WO2018038528A1

WO2018038528A1 - Refrigerator

Info

Publication number: WO2018038528A1
Application number: PCT/KR2017/009205
Authority: WO
Inventors: 세오타츠야; 마츠자키타카시
Original assignee: 삼성전자주식회사
Priority date: 2016-08-24
Filing date: 2017-08-23
Publication date: 2018-03-01
Also published as: KR20190035604A; KR102403519B1

Abstract

The present invention provides a valve structure capable of a high-precision control of a flow rate at the time in which fluid starts to flow. The valve structure (20) comprises: a valve seat (3) in which two outlet ports (3a) for discharging fluid are formed; and a valve body (4) which is provided to be rotatable with respect to the valve seat (3) to adjust the opening degree of the outlet ports (3a), wherein the valve body (4) has a flow control groove (4d) along the circumferential direction in which the overlapping area of the valve body (4) with the outlet ports (3a) is changed by rotation, and wherein the center (O) of the outlet ports (3a) is displaced from a rotational trace of a front end (4b) of the flow control groove (4d) which starts to overlap with the outlet ports (3a) by a 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 for a refrigerator, a valve seat having two outlets for flowing out refrigerant, as disclosed in Japanese Unexamined Patent Publication No. 2005-214508, and a valve seat which is rotatably provided with respect to the valve seat in order to open and close each outlet The valve body may be configured so that the refrigerant may be selectively sent to the refrigerating chamber evaporator or the freezing chamber evaporator by rotating the valve body to open one or the other outlet.

In order to control the refrigerant flow rate of the refrigerant | coolant sent to each evaporator, the said valve body is provided with the adjustment groove | channel along the circumferential direction by which the area which overlaps with an outlet port changes by rotation of a valve body. By this structure, by rotating the valve body from the state in which the outlet port is closed, the area where the outlet port and the adjustment groove overlap is large, whereby the refrigerant flow rate can be increased.

However, the valve structure described above has a structure in which the tip end of the adjustment groove which starts to overlap with the outlet port rotates to pass through the center of the outlet port, so that when the coolant starts to flow, the tip end of the adjustment groove overlaps with the outlet port immediately from the front. You start to lose.

As a result, when the coolant starts to flow, the area where the tip of the outlet and the adjustment groove overlap is large, and the flow rate of the coolant flows into the outlet at once, making it difficult to accurately control the coolant flow rate.

Therefore, this invention is made | formed in order to solve the said problem, and makes it a main subject to provide the valve structure which can control the flow volume at the time of starting to flow a fluid with high precision.

That is, the valve structure which concerns on this invention WHEREIN: The valve structure provided with the valve seat in which the two outlets for outflowing a fluid are provided, and the valve body which is movable with respect to the said valve seat, and adjusts the opening degree of the said outlet port, The valve body has an adjustment groove for controlling the flow rate flowing out of the outlet, and the center of the outlet is displaced from the movement trajectory of the distal end of the adjustment groove starting to overlap with the outlet by the movement of the valve body. It is characterized by.

In addition, the movement trace of the front-end | tip part here is a concept in which the movement trace of the front-end | tip of an adjustment groove | channel, the movement trace of the part located behind a front end, etc. are included.

According to the valve structure configured as described above, since the center of the outlet port is displaced from the movement trajectory of the tip end portion of the adjustment groove, when the adjustment groove and the outlet port start to overlap, the tip end portion of the adjustment groove overlaps at an angle shifted from the front directly with respect to the outlet port. .

As a result, when the coolant starts to flow, the area where the tip of the adjusting groove overlaps with the outlet can be made smaller than in the related art. Thus, the coolant flow rate can be increased little by little, and the flow rate at the start of flowing the fluid can be precisely controlled. It becomes possible.

As a specific embodiment, the valve body is rotatably provided with respect to the valve seat, and the adjustment groove is formed along the circumferential direction so that the area overlapping with the outlet port is changed as the valve body rotates. Can be mentioned.

By the way, when the center of the outlet port is largely displaced from the rotational trajectory of the tip end of the adjusting groove, and the area where the tip part and the outlet port overlap is very small, the foreign material does not flow out of the outlet port when foreign material flows into the tip part.

Therefore, when foreign matter flows into the distal end of the adjusting groove, the distal end overlaps with the outlet so that the foreign material flows out of the outlet along with the fluid, so that the center of the outlet is connected with the center of the distal end of the adjusting groove. It is preferable to displace from the rotational trajectory.

With such a configuration, even if foreign matter has flowed into the distal end of the adjustment groove, the foreign matter can flow out with the fluid.

In order to flow out a foreign material certainly, it is preferable that the width dimension of the part which the said tip part of the said adjustment groove overlaps with the said outlet port is set based on the size of the said foreign material.

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

By the way, the position of an adjustment groove | channel and an outflow opening may have the deviation at the time of a process or an assembly, and may deviate radially outward or inward with respect to the designed position (henceforth a reference position).

When the outlet is repositioned radially inward with respect to the reference position, the valve opening degree is greater than when the outlet is at the reference position, and the rotation angle at which the coolant starts to flow becomes faster. Thereby, there is a concern that the flow rate increases all at once when the refrigerant starts to flow. The same problem also arises when the adjusting groove is deviated outward in the radial direction with respect to the reference position.

Accordingly, in view of the fact that the outlet port is repositioned in the radially inward direction and the adjustment groove is repositioned in the radially outward direction, the narrowing part has a narrow width in which the adjusting groove has a constant width from the leading end to the rear end, and the narrowing part. It is preferable to have a widening part from which the width dimension becomes large toward the said rear end side.

With such a structure, even if the area where the adjustment groove and the outlet port overlap by the position change mentioned above becomes an upper limit (maximum), it can reduce that the flow volume increases all at once when the refrigerant starts to flow, so that in the small flow region It becomes possible to control the flow rate by minimizing the influence of the variation in the adjustment groove and the outlet or at the time of processing or assembling.

Even in the case where the area where the adjustment groove and the outlet port overlap is the upper limit (maximum), the narrow width is formed to be substantially parallel to the rotational trajectory of the distal end portion in order to prevent the flow rate from increasing at the same time when the refrigerant starts to flow. It is preferable that it is done.

It is preferable that the outer edge of the said widening part moves away from the rotation trajectory of the said front end part.

By making the outer edge of the widening portion such a shape, the flow rate can be gradually increased after the coolant starts to flow to some extent, and the flow rate increases rapidly when the entire adjusting groove continues to pass through the outlet and the outlet is completely open. Can be prevented.

On the other hand, in order to reduce the deviation of the flow path area ratio occurring in the narrow portion, in order to prevent the flow rate from increasing at a time after the refrigerant starts to flow to some extent and to gradually increase the flow rate, the internal combustion of the widening portion is a rotational trajectory of the tip portion. It is preferably close to or approximately parallel to the rotational trajectory of the tip.

As a specific embodiment, the outer edge and the inner edge of the said wide part are asymmetric with respect to the rotational trajectory of the said tip part.

On the other hand, when the outlet is repositioned outward in the radial direction, the valve opening degree is smaller than the case where the outlet is in the reference position, and the rotation angle at which the coolant starts to flow becomes slow. Thereby, when the coolant starts to flow, the area where the tip of the adjusting groove and the outlet 3a overlap is too small, and the flow rate hardly increases even if the valve body is rotated when the coolant starts to flow. As a result, when the outlet exits outward in the radial direction, the refrigerant may not flow at the same rotational angle as when the outlet is in the reference position, causing trouble such as uncooling, or even basic performance such as an increase in power consumption even if not uncooled. Damage may be a concern. The same problem also occurs when the adjustment groove is repositioned radially inward with respect to the reference position.

Accordingly, in view of the fact that the outlet is repositioned radially outward or the adjustment groove is relocated radially inward, the rotational trajectory of the tip of the adjustment groove is located on the rotation axis side of the valve body rather than the center of the outlet. It is preferable that the said outlet is arrange | positioned so that it may overlap with the said outlet.

With such a configuration, even if the outlet is repositioned outward in the radial direction, the overlapping area can be secured even when the area where the adjustment groove and the outlet overlaps becomes the lower limit (minimum). As a result, the area where the tip of the adjustment groove overlaps with the outlet is not too small when the refrigerant starts to flow, and damage to the basic performance such as trouble and increase in power consumption can be prevented.

Subsequently, a 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 is discharged from two outlets formed in the valve seat will be described. Moreover, as such a three-way valve, what was described in said Japanese document is known.

In the case where the valve structure according to the present invention is used as a three-way valve, for example, in a refrigerator having a refrigerating chamber and a freezing chamber, a fully open area in which the two outlets are completely opened at the same time according to the rotation angle of the valve body It is desirable to configure the valve structure so that it is formed.

With such a configuration, by making the two outlets completely open as the completely open area, the cooling rates of the refrigerating compartment and the freezing compartment can be improved in overload during pull down.

In accordance with the rotation angle of the valve body, while the adjustment groove is overlapped on one of the two outlets, the flow rate variable region in which the other side is in the fully closed state, and the complete closure in which the two outlets are in the fully closed state at the same time. It is desirable to configure the valve structure so that the region is formed.

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

When manufacturing a valve structure capable of forming the fully open region, the variable flow region, and the completely closed region described above, the rotation range of the valve body is less than 360 degrees, for example, by a stopper for starting point correction or position recognition. In addition, since manufacturing conditions are limited in order to make a valve structure small and simple, it is very difficult to form each area mentioned above. In the meantime, the inventor of the present application has intensively studied to form a completely open region, a variable flow region, and a completely closed region using a small and simple valve structure.

As a result, the valve body is formed continuously from the rear end of the adjusting groove, and overlaps with the entirety of the outlet separately from the first fully open groove and the first completely open groove. 2 having a fully open groove, and the adjustment groove is formed within 60 degrees around the axis of rotation of the valve body, using a valve structure such as a small and simple three-way valve, a fully open region, a flow variable region and It was found that it could 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 Unexamined-Japanese-Patent No. 2004-2953573, the 2nd valve seat in which the 3rd outlet port was formed separately from the above-mentioned valve seat and valve body, and this 2nd It is known to have a second valve body provided rotatably with respect to the valve seat.

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

In such a case, the valve structure according to the present invention is provided with a second valve seat having a third outlet port through which fluid is discharged, and rotatably provided with respect to the second valve seat, and rotates in conjunction with the valve body so that It is provided with the 2nd valve body which adjusts an opening degree, and the said 2nd valve body has the adjustment groove along the circumferential direction which the area which overlaps with the said 3rd outlet opening changes by rotating.

In this valve structure, one of two outlets formed in the valve seat and the third outlet formed in the second valve body are completely opened simultaneously according to rotation angles of the first valve body and the second valve body. It is preferable that it is comprised so that the fully open area | region to become a state may be formed.

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

According to the rotation angle of the said valve body and the said 2nd valve body, while the said adjusting groove overlaps with one of the said three outlets, the flow volume variable area | region which the other two will be in a fully closed state, and the said three outlets simultaneously It is desirable to configure the valve structure so that a fully closed region is formed which becomes a fully closed state.

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 in accordance with the load at the time of cooling each of the refrigerating chamber, the freezing chamber, and the temperature changing chamber. 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 area, and to prevent the temperature of each chamber from rising due to the refrigerant flowing in when the compressor is stopped. .

It is as mentioned above that it is very difficult to make the valve structure which can form a fully open area | region, a flow-variable area | region, and a fully closed area | region small and simple.

And as a result of earnest examination by the inventor of this application, the said valve body and the said 2nd valve body are each formed continuously from the rear end of the said adjustment groove, and have a fully open groove which overlaps with the whole said outlet, 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, the fully open area, the flow rate variable area, and the fully closed area using a valve structure such as a small and simple four-way valve Found that can form.

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

As a conventional refrigerator, it is common to arrange a switching valve in a machine room, and to use a capillary tube as a pressure reduction mechanism which connects a switching valve and an evaporator.

In the refrigerator described in this publication, there is no flow rate adjusting width in the decompression by the capillary tube. Therefore, the flow rate adjusting width is expanded by switching a plurality of capillary tubes having different tube diameters to the switching valve.

In addition, as a conventional refrigerator, heat exchange is performed 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 in the capillary tube and the return pipe, the effect of preventing liquid return by heating the return pipe and increasing the freezing capacity by cooling the capillary can be obtained.

In such a conventional refrigerator, when a means for expanding the flow rate adjusting width using a plurality of capillaries is applied to a refrigeration cycle composed of a plurality of evaporators, a plurality of switching valves may be required because of the increase in the number of switching. In addition, when the capillary tube and the return pipe are connected, the number of capillaries that can be connected to one return pipe is limited in processing, so that a capillary tube that cannot be connected to the return pipe is generated. And there is a problem that can not obtain the effect of increasing the freezing capacity.

Therefore, an object of the present invention is to obtain a wider flow rate adjustment range in the refrigeration cycle for switching a plurality of evaporators, and to obtain an effect of preventing liquid return and increasing the freezing capacity.

That is, the refrigerator which concerns on this invention provided the capillary tube between a three-way valve or a four-way valve, and an evaporator. It is characterized by the above-mentioned.

With such a configuration, by using the three-way valve or the four-way valve having the flow rate adjustment zone described above in the refrigerator, each flow rate adjustment range can be widened in the refrigeration cycle for switching a plurality of evaporators.

On the other hand, if the flow rate of the refrigerant 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 is about the same as the evaporation temperature, and the three-way valve and the four-way valve and the evaporator are connected. It is feared that condensation will occur in the part of the machine room in the piping which goes from the machine room into the furnace.

On the other hand, in the above-described configuration, since the primary pressure reduction is performed at the three-way valve and the four-way valve, and the secondary pressure reduction is performed at the capillary tube, the temperature at the three-way valve and the four-way valve outlet can be made higher than the evaporation temperature, and condensation in the machine room part is caused. Can be suppressed, and the effect of preventing the liquid return by the heat exchange between the capillary tube and the return pipe described above and increasing the freezing capacity can also be obtained.

According to the present invention configured as described above, when the fluid such as the refrigerant starts to flow, the fluid can be increased little by little, and the flow rate at the beginning of flowing the fluid can be controlled with high accuracy.

In addition, when used as a three-way valve or a four-way valve, it is possible to form a completely open area, a variable flow rate area, or a completely closed area with a compact and simple configuration. Proper adjustment of the flow rate, prevention of temperature rise in each chamber when the compressor is stopped, prevention of condensation of pipes in the machine room, prevention of liquid return by heat exchange between capillary tubes and return pipes, and improvement of freezing capacity can be achieved.

1A is an internal schematic diagram of the freezer refrigerator of the first embodiment.

1B is a layout view of a refrigerant circuit of the refrigeration refrigerator of the embodiment.

FIG. 2 is a schematic diagram showing a refrigerant circuit of the freezer refrigerator according to the embodiment. FIG.

It is a schematic diagram which looked at the whole valve structure of the same embodiment from upper direction.

It is a schematic diagram which looked at the whole of the valve structure of the same embodiment from the bottom.

It is a schematic diagram which looked at the valve seat and the valve body of the same embodiment from above.

It is a schematic diagram which looked at the valve seat and the valve body of the same embodiment from the bottom.

7 is a plan view illustrating the valve seat and the valve body according to the embodiment.

It is a schematic diagram for demonstrating the adjustment groove | channel of the same embodiment.

9 is a view for explaining the operation of the valve structure and the flow of the refrigerant in the embodiment.

10 is experimental data in which a valve structure in the same embodiment is compared with a conventional valve structure.

11 is a Moriel diagram of a refrigeration cycle in the embodiment.

It is an internal schematic diagram of the refrigeration refrigerator of 2nd Embodiment.

12B is a layout view of a refrigerant circuit of the freezer refrigerator according to the second embodiment.

It is a schematic diagram which shows the refrigerant circuit of the refrigeration refrigerator of 2nd Embodiment.

It is a top view which shows the valve seat and the valve body of the same embodiment.

FIG. 19 is a view for explaining the operation of the valve structure and the flow of refrigerant in the embodiment. FIG.

20A to 20C are schematic views for explaining the positional change of the outlet.

21A to 21C are schematic diagrams for explaining the variation of the valve opening degree with the change of 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 outflow port and adjustment groove | channel in 3rd Embodiment.

It is a figure which shows the flow volume change in 3rd Embodiment.

<1st 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 which concerns on this embodiment is used for the refrigerator refrigerator 100, for example. In addition, this valve structure 20 is not limited to a refrigeration refrigerator and may be used for the fluid circuit which supplies a fluid in multiple places.

First, the refrigerator refrigerator 100 of this embodiment is demonstrated.

As shown in FIGS. 1A to 2, the freezer refrigerator 100 includes a refrigerating chamber 11, a freezing chamber 12 and a temperature changing chamber 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, when distinguishing these, it is called the refrigerator evaporator 231, the freezer compartment evaporator 232, the variable temperature room evaporator 233), and the plurality of inlet sides provided in each of the inlet sides of each evaporator 231-233. The refrigerant circuit 200 having the decompression means 241 to 243 (hereinafter, referred to as the decompression means 241 for the refrigerating chamber, the decompression means 242 for the freezer compartment, and the decompression means 243 for the temperature room chamber) is provided. Equipped.

Here, the evaporator 233 for a temperature change room is provided in the inlet side of the freezer evaporator 232, and the check valve 25 is provided in the outlet side of the freezer compartment evaporator 232. As shown in FIG. The temperature chamber evaporator 233 may be provided on the outlet side of the freezer compartment evaporator 232 or may be provided in parallel with the freezer compartment evaporator 232.

Refrigeration capillary tubes 241 are provided in series at the inlet side of the refrigerating chamber evaporator 231, and refrigeration capillary tubes 242 are provided at the inlet side of the freezer compartment evaporator 232 as freezer compartment decompression means in series. On the inlet side of the chamber evaporator 233, a capillary tube 243 for alternating temperature is provided in series as a pressure reducing means for the chamber.

These capillary tubes 241 to 243 are provided in parallel with each other, and in this case, the chamber evaporator 233 is provided at the inlet side of the freezer compartment evaporator 232, whereby the chamber chamber evaporator 233 and the freezer compartment evaporator 232 are provided. ) And the outlet side of the freezing chamber pressure reducing means 242, and the refrigerant flowing out of the freezing chamber pressure reducing means 242 to the freezer compartment evaporator 232 without flowing to the temperature chamber evaporator 233 I'm trying to.

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 thermally connected with the

capillary tubes

241, 242, 243 described above. And a low temperature refrigerant flowing through the return pipe (L) and a high temperature refrigerant flowing through the capillary tubes (241, 242, 243). Specifically, the return pipe L and the

capillary tubes

241, 242, 243 are connected by soldering or the like, for example.

The

capillary tubes

241, 242, and 243 described above, together with the expansion valve V having the valve structure 20 described later, reduce the high pressure refrigerant flowing out of the condenser 22 into a low pressure refrigerant Z. Consists of.

Next, the valve structure 20 will be described.

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

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

Specifically, this valve structure 20 is provided with at least the valve seat 3 and the valve body 4, as shown to FIG. 3 and FIG. 4, Here, the drive mechanism which rotates the valve body 4 is carried out. (5) and the casing 6 in which the refrigerant | coolant inflow space S into which the valve seat 3 and the valve body 4 are accommodated, and in which the refrigerant | coolant flows is formed is further provided.

The drive mechanism 5 rotates in conjunction with the motor 51 including the stator 511 and the rotor 512 provided inside the stator 511 and the rotor 512 to drive the driving force of the motor 51. It has an output gear 52 for outputting.

As shown in FIG. 4, the casing 6 includes a hollow casing main body 61 having an opening formed in a bottom surface thereof, and a lid for closing the opening to form the refrigerant inflow space S together with the casing main body 61. It has a sieve (62).

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

The cover body 62 has a flat plate shape, and communicates with the coolant inflow space S so that an inlet 621 for introducing a coolant into the coolant inflow space S is formed. Diameter) of 35 mm or less. The inlet 621 is connected to the outlet side of the condenser 22 by the inlet pipe 7, whereby the refrigerant flowing out of the condenser 22 flows into the refrigerant inlet space S.

3 to 6, the valve seat 3 is inserted into the through hole formed in the cover body 62 described above without a gap, and communicates with the coolant inflow space S so as to communicate with the coolant inflow space S. An outlet port 3a for flowing out the refrigerant from the outlet is formed. Moreover, the through hole 3x in which the rotating shaft X of the valve body 4 mentioned later is inserted in the center of this valve seat 3 is formed.

The valve seat 3 of the present embodiment has the upper portion 31 having the same size as the through hole formed in the lid 62 so that the valve seat 3 can be easily mounted on the lid 62. By making the shape larger than 31, when the upper part 31 is inserted into the through hole of the lid body 62 from below, the end portion formed between the upper portion 31 and the lower portion 32 has a lower surface of the lid body 62. FIG. To meet

Specifically, the valve seat 3 has a disk shape having a diameter dimension (diameter) of 16 mm or less, and the upper surface 31 of the valve seat 3 penetrates in the thickness direction, for example, a diameter of 0.8 on the upper surface thereof. The outlet 3a of mm is formed.

In addition, the lower portion 32 communicates with the outlet 3a and is provided with an outlet pipe hole 3s having a diameter larger than that of the outlet port 3a, and the outlet pipe 3s is formed in the outlet pipe hole 3s. 8) is configured to be inserted. By this outlet pipe 8, the outlet port 3a is connected to the inlet side of the evaporators 231 to 233, and any one of the evaporator 231 which has flowed out of the refrigerant inlet space S through the outlet port 3a. ~ 233)

As shown in FIGS. 3 to 6, the valve structure 20 of the present embodiment includes two valve seats 3 (hereinafter, these valve seats 3 are the first valve seat 3A and the second valve seat). (3B)), the first valve seat 3A is attached to one of the two through holes formed in the lid 62, and the second valve seat 3B is attached to the other. Here, the 1st valve seat 3A and the 2nd valve seat 3B are disk shapes of the same diameter dimension mutually.

Two outlets 3a (hereinafter, these outlets 3a are referred to as first outlet 3a1 and second outlet 3a2) are formed in the first valve seat 3A. In the present embodiment, the first outlet 3a1 is connected to the inlet side of the refrigerating chamber evaporator 231 by the first outlet pipe 81, and the second outlet 3a2 is the second outlet pipe 82. Is connected to the inlet side of the freezer evaporator 232.

The said 1st outlet 3a1 and the said 2nd outlet 3a2 are mutually the same diameter dimension, and are arrange | positioned along the circumferential direction around the center of 3 A of valve seats. That is, a 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 equal distances. have.

One outlet 3a (hereinafter, this outlet 3a is called 3rd outlet 3a3) is formed in the 2nd valve seat 3B. In the present embodiment, the third outlet 3a3 is connected to the inlet side of the evaporator 233 for the temperature change chamber by the third outlet pipe 83.

In addition, the 3rd outlet 3a3 is the same diameter dimension as the 1st outlet 3a1 and the 2nd outlet 3a2, and the distance from the center of the 2nd valve seat 3B to the center of the 3rd outlet 3a3 is And a distance 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 rotatably provided 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, and it is an outlet port with rotation The adjustment groove 4a which changes the area which overlaps with 3a is formed.

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

As shown in FIGS. 3-6, this valve body 4 is provided above the valve seat 3, and rotates around the center axis of the valve seat 3, Here, the rotating shaft X penetrates through it. 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 rotary shaft X is provided on the manual gear 9. In more detail, the manual gear 9 is provided with the some convex part 91, The upper surface of the valve body 4 is formed with the some concave part 4y engaging with the said convex part 91, have. Thereby, while inserting the rotating shaft X into the through-hole 4x, the convex part 91 engages with the recessed part 4y, and the valve body 4 is a manual gear by the drive force of the drive mechanism 5 by this. Rotate in conjunction with (9).

In the present embodiment, as described above, the first valve body 4A and the second valve body 4B are provided corresponding to each of the first valve seat 3A and the second valve seat 3B. Two manual gears 9 provided in each of the first valve body 4A and the second valve body 4B mesh with the common output gear 52. As a result, the first valve body 4A and the second valve body 4B rotate together with each other.

The valve body 4 of this embodiment is comprised from the flat part upper part 41 and the flat part lower part 42 which penetrated in the thickness direction, and the above-mentioned adjustment groove 4a was formed. The upper part 41 is a disk-like thing which overlaps the whole of the lower part 42, for example, and the lower part 42 forms the said adjustment groove 4a in the disk. The valve body 4 of this embodiment is a disk shape whose diameter dimension is 12 mm or less, for example, and the adjustment groove 4a is formed so that it may extend along a circumferential direction.

As shown in FIG. 7, the adjustment groove 4a is formed so that the width dimension may change along the circumferential direction, and here the tip part 4b which starts to overlap with the outlet port 3a by rotation of the valve body 4 is shown. ), The width dimension is gradually increased toward the rear end portion 4c on the opposite side. This adjustment groove 4a is comprised so that it may enter from the front end part 4b to the rear end part 4c within 60 degrees centering on the rotating shaft X of the valve body 4. As shown in FIG.

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

Specifically, the tip portion 4b is shaped to have a width dimension of 0.2 mm or more. In this embodiment, the 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 trace P of the front-end | tip 4x.

In addition, as shown in Fig. 7, the rear end portion 4c of the adjustment groove 4a is further formed with the rear end portion 4c continuously and overlaps with the entirety of the outlet port 3a. 4d) is formed. This fully opening groove | channel 4d forms notched the lower part 42 of the valve body 4 along the circumferential direction from the rear end 4c toward the side opposite to the rotation direction of the valve body 4. It is.

In this embodiment, as shown in FIG. 7 and FIG. 8, the center O of the outlet port 3a is displaced from the rotational trajectory of the tip portion 4b of the adjustment groove 4a.

In more detail, here, the tip 4x of the adjustment groove 4a from the imaginary circle Z centering on the rotation axis X of the valve body 4 passing through the center O of the outlet port 3a. The rotational trajectory P of is displaced inward.

By the way, although the refrigeration refrigerator 100 of this embodiment is equipped with the filter which is not shown in the upstream of the valve structure 20, the foreign material, such as a contaminant smaller than the mesh size of a filter, passes through a filter, and it is accompanied with a refrigerant | coolant. There is a possibility of flowing into the refrigerant inflow space S.

Then, in the valve body 4A shown in FIG. 7, for example, when a foreign material enters the front-end | tip part 4b of the adjustment groove 4a, a foreign material cannot be scraped only by the rotation operation of the valve body 4, There exists a possibility of depositing in the front-end | tip part 4b of the adjustment groove 4a.

Therefore, the width dimension of the part which overlaps with the said outlet port 3a in the said tip part 4b is set so that the foreign material which flowed in into the said tip part 4b may flow out from the outlet port 3a with a refrigerant | coolant. This width dimension is set based on the mesh size of the filter so that foreign matter which has passed through the filter flows out from the outlet port 3a.

In this embodiment, as shown in FIG. 8, at least the front end 4x of the adjustment groove 4a overlaps the outlet 3a, the front end part is made into 0.1 mm or more of radius OL of the front end part 4b. The width dimension of the part which overlaps with the outlet port 3a in (4b) is made larger than a foreign material.

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

As shown in FIG. 9, the valve structure 20 of the present embodiment rotates the first valve body 4A and the second valve body 4B in conjunction with these first valve bodies 4A and According to the rotation angle of the 2nd valve body 4B, it is comprised so that a fully closed area | region, a fully open area | region, and three flow volume variable regions are 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.

A fully open area | region is an area | region in which either the 1st outflow port 3a1 or the 2nd outflow port 3a2 and the 3rd outflow port 3a3 become a fully open state simultaneously. The fully open area | region of this embodiment is an area | region in which the 1st outflow port 3a1 and the 3rd outflow port 3a3 become a fully open state simultaneously, in other words, the 1st valve body 4A in the whole 1st outflow port 3a1. (4d) of the fully open groove | channel of (), and the fully open groove | channel 4d of the 2nd valve body 4B overlap with the whole 3rd outlet port 3a3.

The flow rate variable region is a region in which the flow rate of the refrigerant flowing out of each of the outlets 3a1 to 3a3 can be adjusted independently, that is, the first outlet 3a1, the second outlet 3a2, or the third outlet 3a3. The adjustment groove 4a overlaps any one of them, and the other two are regions to be completely closed. The flow rate variable region is provided for each of the outlets 3a1 to 3a3.

In the flow rate variable region of the present embodiment, the flow rate of the refrigerant flowing out of the first outlet 3a1 and the second outlet 3a2 gradually increases, and the flow rate of the refrigerant flowing out of the third outlet 3a3 gradually decreases. Consists of.

As shown in FIG. 9, any one of the first outlet 3a1, the second outlet 3a2, or the third outlet 3a3 is completely open except for the completely closed region, the fully open region, and the variable flow region described above. It is a state and the area | region in which the other two become a fully closed state is provided. In other words, this area has a fully open groove 4d overlapping any one of the first outlet 3a1, the second outlet 3a2, or the third outlet 3a3, and the other two It is an enclosed area.

In addition, between the flow rate variable region formed with respect to the third outlet 3a3 and the flow rate variable region formed with respect to the second outlet 3a2, the first outlet 3a1, the second outlet 3a2, and the second outlet are provided as spare sections. The area | region in which all 3 outflow openings 3a3 become a fully closed state is provided.

In the refrigerator refrigerator 100 of this embodiment comprised in this way, since the center O of the outlet port 3a is displaced from the rotation trace P of the front-end | tip part 4b of the adjustment groove 4a, the valve body 4 By rotating, the tip 4b of the adjusting groove 4a starts to overlap from the direction immediately away from the front with respect to the outlet port 3a. As a result, as can be seen from the design data in FIG. 10, the area where the tip portion 4b of the adjusting groove 4a overlaps with the outlet port 3a when the coolant starts to flow can be made smaller than in the related art. As a result, the coolant flow rate can be increased little by little when the coolant starts to flow, and the flow rate at the start of flowing the fluid can be controlled with high accuracy.

Moreover, since the valve body 4 rotates and the front end 4x of the adjustment groove 4a overlaps with the outlet port 3a, since the magnitude | size of the overlapping part is made larger than the foreign material to be assumed, the adjustment groove ( Even if foreign matter has flowed into the distal end portion 4b of 4a, the foreign matter can flow out from the outlet port 3a together with the refrigerant.

In addition, since the three outlets 3a1 to 3a3 can be completely closed at the same time in a completely closed state, a high temperature refrigerant is supplied to each evaporator 231 to 233 from the condenser 22 side when the compressor 21 is stopped. Inflow can be prevented and the temperature of each chamber 11-13 can be prevented from rising by the inflow of a refrigerant | coolant at the time of the compressor 21 stop.

Further, since the two outlets 3a1 and the outlets 3a3 can be completely opened at the same time in a fully open state, the refrigerant is stored in the refrigerating chamber 11, the freezing chamber 12, and the temperature changing chamber ( 13 can be supplied to three rooms, and the cooling rate of each room can be improved in overload, such as a pull-down.

In addition, since it is possible to set the flow rate variable region in which the flow rate alone can be adjusted for each of the three outlets 3a1 to 3a3, the refrigerant is appropriately flown according to the load at the time of cooling each of the chambers 11 to 13. I can adjust it.

Fig. 11 shows a Moriel diagram of the refrigerating circuit in the present embodiment. In this embodiment, since the pressure reduction mechanism Z has the expansion valve V and the

capillary tubes

241, 242, and 243, the refrigerant flowing out of the condenser 22 is used to expand the valve V and the

capillary tubes

241, 242, 243. Can be depressurized step by step.

As a result, as shown in FIG. 11, the refrigerant flowing through the

capillary tubes

241, 242, and 243 from the expansion valve V can be made hotter than the refrigerant before flowing into the

evaporators

231, 232, and 233. V) Pipe condensation in the machine room part of the

capillary tubes

241, 242, and 243 from the outlet to the furnace can be prevented.

In addition, since the refrigerant return pipe L and the

capillary tubes

241, 242, and 243 are thermally connected by, for example, soldering or the like, the refrigerant returned from the

evaporators

231, 232, and 233 to the compressor 21, and the expansion are expanded. Heat exchange takes place between the refrigerant from the valve V and through the

capillary tubes

241, 242, 243 towards the evaporator.

Thereby, the liquid refrigerant which has 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, thereby allowing the liquid refrigerant to the compressor 21. The return can be prevented.

As shown in FIG. 11, the refrigerant in the

capillaries

241, 242, and 243 is cooled during the reduced pressure, whereby the refrigerating capacity can be increased, and the efficiency of the refrigeration cycle can be improved.

<2nd 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. Moreover, the valve structure 20 in 2nd Embodiment is provided in the expansion valve V similarly to the said 1st Embodiment, and this expansion valve V and the

capillary tubes

241 and 242 are a condenser. The pressure reduction mechanism Z which changes the high pressure refrigerant | coolant from 22 into a low pressure refrigerant | coolant is comprised.

The valve structure 20 which concerns on this embodiment is used for the refrigerator refrigerator 100, for example as shown to FIG. 12A-FIG. The freezer refrigerator 100 of the present embodiment differs from the freezer refrigerator 100 of the first embodiment in that the refrigerator compartment 100 does not include the temperature changing room, the evaporator for the temperature changing room, and the pressure reducing means for the temperature changing room, but in other respects, the first embodiment is the first embodiment. Since the configuration is the same as, detailed description thereof will be omitted.

The valve structure 20 of the present embodiment is a so-called three-way valve for flowing refrigerant into one or both of the refrigerating chamber evaporator 231 or the freezing chamber evaporator 232, and flows to each of the

evaporators

231 and 232. It is comprised so that adjustment of a refrigerant flow volume is possible.

Specifically, this valve structure 20 is provided with at least the valve seat 3 and the valve body 4, as shown to FIG. 14 and FIG. 15, Here, the drive mechanism which rotates the valve body 4 is carried out. (5) and a casing (6) in which the valve seat (3) and the valve body (4) are accommodated, and a coolant inflow space into which a coolant flows is formed.

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 each of these valve seats 3, respectively. Although two valve bodies 4 (the first valve body 4A and the second valve body 4B) were provided, the valve structure 20 of the present embodiment includes the valve seat 3 and the valve body ( 4) is provided one by one.

The valve seat 3 of the present embodiment has the same configuration as the first valve seat 3A of the first embodiment, and as shown in FIG. 16, two outlets 3a (hereinafter, these outlets 3a) are provided. The first outlet 3a1 and the 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 the first outlet pipe 81, and the second outlet 3a2 is the second outlet pipe 82. Is connected to the inlet side of the freezer evaporator 232. In addition, although the dimension of the valve seat 3, the diameter dimension of each outlet 3a1, 3a2, and the distance from the center of the valve seat 3 to the center of each outlet 3a1, 3a2 are the same as that of 1st Embodiment, Since the operation | movement of the valve structure 20 differs, arrangement | positioning of each outlet 3a1, 3a2 differs from 1st Embodiment.

The valve body 4 is basically the same structure as the valve body 4 of 1st Embodiment. That is, the valve body 4 is rotatably provided 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. As shown in FIG. 17 and FIG. 18, the valve body 4 is completely open to overlap with the adjustment groove 4a in which the area overlapping with the outlet port 3a changes with the rotation and the entire outlet port 3a. A groove 4d (hereinafter also referred to as a first fully open groove 4d) is formed.

Similarly to the first embodiment, the adjusting groove 4a is configured such that the front end 4b to the rear end 4c fall within 60 degrees around the rotational axis X of the valve body 4.

On the other hand, the first full opening groove 4d is angled from the first embodiment in order to bring the two outlets 3a1 and the outlet 3a2 into the fully open state at the same time by using one valve body 4. It is composed widely.

Moreover, the width dimension of the part which displaces the center O of the outlet port 3a from the rotational trajectory of the front-end | tip part 4b of the adjustment groove 4a, and overlaps with the outflow port 3a in the front-end | tip part 4b. Is set in view of the size of the foreign matter that can flow into the tip portion 4b, as in the first embodiment.

And the valve body 4 of this embodiment overlaps with the whole outflow opening 3a1 separately from the said adjustment groove 4a and the 1st full opening groove 4d, as shown to FIG. 17 and FIG. The second full opening groove 4f is formed, which is different from the valve body of the first embodiment.

The second full opening groove 4f is formed by digging the lower portion 42 of the valve body 4 in the circumferential direction, and is provided so as not to be continuous with the first full opening groove 4d and the adjustment groove 4a. have. This 2nd full opening groove | channel 4f is comprised so that it may overlap with the whole outflow opening 3a1.

In more detail, when the 1st fully open groove 4d overlaps with the whole one outlet 3a, the said 2nd fully open groove 4f will be made into the whole of the other outlet 3a. It is formed in the position where it overlaps.

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 here the second fully open groove ( The rotary shaft X of the valve body 4 is arranged between 4f) and the first full opening groove 4d.

As shown in FIG. 19, the valve structure 20 of this embodiment is a fully closed area | region, a fully open area | region, according to the rotation angle of this valve body 4 by rotating the valve body 4, and Two flow rate variable regions are formed.

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

A fully open area | region is an area | region in which the 1st outflow port 3a1 and the 2nd outflow port 3a2 become a fully open state simultaneously, in other words, the 1st full opening groove | channel 4d or the 1st whole opening 3a1 whole is made. 2 A region in which one of the fully open grooves 4f overlaps and the other of the first fully open grooves 4d or the second fully open grooves 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 of each of the outlets 3a1 and 3a2 can be independently adjusted, that is, in one of the first outlet 3a1 or the second outlet 3a2, the adjustment groove 4a is provided. Along with this overlap, the other side is an area that is completely closed. This flow rate variable region is provided for each of the outlets 3a1 and 3a2.

In the flow rate variable region of the present embodiment, the flow rate of the refrigerant flowing out from the first outlet 3a1 and the second outlet 3a2 is gradually increased.

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

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

As a result, by setting it as a fully open area | region, a refrigerant | coolant can be sent to both the refrigerating chamber evaporator 231 and the freezing chamber evaporator 232, and the cooling rate in overload at the time of pulldown etc. can be improved.

Moreover, by setting it as a fully closed area | region, it can prevent that a high temperature refrigerant | coolant flows into each

evaporator

231, 232 from the condenser 22 side at the time of the compressor 21 stop, and it cools at the time of the compressor 21 stop. It can prevent that the temperature of each

chamber

11 and 12 raises by inflow.

Moreover, by setting it as a flow volume variable area | region, it can adjust a refrigerant | coolant to appropriate flow volume according to the load at the time of each cooling of each

chamber

11 and 12.

Further, since the rotational trajectory of the tip 4b of the adjusting groove 4a is displaced from the center O of the outlet port 3a, the tip 4b of the adjusting groove 4a is rotated by rotating the valve body 4. Starts to overlap from the direction away from the front immediately with respect to the outlet port 3a.

As a result, when the coolant starts to flow, the area where the tip portion 4b of the adjusting groove 4a overlaps with the outlet port 3a is made smaller than in the related art, and the coolant flow rate can be increased little by little, and when the fluid starts to flow. The flow rate of can be controlled with high accuracy.

On the other hand, in the conventional structure in which the tip of the adjusting groove passes through the center of the outlet, if the flow rate cannot be adjusted with high precision and the flow rate is changed by the fully open groove without using the adjusting groove, the accuracy is remarkably high. Since it falls, it cannot be said that flow rate can be controlled.

Moreover, the foreign material, such as the contaminant which flowed in the tip part 4b of the adjustment groove 4a and overlaps with the outlet port 3a in the front end part 4b, flows from the outlet port 3a with a refrigerant | coolant. Since it is set to go out, even if a foreign material flowed into the front-end | tip part 4b of the adjustment groove 4a, it can flow out from the outlet port 3a with a refrigerant | coolant.

In addition, as in the first embodiment, the expansion valve V and the

capillary tubes

241 and 242 are provided as the pressure reducing mechanism Z, thereby allowing the liquid refrigerant condensed in the condenser 22 to expand the expansion valve V and the capillary tube ( 241, 242 may be reduced in stages.

Similarly to the first embodiment, the effect thereof can be made to be higher than the evaporation temperature of the refrigerant flowing out of the expansion valve V, so that the pipe in the machine room part of the

capillary tubes

241 and 242 can be used. Condensation can be prevented.

In addition, since the

capillary tubes

241 and 242 and the refrigerant return pipe L are thermally connected, for example, by soldering or the like, as in the first embodiment, the liquid refrigerant returned from the

evaporators

231 and 232 to the compressor is heated. And the effect of increasing the refrigerating capacity by cooling the refrigerant directed from the expansion valve V to the

evaporators

231 and 232 through the

capillary tubes

241 and 242.

In addition, 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. It is possible to make the pipe diameter of the outflow pipe 8 the same, or to make the pipe diameter 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 adjusting groove is displaced from the imaginary circle so that the tip of the adjusting groove overlaps the outlet, but the tip of the adjusting groove does not overlap the outlet, A portion other than the tip may overlap the outlet.

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 which concerns on 3rd Embodiment, this point is demonstrated in detail below.

First, in the outlet 3a of 1st Embodiment or 2nd Embodiment, as shown in FIG. 8, the rotation trace P of the front-end | tip 4x of the adjustment groove 4a is in contact with the outer edge of the outlet 3a. It is formed to.

By the way, since there is a deviation at the time of processing or assembly at the position of the outlet 3a, ie, the position of the center O of the outlet 3a, as shown in FIG. 20A, for example, the outlet in each said embodiment ( When the center O of 3a) is the reference position, the actual center O may deviate radially outward or radially inward (for example, 0.15 mm) as shown in FIG. 20B or 20C compared to the reference position. have.

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

Moreover, when the center O of the outlet port 3a deviates radially outward from a reference position, if it is the structure of the said 1st Embodiment and the said 2nd Embodiment, the adjustment groove 4a at the time of starting to flow a refrigerant | coolant will flow. The area where the tip portion 4b and the outlet port 3a overlap with each other becomes too small, and as shown in FIG. 22, even if the valve body 4 is rotated when the coolant starts to flow, the flow rate hardly increases.

In this regard, when the outlet port 3a deviates outward in the radial direction, there is a possibility that a trouble such as uncooling that the coolant is insufficient because the refrigerant does not flow at the same rotation angle as when the outlet port 3a is at the reference position is caused. There is a fear that the basic performance, such as the increase in the amount of power consumption, even if there is no, or even not cold.

Therefore, in the valve structure 20 which concerns on this embodiment, as shown in FIG. 23, the outlet port 3a of a reference position was arrange | positioned inside radial direction from each said embodiment. More specifically, the rotational trace P of the tip 4x of the adjustment groove 4a is located on the rotational axis X side of the valve body 4 rather than the center O of the outlet 3a on the outlet 3a. The outlet 3a is arrange | positioned so that it may overlap with.

Thus, by arrange | positioning the outlet 3a of a reference position in radial direction inner side than each said embodiment, as shown in FIG. 24, even if the outlet 3a deviates outward in the radial direction, ie, the adjustment groove 4a, Even when the area where the outlet port 3a overlaps becomes the lower limit, the area where the tip portion 4b of the adjustment groove 4a overlaps with the outlet port 3a can be prevented from becoming too small when the refrigerant starts to flow. In addition, it is possible to avoid the damage of the basic performance such as the trouble described above and an increase in the amount of power consumption.

On the other hand, in the structure of this embodiment, when the exit port 3a deviates inwardly in the radial direction as shown to FIG. 21C by the deviation at the time of processing or assembly, the front-end | tip part 4b of the adjustment groove 4a, and the exit port 3a ) And the overlapping area when the valve body 4 is rotated after the start of overlapping becomes larger than the configuration of the first embodiment or the second embodiment, and the flow rate increases all at once, so that in the small flow range The flow rate control may become difficult.

In view of this point, the adjusting groove 4a of the present embodiment has a shape different from that of the first embodiment and the second embodiment, and specifically, as shown in FIG. It has a narrow part 4g formed toward the edge part 4c side, and the wide part 4h formed from the narrow part 4g toward the rear end part 4c side.

In addition, in the point where the shape of the adjustment groove 4a is asymmetrical with respect to the rotational track P of the tip 4x, and the point 4b is partially circular, it is common to 1st Embodiment and 2nd Embodiment. have.

The narrow portion 4g is shaped to have a smaller width dimension than the wider portion 4h, and is formed here so that the width dimension does not change along the circumferential direction, that is, the width dimension becomes constant along the circumferential direction. Specifically, the narrow portion 4g has a pair of opposing inner edges 4g1 parallel to each other, and the width dimension thereof is the same as the diameter of the tip portion 4b constituting the partially circular shape (for example, the minimum that can be machined). Dimensions). All of these internal edges 4g1 extend in a tangential direction from both ends of the front end part 4b, and are parallel to the rotation trace P of the front end 4x.

The wide part 4h is formed so that the width dimension may change along the circumferential direction, specifically, the shape where the width dimension gradually increases toward the rear end part 4c, in other words, from the narrow part 4g to the rear end part 4c. It is a shape spreading toward).

More specifically, the outer edge 4h1 of the widening portion 4h is formed so as to move outward from the rotational trajectory P of the tip 4x, and the inner edge 4h2 of the widening portion 4h is the tip ( It is formed so as to be close to the rotation trajectory P of 4x). As a result, the outer edge 4h1 and the inner edge 4h2 of the widened portion 4h are asymmetric with respect to the rotational trajectory P of the tip 4x. In addition, the internal combustion 4h2 may be parallel to the rotation trajectory P of the tip 4x.

In this way, even when the outlet port 3a is repositioned in the radial direction by making the narrow portion 4g formed from the tip portion 4b toward the rear end portion 4c to have a shape in which the width dimension is constant along the circumferential direction Since the front end part 4b of the adjustment groove 4a and the outlet port 3a start to overlap, the increase of the overlapping area at the time of rotating the valve body 4 can be suppressed.

For this reason, even if the area where the adjustment groove 4a and the outlet port 3a overlap is at the upper limit, it is possible to prevent the flow rate from increasing all at once when the refrigerant starts to flow, and thus the adjustment groove 4a in the minute flow range. ) And flow rate control can be minimized with the influence of the variation during processing or assembling of the outlet port 3a.

Moreover, since the narrow part 4g is formed in parallel with the rotation trace P of the front-end | tip 4x, even if the area which the adjustment groove 4a and the outflow opening 3a overlap becomes an upper limit (maximum), When the refrigerant starts to flow, the flow rate can be prevented from increasing all at once.

Moreover, since the outer edge 4h1 of the wide part 4h is formed so that it may move away from the rotational trace P of the front end 4x, the flow volume can gradually increase after a coolant starts to flow to some extent, and it will adjust. When the entirety of the grooves 4a continues to pass through the outlet port 3a and the outlet port 3a is fully opened, the flow rate can be prevented from increasing rapidly.

In addition, since the inner edge of the wide portion is formed so as to be close to the rotational trajectory of the tip portion, after the coolant starts to flow to some extent, the flow rate can be prevented from increasing at once, and the flow rate can be gradually increased, so that the flow path area generated in the narrow portion. The variation in ratio can be reduced.

As described above, in the valve structure 20 of the present embodiment, as shown in FIG. 24, even when the outlet port 3a is positioned outward in the radial direction, the flow rate at the start of flowing the refrigerant can be ensured. In addition, even when the outlet port 3a is positioned in the radially outer side, it is possible to prevent the flow rate from increasing at the same time when the coolant starts to flow.

In addition, in 3rd Embodiment, although the aspect which arrange | positioned the outlet 3a of the reference position in radial direction inner side than the said 1st Embodiment or the said 2nd Embodiment was demonstrated, the adjustment groove 4a of the reference position was described above. Even if it arrange | positions radially outer side rather than 1st Embodiment or the said 2nd Embodiment, the effect similar to 3rd Embodiment can be acquired.

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

Claims

Compressors, condensers, evaporators;

And a valve configured to transfer 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 that is movable relative to the outlet and adjusts the opening degree of the outlet.

The valve body includes an adjustment groove for adjusting the opening of the outlet,

The center of the outlet is provided on the outside of the movement trajectory of the end center of the adjustment groove.
The method of claim 1,

The valve body is provided rotatably with respect to the valve seat,

When the adjustment groove is disposed to overlap with the outlet by the rotation of the valve body, the outlet is provided in communication with the evaporator,

And the overlapping area of the adjusting groove is irregularly increased with respect to the rotation angle of the adjusting groove when the adjusting groove is rotated along the movement trajectory and starts to overlap with the outlet.
The method of claim 2,

The adjustment groove is provided to open in the opening direction of the outlet, extend in the circumferential direction of the rotation axis of the valve body,

And an opening part provided at the end to open in a direction opposite to the rotation direction of the valve body.
The method of claim 3, wherein

The adjusting groove is provided so as to increase in width in the direction of the opening portion from the end.
The method of claim 3, wherein

And the adjustment groove has a first region having a constant width in the direction of the opening from the end portion and a second region having a width extending from the first region toward the opening.
The method of claim 5, wherein

The width of the first region is provided in parallel with the movement trajectory of the end center.
The method of claim 5, wherein

The outer circumferential surface of the second region is formed to move away from the movement trajectory of the end center in the opening direction.
The method of claim 5, wherein

The inner circumferential surface and the outer circumferential surface of the second region extend asymmetrically in the direction of the opening.
The method of claim 2,

The center of the said outlet port is provided in the radially outer side with respect to the rotating shaft of the said valve body rather than the movement trace of the center of the edge part of the said adjustment groove.
The method of claim 1,

And a filter disposed between the condenser and the valve and having a plurality of through holes.

When the end of the adjustment groove is disposed to overlap the outlet, the overlapping area when the end is disposed to overlap with the outlet is greater than the area of any one of the plurality of transmission holes.
The method of claim 2,

The adjustment groove is a refrigerator disposed in an area within 60 degrees in the radial direction about the axis of rotation of the valve body.
The method of claim 2,

Further comprising a second evaporator,

The valve delivers the refrigerant flowing out of the condenser to the first evaporator and the second evaporator,

A second valve seat having a second outlet port through which refrigerant flows into the second evaporator and a second valve rotatably provided with respect to the second valve seat and having a second adjustment groove for adjusting the opening degree of the second outlet port; More sieves,

When the second adjustment groove is arranged to overlap the second outlet by the rotation of the second valve body, the second outlet is provided so as to be in communication with the second evaporator,

The center of the second outlet is provided on the outside of the movement trajectory of the end center of the second adjustment groove.
The method of claim 12,

The valve further includes a drive gear coupled to the motor and the rotating shaft of the motor,

And the first valve body and the second valve body are engaged with the driving gear, respectively, and rotated in association with the rotation of the driving gear.
The method of claim 2,

Further comprising a second evaporator,

The valve delivers the refrigerant flowing out of the condenser to the first evaporator and the second evaporator,

The valve seat further includes a second outlet port through which refrigerant flows into the second evaporator,

The adjustment groove adjusts the opening degree of the second outlet,

The first outlet and the second outlet are opened when the valve body is rotated at a first rotational angle;

When the valve body is rotated at a second rotational angle, one of the first outlet port and the second outlet port is disposed to overlap the adjustment groove, and the other is closed.

And the first outlet and the second outlet are closed when the valve body is rotated at a third rotational angle.
The method of claim 13,

When the drive gear is rotated at the first rotation angle,

The valve body and the second valve body are provided such that the first outlet port and the second outlet port are opened, respectively.

When the drive gear is rotated at the second rotation angle,

The valve body is provided so that the first outlet port overlaps with the adjustment groove, and the second valve body is provided so that the second outlet port is closed.

When the drive gear is rotated at a third rotational angle,

The valve body and the second valve body are provided such that the first outlet port and the second outlet port are closed, respectively.

When the drive gear is rotated at the fourth rotation angle,

And the valve body is provided such that the first outlet port is closed, and the second valve body is provided such that the second adjustment groove of the second valve body overlaps with the second outlet port.