrigerant by adiabatic expansion. . Therefore, the liquid refrigerant supply port 33
c, by the refrigerant receiving port 36a, and the refrigerant communication hole 36b,
The function of the expansion valve is realized. The opening degree of the valve that functions as the expansion valve can be controlled by adjusting the rotational position of the small-diameter cylindrical member 33 using the coil 41 operated by the controller C.
The same operation as in the third embodiment is provided. ,

(Modifications) Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above-described embodiments, but falls within the scope of the present invention described in the appended claims. Thus, various small design changes can be made.

For example, the present invention can be applied to a condenser for a cooling device for various vehicles other than an aircraft. Further, as a modification of the third embodiment shown in FIG. 7, the configuration shown in FIG. 10 can be adopted. In FIG. 10, an annular refrigerant distribution chamber 42 is formed inside a small-diameter cylindrical member 33. The outer surface of the small-diameter cylindrical member 33 has a plurality of liquid coolant supply ports 3 along its circumferential surface.
3c is formed. The liquid refrigerant supply port 33c is connected to the refrigerant distribution chamber 42. Further, a coolant receiving port 34b is formed on the inner surface of the large-diameter cylindrical member 34 so as to correspond to the liquid coolant supply port 33c. Each of the refrigerant receiving ports 34b communicates with the external refrigerant connection path 13 through a refrigerant communication hole 34c. The modification shown in FIG. 10 has the same operation as the third embodiment. Further, as a modification of the fourth embodiment shown in FIG. 9, the configuration shown in FIG. 11 can be adopted. This embodiment shown in FIG. 11 differs from the fourth embodiment shown in FIG. 9 in that an annular refrigerant distribution chamber 42 is formed inside the large-diameter cylindrical member 34. The modification shown in FIG. 11 also has the same operation as that of the fourth embodiment shown in FIG. Further, in the third and fourth embodiments or the modified examples shown in FIGS. 10 and 11, the refrigerant distribution chambers 42 are arranged in multiple stages vertically, and a liquid refrigerant supply port is provided for each refrigerant distribution chamber 42. It is also possible to adopt a structure in which a coolant receiving port is provided. Furthermore,
The liquid refrigerant supply port 33c and the refrigerant receiving ports 34b, 36
Any shape can be adopted as the shape of a, and for example, a circle or an ellipse can be adopted. Further, the opening degree of the expansion valve 9 is determined by the connection pipe 16.
It is possible to directly control by the pressure of the temperature-sensitive cylinder attached to the controller without using a controller.

[0037]

The refrigerant supply device for an evaporator according to the present invention having the above-described structure has the following effect (E01). (E01) Even if acceleration or deceleration occurs in the vehicle, the refrigerant can be made to flow uniformly in the refrigerant flow path of the evaporator.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram of a cooling device U having a refrigerant supply device for an evaporator according to a first embodiment of the present invention.

FIG. 2 is a gas-liquid multiphase flow transfer pipe 1 shown in FIG.
1 is a detailed explanatory view of a refrigerant supply device 12 for an evaporator, a refrigerant connection path 13, and an evaporator 14.

FIG. 3 is a sectional view taken along the line III-III of FIG. 2;

FIG. 4 is an operation explanatory view of the first embodiment of the present invention.

FIG. 5 is an explanatory diagram of Embodiment 2 of the present invention.

FIG. 6 is an explanatory view of a cooling device U having a refrigerant supply device for an evaporator according to a third embodiment of the present invention.

FIG. 7 is a detailed explanatory view of the liquid refrigerant transfer pipe 8, the evaporator refrigerant supply device 32, the refrigerant connection path 13, and the evaporator 14 shown in FIG.

8 is a detailed explanatory view of the refrigerant supply device 32 for the evaporator, FIG. 8A is a sectional view taken along the line VIIIA-VIIIA of FIG. 7, and FIG. 8B is a sectional view taken along the line VIIIB-VIIIB of FIG.

FIG. 9 is an explanatory diagram of Embodiment 4 of the present invention.

FIG. 10 is an explanatory diagram of a modification of the third embodiment of the present invention.

FIG. 11 is an explanatory diagram of a modification of the fourth embodiment of the present invention.

FIG. 12 is an explanatory diagram of a conventional technique.

FIG. 13 is an operation explanatory view of the conventional technique.

[Explanation of symbols]

12: refrigerant supply device for evaporator, 13: refrigerant connection path, 14
... Evaporator, 14a ... Refrigerant flow path, 14b ... Cooling fluid flow path,
21a: small-diameter inner wall, 21b: refrigerant inlet, 22a: large-diameter inner wall, 22b: refrigerant outlet, 23: refrigerant distribution chamber, 32: evaporator refrigerant supply device, 33: liquid refrigerant supply member (small-diameter cylindrical member), 33c: liquid refrigerant supply port, 34: gas-liquid mixed-phase refrigerant outflow member (large-diameter cylindrical member), 34b: refrigerant receiving port, 36 ... gas-liquid mixed-phase refrigerant outflow member (lower cover), 36a
… Refrigerant inlet,

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-61-147071 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F25B 41/00 F25B 39/02

Claims (2)

(57) [Claims] An evaporator is provided with a plurality of refrigerant flow paths through which a gas-liquid mixed-phase refrigerant flows and a plurality of cooling fluid flow paths through which a cooling fluid flows, and performs heat exchange between the refrigerant and the cooling fluid. A refrigerant supply device for an evaporator for supplying the refrigerant, comprising the following constituent features (A01) to (A05): (A01) a cylindrical small-diameter inner wall and a large diameter An annular refrigerant distribution chamber formed by an inner wall, (A02) a plurality of refrigerant flows provided along a circumferential direction of the small-diameter inner wall and for causing a gas-liquid mixed-phase refrigerant to flow into the annular refrigerant distribution chamber so as to swirl; An inlet, (A03) a plurality of refrigerant outlets that are provided along the circumferential direction of the large-diameter inner wall and allow the refrigerant to flow into the annular refrigerant distribution chamber;
04) A device for supplying a gas-liquid mixed-phase refrigerant to the plurality of refrigerant inflow ports, (A05) a plurality of refrigerant connection paths respectively connecting the plurality of refrigerant outflow ports to predetermined refrigerant flow paths of the evaporator. 2. An evaporator provided with a plurality of refrigerant flow paths through which a gas-liquid mixed-phase refrigerant flows and a plurality of cooling fluid flow paths through which a cooling fluid flows, and performing heat exchange between the refrigerant and the cooling fluid. Further, in the refrigerant supply device for an evaporator for supplying the refrigerant, the following configuration requirements (A06) to (A010) are provided, and the refrigerant supply device for an evaporator (A06) is in surface contact with each other. A liquid refrigerant supply member and a gas-liquid mixed phase refrigerant outflow member that are relatively rotatable in a state, (A07) a plurality of liquid refrigerant supply ports formed along the circumference on the contact surface of the liquid refrigerant supply member, (A08) A plurality of refrigerant receiving ports formed on the contact surface of the gas-liquid mixed phase refrigerant outflow member so as to correspond to the plurality of liquid refrigerant supply ports; (A09) supplying a liquid refrigerant to the plurality of refrigerant supply ports; Device, (A01
0) A plurality of refrigerant connection paths for connecting the plurality of refrigerant receiving ports to predetermined refrigerant channels of the evaporator, respectively.