KR102403519B1 - refrigerator - Google Patents

Abstract

It provides a valve structure that can precisely control the flow rate when the fluid starts flowing. A valve structure including a valve seat 3 having two outlet ports 3a for discharging fluid, and a valve body 4 rotatably provided with respect to the valve seat 3 to adjust the opening degree of the outlet port 3a In (20), the valve body (4) has a flow rate control groove (4d) along the circumferential direction in which the overlapping area with the outlet port (3a) is changed by rotation, and the center (O) of the outlet port (3a) is , was displaced from the rotational locus of the distal end 4b of the flow control groove 4d, which begins to overlap with the outlet 3a due to rotation of the valve body 4 .

Description

refrigerator

The present invention relates to, for example, a valve structure used in a refrigeration refrigerator and a refrigerator using the same.

As a valve structure used in a refrigerator, in the conventional case, as disclosed in Japanese Patent Application Laid-Open No. 2005-214508, a valve seat having two outlets for discharging a refrigerant, and a valve seat rotatably provided with respect to the valve seat to open and close each outlet Some have a valve body and are configured to selectively send a refrigerant to an evaporator for a refrigerating compartment or an evaporator for a freezing compartment by rotating the valve body and opening one or the other outlet.

In order to control the refrigerant flow rate of the refrigerant sent to each evaporator, the valve body is provided with an adjustment groove along the circumferential direction in which the area overlapping the outlet port changes as the valve body rotates. With this configuration, by rotating the valve body from the state in which the outlet port is closed, the overlapping area between the outlet port and the adjustment groove becomes large, whereby the refrigerant flow rate can be increased.

However, in the valve structure described above, since the tip of the adjustment groove, which begins to overlap with the outlet, is rotated to pass through the center of the outlet, when starting to flow the refrigerant, the tip of the adjustment groove overlaps from the front with respect to the outlet. start to lose

As a result, when starting to flow the refrigerant, the overlapping area between the outlet and the tip of the adjustment groove is large, so that the refrigerant flow flows into the outlet at once, so that it is difficult to control the refrigerant flow rate with high precision.

Accordingly, the present invention has been made in order to solve the above problems, and it is a main object to provide a valve structure capable of controlling the flow rate when starting to flow a fluid with high precision.

That is, the valve structure according to the present invention is a valve structure including a valve seat having two outlet ports for discharging a fluid, and a valve body provided to be movable with respect to the valve seat to adjust the opening degree of the outlet port, The valve body has an adjustment groove for controlling the flow rate flowing out from the outlet, and the center of the outlet is displaced from the movement trajectory of the distal end of the adjustment groove that begins to overlap with the outlet by the movement of the valve body, It is characterized by having

In addition, the movement locus|trajectory of the front-end|tip part here is a concept containing the movement trace of the front-end|tip of an adjustment groove, the movement trace of the part located behind the front-end|tip, etc.

With the valve structure configured in this way, since the center of the outlet is displaced from the movement trajectory of the distal end of the adjustment groove, when the adjustment groove and the outlet start to overlap, the front end of the adjustment groove overlaps at an angle deviated from the front with respect to the outlet. .

As a result, when starting to flow the coolant, the area where the front end of the adjustment groove and the outlet overlap can be made smaller than before, so that the coolant flow rate can be increased little by little, and the flow rate when the fluid starts flowing can be controlled with high precision. thing becomes possible

As a specific embodiment, the valve body is provided rotatably with respect to the valve seat, and the adjustment groove is formed along the circumferential direction so that the area overlapped with the outlet port changes as the valve body rotates. can be heard

However, if the center of the outlet is greatly displaced from the rotation trajectory of the distal end of the adjustment groove and the overlapping area of the distal end and the outlet becomes very small, when foreign matter flows into the distal end, the foreign material cannot flow out from the outlet.

Therefore, when a foreign material flows into the front end of the adjustment groove, the center of the outlet is positioned so that the front end overlaps the outlet, so that the foreign material flows out from the outlet together with the fluid. It is preferable to displace from the rotation trajectory.

With such a configuration, even if a foreign material flows into the distal end of the adjustment groove, the foreign material can be flushed out together with the fluid.

In order to reliably flush out the foreign material, it is preferable that the width dimension of the portion where the distal end of the adjustment groove and the outlet overlap is set based on the size of the foreign material.

As a specific shape of the said adjustment groove|channel, the shape which a width dimension becomes large from a front-end|tip part toward the rear-end part on the opposite side is mentioned.

However, the positions of the adjustment grooves and outlets have variations during processing and assembly, and may deviate radially outward or inward from the designed position (hereinafter referred to as a reference position).

When the outlet port is positioned radially inward with respect to the reference position, the valve opening degree is larger and the rotational angle at which the refrigerant starts to flow becomes faster than when the outlet port is at the reference position. Thereby, when starting to flow a refrigerant|coolant, there is a concern that the flow volume will increase all at once. The same problem also arises when the adjustment groove deviates radially outward with respect to the reference position.

Accordingly, considering that the outlet port is repositioned in the radial direction and the adjustment groove is repositioned radially outward, the adjustment groove includes a narrow portion having a constant width from the front end to the rear end, and the narrow portion It is preferable to have a wide part whose width becomes large toward the said rear end side.

With such a configuration, even when the overlapping area of the adjustment groove and the outlet becomes the upper limit (maximum) due to the position change described above, it is possible to reduce the increase in the flow rate when starting to flow the refrigerant, and in the micro flow rate region It becomes possible to control the flow rate by minimizing the influence of variations at the time of machining or assembly of the adjustment groove and the outlet.

Even when the overlapping area of the adjustment groove and the outlet reaches the upper limit (maximum), in order to prevent the flow rate from increasing all at once when the coolant starts flowing, the narrow width is formed substantially parallel to the rotational trajectory of the tip It is preferable to be

It is preferable that the outer edge of the said wide part moves away from the rotation trajectory of the said front-end|tip part to the outside.

By making the outer edge of the widening part in this shape, after the refrigerant starts to flow to some extent, the flow rate can be increased gradually, so that the flow rate rapidly increases when the entire adjustment groove continues to pass through the outlet port and the outlet port is completely opened. it can be prevented

On the other hand, in order to reduce the variation in the flow path area ratio occurring in the narrow part, after the refrigerant starts to flow to a certain extent, in order to prevent the flow rate from increasing all at once and increase the flow rate gradually, the inner edge of the widening part has a rotation trajectory of the tip part Preferably, it is close to or approximately parallel to the rotational trajectory of the tip.

As a specific embodiment, the structure in which the outer edge and inner edge of the said widening part are asymmetric with respect to the rotation trajectory of the said front-end|tip part is mentioned.

On the other hand, when the outlet port is displaced radially outward, the valve opening degree is smaller than when the outlet port is at the reference position, and the rotation angle at which the refrigerant starts to flow is delayed. Accordingly, when the coolant starts flowing, the overlapping area between the tip end of the adjustment groove and the outlet 3a becomes too small, and the flow rate hardly increases even if the valve body is rotated when the coolant starts flowing. As a result, if the outlet deviates outward in the radial direction, the refrigerant does not flow at the same rotation angle as when the outlet is at the reference position, so there is a possibility that a trouble such as non-cooling may occur, or basic performance such as an increase in power consumption even if not boiling. damage is concerned. Also, the same problem arises when the adjustment groove is displaced radially inward with respect to the reference position.

Therefore, considering that the outlet port is displaced radially outward and the adjustment groove is repositioned radially inward, the rotational trajectory of the tip of the adjustment groove is on the rotational axis side of the valve body rather than the center of the outlet port Preferably, the outlet is arranged so as to overlap the outlet.

With such a configuration, even when the outlet port is repositioned radially outward, the overlapping area can be secured even when the overlapping area between the adjustment groove and the outlet becomes the lower limit (minimum). Thereby, the overlapping area of the front-end|tip part of an adjustment groove and an outlet does not become too small when a refrigerant|coolant begins to flow, and it can prevent the trouble of a non-cooling or damage to basic performance, such as an increase in power consumption.

Next, the case where the valve structure according to the present invention is used as a three-way valve, that is, a case where the fluid flowing in from the inlet provided in the valve structure flows out from the two outlet ports formed in the valve seat will be described. Moreover, as such a three-way valve, what was described in said Japanese document is known.

When the valve structure according to the present invention is used as a three-way valve and is used in, for example, a refrigerator and freezer having a refrigerating compartment and a freezing compartment, the fully open region in which the two outlets are simultaneously fully opened according to the rotation angle of the valve body It is desirable to configure the valve structure to be formed.

With such a configuration, the cooling rate of the refrigerating compartment and the freezing compartment can be improved in the case of overload such as during pull-down by setting the two outlets as the fully open region to the fully open state.

According to the rotation angle of the valve body, while the adjustment groove is overlapped on one of the two outlets, a flow rate variable region in which the other is in a fully closed state, and a fully closed in which the two outlets are simultaneously in a fully closed state It is desirable to configure the valve structure so that a region is formed.

With such a configuration, by setting the flow rate variable region, the refrigerant can be adjusted to an appropriate flow rate according to the load at the time of cooling each of the refrigerating compartment and the freezing compartment. In addition, when the compressor is stopped, it is possible to prevent the high-temperature refrigerant from flowing into the evaporator from the condenser side by making the area completely closed, and it is possible to prevent the temperature of each room from rising due to the refrigerant flowing in when the compressor is stopped. .

When manufacturing the valve structure capable of forming the above-described fully open region, variable flow rate region, and completely closed region, the rotation range of the valve body is reduced to less than 360 degrees by, for example, a stopper for the purpose of correction of the origin or position recognition. In order to make the valve structure small and simple, it is very difficult to form each region described above because manufacturing conditions are limited. In the meantime, the inventor of the present application repeated intensive studies in order to form a fully open region, a variable flow rate region, and a completely closed region using a compact and simple valve structure.

As a result, the valve body is continuously formed from the rear end of the adjustment groove, and includes a first fully opening groove overlapping the entire outlet port, and a second fully opening groove overlapping the entire outlet port separately from the first fully opening groove. 2 If it has a groove for fully opening, and the adjustment groove is formed within 60 degrees of the rotation axis of the valve body, a fully open region, a variable flow rate region and It has been found that it is possible to form a completely closed region.

Next, the case where the valve structure which concerns on this invention is used as a four-way valve is demonstrated. In addition, as a four-way valve, as described in, for example, Unexamined-Japanese-Patent No. 2004-293573, the 2nd valve seat in which the 3rd outlet port was formed separately from the valve seat and valve body demonstrated above, and this 2nd What was provided with the 2nd valve body rotatably provided with respect to a valve seat is known.

It is conceivable that such a four-way valve is used, for example, in a refrigerator or freezer having an alternate temperature chamber in addition to the refrigerating chamber and the freezing chamber.

In this case, the valve structure according to the present invention includes a second valve seat in which a third outlet for discharging a fluid is formed, a second valve seat rotatably provided with respect to the second valve seat, and rotates in association with the valve body to form the outlet of the outlet. The 2nd valve body which adjusts an opening degree is provided, The said 2nd valve body has an adjustment groove along the circumferential direction in which the area overlapping with the said 3rd outlet port changes by rotation.

And this valve structure is, according to the rotation angle of the first valve body and the second valve body, one of the two outlets formed in the valve seat and the third outlet formed in the second valve body are fully opened at the same time It is preferably configured so that a fully open region to be in the state is formed.

With such a configuration, as in the case of the three-way valve described above, the cooling rate of the refrigerating chamber, the freezing chamber or the alternate temperature chamber can be improved in the case of overload such as during pull-down by making the two outlets in the fully open state as the fully open region. .

According to the rotation angle of the valve body and the second valve body, while the adjustment groove is superimposed on one of the three outlets, the flow rate variable region in which the other two are in a completely closed state, and the three outlets simultaneously It is preferable to configure the valve structure so that a fully closed region that is in a fully closed state is formed.

With such a configuration, similarly to the three-way valve described above, by setting the flow rate variable region, the refrigerant can be adjusted to an appropriate flow rate according to the load during cooling of each of the refrigerating compartment, the freezing compartment, and the alternate temperature compartment. In addition, when the compressor is stopped, it is possible to prevent the high-temperature refrigerant from flowing into the evaporator from the condenser side by setting it as a completely closed region, and it is possible to prevent the temperature of each room from rising due to the refrigerant flowing in when the compressor is stopped. .

It is as described above that it is very difficult to make a valve structure capable of forming a fully open region, a variable flow rate region, and a completely closed region into a compact and simple one.

And as a result of the inventor's earnest examination, the said valve body and the said 2nd valve body are each continuously formed from the rear end of the said adjustment groove, and have the groove|channel for full opening which overlaps with the whole said outlet port, and each said adjustment If the grooves are formed within 60 degrees of the rotation axis of the valve body or the second valve body, respectively, a fully open area, a variable flow rate area, and a fully closed area using a valve structure such as a small and simple four-way valve found to be able to form

Next, the refrigerator equipped with switching valves, such as a three-way valve and a four-way valve demonstrated above, is demonstrated.

In a conventional refrigerator, a switching valve is disposed in a machine room, and a capillary tube is generally used as a pressure reducing mechanism for connecting the switching valve and the evaporator.

In the refrigerator described in this publication, since there is no flow rate adjustment range in the pressure reduction using a capillary tube, the flow rate adjustment range is expanded by switching a plurality of capillary tubes having different tube diameters with a switching valve.

Also, in conventional refrigerators, it is common to heat exchange by connecting a capillary tube and a return pipe returning from the evaporator to the compressor by soldering or the like. By performing heat exchange between the capillary tube and the return piping, the effect of preventing liquid return by heating the return piping and increasing the refrigeration capacity by cooling the capillary can be obtained.

In such a conventional refrigerator, when a means for expanding the flow rate adjustment range using a plurality of capillaries is applied to a refrigeration cycle comprising a plurality of evaporators, a plurality of switching valves may be required because the number of switching increases, and there is a risk of cost increase Also, when the capillary tube and the return piping are connected, the number of capillaries that can be connected to one return piping is limited for processing, so there is a capillary that cannot be connected to the return piping. And there is a problem that the effect of increasing the refrigeration capacity cannot be obtained.

Accordingly, an object of the present invention is to obtain the effect of preventing liquid return and increasing the refrigeration capacity while widening each flow rate adjustment range in a refrigeration cycle in which a plurality of evaporators are switched.

That is, the refrigerator according to the present invention is characterized in that a capillary tube is provided between the three-way valve or the four-way valve and the evaporator.

With such a configuration, by using the three-way valve or four-way valve having the above-described flow control range in the refrigerator, it is possible to widen the flow control range in the refrigeration cycle in which a plurality of evaporators are switched.

On the other hand, if the refrigerant flow rate is adjusted only by the three-way valve and the four-way valve in the machine room, the refrigerant temperature at the outlet of the three-way valve and the four-way valve becomes approximately the same as the evaporation temperature, and the three-way valve and the four-way valve are connected to the evaporator. There is a concern that dew condensation may occur in the machine room portion of the piping from the machine room to the inside of the vault.

In the case of the configuration described above, the temperature at the outlet of the three-way valve and the four-way valve is higher than the evaporation temperature because the three-way valve and the four-way valve perform the primary pressure reduction and the capillary tube perform the second pressure reduction, so that the pipe condensation in the machine room part In addition to being able to suppress the generation of , the effect of preventing liquid return and increasing the refrigeration capacity by heat exchange between the capillary tube and the return pipe described above can also be obtained.

According to the present invention constituted in this way, when starting to flow a fluid such as a refrigerant, the fluid can be increased little by little, and it becomes possible to control the flow rate when starting to flow the fluid with high precision.

Further, when used as a three-way valve or a four-way valve, a fully open region, a variable flow rate region, or a completely closed region can be formed with a compact and simple configuration. Appropriate adjustment of the flow rate, prevention of temperature rise in each chamber when the compressor is stopped, prevention of condensation in piping in the machine room, prevention of liquid return by heat exchange between capillary tube and return piping, increase of refrigeration capacity, and the like can be achieved.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic internal diagram of the refrigerating-refrigerator of 1st Embodiment.
Fig. 1B is a layout diagram of a refrigerant circuit of the refrigerator refrigerator according to the embodiment.
Fig. 2 is a schematic diagram showing a refrigerant circuit of the refrigerator refrigerator according to the embodiment.
It is the schematic diagram which looked at the whole of the valve structure of the same embodiment from upper direction.
It is the schematic diagram which looked at the whole of the valve structure of the same embodiment from below.
It is the schematic diagram which looked at the valve seat and the valve body of the same embodiment from upper direction.
It is the schematic diagram which looked at the valve seat and the valve body of the same embodiment from below.
It is a top view which shows the valve seat of the same embodiment, and a valve body.
It is a schematic diagram for demonstrating the adjustment groove|channel of the same embodiment.
It is a figure for demonstrating the operation|movement of the valve structure in the same embodiment, and the flow of a refrigerant|coolant.
It is experimental data which compared the valve structure in the same embodiment with the conventional valve structure.
11 is a Moriel diagram of the refrigeration cycle in the embodiment.
12A is an internal schematic diagram of the refrigerator refrigerator according to the second embodiment.
Fig. 12B is a layout diagram of a refrigerant circuit of a refrigerator-freezer according to the second embodiment.
It is a schematic diagram which shows the refrigerant circuit of the refrigeration refrigerator of 2nd Embodiment.
It is the schematic diagram which looked at the whole valve structure of the same embodiment from upper direction.
It is the schematic diagram which looked at the whole of the valve structure of the same embodiment from below.
It is the schematic diagram which looked at the valve seat and the valve body of the same embodiment from upper direction.
It is the schematic diagram which looked at the valve seat and the valve body of the same embodiment from below.
It is a top view which shows the valve seat and valve body of the same embodiment.
It is a figure for demonstrating the operation|movement of the valve structure in the same embodiment, and the flow of a refrigerant|coolant.
20A to 20C are schematic diagrams for explaining a change in the position of the outlet.
21A to 21C are schematic diagrams for explaining the variation in the valve opening degree accompanying the change in the position of the outlet.
It is a figure which shows the flow volume change in 1st Embodiment and 2nd Embodiment.
It is a schematic diagram for demonstrating the outlet port and adjustment groove|channel in 3rd Embodiment.
It is a figure which shows the flow volume change in 3rd Embodiment.

<First embodiment>

First, a first embodiment of the present invention will be described with reference to the drawings.

The valve structure according to the first embodiment is used as a so-called four-way valve.

As shown in FIG. 1 , the valve structure 20 according to the present embodiment is used, for example, in a refrigerator/freezer 100 . In addition, this valve structure 20 is not limited to a refrigerator-freezer, You may use for the fluid circuit which supplies a fluid to a plurality of places.

First, the refrigerator 100 of this embodiment is demonstrated.

As shown in Figs. 1A to 2, the refrigerator-freezer 100 has a refrigerating compartment 11, a freezing compartment 12, and an alternate temperature compartment 13, and is provided in a machine room as shown in Figs. 1A and 1B. One compressor 21, a condenser 22 provided on the discharge side of the compressor 21, and a plurality of evaporators 231 to 233 provided in each chamber between the outlet side of the condenser 22 and the suction side of the compressor 21 ) (hereinafter referred to as an evaporator 231 for a refrigerating chamber, an evaporator 232 for a freezer compartment, and an evaporator 233 for an alternate temperature room when these are distinguished), and a plurality of evaporators 231 to 233 provided on the inlet side, respectively. Refrigerant circuit 200 having decompression means 241 to 243 (hereinafter referred to as decompression means 241 for refrigerating compartment, decompression means 242 for freezer compartment, and decompression means 243 for alternate temperature room when these are distinguished) are being prepared

Here, the evaporator 233 for alternate temperature room is provided on the inlet side of the evaporator 232 for freezing chambers, and the check valve 25 is provided at the outlet side of the evaporator 232 for freezing chambers. In addition, the evaporator 233 for alternate temperature chambers may be provided in the exit side of the evaporator 232 for freezing chambers, and may be provided in parallel with the evaporator 232 for freezing chambers.

At the inlet side of the refrigerating chamber evaporator 231, a refrigeration capillary 241 is provided in series as a decompression means for the refrigerating chamber, and at the inlet side of the freezing chamber evaporator 232, a freezing capillary 242 is provided in series as a decompression means for the freezing chamber. Also, at the inlet side of the evaporator 233 for an alternate temperature room, a capillary tube 243 for alternate temperature is provided in series as a pressure reducing means for an alternate temperature room.

These capillaries 241 to 243 are provided in parallel with each other, and since the evaporator 233 for the alternate temperature room is provided on the inlet side of the evaporator 232 for the freezing chamber, the evaporator 233 for the alternate temperature chamber and the evaporator 232 for the freezing chamber ) and the outlet side of the decompression means 242 for the freezer compartment, and the refrigerant flowing out from the decompression means 242 for the freezing chamber flows to the evaporator for the freezing chamber 232 without flowing into the evaporator 233 for the alternate temperature room. making it happen

In the refrigerant circuit 200 of the present embodiment, the return pipe L connecting the outlet side of each evaporator 231 , 232 , 233 and the suction side of the compressor is connected to the capillary tube 241 , 242 , 243 described above and thermally. is connected to, and is configured to exchange heat between the low-temperature refrigerant flowing through the return pipe (L) and the high-temperature refrigerant flowing through the capillary tubes (241, 242, 243). Specifically, the return pipe L and the capillary tubes 241, 242, and 243 are connected by soldering or the like, for example.

The capillary tubes 241, 242, and 243 described above, together with an expansion valve V having a valve structure 20 to be described later, a pressure reducing mechanism Z for changing the high-pressure refrigerant flowing out from the condenser 22 into a low-pressure refrigerant constitutes

Next, the valve structure 20 will be described.

The valve structure 20 is for flowing the refrigerant to one or more of the plurality of evaporators 231 to 233, and as shown in FIGS. 1A to 2, the outlet side of the condenser 22 in the machine room and the capillary tube ( 241 to 243) are provided in the form of connecting the inlet side.

The valve structure 20 of the present embodiment is a so-called four-way valve for flowing the refrigerant flowing in to one or two of the three evaporators 231 to 233, and the refrigerant flowing into each of the evaporators 231 to 233. The flow rate is adjustable.

Specifically, as shown in FIGS. 3 and 4 , this valve structure 20 includes at least a valve seat 3 and a valve body 4 , and here, a drive mechanism for rotating the valve body 4 . (5) and the casing 6 in which the refrigerant|coolant inflow space S into which the refrigerant|coolant flows in while accommodating the valve seat 3 and the valve body 4 was further provided.

The driving mechanism 5 includes a motor 51 including a stator 511 and a rotor 512 provided inside the stator 511 , and a driving force of the motor 51 by rotating in association with the rotor 512 . It has an output gear 52 that outputs

The casing 6, as shown in FIG. 4, has a hollow casing body 61 having an opening formed on the bottom surface, and a cover that closes the opening to form the refrigerant inflow space S together with the casing body 61 It has a sieve (62).

The casing body 61 is formed of, for example, a rotating body formed of metal or the like, and is disposed inside the stator 511 in a state in which the rotor 512 is accommodated in the hollow.

The cover body 62 has a flat plate shape, and an inlet 621 for introducing a refrigerant into the refrigerant inlet space S is formed in communication with the refrigerant inlet space S, and here, for example, a diameter dimension ( It forms a disk shape with a diameter) of 35 mm or less. This inlet 621 is connected to the outlet side of the condenser 22 by the inlet pipe 7, whereby the refrigerant flowing out from the condenser 22 flows into the refrigerant inlet space S.

As shown in FIGS. 3 to 6 , the valve seat 3 is inserted without a gap into the through hole formed in the cover body 62 described above, and communicates with the refrigerant inflow space S to communicate with the refrigerant inflow space S. An outlet (3a) for allowing the refrigerant to flow out is formed. Moreover, in the center of this valve seat 3, the through-hole 3x into which the rotation shaft X of the valve body 4 mentioned later is inserted is formed.

The valve seat 3 of this embodiment has the upper part 31 the same size as the through hole formed in the cover body 62, and the lower part 32 is the upper part ( 31), when the upper part 31 is fitted into the through hole of the cover body 62 from below, the end formed between the upper part 31 and the lower part 32 is the lower surface of the cover body 62. is meant to be met.

Specifically, this valve seat 3 has a disk shape having a diameter dimension (diameter) of 16 mm or less, and by penetrating the upper portion 31 of the valve seat 3 in the thickness direction, the upper surface thereof is, for example, 0.8 in diameter. An outlet port 3a of mm is formed.

In addition, in the lower part 32, a hole 3s for an outlet pipe communicating with the outlet 3a and having a larger diameter dimension than the outlet 3a is formed, and the outlet pipe 3s is provided in this outlet hole 3s. 8) is configured to be inserted. Through the outlet pipe 8, the outlet 3a is connected to the inlet side of the evaporators 231 to 233, and the refrigerant flowing out from the refrigerant inlet space S through the outlet 3a is transferred to any one evaporator 231. ~233).

As shown in FIGS. 3-6, the valve structure 20 of this embodiment has two valve seats 3 (Hereinafter, these valve seats 3 are 1st valve seat 3A, 2nd valve seat (referred to as 3B), the first valve seat 3A is attached to one of the two through holes formed in the cover body 62 , and the second valve seat 3B is attached to the other one. Here, the 1st valve seat 3A and the 2nd valve seat 3B are disk-shaped things of mutually the same diameter dimension.

The first valve seat 3A is provided with two outlet ports 3a (hereinafter, these outlet ports 3a will be referred to as a first outlet port 3a1 and a second outlet port 3a2). In the present embodiment, the first outlet 3a1 is connected to the inlet side of the refrigerating chamber evaporator 231 by a first outlet pipe 81 , and the second outlet 3a2 is connected to the second outlet pipe 82 . ) is connected to the inlet side of the evaporator 232 for the freezing chamber.

The first outlet port 3a1 and the second outlet port 3a2 have the same diameter dimension as each other, and are arranged along the circumferential direction around the center of the first valve seat 3A. That is, the distance from the center of the first valve seat 3A to the center of the first outlet port 3a1 and the distance from the center of the first valve seat 3A to the center of the second outlet port 3a2 are equidistant, have.

One outlet port 3a (hereinafter, this outlet port 3a is referred to as a third outlet port 3a3) is formed in the second valve seat 3B. In the present embodiment, the third outlet 3a3 is connected to the inlet side of the evaporator 233 for alternate temperature room by a third outlet pipe 83 .

Further, the third outlet port 3a3 has the same diameter dimension as the first outlet port 3a1 and the second outlet port 3a2, and the distance from the center of the second valve seat 3B to the center of the third outlet port 3a3 is , equidistant from the center of the first valve seat 3A to the center of the first outlet 3a1 and the second outlet 3a2.

The valve body 4 is provided rotatably with respect to the valve seat 3, is for adjusting the opening degree of the said outlet 3a between a fully open state and a fully closed state, The outlet port 3a with rotation. The adjustment groove 4a in which the area overlapping with (3a) changes is formed.

In this embodiment, although the 1st valve body 4A and the 2nd valve body 4B are provided corresponding to each 1st valve seat 3A and the 2nd valve seat 3B, here, the 1st valve body ( Since 4A) and the 2nd valve body 4B are mutually the same structure, below, 4 A of 1st valve bodies (henceforth simply the valve body 4) are demonstrated on behalf of these.

This valve body 4 is provided above the valve seat 3 and rotates about the central axis of the valve seat 3, as shown in FIGS. A through hole 4x is formed. The valve body 4 is equipped with a manual gear 9 meshing with the output gear 52 described above, and the rotation shaft X is provided on the manual gear 9 . In more detail, the manual gear 9 is provided with a plurality of convex portions 91 , and a plurality of concave portions 4y engaged with the convex portions 91 are formed on the upper surface of the valve body 4 , have. Thereby, by inserting the rotating shaft X into the through hole 4x and engaging the convex part 91 with the recessed part 4y, the valve body 4 is a manual gear by the driving force of the drive mechanism 5. It rotates in conjunction with (9).

In addition, in this embodiment, as described above, the first valve body 4A and the second valve body 4B are provided corresponding to the first valve seat 3A and the second valve seat 3B, respectively, and the first valve body 4B is provided. Two manual gears 9 provided in each of the first valve body 4A and the second valve body 4B are meshed with the common output gear 52 . Thereby, the 1st valve body 4A and the 2nd valve body 4B interlock|cooperate and rotate.

The valve body 4 of this embodiment is comprised from the flat upper part 41, and the flat lower part 42 in which the above-mentioned adjustment groove 4a penetrated in the thickness direction was formed. The upper portion 41 overlaps the entire lower portion 42, for example, in the shape of a disk, and the lower portion 42 has the adjustment groove 4a formed on the disk. The valve body 4 of the present embodiment has, for example, a disk shape having a diameter of 12 mm or less, and the adjustment groove 4a is formed to extend along the circumferential direction.

As shown in Fig. 7, the adjustment groove 4a is formed so that its width changes along the circumferential direction, and here the distal end 4b starts to overlap with the outlet 3a due to the rotation of the valve body 4 . ), it is formed so that the width may gradually increase toward the rear end 4c on the opposite side. This adjustment groove 4a is comprised so that from the front-end|tip part 4b to the rear-end part 4c may enter within 60 degrees centering on the rotation axis X of the valve body 4 .

As shown in FIG. 8, the tip part 4b is a part of a circle (here, a semicircle part) centering on the point Q located on the rotation trajectory P of the tip part 4x. In addition, the front-end|tip 4x of the adjustment groove 4a is the end of the front-end|tip part 4b along the rotation direction of the valve body 4 .

Specifically, the tip portion 4b is shaped to have a width of 0.2 mm or more, and in the present embodiment, a semicircular portion of a circle having a diameter of 0.2 mm or more is used as the tip portion 4b. In addition, the width dimension here is a dimension along the direction perpendicular|vertical to the rotation trajectory P of the front-end|tip 4x.

Further, as shown in Fig. 7, further back of the rear end 4c of the adjustment groove 4a, a groove for full opening is formed continuously with the rear end 4c and overlaps the entire outlet 3a ( 4d) is formed. This groove 4d for full opening is notched along the circumferential direction of the lower part 42 of the valve body 4 toward the side opposite to the rotation direction of the valve body 4 from the rear end 4c. did it

And in this embodiment, as shown in FIG.7 and FIG.8, the center O of the outlet port 3a is displaced from the rotation trajectory of the front-end|tip part 4b of the adjustment groove 4a.

More specifically, here, from an imaginary circle Z centered on the rotation axis X of the valve body 4 through the center O of the outlet 3a, the tip 4x of the adjustment groove 4a The rotation trajectory P of is displaced inward.

By the way, although the refrigerator 100 of this embodiment is provided with a filter (not shown) provided on the upstream side of the valve structure 20, foreign substances such as contaminants smaller than the mesh size of the filter pass through the filter and are together with the refrigerant. There is a possibility that the refrigerant flows into the inlet space (S).

Then, for example, in the valve body 4A shown in Fig. 7, if a foreign material enters the tip end portion 4b of the adjustment groove 4a, the foreign material cannot be scraped off only by the rotational operation of the valve body 4, so that the foreign material cannot be removed. There is a risk of being deposited on the tip portion 4b of the adjustment groove 4a.

Therefore, the width of the portion overlapping with the outlet 3a in the tip 4b is set so that the foreign matter flowing into the tip 4b flows out from the outlet 3a together with the refrigerant. This width dimension is set based on the mesh size of the filter so that the foreign material passing through the filter flows out from the outlet 3a, for example, it is set to 0.1 mm or more in consideration of the size of the assumed foreign material.

In the present embodiment, at least the tip 4x of the adjustment groove 4a overlaps the outlet 3a, and as shown in FIG. 8, the radius OL of the tip 4b is 0.1 mm or more. In (4b), the width of the portion overlapping with the outlet 3a is larger than that of the foreign matter.

Next, the operation of the valve structure 20 and the flow of the refrigerant will be described.

The valve structure 20 of this embodiment, as shown in FIG. 9, when the 1st valve body 4A and the 2nd valve body 4B interlock|cooperate and rotate, these 1st valve body 4A and According to the rotation angle of the 2nd valve body 4B, it is comprised so that a completely closed area|region, a fully open area|region, and three flow volume variable areas|regions may be formed.

The completely closed region is a region in which the first outlet 3a1 , the second outlet 3a2 , and the third outlet 3a3 are in a completely closed state at the same time.

The fully open area is an area in which either the first outlet 3a1 or the second outlet 3a2 and the third outlet 3a3 are in a fully open state at the same time. The fully open region of this embodiment is a region in which the first outlet 3a1 and the third outlet 3a3 are in a fully open state at the same time, in other words, the first valve body 4A over the entire first outlet 3a1. ) is a region in which the groove 4d for full opening overlaps and the groove 4d for full opening of the second valve body 4B overlaps the entire third outlet 3a3.

The flow rate variable region is a region in which the flow rate of the refrigerant flowing out from the respective outlets 3a1 to 3a3 can be adjusted independently, in other words, the first outlet 3a1, the second outlet 3a2, or the third outlet 3a3. It is an area|region from which the other two will be in a completely closed state while the adjustment groove|channel 4a overlaps in any one. This flow rate variable region is provided for each of the respective outlets 3a1 to 3a3.

In addition, in the flow rate variable region of this embodiment, the refrigerant flow rate flowing out from the first outlet port 3a1 and the second outlet port 3a2 is gradually increased, and the refrigerant flow rate flowing out from the third outlet port 3a3 is gradually decreased. Consists of.

Any one of the first outlet port 3a1, the second outlet port 3a2, or the third outlet port 3a3 is fully open as shown in FIG. 9 except for the fully closed region, the fully open region, and the flow rate variable region described above It is a state, and the area|region used as the other two completely closed state is provided. In other words, in this area, the groove 4d for full opening overlaps any one of the first outlet 3a1, the second outlet 3a2, or the third outlet 3a3, and the other two It is a closed area.

Further, between the variable flow rate region formed with respect to the third outlet 3a3 and the variable flow rate region formed with respect to the second outlet 3a2, the first outlet 3a1, the second outlet 3a2, and the 3 A region is provided in which all of the outlet ports 3a3 are in a completely closed state.

In the refrigerator 100 of the present embodiment configured as described above, since the center O of the outlet 3a is displaced from the rotational trajectory P of the distal end 4b of the adjustment groove 4a, the valve body 4 By rotating , the distal end 4b of the adjustment groove 4a starts to overlap from the direction deviated from the front directly with respect to the outlet 3a. Thereby, as seen from the design data of FIG. 10, when starting to flow a refrigerant|coolant, the area where the front-end|tip part 4b of the adjustment groove 4a and the outlet 3a overlap can be made small compared with the prior art. As a result, when starting to flow a refrigerant, the flow rate of the refrigerant can be increased little by little, and it becomes possible to control the flow rate when starting to flow the fluid with high precision.

Further, in the state where the valve body 4 rotates and the tip 4x of the adjustment groove 4a overlaps the outlet 3a, the size of the overlapping portion is made larger than the assumed foreign matter, so the adjustment groove ( Even if foreign matter flows into the tip portion 4b of 4a), the foreign material can flow out from the outlet 3a together with the refrigerant.

In addition, since the three outlets 3a1 to 3a3 can be made into a completely closed region in which the three outlets 3a1 to 3a3 are in a completely closed state at the same time, high-temperature refrigerant flows from the condenser 22 side to each evaporator 231 to 233 when the compressor 21 is stopped. It is possible to prevent the inflow, and it is possible to prevent the temperature of each of the chambers 11 to 13 from rising due to the refrigerant inflow when the compressor 21 is stopped.

In addition, since the two outlets 3a1 and 3a3 can be made into a fully open region in which the two outlets 3a1 and 3a3 are simultaneously fully open, the refrigerant is transferred to the refrigerating chamber 11, the freezing chamber 12, and the alternate temperature chamber in this fully open state. 13) can be supplied to the three rooms, and the cooling rate of each room can be improved in case of overload such as during pull-down.

In addition, since it can be set as a flow rate variable region in which individual flow rate adjustment is possible for each of the three outlets 3a1 to 3a3, the refrigerant is adjusted to an appropriate flow rate according to the load at the time of cooling of each of the rooms 11 to 13. Can be adjusted.

The Moriel diagram of the refrigeration circuit in this embodiment is shown in FIG. In this embodiment, since the pressure reducing mechanism Z has the expansion valve V and the capillary tubes 241, 242, 243, the refrigerant flowing out from the condenser 22 is transferred to the expansion valve V and the capillary tubes 241, 242, 243. ) can be used to reduce the pressure in stages.

As a result, as shown in Fig. 11, the refrigerant flowing from the expansion valve V to the capillary tubes 241, 242, 243 can be heated to a higher temperature than the refrigerant before flowing into the evaporators 231, 232, 233, and the expansion valve ( V) Condensation of piping in the machine room part of the capillary tubes 241, 242, 243 directed into the furnace from the outlet can be prevented.

Further, since the refrigerant return pipe L and the capillary tubes 241, 242, and 243 are thermally connected by, for example, soldering, the refrigerant returning from the evaporators 231, 232, 233 to the compressor 21 and the expansion Heat exchange takes place between the refrigerant from the valve V to the evaporator through the capillaries 241 , 242 , 243 .

Accordingly, the liquid refrigerant not evaporated in the evaporators 231 , 232 , 233 can be evaporated before returning to the compressor 21 by heating in the refrigerant return pipe L, and the liquid refrigerant to the compressor 21 is heated. return can be prevented.

Further, as shown in Fig. 11, when the refrigerant in the capillary tubes 241, 242, and 243 is cooled under reduced pressure, the refrigerating capacity can be increased, and the efficiency of the refrigerating cycle can be improved.

<Second embodiment>

Next, a second embodiment of the present invention will be described with reference to the drawings.

The valve structure 20 according to the second embodiment is used as a so-called three-way valve. Further, the valve structure 20 in the second embodiment is provided in the expansion valve V as in the first embodiment, and the expansion valve V and the capillary tubes 241 and 242 are condensers. A decompression mechanism Z for changing the high-pressure refrigerant from (22) into a low-pressure refrigerant is constituted.

As shown in FIGS. 12A to 13 , the valve structure 20 according to the present embodiment is used, for example, in a refrigerator/freezer 100 . The refrigerator-freezer 100 of this embodiment is different from the refrigerator-freezer 100 of the first embodiment in that it does not include an alternate-temperature room, an evaporator for an alternate-temperature chamber, and a decompression means for an alternate-temperature chamber, but in other respects, the first embodiment Since it has the same configuration as , a detailed description thereof will be omitted.

The valve structure 20 of this embodiment is a so-called three-way valve for flowing a refrigerant to one or both of the evaporator 231 for the refrigerating compartment or the evaporator 232 for the freezing compartment, and flows to each of the evaporators 231 and 232 The refrigerant flow rate is adjustable.

Specifically, as shown in FIGS. 14 and 15 , this valve structure 20 includes at least a valve seat 3 and a valve body 4 , and here, a drive mechanism for rotating the valve body 4 . (5) and the casing 6 in which the refrigerant|coolant inflow space which accommodates the valve seat 3 and the valve body 4 and the refrigerant|coolant flows in was further provided.

Since the drive mechanism 5 and the casing 6 are the same structures as 1st Embodiment, detailed description is abbreviate|omitted.

Moreover, the valve structure 20 of 1st Embodiment respond|corresponds to two valve seats 3 (1st valve seat 3A and 2nd valve seat 3B), and these valve seats 3 respectively, Although the provided two valve bodies 4 (1st valve body 4A and 2nd valve body 4B) were provided, the valve structure 20 of this embodiment has the valve seat 3 and the valve body ( 4) is provided one by one.

The valve seat 3 of this embodiment has the same configuration as that of the first valve seat 3A of the first embodiment, and as shown in Fig. 16 , two outlet ports 3a (hereinafter, these outlet ports 3a) are provided. A first outlet 3a1 and a second outlet 3a2) are formed. In the present embodiment, the first outlet 3a1 is connected to the inlet side of the refrigerating chamber evaporator 231 by a first outlet pipe 81 , and the second outlet 3a2 is connected to the second outlet pipe 82 . ) is connected to the inlet side of the evaporator 232 for the freezing chamber. In addition, the dimension of the valve seat 3, the diameter dimension of each outlet port 3a1, 3a2, and the distance from the center of the valve seat 3 to the center of each outlet port 3a1, 3a2 are the same as in the first embodiment, but , since the operation of the valve structure 20 is different, the arrangement of the respective outlet ports 3a1 and 3a2 is different from that of the first embodiment.

The valve body 4 has the same structure as the valve body 4 of 1st Embodiment basically. That is, the valve body 4 is provided rotatably with respect to the valve seat 3, and adjusts the opening degree of the said outlet 3a between a fully open state and a fully closed state. In this valve body 4, as shown in Figs. 17 and 18, an adjustment groove 4a in which the area overlapping with the outlet 3a changes with rotation, and fully open overlapping with the entire outlet 3a. The groove 4d (henceforth the 1st groove|channel 4d for full opening) is formed.

The adjustment groove 4a is comprised so that the front-end|tip part 4b to the rear-end part 4c may enter within 60 degrees centering on the rotation axis X of the valve body 4 similarly to 1st Embodiment.

On the other hand, the first full opening groove 4d has an angle higher than that of the first embodiment in order to make the two outlet ports 3a1 and the outlet port 3a2 completely open at the same time using one valve body 4 . It is made wide.

In addition, the center O of the outlet 3a is displaced from the rotational trajectory of the distal end 4b of the adjustment groove 4a, and the width dimension of the portion overlapping the outlet 3a in the distal end 4b. It is set in consideration of the size of foreign matter that can flow into the tip portion 4b, as in the first embodiment.

And as shown in FIGS. 17 and 18, the valve body 4 of this embodiment overlaps the whole outlet 3a1 separately from the said adjustment groove 4a and the 1st full opening groove 4d. It differs from the valve body of 1st Embodiment in the point in which the 2nd groove|channel 4f for fully opening is formed.

The 2nd groove|channel 4f for fully opening is formed by corrugating the lower part 42 of the valve body 4 along the circumferential direction, and is provided not to be continuous with the 1st groove|channel 4d for fully opening and the adjustment groove 4a. have. This 2nd groove|channel for fully opening 4f is comprised so that it may overlap with the whole outlet 3a1.

In more detail, the second full opening groove 4f is, when the first fully opening groove 4d overlaps the one outlet port 3a as a whole, the other outlet port 3a as a whole. It is formed in an overlapping position.

That is, the relative positional relationship between the first fully open groove 4d and the second fully open groove 4f is designed based on the relative positional relationship between the two outlets, and in this case, the second fully open groove ( It is trying to arrange|position the rotation shaft X of the valve body 4 between 4f) and the 1st groove|channel 4d for full opening.

Next, the operation of the valve structure 20 of the present embodiment and the flow of the refrigerant will be described.

As shown in Fig. 19, the valve structure 20 of the present embodiment has a fully closed region, a fully open region, and It is configured to form two flow rate variable regions.

The completely closed area is an area in which the first outlet 3a1 and the second outlet 3a2 are in a completely closed state at the same time.

The fully open area is an area in which the first outlet 3a1 and the second outlet 3a2 are in a fully open state at the same time, in other words, the first fully open groove 4d or the second outlet 3a1 as a whole. 2 Area where one of the grooves for full opening 4f overlaps, and the other one of the grooves for full opening 4d or the second groove for fully opening 4f overlaps the entire second outlet 3a2 to be.

The flow rate variable region is a region in which the flow rate of the refrigerant flowing out from each of the outlets 3a1 and 3a2 can be adjusted independently, in other words, an adjustment groove 4a is provided in one of the first outlet 3a1 or the second outlet 3a2. With this overlap, the other side is a region in a completely closed state. This flow rate variable region is provided for each of the respective outlets 3a1 and 3a2.

Moreover, in the flow rate variable area|region of this embodiment, it is comprised so that the refrigerant|coolant flow volume flowing out from the 1st outlet 3a1 and the 2nd outlet 3a2 may increase gradually.

Except for the fully closed region, fully open region, and flow rate variable region described above, as shown in FIG. 16 , one of the first outlet ports 3a1 and the second outlet port 3a2 is in a fully open state, and the other is in a fully closed state. There is an area for In other words, in this area, the second fully opening groove 4f does not overlap on one of the first outlet 3a1 or the second outlet 3a2, and the fully opening groove 4d overlaps on the other side. It is an area|region, and this is an area|region obtained by the angle difference in which the 1st groove|channel 4d for full opening and the 2nd groove|channel 4f for full opening are formed.

In the refrigerator 100 of this embodiment comprised in this way, the 2nd groove|channel 4f for fully opening is formed in the valve body 4 separately from the 1st groove|channel 4d for fully opening, and the 1st When the full opening groove 4d overlaps the entire outlet 3a of one side, the second fully open groove 4f is configured to overlap the entire other outlet 3a, so that a pair of valves By using the seat 3 and the valve body 4, not only the fully closed state and flow rate variable region but also the fully open region can be formed.

As a result, by setting it as a completely open area|region, the refrigerant|coolant can flow through both the evaporator for refrigerating chambers 231 and the evaporator for freezing chambers 232, and the cooling rate in the case of an overload, such as a pull-down, can be improved.

Moreover, by setting it as a completely closed region, it is possible to prevent high-temperature refrigerant from flowing into each of the evaporators 231 and 232 from the condenser 22 side when the compressor 21 is stopped, and the refrigerant when the compressor 21 is stopped. It is possible to prevent the temperature of each of the chambers 11 and 12 from rising due to the inflow.

Moreover, by setting it as a flow volume variable area|region, the refrigerant|coolant can be adjusted to the appropriate flow volume according to the load at the time of each cooling of each chamber 11 and 12.

In addition, since the rotation trajectory of the distal end 4b of the adjustment groove 4a is displaced from the center O of the outlet 3a, by rotating the valve body 4, the distal end 4b of the adjustment groove 4a is starts to overlap from the direction deviated from the front directly with respect to the outlet 3a.

Accordingly, when starting to flow the coolant, the area where the tip portion 4b of the adjustment groove 4a and the outlet 3a overlap is made smaller than in the prior art, so that the coolant flow rate can be increased little by little, when starting to flow the fluid It becomes possible to control the flow rate with high precision.

On the other hand, in the conventional configuration in which the tip of the adjustment groove passes through the center of the outlet, the flow rate cannot be adjusted with high precision. As it decreases, it cannot be said that the flow rate can be controlled.

In addition, the width of the portion overlapping the outlet 3a in the distal end 4b of the adjustment groove 4a is the same as that of the contaminant or other foreign matter flowing into the distal end 4b from the outlet 3a together with the refrigerant. Since it is set so that it may come out, even if a foreign material flows into the front-end|tip part 4b of the adjustment groove 4a, it can flow out from the outlet 3a together with a refrigerant|coolant.

Further, as in the first embodiment, by having the expansion valve V and the capillary tubes 241 and 242 as the pressure reducing mechanism Z, the liquid refrigerant condensed in the condenser 22 is transferred to the expansion valve V and the capillary tube ( 241, 242) can be stepwise reduced pressure.

As shown in Fig. 11, as shown in Fig. 11, the temperature of the refrigerant flowing out from the expansion valve V can be made higher than the evaporation temperature, so that the pipe in the machine room portion of the capillary tubes 241 and 242 is also effective. Condensation can be prevented.

In addition, as in the first embodiment, since the capillary tubes 241 and 242 and the refrigerant return pipe L are thermally connected by, for example, soldering, the liquid refrigerant returning from the evaporators 231 and 232 to the compressor is heated. Accordingly, the effect of preventing liquid return and the effect of increasing the refrigeration capacity by cooling the refrigerant from the expansion valve V to the evaporators 231 and 232 through the capillary tubes 241 and 242 can be obtained.

Moreover, since the refrigerant flow rate is controlled by the fluid control groove provided in the valve body, the pipe diameters of the inlet pipe 7 and the plurality of outlet pipes 8 can be variously changed regardless of the refrigerant flow rate, for example, a plurality of It becomes possible to make the pipe diameter of the outflow pipe|tube 8 the same, or to make the pipe diameters of the inflow pipe 7 and the outflow pipe 8 the same.

However, this invention is not limited to 1st Embodiment and 2nd Embodiment.

For example, in the first embodiment, the rotational trajectory of the tip of the adjustment groove is displaced from the imaginary circle so that the tip of the adjustment groove overlaps with the outlet, but the tip of the adjustment groove does not overlap with the outlet, and the tip of the adjustment groove does not overlap with the outlet. A part other than the tip may overlap the outlet.

<Third embodiment>

Next, a third embodiment of the present invention will be described with reference to the drawings.

Since the position of the outlet port 3a is characteristic of the valve structure 20 according to the third embodiment, this point will be described in detail below.

First, in the outlet 3a of the first embodiment or the second embodiment, as shown in Fig. 8, the rotation trajectory P of the tip 4x of the adjustment groove 4a is in contact with the outer edge of the outlet 3a. formed to do so.

However, since the position of the outlet 3a, that is, the position of the center O of the outlet 3a, varies during processing and assembly, as shown in Fig. 20A, for example, the outlet ( When the center (O) of 3a) is used as the reference position, the actual center (O) is outward in the radial direction or inward in the radial direction (for example, 0.15 mm) compared to the reference position as in FIG. 20b or 20c. have.

With this change, as shown in Figs. 21A to 21C, the difference in the valve opening degree (rotation angle at which the refrigerant starts flowing) of the valve body 4 when the adjustment groove 4a and the outlet port 3a overlap Occurs. Specifically, as shown in Fig. 21B, when the outlet port 3a deviates outward in the radial direction, the valve opening degree is smaller than when the outlet port 3a is at the reference position as shown in Fig. 21A, and also When the rotation angle at which the refrigerant starts to flow becomes slow, and the outlet 3a deviates inward in the radial direction, the valve opening degree is larger than when the outlet 3a is at the reference position, and the rotation angle at which the refrigerant starts flowing is faster

In the case where the center O of the outlet 3a is outward in the radial direction from the reference position, in the configuration of the first embodiment and the second embodiment, when the coolant starts flowing, the adjustment groove 4a The area where the tip end portion 4b and the outlet port 3a overlap becomes too small, and as shown in FIG. 22 , the flow rate hardly increases even when the valve body 4 is rotated when the coolant starts flowing.

In this regard, when the outlet port 3a is deviated outward in the radial direction, the refrigerant does not flow at the same rotation angle as when the outlet port 3a is at the reference position, so that a problem of insufficient cooling may occur. There is a concern that basic performance, such as an increase in power consumption, will be impaired even if it is not there.

Therefore, in the valve structure 20 which concerns on this embodiment, as shown in FIG. 23, the outlet 3a of a reference position is arrange|positioned radially inner side rather than each said embodiment. More specifically, the rotation trajectory P of the tip 4x of the adjustment groove 4a is at the rotation axis X side of the valve body 4 rather than the center O of the outlet port 3a at the outlet 3a. The outlet 3a is disposed so as to overlap with the .

By disposing the outlet port 3a at the reference position radially inside the respective embodiments in this way, as shown in Fig. 24 , even if the outlet port 3a deviates radially outward, that is, the adjustment groove 4a and Even when the overlapping area of the outlet 3a becomes the lower limit, the overlapping area of the front end 4b of the adjustment groove 4a and the outlet 3a can be prevented from becoming too small when the coolant starts flowing. , it is possible to avoid damage to basic performance, such as the above-described troubles such as inflammation or increase in the amount of power consumption.

On the other hand, in the configuration of the present embodiment, when the outlet 3a deviates radially inwardly as shown in Fig. 21C due to variations during machining or assembly, the distal end 4b of the adjustment groove 4a and the outlet 3a ) after starting to overlap, the overlapping area when the valve body 4 is further rotated becomes larger than that of the first embodiment or the second embodiment, and the flow rate increases all at once, and in the micro flow rate region There is a risk that the flow rate control of the

In view of this point, the adjustment groove 4a of this embodiment has a shape different from 1st Embodiment or 2nd Embodiment, and, as specifically shown in FIG. It has the narrow part 4g formed toward the edge part 4c side, and the wide part 4h formed toward the rear-end part 4c side from the narrow part 4g.

Moreover, in the point that the shape of the adjustment groove 4a is asymmetric with respect to the rotation trajectory P of the front-end|tip 4x, and the point 4b of the front-end|tip part is a partial circular shape, it is common with 1st Embodiment and 2nd Embodiment. have.

The narrow portion 4g has a shape smaller in width than the wide portion 4h, and is formed here so that the width does not change along the circumferential direction, that is, the width becomes constant along the circumferential direction. Specifically, in the narrow portion 4g, a pair of opposed inner edges 4g1 are parallel to each other, and the width thereof is the same as the diameter of the tip portion 4b forming a partial circular shape (for example, the smallest possible machinability). dimensions). All of these inner edges 4g1 extend in a tangential direction from both ends of the tip portion 4b, and are parallel to the rotation trajectory P of the tip portion 4x.

The wide portion 4h is formed so that the width thereof changes along the circumferential direction, and specifically, the width dimension gradually increases toward the rear end 4c, in other words, from the narrow portion 4g to the rear end 4c. ), which spreads toward the

More specifically, the outer edge 4h1 of the widened portion 4h is formed to go away from the rotational trajectory P of the tip 4x outward, and the inner edge 4h2 of the widened portion 4h has a tip ( It is formed so as to be close to the rotation trajectory P of 4x). Thereby, the outer edge 4h1 and the inner edge 4h2 of the wide part 4h are asymmetric with respect to the rotation trajectory P of the front-end|tip 4x. In addition, the inner edge 4h2 may be parallel to the rotation trajectory P of the front-end|tip 4x.

In this way, by making the narrow portion 4g formed from the front end 4b toward the rear end 4c side into a shape in which the width dimension becomes constant along the circumferential direction, even if the outlet 3a is repositioned in the radial direction , it is possible to suppress an increase in the overlapping area when the valve body 4 is further rotated after the distal end 4b of the adjustment groove 4a and the outlet 3a start to overlap.

For this reason, even when the overlapping area of the adjustment groove 4a and the outlet port 3a becomes the upper limit value, it is possible to prevent the flow rate from increasing all at once when the coolant starts flowing, and the adjustment groove 4a in the micro flow rate range ), it becomes possible to control the flow rate by minimizing the influence of variations during processing or assembly of the outlet 3a.

In addition, since the narrow portion 4g is formed parallel to the rotation trajectory P of the tip 4x, the overlapping area of the adjustment groove 4a and the outlet 3a becomes the upper limit (maximum), When starting to flow the refrigerant, it is possible to prevent the flow rate from increasing all at once.

In addition, since the outer edge 4h1 of the widened portion 4h is formed so as to move away from the rotational trajectory P of the tip 4x to the outside, after the coolant starts to flow to some extent, the flow rate can be gradually increased and adjusted When the entire groove 4a continues to pass through the outlet 3a and the outlet 3a is fully opened, it is possible to prevent the flow rate from rapidly increasing.

In addition, since the inner edge of the widening part is formed to be close to the rotational trajectory of the tip part, after the refrigerant starts to flow to some extent, it is possible to prevent the flow rate from increasing all at once and increase the flow rate gradually, so that the flow path area generated in the narrow part Variation in the ratio can be reduced.

As described above, in the case of the valve structure 20 of the present embodiment, as shown in Fig. 24, even if the outlet 3a is positioned radially outward, the flow rate at the time of starting to flow the refrigerant can be secured. Together with this, even if the outlet 3a is shifted outward in the radial direction, it is possible to prevent the flow rate from increasing all at once when the coolant is started to flow.

However, in 3rd Embodiment, although the aspect which arrange|positioned the outlet 3a of a reference position radially inside rather than said 1st Embodiment or said 2nd embodiment was demonstrated, the adjustment groove 4a of a reference position was Even if it arrange|positions radially outward rather than 1st Embodiment or said 2nd Embodiment, the effect similar to 3rd Embodiment can be acquired.

In addition, this invention is not limited to each said embodiment, It cannot be overemphasized that various deformation|transformation is possible in the range which does not deviate from the meaning.

Claims (15)

compressors, condensers, evaporators;
Including; a valve for transferring the refrigerant flowing out of the condenser to the evaporator;
The valve includes a valve seat having an outlet through which the refrigerant in the valve flows, and a valve body,
The valve body is
A rotation shaft provided to correspond to the central axis of the valve seat and to be the center of rotation of the valve body;
and an adjustment groove extending in the circumferential direction of the valve body and moving with respect to the outlet to adjust the opening degree of the outlet;
The center of the outlet is provided outside the movement trajectory of the valve body in the rotational direction of the center of the end of the adjustment groove in the radial direction of the rotational axis of the valve body. The method of claim 1,
When the adjustment groove is disposed to overlap the outlet by rotation of the valve body, the outlet is provided to communicate with the evaporator,
and when the adjustment groove rotates along the movement trajectory to overlap the outlet, the overlapping area of the adjustment groove increases irregularly with respect to the rotation angle of the adjustment groove. 3. The method of claim 2,
The adjustment groove includes an open end and a closed end. 4. The method of claim 3,
The width of the adjustment groove is provided to increase in a direction from the closed end to the open end. 4. The method of claim 3,
The adjustment groove is provided to have a first area formed in the closed end and having a constant width and a second area increasing in width from the first area toward the open end. 6. The method of claim 5,
In the first region, a pair of opposed inner edges is provided parallel to each other, and the pair of inner edges are provided parallel to a movement trajectory of a center of the closed end. 6. The method of claim 5,
The outer peripheral surface of the second region in the radial direction of the rotation shaft of the valve body is formed to extend from a movement trajectory of the center of the closed end in the radial direction of the rotation shaft of the valve body. 6. The method of claim 5,
An inner peripheral surface and an outer peripheral surface of the second region in a radial direction of the rotation shaft of the valve body extend asymmetrically in the direction of the open end. delete The method of claim 1,
and a filter disposed between the condenser and the valve and having a plurality of permeation holes,
When the end of the adjustment groove is disposed to overlap the outlet, the overlapping area when the end is disposed to overlap the outlet is greater than an area of any one of the plurality of through holes. 3. The method of claim 2,
The adjustment groove is disposed in an area within 60 degrees in a radial direction of the valve body with respect to a rotation axis of the valve body. 3. The method of claim 2,
The evaporator includes a first evaporator and a second evaporator,
The valve transfers the refrigerant flowing out from the condenser to the first evaporator and the second evaporator,
The valve seat includes a first valve seat having a first outlet through which the refrigerant flows to the first evaporator and a second valve seat having a second outlet through which the refrigerant flows to the second evaporator,
The valve body is provided rotatably with respect to the first valve seat and includes a first valve body having a first adjustment groove for adjusting an opening degree of the first outlet, and a first valve body rotatably provided with respect to the second valve seat, a second valve body having a second adjustment groove for adjusting the opening degree of the second outlet;
When the second adjustment groove is disposed to overlap the second outlet by rotation of the second valve body, the second outlet is provided to communicate with the second evaporator;
The center of the second outlet is provided on the outside of the movement trajectory of the center of the end of the second adjustment groove. 13. The method of claim 12,
The valve further comprises a motor having a rotating shaft and a driving gear coupled to the rotating shaft of the motor,
The first valve body and the second valve body mesh with a driving gear, respectively, and are rotated in association with the rotation of the driving gear, respectively. 3. The method of claim 2,
The evaporator includes a first evaporator and a second evaporator,
The valve transfers the refrigerant flowing out from the condenser to the first evaporator and the second evaporator,
The outlet includes a first outlet through which the refrigerant flows to the first evaporator, and a second outlet through which the refrigerant flows out to the second evaporator,
The adjustment groove adjusts the opening degree of the second outlet,
When the valve body is rotated at a first rotation angle, the first outlet and the second outlet are opened,
When the valve body is rotated at a second rotation angle, one of the first outlet and the second outlet is disposed to overlap the adjustment groove and the other is closed;
The refrigerator is provided such that the first outlet and the second outlet are closed when the valve body is rotated at a third rotation angle. 14. The method of claim 13,
When the drive gear is rotated to the first rotation angle,
The first valve body and the second valve body are provided such that the first outlet and the second outlet are opened, respectively;
When the driving gear is rotated to the second rotation angle,
The first valve body is provided such that the first outlet overlaps the adjustment groove, the second valve body is provided so that the second outlet is closed;
When the drive gear is rotated to the third rotation angle,
The first valve body and the second valve body are provided such that the first outlet and the second outlet are closed, respectively;
When the drive gear is rotated to the fourth rotation angle,
The first valve body is provided to close the first outlet, and the second valve body is provided so that the second adjustment groove of the second valve body overlaps the second outlet.

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