JPH0280879A - Temperature differential valve - Google Patents

Abstract

PURPOSE:To automatically keep a temperature difference between fluids within a designated temperature range by automatically driving a valve member by the first and second temperature sensing springs made of a shape memory alloy, which have sensed the temperature of both fluids to change the flow ratio between both fluids. CONSTITUTION:The acting force Fx of the first temperature sensing spring 10 which is made of a shape memory alloy and deformed on sensing the temperature Tx of the first fluid X and the acting force Fy of the second temperature sensing spring 20 adapted to deform on sensing the temperature Ty of the second fluid Y are loaded on a valve member 6, and the opening Gx of the first valve passage portion 16 and the opening Gy of the second valve passage portion 26 are regulated to decide the flow rate Sx, Sy of both fluids X, Y. For example, in case of applying the valve to a distribution valve of a refrigerating unit, though the first fluid X passes through the first evaporating coil 41 in the refrigerating unit and the second fluid Y passes through the second evaporating coil 42, the valve member 6 is displaced in either direction to reduce a temperature difference DELTAT between both cooling media X, Y. Thus, various apparatus to which both the first and second fluids are supplied can be operated with the maximum efficiency.

Description

Detailed Description of the Invention (Industrial Application Field) The present invention detects the respective temperatures of the first and second fluids whose temperatures change according to changes in flow rate, and detects the temperature difference between the fluids in the core. The present invention relates to a temperature differential valve used to control the flow rate ratio of both fluids so as to stay within a predetermined temperature range.

(Prior art) Conventionally, for example, in a refrigeration system in which multiple systems of evaporator coils are incorporated in the evaporator, if the flow rate ratio of refrigerant distributed to each evaporator coil of the evaporator is not appropriate, each evaporator coil The degree of superheat is different between the two, and the maximum cooling capacity of the evaporator as a whole cannot be achieved.

In addition, when it is necessary to evenly distribute the refrigerant to the indoor units installed in each room, such as in an air conditioning system where one refrigeration system cools and heats multiple rooms, it is necessary to distribute the refrigerant evenly to the indoor units installed in each room. If not, the heating and cooling capacity will vary from room to room, which can be inconvenient.

Conventionally, there are various types of refrigerant distributors in refrigeration equipment (for example, Japanese Utility Model Application No. 57-167377), but most of them simply distribute refrigerant at a fixed ratio to multiple systems of evaporator coils or indoor units. It only has the function of distributing the refrigerant, and there is no one that has the function of adjusting the flow rate ratio of the refrigerant according to the demand of each evaporator coil of the evaporator or each indoor unit.

(Problems to be Solved by the Invention) The present invention provides a method for controlling the flow rate ratio of the filtrate fluid flowing through multiple systems, such as the refrigerant distributor in the refrigeration equipment described in ``-'', by controlling the temperature of the fluid in each system. is detected, and the temperature difference between each fluid is automatically kept within a predetermined temperature range.
The aim is to ensure that the various devices through which these fluids flow can function with the highest overall efficiency by ensuring that the temperature of each fluid does not drop. A means for detecting the temperature and a means for controlling the flow rate ratio of each fluid according to the temperature can be housed and integrated in one caning so that its handling (installation and removal work for various devices, etc.) can be made easier. That is.

(Unlikely means for solving the problem) In the present application, as a means for solving the above problem, in the invention of claim 1, as illustrated in FIGS. 1 and 2, the flow rate Sx is A first fluid passage 14 through which a first fluid X whose temperature TX changes according to the change in temperature passes through it.
and a second fluid passage 24 through which a second fluid Y whose temperature 'h''y changes as the flow rate sy changes; a valve member 6 which acts to change the flow rate ratio Sx/Sy of the first fluid X flowing through the second fluid passage 24 and the second fluid Y flowing through the second fluid passage 24; While pushing the valve member 6 upward, the first
A first temperature-sensitive spring IO made of a shape memory alloy whose acting force Fx on the valve member 6 changes depending on the temperature Tx of the fluid (
= 1 force, and a second temperature-sensitive spring 20 made of a shape memory alloy that changes the acting force Fy on the valve member 6 in accordance with the temperature 1y of the second fluid Y; The temperature sensitive spring 10 and the second temperature sensitive spring 20 are operated by the valve portion +A6 so as to maintain the temperature difference ΔT between the temperature Tx of the first fluid X and the temperature TV of the second fluid Y within a certain temperature range. In order to control the flow rate ratio of both the first and second fluids x and y, the respective temperature-acting force characteristics for the valve member 6 are defined (
7.

In addition, in the invention of claim 2, the first fluid , which is a second branched refrigerant flow, and senses the temperature TX, Ty of each branched refrigerant flow after passing through the two systems of evaporator coils 4+, 42 through the first temperature-sensing spring 10 and the second temperature-sensing spring 20. It is characterized by what happened.

Furthermore, in the invention of claim 3, the Goo Song 5
The first fluid passage 14 in the outgoing path portion 14 is the outgoing path of the wet second branched refrigerant flow X1 toward the first evaporator coil 41.
A and a return path section 14B, which is the return path of the second branched refrigerant flow X1 in a recirculated or dry state from the first evaporator coil 41, and the second fluid passage 24 in the casing 5 is connected to the second evaporator coil. A wet second branch refrigerant flow Y toward 42
, and a return path section 24B, which is the return path of the dry second branch refrigerant flow Y flowing back from the second evaporator coil 42. Each temperature sensitive spring 10.20 is connected to a respective fluid passage 14.24.
Each return portion 14B, 24. B, valve part +A'
6 is located at each outgoing path portion of the first and second fluid passages 14.24 + 4 A, 24△ and each of the temperature sensitive springs 10.20
Both the first and second branch refrigerant flows X in each dry state sensed by
The wet first and second branch refrigerant flows X1, y, which pass through the outgoing portions 14A and 24A of the first and second fluid passages 14.24 according to the temperatures Tx and Ty of Y, respectively. It is said that the feature is that the flow rate ratio Sx/Sy of is controlled.

(Function) In the invention of claim 1 of the present application, the acting force Fx of the first temperature-sensitive spring 10 made of a shape memory alloy that deforms by sensing the temperature TX of the first fluid X and the second fluid Y The acting force Fy of the second temperature-sensitive spring 20, which deforms upon sensing the temperature 'ry, is applied to the valve member 6, and the flow rate of the first fluid First valve passage section 1
The opening degree GX of 6 and the opening degree Gy of the second valve passage section 26 that controls the flow rate of the second fluid Y are defined. And its opening Gx
The flow rates sx and sy of both fluids X and Y are determined according to Gy.

When the temperature Tx of the first fluid X and the temperature Ty of the second fluid Y change relatively and a change occurs in the temperature difference ΔT, the acting force of the two temperature-sensitive springs that was previously loaded on the valve member 6 Fx,
Fy becomes unbalanced and the valve member 6 is displaced.

Along with this, the opening degrees Gx and Gy of both the valve passages 16.26 change, and the flows ff1sx and sy of both the fluids X and Y change. Temperature difference Δ
Produce in the direction that makes T smaller.

Next, the invention of claim 2 of the present application relates to the case where the invention of claim 1 is applied to a distribution valve of a refrigeration system, and the first fluid
1, and the second fluid Y passes through the second evaporator coil 42. That is, the first temperature sensitive spring 10 and the second temperature sensitive spring 2
0 contact the gas refrigerants X and Y after passing through the evaporator coils and deform according to the change in temperature TXTy, and the valve parts f,
The acting force on A6 changes. The change in the acting force is
The valve member 6 is displaced in either direction due to the change in the acting force, and the flow rate ratio of both refrigerants X and Y changes according to the displacement, and further, the flow rate ratio of both refrigerants X and Y changes according to the change in the flow rate ratio.
occurs in the direction in which the temperature difference Δ'F becomes smaller.

Next, the invention of claim 3 of the present application is as follows. Outgoing path portions 14A and 24A through which wet refrigerant passes through fluid passages 14 and 24 through which second fluids (refrigerants) x and y flow, respectively, to reach the evaporator coils 41 and 42 of the evaporator 4; The evaporator 4 is divided into return path sections 14B and 24B through which dry refrigerant passes after passing through each evaporator coil 4142 of the evaporator 4.
The temperature 'I'', x, Ty of the dry refrigerant after passing through is detected, and the flow rate ratio S of the wet refrigerant supplied to the evaporator 4 is determined.
The purpose is to control X/SY. It's so hot,
According to the invention of claim 3, the temperature of the dry refrigerant after passing through each of the evaporator coils 41 and 42 of the evaporator 4 corresponds to the temperature of the wet refrigerant supplied to each of the evaporator coils 4142. The flow rate of the compressor is adjusted to each evaporator coil 41, 4.
This is an attempt to make adjustments on the input side of 2.

(Effects of the Invention) According to the temperature differential valve of the invention set forth in claim 1 of the present application, both the first and second fluids X and Y flowing through the volume valve have their respective temperatures T x and T y. Since the flow rate ratio is controlled depending on the change, if for some reason an imbalance occurs in the flow rates between both fluids X and Y, the temperature difference between the two fluids Even if the situation arises, the first one made of shape memory alloy that senses the temperature of both fluids X and Y
, the second planetary spring 10.20 automatically drives the valve member 6 to change the flow rate ratio of both fluids X and Y, so that the imbalance in the flow rates between both fluids x and y as described above Corrected automatically. Therefore, various devices that rely on the supply of both the first and second fluids, such as the evaporator 4 of the refrigeration system and the indoor units of the multi-room air conditioner, can each operate at maximum efficiency.

Next, in the invention of claim 2 of the present application, the effect of the invention of claim 1 is particularly effectively realized in the evaporator 4 of the refrigeration system.

Further, in the invention of claim 3 of the present application, the temperature of the dry refrigerant in each system after passing through each evaporator coil 41, 42 of the evaporator 4 is sensed, and the temperature of the dry refrigerant is supplied to each evaporator coil 41, 42. The flow rate ratio of the wet refrigerant is determined by each evaporator coil/II,
Since the control is performed on the inlet side of 42, it has the effect that the imbalance in the flow rate ratio can be quickly corrected.

(Embodiments) Hereinafter, preferred embodiments of each invention of the present application will be described with reference to FIGS. 1 to 4.

FIG. 1 shows a temperature differential valve according to an embodiment corresponding to the inventions of claims 1 and 2. Here, the temperature differential valve is used in two systems in an evaporator of a refrigeration system. It is used to control the flow rate ratio of refrigerant flowing through the evaporator coil.

In Fig. 1, the number 1 is a compressor, 2 is a condenser, 3 is an expansion valve or a pressure reducing device such as a J capillary reach cove, and 4 is an evaporator. 1
1.42 is incorporated, and the reduced pressure liquid refrigerant after passing through the pressure reducing device 3 is divided into the first evaporator coil 41 and the second evaporator coil 42 of these two systems and passes through the evaporator 4. Claim 1
The temperature differential valve 50 according to the embodiment of the invention in section
A first refrigerant branch flow that is interposed between the compressor 1 and the compressor 1 and passes through the first evaporator coil 41 of the evaporator 4.
The second refrigerant branch flow passing through the second evaporator coil 42 of the evaporator 4 (corresponding to the second fluid in the first and second claims) ) Y flow rate S
The ratio Sx/Sy of y is controlled.

The first refrigerant branch flow X and the second refrigerant branch flow Y are controlled by a temperature differential valve 50.
The two converge and flow back to compressor I.

The structure and operation of the temperature differential valve 50 will be explained with reference to FIGS. 1 and 2. In the temperature differential valve 50, the first refrigerant branch flow X flows into both ends of the cylindrical casing 5. It has a second artificial boat 21 into which the first artificial boat 11 and the second refrigerant branch flow Y flow, and further has an outlet boat 31 in the middle thereof through which both the eleventh and second refrigerant branch flows merge and flow out. There is.

A valve member 6 is housed in the cane ac 5 at a position facing the outlet port 3I, and the first robot 1 is inserted into the casing 5.
1 and the outlet boat 31 .
and a second fluid passage 24 formed between the second person L1 boat 21 and the exit boat 31.

Two valve body parts, a first valve body part 61 and a second valve body part 62, are formed at both ends of the valve part 44'G. One first valve body portion 61 is disposed within one first fluid passage 14 in the casing 5.
A first valve seat portion 15 is formed opposite to the first valve body portion 61 and a first valve passage portion 16 through which the first refrigerant branch flow X flows is formed between the first valve body portion 61 and the first valve seat portion 15. A second valve seat portion 25 is formed in the other second fluid passage 24 facing the other second valve body portion 62, and the second valve body portion 62 and the second valve seat portion 25
a second valve passage section 26 through which the second refrigerant branch flow Y flows;
is formed. The opening degree GX of these two first and second valve passage sections 16.26 is changed by the displacement of the valve member 6.
, Gy are changed. That is, the opening degree G of one of the two valve passage portions 16.26 changes depending on the displacement of the valve member 6.
As X (or Gy) increases, the opening degree Gy (or GX) of the other side decreases. , Y to change the flow rate ratio SX/SY.

Each of the eleventh and second fluid passages 1424 of the casing 5 is provided with a spring (first temperature-sensitive spring I) for biasing the valve member 6.
O and a second temperature-sensitive spring 20) are provided. Each of these temperature-sensitive springs 10, 20 has characteristics such that the force (FxFy) applied to the valve member 6 changes accordingly. It is made from a shape memory alloy.

In FIGS. 1 and 2, reference numeral 45 indicates the first temperature-sensitive spring l0.
Z) Perforated spring receiving plate for positioning one end, 46 (J second
This is a perforated spring receiving plate that positions one end of the temperature-sensitive spring 20, and Iy11 to LIB each indicate a refrigerant pipe.

FIGS. 2 and 3 show the changes in the acting forces (Fx, Fy) of the first and second temperature-sensing springs 10 and 20, and the
FIG. 2 is an explanatory diagram showing the relationship between changes in the opening degree Gx of the valve passage section 16 and the opening degree cy of the second valve passage section 26;

1 and 2, the first temperature-sensitive spring 10 is connected to a first refrigerant branch flow after passing through the first evaporator coil 41 of the evaporator 4.
It is in contact with fluid (fluid) X and is in a state of temperature Tx=Tx. Furthermore, the second temperature-sensitive spring 20 comes into contact with the second branched refrigerant flow (second fluid) Y after passing through the second evaporator coil 42 of the evaporator 4, and the temperature T
"l"" T Y l state. Also, the valve member 6
is an arbitrary random point S. From stroke S u= S L+,
, and at that time, the first valve passage section 16 has an opening degree G
X=G x, the second valve passage section 26 has an opening degree G Y ”
G)' +.

In FIG. 2, reference numeral 10' indicates the free state (free length (lX=
QX, ), and 20' indicates the free state (free length (
ly=uy+).

Each of these springs 10 and 20 is compressed from its free state when it is assembled in the casing 5, and the first temperature-sensitive spring 10 has a canon inner length (lxmuxm, (amount of compression at that time (C1xn) = nxn , = (lx.

- Ilxm, ), the second temperature-sensitive spring 20 has a caissonk inner length uym - σym + (amount of compression at that time (σyn) = (
lyn+(l Y+-fl ym+).

”-KxKx+ for the first temperature-sensitive spring lO
(at temperature TX - TX +), second temperature sensing node 2
0E just "i:L:LKy=Ky+(?W degree T V-"
In each temperature state, the acting force (Nokune constant x spring compression amount) that each spring 10.20 loads on the valve member 6 is as follows.

Acting force of the first temperature-sensitive spring 10 (Fx-・FX1) F XI
= K XI X (l X11+Kx+X(ux+
nxm+) ・ ・ ・ ・ (])
Acting force of the second temperature-sensitive spring 20 (F y=F y+)F'
/+ =Ky+X 1lyn Ky+X (seeyl-tanym+)...(2) Part 1. Then, the acting force F x (F
XI), F y (-P y+) is F X l =
The valve part kA6 is stopped when the relationship P y is reached, and the opening degree G of each of the first and second valve passage parts 1626 is determined according to that position (opening degree Gx=Gx, , GyGy+).

In this embodiment, by applying the present invention, the first temperature-sensitive spring 10 and the second temperature-sensitive spring 20 are deformed (the free lengths αX and αy are changed) according to temperature changes in a predetermined temperature range. ) and uses a shape memory alloy whose spring constants K x and K y change.

That is, these first and second temperature-sensitive springs 1020 are as follows:
Each has a specific spring constant and a specific free length (in other words, the amount of spring compression within the casing 5) for each specific temperature, and therefore the acting force characteristics on the valve member 6 for each specific temperature. (spring characteristics).

In FIG. 3, (I,) is a spring characteristic diagram of the first temperature-sensitive spring 10 at temperature T x = T, XI, (I2)
is the same temperature T x = T x2 (T x2 > T x+)
i: The characteristic diagram of the spring at the same temperature, (I3) is the same temperature T
x= T X3 (T X3 < T

Moreover, (■,) is the temperature T V −' of the second temperature-sensitive spring 20
The spring characteristic diagram at T ''/1, (■,) is the spring characteristic diagram of the same spring at the same temperature Ty = T V2 (Ty2>Tx1), (■,) is the spring characteristic diagram at the same temperature Ty = T TY
3 (T Y3 < T Y1).

In the temperature differential valve 50 shown in FIGS. 1 and 2, the acting force on the valve member 6 is caused by the first temperature-sensitive spring 10 and the second
Since the temperature sensitive springs 20 act in opposite directions, the slopes of their spring characteristic diagrams shown in FIG. 3 are in opposite directions.

In FIGS. 1 and 2, the temperature of the first refrigerant branch flow (first fluid)
When the temperature of the valve member 6 is T V = T Y +,
- Loaf S u = S ul (opening degree GXG X of the first valve passage section 16, opening degree Gy of the second valve passage section 26 = Gy
+) and is at rest. At this time, the forces (Fx, Fy) of the two springs loaded on the valve member 6 are calculated as Fx=Px for the first temperature-sensitive spring 10 and
When F Stroke 1 - Stroke 5u = Su+ position.

At this time, the temperature TX1 of the first refrigerant branch flow (first fluid)
and the temperature TY+ of the second refrigerant branch flow (second fluid) Y
r is TXI Txl−ΔT, and this temperature difference ΔT1 is
It is within the predetermined allowable temperature range Tc that has been set from the beginning.

Next, the temperature difference ΔT between the first and second fluids X and Y (temporarily,
Txl<Tyl), for example, the second evaporator coil 4
The temperature rise of the second refrigerant branch flow (second fluid) Y due to the increase in the heat absorption load on the second side (T y=T
Expansion change due to yJ (ΔT−ΔT, −ΔT2sS, −3
2) L, the spring characteristics of the second temperature-sensitive spring 20 change accordingly, that is, the spring characteristics diagram of the second temperature-sensitive spring 20 changes to the third temperature-sensitive spring 20.
Suppose that the transition occurs from (II,) to (■,) in the diagram (at this time, the temperature of the first refrigerant branch flow (first fluid) X remains Txl and does not change, right?). Assume that there is no change in the spring characteristics as shown in the characteristic diagram (1,) for the warm spring 10).

In this case, the second temperature-sensitive spring 20 has an increased acting force on the valve member 6 due to its temperature, and the second temperature-sensitive spring 20 acts on the valve member 6 against the acting force of the first temperature-sensitive spring 10. 1 Displace the temperature-sensitive spring 10 in the direction of compression and shift the valve member 6 to a new balanced state at the position (Su2) where it is displaced by ΔSL+ - Shichiro (point in Figure 3)] 2 condition).

When the valve member 6 is displaced to the right by ΔSu2, the opening degree OX of the first valve passage portion I6 decreases from Gx to OX2, reducing the refrigerant branch flow rate on the first evaporator coil 41 side, while reducing the second valve passage portion I6. Opening degree of the valve passage section 26 Gyh<Gy+ to G
x2, increasing the refrigerant branch flow rate to the second evaporator coil 42 and suppressing the temperature -1 rise of the second refrigerant branch flow (second fluid) Y. As a result, the temperature difference ΔT between the G1 and second fluids X and Y is set within a predetermined temperature range Tc.
Converge within.

In addition, contrary to the description in "-", due to a decrease in the amount of heat absorbed on the second evaporator coil 42 side, etc., the temperature of the first refrigerant branch flow (first fluid) X remains T x +, and the temperature of the second refrigerant branch flow ( When the temperature Ty of the second fluid) Y decreases (Ty=-'1."y+-"Fy3), both springs l0120 in the state of point P3 in FIG.
The acting force (Fx3. Increasing the refrigerant division flow rate on the II side, the opening degree Gy of the second valve passage portion 26 side decreases from GY+ to Gx3, thereby reducing the refrigerant division flow rate to the second evaporator coil 42. , increasing the temperature TY of the second refrigerant branch Y). In this way, the temperature balance of both the eleventh and second fluids XY is maintained at t(B
held.

In addition, in Fig. 3, point P 4 (T X = T
TYTY4) is the point P1 (Tx=Tx+, Ty=T
y+) as a reference, (T X4 > T XI, TY
Balance state of the acting force of each spring in the case of t-'TV+), point P s (T x = T X5T y1'', Y:,)
is (Tx5<Tx,,Tl/,=-Ty+)
In the case of , the point P6 (Tx='f''x6.Ty-Tye) is (Txe<TXI, Tye<Ty1),
Point P 7 (T X −TX7.T y−'r )”r
) is TX? > T X l, i'," Y 7 > T
Y + ), then point P 8 (T x = T
ry "'I"Ys) is (Tx8<'rXI,TYe>
TY+), point P 9 (T x= T
y = 'I' y9) is (Tx9 >'r X l
, Tys < Ty + ), the balance state of the acting force between each spring is shown.

4-As an example of the registered state, let us explain the state of point P7.This state is compared to the state of point P1.
This shows a case where both the temperature T''X of the fluid X and the temperature Ty of the second fluid Y have increased, but in this case, the temperature difference ΔTΔ1'7 between the first and second fluids X and Y is itself small. Therefore, the temperature difference △1゛7 is converged within the predetermined temperature range Tc.
Both the first and second valve passages + 6, 26 opening degrees Gx, G
The amount of change in y, that is, the amount of displacement of the valve member 6 (ΔSu−Δ
This shows that S u7) may be small.

Furthermore, as another example of the traveling state, the state at point P8 will be explained. If this state is compared to the state at point P, the temperature Tx of the first refrigerant branch flow (first fluid) X is Decrease (
Although Tx=Tx8<Tx+), the second
The increase in heat load on the evaporator coil 42 side is large, and the temperature TY of the second refrigerant branch flow (second fluid) Y increases (Ty=Ty
a>Ty+), but in this case, the temperature difference ΔT−ΔT8 between the 11th and 2nd fluids X and Y is large, so the temperature difference ΔT8 is kept within the predetermined temperature range Tc. The amount of adjustment of the opening degree GXay of both the first and second valve passage portions 16.26 for convergence, that is, the amount of displacement of the valve member 6 (Δ
SuΔS u8) increases in the direction of the above-mentioned opening Gx decrease and Gy increase (the refrigerant divided flow rate to the second evaporator coil 42 side becomes extremely large compared to the first evaporator coil 4I side). .

FIG. 4 shows an embodiment corresponding to the invention of claim 3, in which reference numeral 1 is a compressor, 2 is a condenser, 3 is a pressure reducing device, 4 is an evaporator, I72. - I7, 9 indicate refrigerant piping. The evaporator 4 has two systems of first evaporator coils 41.
and a second evaporator coil 42 are incorporated.

The temperature differential valve used in this embodiment has a passage structure that divides the refrigerant after passing through the pressure reducing device 3 into two branched flows and allows them to flow. That is, the temperature differential valve 50 shown in FIG. Two temperature-sensitive springs 10.2
0, and the casing 5 includes a pressure reducing device 3.
Main inlet port 31 into which the wet refrigerant W flows after passing through
and the first refrigerant branch flow X (the first evaporator coil 41 of the evaporator 4
The first branch flow from which the wet refrigerant
A first branch inflow robot into which the first refrigerant branch flow X (wet refrigerant X) flows as dry refrigerant X after passing through the first evaporator coil 41 of the evaporator 4. 18 and the same dry refrigerant branch flow X2 flows out from the first
The second branched flow robot 19 and the second branched refrigerant flow Y (wet refrigerant Y heading toward the second evaporator coil 7I2 of the evaporator 4,
) ga flow 1) Tokikeru 2nd branch flow 1st dehibo) ・27 and,
The second refrigerant branch flow Y (wet refrigerant Y) is transferred to the evaporator 4
It has a second branch inflow robot 28 into which the dry refrigerant Y2 flows after passing through the second evaporator coil 42, and a second branch flow second outflow robot 29 through which the dry refrigerant branch flow Y2 flows out. ing.

In the temperature differential valve 50 shown in FIG.
Branch flow First refrigerant branch flow X toward the first output robot 17 (
X ,) and the second branch stream 1st exit 1'' 2nd heading towards boat 27
The refrigerant branches Mty(y,) and controls the flow rate ratio thereof.

As described above, in this embodiment, the first fluid passage 14 for the first branched refrigerant flow X
(X,) flows through the outgoing path section 14A and the first
Dry first refrigerant branch flow X after passing through the evaporator coil 41
(X,) is divided into a return route section 14B through which
The second fluid passage 24 for the second branched refrigerant flow Y includes an outgoing path portion 2/IA through which a wet second branched refrigerant flow Y (Y,) toward the second evaporator coil 42 of the evaporator 4 flows; The second refrigerant branch A (Y2) in a dry state after passing through the second evaporator coil 42 of the evaporator 4 is divided into a return path section 24B and a return path section 24B.

First fluid passageway section+4. A valve seat portion (first valve seat portion) 15 is formed in the middle of A at a position facing one valve body portion (first valve body portion) 61 of the valve member 6, and this first valve body portion 6I and the first valve seat part 15 in a wet state.
Valve passage section (first
A valve passage portion) 16 is formed.

Also, the second fluid passage outward path portion 24. There is a valve member 6 in the middle of A.
A valve seat portion (second valve seat portion) 25 is formed at a position facing the other valve body portion (second valve body portion) 62,
A valve passage portion (second valve passage portion) 26 is formed between the second valve body portion 62 and the second valve seat portion 25, and serves as a passage for the wet second refrigerant branch flow y (y 1). There is.

In the temperature differential valve 50 shown in FIG.
The first and second temperature-sensitive springs 10.20 made of a shape memory alloy are applied to the return path 14B of the first fluid passage 14 for the first temperature-sensing spring 10, and to the return path 14B of the first fluid passage 14. Regarding the spring 20, the return path 24 of the second fluid passage 24. They are placed in B respectively.

On the other hand, the valve member 6 is provided with a tenth throat 63 that reaches the first fluid passage return passage portion 1413 and a twentieth throat 64 that reaches the second fluid passage return passage portion 24B. It receives the action horn FX from the first temperature-sensitive spring 10 through the 20th horn 64, and receives the action horn FX from the second temperature-sensing spring 2 through the 20th horn 64.
It is adapted to receive an acting force Fy from 0.

That is, in the temperature differential valve 50 shown in FIG. 4, the valve member 6 contacts the dry first refrigerant branch flow 1 The second refrigerant branch flow Y in a dry state like the temperature-sensitive spring 10
(Y2) and whose acting force Fy changes according to the change in temperature Ty, is displaced by the acting force () from both of them, and according to the displacement, the first temperature sensitive spring 20 in a wet state
It acts to control the ratio Sx/Sy between the flow rate SX of the refrigerant branch flow X (X,) and the flow m S y of the second refrigerant branch flow y (y,) which is also wet.

In this way, on the inlet side of the evaporator 4, each refrigerant branch flow x
, y, first and second temperature sensing springs 10.20 detect the imbalance in the temperatures TxTy of both fluids X and Y, and then correct the imbalance. The time required to control the flow rate ratio SX/Sy of fluids X and Y is shortened, and the responsiveness and accuracy of the control system are improved.

In the temperature differential valve 50 shown in FIG.
The process in which each temperature-sensitive spring 10.20 changes the acting force Fx, FY on the valve member 6 according to the change in temperature, and controls the flow rate ratio SX/SY of the first and second fluids XY accordingly is as follows. This is the same as the case of the temperature differential valve 50 shown in FIG. 1, so let's explain it! J is omitted.

In Fig. 4, piping not shown by imaginary lines, 3o, 1
．． -3 is the first and second refrigerant branch flow X 2 in a dry state
, Y2 (x7., y2.) bypassing the temperature differential valve 50 and directly returning it to the compressor I. This kind of path piping L
When installing 3゜■731, install the first one in a dry state,
Second respective refrigerant branch flow X7. Y2 is part of X 2 , +
Y 22 is the return path portion 14 of the first fluid passage 14 of the temperature differential valve 50 as a control fluid for the first and second temperature sensitive springs 10.20.
．． B or the return path 24B of the second fluid passage 24, and the remaining mainstream portion X, 1. Y2+ is directly sucked into the compressor 1.

In addition, in the description of each embodiment, it is assumed that both the first and second fluids X and Y flow through two systems of evaporator coils/II and 42 in a single evaporator 4. Although described above, each invention of the present application can also be implemented in a case where refrigerant is divided into indoor units in different rooms in a multi-room air conditioner in which a plurality of indoor units are connected to one refrigeration system. It is something.

In this case, each evaporator coil 41 shown in FIG. 1 and FIG.
42 corresponds to the evaporator attached to each indoor unit.

[Brief explanation of the drawing]

Fig. 1 is a refrigerant circuit diagram of a refrigeration system using a temperature differential valve corresponding to an embodiment of the invention of claims 1 and 2 of the present application, and Fig. 2 and 3 are the same temperature differential valve. Operation explanatory diagram, 4th
The figure is a refrigerant circuit diagram of a refrigeration system using a temperature differential valve according to an embodiment of the invention set forth in claim 3 of the present application. 1... Compressor 2... Condenser 3... Pressure reducing device 4... Evaporator 5... Casing roller... Valve member lO... ...First temperature-sensitive spring 14...First fluid passage 14A...First fluid passage outward path section 14+3...First fluid passage return path section 16...First valve passage section 20...・Second temperature-sensitive spring 24...Second t & body passage 24 A...Second fluid passage outward path part 24I3...Second fluid passage return path part 26...Second valve passage part 41...・First evaporator coil 42 ・・Second evaporator coil

Claims (1)

[Claims] 1. A first fluid passage (
14) and temperature (Ty) according to changes in flow rate (Sy).
a casing (5) having a second fluid passageway (24) through which a second fluid (Y) is changed; and a second fluid passageway (24) that is displaced within the casing (5) and flows through the first fluid passageway (14). a valve member (6) that acts to change the flow rate ratio (Sx/Sy) of the first fluid (X) and the second fluid (Y) flowing through the second fluid passage (24); and the first fluid passage (14
) to bias the valve member (6) and deform in response to the temperature (Tx) of the first fluid (X), changing the acting force (Fx) on the valve member (6). A first temperature-sensitive spring (10) made of a shape memory alloy is placed in the second fluid passage (24) to bias the valve member (6) and adjust the temperature (Y) of the second fluid (Y). A second temperature-sensitive spring (20) made of a shape memory alloy that deforms in response to temperature (Ty) and changes the acting force (Fy) on the valve member (6) is provided, and the first temperature-sensitive spring (10) ) and the second temperature-sensitive spring (
20) is the valve member (6) so that the temperature difference (ΔT) between the temperature (Tx) of the first fluid (X) and the temperature (Ty) of the second fluid (Y) is maintained within a certain temperature range. ) according to the first
, a temperature differential valve characterized in that respective temperature-acting force characteristics are defined for the valve member (6) so that flow rate ratio control of both second fluids (X, Y) is performed. 2. The first fluid (X) and the second fluid (Y) are connected to two systems of first and second evaporator coils (41, 42) in the refrigeration system.
The first and second branched refrigerant flows pass through the first and second temperature-sensitive springs (10) and the second temperature-sensitive springs (20), respectively, after passing through the two systems of evaporator coils (41, 42). 2. A temperature differential valve according to claim 1, wherein the temperature differential valve is adapted to sense the temperature (Tx, Ty) of the branched refrigerant stream. 3. The first fluid passage (14) in the casing (5) is the first
A wet first branch refrigerant flow (
The dry first branch refrigerant flow (
A second fluid passage (24) in the casing (5) is divided into a return passage section (14B) which is the return passage of X_2).
The outgoing path portion (24A) is the outgoing path of the wet second branch refrigerant flow (Y_1) heading toward the second evaporator coil (42);
The second branch refrigerant flow (Y_2) in a dry state returns from the evaporator coil (42).
) of each return path (1) of each fluid passage (14, 24).
4B, 24B), a valve member (6) is located in each outgoing path portion (14A, 24A) of the first and second fluid passages (14, 24), and each temperature-sensitive spring (10, 20) senses the temperature. Both the first and second fluid passages (
Both first and second branch refrigerant flows (X_1, Y_1) in a wet state pass through each outgoing path section (14A, 24A) of 14, 24)
3. The temperature differential valve according to claim 2, wherein the temperature differential valve is configured to control a flow rate ratio (Sx/Sy) of the temperature differential valve.