JP6585581B2 - Motorized valve and cooling system using motorized valve - Google Patents

Description

  The present invention relates to an electric valve used as a flow control valve for a freezer or a refrigerator, and a cooling system using the electric valve.

  Conventionally, in a cooling system such as a home refrigerator, as shown in FIG. 17, a refrigerant supplied to a refrigerator for refrigerator (R. Evap) and a refrigerator for freezer (F. Evap) is supplied with a three-way valve (3-way). There is known one that employs a method of switching according to (valve). According to this cooling system, temperature control can be performed by alternately cooling the refrigerator compartment and the freezer compartment.

  By the way, in this cooling system, the refrigerant supplied to the refrigerator for the refrigerator compartment (R. Evap) and the refrigerator for the freezer compartment (F. Evap) is expanded by the capillary tube (C. Tube). As described above, when the capillary tube (C. Tube) is used, it is difficult to finely control the temperature of the refrigerant because the throttle amount of the refrigerant cannot be freely adjusted like an electronic expansion valve. It becomes difficult to cool down and save energy when the temperature is stable.

  Therefore, a cooling system in which the capillary tube (C. Tube) is replaced with an electronic expansion valve (for example, see Patent Document 1) has been put into practical use in order to improve the temperature control capability and improve the energy saving performance when the temperature is stable. .

JP 2004-263725 A

  However, in the cooling system shown in FIG. 17, when the capillary tube (C. Tube) is replaced with the electronic expansion valve described above, fine temperature control becomes possible, and appropriate temperature management becomes possible. Thus, two electronic expansion valves are used in one cooling system, and a space for installing the electronic expansion valves is required. Furthermore, the electronic expansion valve has a problem that the cost is increased. Moreover, in order to operate two electronic expansion valves, the electric power for that is also required.

  An object of the present invention is to provide a motor-operated valve and a motor-operated valve that can perform temperature control with higher accuracy than the indoor temperature control using a capillary tube in a cooling system, and can suppress power consumption without expanding the installation space of the expansion valve. It is to provide a cooling system used.

The motor operated valve of the present invention is
An electric valve that controls a throttle flow rate by rotating a single valve element disposed opposite to a valve seat surface around an axis,
The valve seat surface is formed with a first groove and a second groove that extend in an arc shape in the same direction as the rotation direction of the valve body, and the groove width gradually changes.
On the valve seat surface side of the valve body, a main valve portion is disposed that communicates the first inlet port and the first outlet port communicating with the first concave groove via the first concave groove,
A communication groove that extends in a circular arc shape in the same direction as the rotation direction of the valve body and communicates with the second inlet port and the second outlet port that communicates with the second concave groove on the seal surface of the main valve portion. Is formed.

  As described above, the first valve groove and the second groove are formed on the valve seat surface, and the main valve portion, the second inlet, and the valve body communicate with the first inlet port and the first outlet port via the first groove. By providing a communication groove that allows the port and the second outlet port to communicate with each other via the second concave groove, it is possible to control the flow rates of two different flow paths with one motor-operated valve. For this reason, space saving of a cooling system can be achieved. Further, by forming a concave groove for variably setting the throttle flow rate on the valve seat surface, temperature control can be performed with higher accuracy than indoor temperature control using a capillary tube (see FIG. 17).

Moreover, the motor operated valve of the present invention is
The main valve portion is
A notch formed in an outer diameter for communicating the first inlet port and the first outlet port through the first concave groove;
It has at least one of the space provided in the center in order to connect the 1st entrance port and the 1st exit port via the 1st concave groove.
Thereby, the 1st entrance port and the 1st exit port can be made to communicate exactly.

Moreover, the motor operated valve of the present invention is
The groove width of the first groove and the groove width of the second groove are gradually changed in the same direction.
Thereby, two flow characteristics can be made the same direction, and when the pulse applied to a stepping motor is raised, both flow volume can be made to increase.

Moreover, the motor operated valve of the present invention is
The groove width of the first groove and the groove width of the second groove are gradually changed in opposite directions.
Thereby, when supplying a refrigerant to one cooler, it becomes possible to stop or restrict the supply of the refrigerant to the other cooler, and a cooling system that does not use a three-way valve can be realized. Space saving and cost improvement can be achieved. In addition, when cooling mainly in the refrigerator compartment cooler or the freezer compartment cooler, since a small amount of refrigerant is always supplied to the other cooler that is not the main, the temperature rise of the other cooler is suppressed. be able to.

Moreover, the motor operated valve of the present invention is
The first concave groove and the second concave groove are formed on the same circumference.
Thereby, arrangement | positioning of a ditch | groove can be put together compactly.

Moreover, the motor operated valve of the present invention is
The first concave groove and the second concave groove are formed on circumferences having different diameters.
Thereby, the length of each ditch | groove can be lengthened. Therefore, the range of pulses that can control the flow rate can be widened, and precise temperature control can be performed.

Moreover, the cooling system of the present invention is characterized by using the above-described motor-operated valve.
In this way, by using the motor-operated valve described above for the cooling system, it is not necessary to use a plurality of electronic expansion valves and the like, so that the space of the cooling system can be saved. In addition, since only one electronic expansion valve is arranged in the cooling system, power consumption can be saved and the number of parts can be reduced, so that a low-cost cooling system can be provided.

  According to the invention of the present invention, an electrically operated valve that can accurately control the temperature, does not expand the installation space of the expansion valve, and can suppress power consumption, and an inexpensive cooling system that uses the electrically operated valve and has low power consumption. Can be provided.

It is sectional drawing of the motor operated valve which concerns on 1st Embodiment. It is a disassembled perspective view of the motor operated valve concerning a 1st embodiment. It is the figure which looked at the valve seat which concerns on 1st Embodiment from upper direction. It is a perspective view of the valve element concerning a 1st embodiment. It is the figure which looked at the valve body which concerns on 1st Embodiment from the upper direction and the downward direction, respectively. It is a figure which shows the refrigerant circuit of the cooling system which concerns on 1st Embodiment. It is the figure which looked at the valve body rotated by the division | segmentation rotational motion of a stepping motor from the upper direction in the electrically operated valve which concerns on 1st Embodiment. It is a figure which shows the flow path of the refrigerant | coolant which changes with the rotation angle of the valve body which concerns on 1st Embodiment. It is a graph which shows the flow characteristic of the motor operated valve concerning a 1st embodiment. It is a figure which shows the refrigerant circuit of the cooling system which concerns on 2nd Embodiment. It is the figure which looked at the valve body rotated by the division | segmentation rotational motion of a stepping motor from the upper direction in the electrically operated valve which concerns on 2nd Embodiment. It is a figure which shows the flow path of the refrigerant | coolant which changes with the rotation angle of the valve body which concerns on 2nd Embodiment. It is a graph which shows the flow characteristic of the motor operated valve concerning a 2nd embodiment. It is the figure which looked at the valve body rotated by the division | segmentation rotational motion of a stepping motor from the upper direction in the electrically operated valve which concerns on 3rd Embodiment. It is a graph which shows the flow characteristic of the motor operated valve concerning a 3rd embodiment. It is the figure which looked at the valve body which rotates by the division | segmentation rotational motion of a stepping motor from the upper direction in the electrically operated valve which concerns on the modification of 3rd Embodiment. It is a figure which shows the refrigerant circuit of the conventional cooling system.

  Hereinafter, the motor-operated valve according to the first embodiment will be described with reference to the drawings. FIG. 1 is a cross-sectional view of the motor-operated valve according to the first embodiment, and FIG. 2 is an exploded perspective view of the motor-operated valve shown in FIG. In the present specification, “upper” or “lower” is defined based on the motor-operated valve 10 shown in FIG.

  As shown in FIG. 1, the motor-operated valve 10 includes a disk-shaped bottom lid member 11 and a case 12 welded on the bottom lid member 11 in an airtight manner. A valve chamber 13 having an airtight chamber structure is formed inside the case 12. A stator assembly (not shown), which will be described later, is mounted on the outer periphery of the case 12.

  As shown in FIG. 2, the upper dome portion 12B of the case 12 has a concentricity between the rotor accommodating cylindrical portion 12A and the bearing engaging recess 12C formed at the center of the upper dome portion 12B. It is integrally formed with the rotor accommodating cylindrical portion 12A. The lower opening 12D of the case 12 joined to the bottom lid member 11 is set to have a larger diameter than the outer diameter of the rotor accommodating cylindrical portion 12A.

  A step portion 11A having an outer diameter substantially equal to the inner diameter of the lower opening portion 12D of the case 12 is formed on the upper surface of the bottom cover member 11, and the lower opening portion 12D of the case 12 is fitted to the step portion 11A. (See FIG. 1). By this fitting, the concentricity between the bottom cover member 11 and the case 12 can be obtained.

  The welding of the bottom cover member 11 and the case 12 is performed at the fitting portion between the step portion 11A and the lower opening 12D. Thereby, reduction of the thermal influence at the time of welding and scattering of spatter to the valve chamber 13 can be prevented.

  Here, the bottom lid member 11 is formed with a plurality of through-holes 11B that secure a brazing allowance for inserting a pipe joint. In this through hole 11B, a through hole 11Ba into which the upper end of the pipe joint 14a is inserted, a through hole 11Bb into which the upper end of the pipe joint 14b is inserted, a through hole 11Bc into which the upper end of the pipe joint 14c is inserted, and There are through holes 11Bd into which the upper ends of the pipe joints 14d are inserted. Each of the four pipe joints 14 is fixed to a bottom cover member 11 and an intermediate plate 17 which are integrated by joining, which will be described later, by brazing, and extends below the bottom cover member 11.

  In addition, in order to prevent the brazing material of the pipe joint 14 and the intermediate plate 17 from flowing to the welding surface between the bottom lid member 11 and the case 12 on the upper surface of the bottom lid member 11, from the step portion 11 </ b> A. An annular U groove 11H having a slightly smaller diameter is formed.

  An intermediate plate 17 is fixed to the upper surface of the bottom cover member 11 by brazing. A shaft support hole 17 </ b> F is formed at the center of the intermediate plate 17. On the lower surface side of the intermediate plate 17, there is an annular protrusion 17 </ b> A around the shaft support hole 17 </ b> F, and this annular protrusion 17 </ b> A is fitted in the center recess 11 </ b> E at the center of the bottom cover member 11. Further, the intermediate plate 17 is formed with a positioning hole 17B that fits into the positioning projection 11F in the bottom lid member 11. The intermediate plate 17 and the bottom cover member 11 are concentric and aligned by the fitting at these two locations.

  The central recess 11E of the bottom cover member 11 has a sufficient depth, acts as a brazing material reservoir, and prevents the brazing material from flowing into the shaft support hole 17F. Further, the central recess 11E also functions as a relief for variation in the axial length of the central shaft 21 described later.

  The intermediate plate 17 is formed with a notch 17C that opens the through hole (first inlet port) 11Ba to the valve chamber 13. In addition, the intermediate plate 17 is formed with a plurality of oval communication openings 17D communicating with the through holes 11B. Specifically, the communication opening 17Db communicating with the through hole (first outlet port) 11Bb, the communication opening 17Dc communicating with the through hole (second inlet port) 11Bc, and the communication communicating with the through hole (second outlet port) 11Bd An opening 17Dd is formed.

  The intermediate plate 17 is formed by bending a base-pointing stopper piece 17G on which a first stopper piece 20F of the valve body 20 described later contacts. An O-ring 18 is attached to the stopper piece 17G so as to surround the stopper piece 17G.

  A valve seat 19 is attached to the upper surface of the intermediate plate 17. The valve seat 19 is obtained by etching a flat stainless steel plate into a predetermined shape on both sides. The valve seat 19 is subjected to carefully selected barrel processing for the purpose of removing end edges by double-side etching, improving the smoothness and surface roughness of the valve seat surface 19G, and obtaining the sliding lubricity of the valve body 20. It has been broken.

  The valve seat 19 has positioning holes 19A and 19B that fit into the two positioning protrusions 17H and 17J of the intermediate plate 17, a plurality of fully open ports 19C that communicate with the respective communication openings 17D, and a central shaft 21. A penetrating center hole 19D is formed. Here, the fully open port 19C includes a fully open port 19Cb communicating with the communication opening 17Db, a fully open port 19Cc communicating with the communication opening 17Dc, and a fully open port 19Cd communicating with the communication opening 17Dd.

  A concave groove 16A for variably setting the throttle flow rate is formed in the valve seat surface 19G on the upper surface of the valve seat 19. In this concave groove 16A, there are a first concave groove 16A1 and a second concave groove 16A2, each extending in an arc shape in the same direction as the rotation direction of a valve body 20 described later, as shown in FIG. The groove width is gradually changed in the extending direction at a uniform depth. The first groove 16A1 communicates with the fully open port 19Cb at the maximum groove width portion 16B1 at one end, and the minimum groove width portion 16B2 is formed at the other end. Similarly, the second groove 16A2 communicates with the fully opened port 19Cd at the maximum groove width portion 16B3 at one end, and the minimum groove width portion 16B4 is formed at the other end. Note that both the first concave groove 16A1 and the second concave groove 16A2 are formed such that the groove width gradually decreases in the clockwise direction of FIG.

  The valve seat 19 is positioned and angled by fitting the positioning holes 19A and 19B to the positioning projections 17H and 17J of the intermediate plate 17, respectively. For joining the valve seat 19 to the intermediate plate 17, there are methods such as adhesive / sealant, brazing, soldering, thermocompression bonding and welding.

The valve seat 19 is provided with a notch 19F that opens the through hole (first inlet port) 11Ba to the valve chamber 13 in the same manner as the notch 17C of the intermediate plate 17.
The valve body 20 is a molded article made of a resin material, which is disposed opposite to the valve seat surface 19G and takes into consideration sliding and refrigerant resistance. FIG. 4 is a perspective view showing the valve body 20. 5A is a view of the valve body 20 viewed from above, and FIG. 5B is a view of the valve body 20 viewed from below.

  As shown in FIGS. 4 and 5, a C-shaped main valve portion 20 </ b> A protrudes from the lower bottom surface. The main valve portion 20A is configured such that the groove 16A and the fully open port 19C are all located inside the outer diameter of the main valve portion 20A when the main valve portion 20A on the valve seat 19 is viewed from above. (See FIG. 7A), the outer diameter is provided with a notch 20A2, and the center is provided with a substantially cylindrical space 20P. Further, a seal surface 20B that is slidably contacted with the valve seat surface 19G is formed at the bottom of the main valve portion 20A, and the seal surface 20B extends with a uniform depth and width in the same direction as the rotation direction of the valve body 20. A communication groove 20A1 is formed. As will be described later, the communication groove 20A1 communicates the fully open port 19Cc and the fully open port 19Cd when the rotation angle of the valve body 20 is within a predetermined range.

  A central hole 20D through which the central shaft 21 is rotatably penetrated is formed in the central portion of the valve body 20, the rotational center is set by the central shaft 21, and the central shaft 21 is guided to rotate around the central axis. .

  Two protruding pieces 20H and 20J protruding outward in the radial direction are integrally formed on the valve body 20 with a small interval in the circumferential direction. The protruding piece 20H is at the same circumferential position as the first stopper piece 20F. The valve body 20 is positioned in the rotational direction by engaging a protruding piece 31A provided on a rotor 31 (see FIG. 2) of the stepping motor between the two protruding pieces 20H and 20J. The rotor 31 and the rotor 31 are connected in a torque transmission relationship, whereby the valve body 20 and the rotor 31 rotate synchronously.

  The first stopper piece 20F of the valve body 20 comes into contact with the O-ring 18 covered with the reference point stopper piece 17G by the rotation of the rotor 31 in the reference direction (see FIG. 7A). I do. Further, the valve body 20 is formed with a second stopper piece 20G for terminating the rotation in the base direction, and the rotation of the rotor 31 and the valve body 20 is completed when the second stopper piece 20G comes into contact with the O-ring 18. (See FIG. 7 (e)).

Further, the valve body 20 has a tapered guide shaft portion 20K for facilitating the assembly of the holding spring 23.
The center shaft 21 (see FIG. 2) is rotatably supported by the intermediate plate 17 by fitting the lower end 21A with the shaft support hole 17A. An upper end 21 </ b> B of the center shaft 21 is rotatably fitted in a bearing hole 22 </ b> A of the bearing member 22. The bearing member 22 is engaged with the bearing engaging recess 12C of the case 12 by the upper center protrusion 22B (see FIG. 1).

  A rotor 31 is rotatably provided in the valve chamber 13. The rotor 31 is a plastic magnet in which the outer peripheral portion 31B is magnetized in multiple poles. As described above, the rotor 31 is connected in a torque transmission relationship with the valve body 20 by the protruding piece 31A, and rotates the valve body 20.

  A through hole 31D through which the central shaft 21 passes is formed in the boss part 31C of the rotor 31, and a pressure equalizing communication hole 31F is provided in the rib-shaped part 31E connecting the outer peripheral part 31B and the boss part 31C. The axial length of the through hole 31D is made as long as possible in order to prevent rotational shake of the rotor 31 such as rattling or inclination. At least one pressure equalizing communication hole 31 </ b> F may be provided and has a function of preventing the upper accumulation of refrigerating machine oil and liquid refrigerant in addition to balancing the upper and lower pressures of the rotor 31.

  Between the lower end portion of the boss portion 31C of the rotor 31 and the step 20L formed on the inner side of the upper surface portion 20E of the valve body 20, a holding spring 23 by a compression coil spring is sandwiched. The holding spring 23 presses the sealing surface 20B of the valve body 20 against the valve seat surface 19G of the valve seat 19 to ensure the stability of the valve seal in a low differential pressure state. At the same time, the holding spring 23 urges the rotor 31 and the bearing member 22 upward, and presses the upper center protrusion 22B of the bearing member 22 against the bearing engaging recess 12C of the case 12.

  Although not shown here, a stator assembly of a stepping motor is positioned and fixed to the outer periphery of the case 12. The stator assembly includes upper and lower two-stage stator coils, a plurality of magnetic pole teeth, an electrical connector portion, and the like.

FIG. 6 is a diagram illustrating a refrigerant circuit of the cooling system using the motor operated valve 10 according to the first embodiment. The operation of the cooling system shown in FIG. 6 is performed as described below.
First, when the refrigerant discharged from the compressor 41 flows into the condenser 42, the heat of the refrigerant is released into the room and the refrigerant is condensed. The refrigerant that has passed through the condenser 42 is branched by the three-way valve 43 and sent to the pipe joint 14a and the pipe joint 14c.

  The refrigerant sent to the pipe joint 14a is supplied to the refrigerator 44 for the refrigerating chamber after the flow rate is controlled by the divided rotary drive of the valve body 20 in the motor-operated valve 10 that acts as an expansion valve of the cooling system (hereinafter referred to as the cooler 44). , This channel is referred to as channel AB). Similarly, the flow rate of the refrigerant sent into the pipe joint 14c is controlled by the rotary rotation of the valve body 20 in the motor-operated valve 10, and then supplied to the freezer cooler 45 (hereinafter referred to as this flow path). Referred to as channel CD). Details of the refrigeration path and the freezing path, and control of the flow rate by the split rotation drive of the valve body 20 will be described in detail later.

  The refrigerant supplied to the refrigerator 44 for the refrigerator compartment and the refrigerator 45 for the freezer compartment is again sucked into the compressor 41. The compressor 41 compresses and discharges the sucked refrigerant. Thereafter, the same operation is repeated to perform refrigeration and freezing in the household refrigerator.

  Next, a change in the flow rate characteristic when the valve body 20 is driven to be divided and rotated in the above-described cooling system will be described with reference to FIGS. FIG. 7 is a view of the valve body 20 that is rotated by the split rotation drive of the stepping motor as viewed from above, and FIG. 8 shows the flow of the refrigerant that changes depending on the rotation angle of the main valve portion 20A (valve body 20). Yes. FIG. 9 is a graph showing the flow characteristics of the electric valve. In FIG. 9, the horizontal axis of the graph represents the amount of pulses applied to the stepping motor, and the vertical axis of the graph represents the flow rate.

  First, in a 0 pulse state in which no pulse is applied to the stepping motor, the valve body 20 has a base position where the first stopper piece 20F of the valve body 20 contacts the O-ring 18 as shown in FIG. It is in. Thus, when the valve body 20 is at the base position, the concave groove 16A and the fully open port 19C are all closed by the main valve portion 20A, and a complete valve closed state in which the flow rate becomes 0 is realized (FIG. 9). Refer to the graph origin).

  Specifically, the refrigerant branched by the three-way valve 43 and passing through the pipe joint 14a and flowing into the valve chamber 13 from the through hole 11Ba was formed in the main valve portion 20A as shown in FIG. The C-shaped notch 20A2 is reached. Here, since the first concave groove 16A1 is completely closed by the main valve portion 20A, the refrigerant that has reached the notch 20A2 is prevented from flowing out to the fully open port 19Cb via the first concave groove 16A1. Path AB is blocked.

  Similarly, the refrigerant branched by the three-way valve 43 and passing through the pipe joint 14b flows into the communication groove 20A1 from the fully open port 19Cc. Here, in the 0-pulse state, since the communication groove 20A1 is not located at the position overlapping the second concave groove 16A2, the refrigerant is prevented from flowing out from the communication groove 20A1 to the fully open port 19Cd via the second concave groove 16A2. The flow path CD is blocked.

Note that the state where the flow path AB and the flow path CD are blocked is maintained until two pulses are applied to the stepping motor, as shown in FIG. 7B.
When the voltage applied to the stepping motor exceeds two pulses, the first concave groove 16A1 and the second concave groove 16A1 and the notch 20A2 and the second concave groove 16A2 and the communication groove 20A1 partially overlap each other. The refrigerant flows into the groove 16A2, and the flow path AB and the flow path CD are opened. Thereafter, the flow rates of the flow channel AB and the flow channel CD increase linearly with the amount of pulse applied (linear range). This is because, as described above, the first groove 16A1 and the second groove 16A2 are both formed so that the groove width gradually decreases in the clockwise direction in FIG.

  FIG.7 (c) is a figure which shows the valve body 20 in the state in which the voltage of 11 pulses was applied to the stepping motor. In this state, the refrigerant flowing into the valve chamber 13 from the through hole 11Ba flows out from the notch 20A2 to the fully open port 19Cb through the first concave groove 16A1 as shown in FIG. 8B. The refrigerant supplied from the fully open port 19Cc flows out to the fully open port 19Cd through the communication groove 20A1 and the second concave groove 16A2.

  Here, the flow rate of the refrigerant in the motor-operated valve 10 is determined by the minimum cross-sectional area of the portion constituting the refrigerant flow path in the concave groove 16A. For example, the flow rate of the flow channel AB is determined by the cross-sectional area of the first concave groove 16A1 immediately below the portion where the one end portion 20X of the notch 20A2 is located, and the flow rate of the flow channel CD is the position of the one end portion 20Y of the communication groove 20A1. It is determined by the cross-sectional area of the second concave groove 16A2 immediately below the portion to be.

  Therefore, in the state where the voltage of 11 pulses is applied to the stepping motor, the one end 20X of the notch 20A2 and the one end 20Y of the communication groove 20A1 are located at the center in the length direction of the concave groove 16A. The flow rates of the flow channel AB and the flow channel CD are about 50% of the flow rate in the fully opened state (see FIG. 7D).

  When the voltage applied to the stepping motor becomes 20 pulses, as shown in FIG. 7 (d), one end 20X of the notch 20A2 and one end 20Y of the communication groove 20A1 are positioned in front of the fully open ports 19Cb and 19Cd, respectively. The flow rate of the flow path AB becomes the maximum value in the linear range, and the flow rate of the flow path CD becomes the maximum value in the entire divided rotation range (see FIG. 9).

  When a voltage of 20 pulses or more is applied to the stepping motor, the linear range ends and the flow rates of the flow paths AB and CD change rapidly. Here, FIG. 7E is a diagram showing a state in which a voltage of 23 pulses is applied to the stepping motor. In this state, as shown in FIG. 8C, the refrigerant flowing into the valve chamber 13 from the through hole 11Ba is directly discharged from the notch 20A2 to the fully open port 19Cb without passing through the first concave groove 16A1. On the other hand, since the communication groove 20A1 is not positioned on the fully open port 19Cc, the fully open port 19Cc is blocked by the seal surface 20B of the main valve portion 20A, and the flow rate of the flow path CD becomes zero. Note that, when a voltage of 23 pulses is applied to the stepping motor, the second stopper piece 20G comes into contact with the O-ring 18 and the rotation of the rotor 31 and the valve body 20 is completed.

  According to the motor-operated valve 10 of the first embodiment, the first concave groove 16A1 and the second concave groove 16A2 are formed in the valve seat surface 19G, and the through hole (first inlet port) 11Ba and the valve body 20 are penetrated. A notch 20A2 for communicating the hole (first outlet port) 11Bb via the first concave groove 16A1, and a through hole (second inlet port) 11Bc and the through hole (second outlet port) 11Bd via the second concave groove 16A2. By providing the communication groove 20 </ b> A <b> 1 that communicates with each other, the flow rate of two different flow paths can be controlled by one motor-operated valve 10.

  In addition, according to the cooling system of the first embodiment, the flow rate of the refrigerant supplied to the refrigerator chiller 44 and the refrigerator chiller 45 can be controlled by one motor operated valve 10. It is not necessary to arrange an electronic expansion valve or the like, and the space of the cooling system can be saved. In addition, by using one control valve, power consumption can be saved and the number of parts can be reduced, so that an inexpensive cooling system can be provided. Further, by forming the concave groove 16A for variably setting the throttle flow rate on the valve seat surface 19G, temperature control can be performed with higher accuracy compared to the indoor temperature control using a capillary tube (see FIG. 17).

  Next, the motor operated valve according to the second embodiment will be described. In the second embodiment, portions different from the first embodiment will be described in detail, and descriptions of overlapping portions will be omitted. Here, FIG. 10 is a diagram illustrating a refrigerant circuit of the cooling system according to the second embodiment. Moreover, FIG. 11 is the figure which looked at the valve body rotated by the division | segmentation rotational motion of a stepping motor from the upper direction in the electrically operated valve which concerns on 2nd Embodiment.

  As shown in FIG. 11A, the first concave groove 16A1, the second concave groove 16A2, and the communication groove 20A1 in the second embodiment are positioned in the first embodiment (see FIG. 7A). ) Is rotated approximately 90 degrees clockwise. Further, the first concave groove 16A1 is formed so that the groove width gradually becomes narrower in the opposite direction to the first embodiment, that is, counterclockwise.

  Next, in the cooling system of the second embodiment, a change in the flow rate characteristic when the valve body 20 is driven to be divided and rotated will be described. First, as shown in FIG. 11A, when the valve body 20 in the 0-pulse state is at the base position, one end 20X of the notch 20A2 is located on the fully open port 19Cb, and the fully open port 19Cb is in a half-open state. In this case, as shown in FIG. 12A, the refrigerant flowing into the C-shaped notch 20A2 from the through hole 11Ba is discharged to the fully open port 19Cb without the flow rate being reduced by the first concave groove 16A1. For this reason, as shown in FIG. 13, the flow rate of the flow path AB is maximized.

  On the other hand, since the one end 20Y of the communication groove 20A1 does not overlap with the position of the second groove 16A2, the second groove 16A2 is closed by the seal surface 20B of the main valve portion 20A. For this reason, the refrigerant flowing into the communication groove 20A1 from the fully open port 19Cc is prevented from being discharged from the fully open port 19Cd. Therefore, the flow rate of the flow path CD in the 0 pulse state is zero.

  When the voltage applied to the stepping motor becomes two pulses, as shown in FIG. 11B, the one end 20X of the notch 20A2 moves onto the first concave groove 16A1, and the flow control by the first concave groove 16A1 starts. Is done. That is, as shown in FIG. 13, the flow rate characteristic of the flow path AB shifts to the linear range. For this reason, the flow rate of the flow path AB at this time is the maximum flow rate in the linear range. Note that the fully open port 19Cd is still closed by the seal surface 20B of the main valve portion 20A, so the flow rate of the flow path CD remains zero.

  When the voltage applied to the stepping motor exceeds two pulses for a while, the one end portion 20Y of the communication groove 20A1 is also located on the second concave groove 16A2, so that the flow rate characteristic of the flow path CD also shifts to the linear range. .

  When the voltage applied to the stepping motor becomes 11 pulses, as shown in FIG. 11C, the one end 20X of the notch 20A2 and the one end 20Y of the communication groove 20A1 are respectively in the center in the length direction of the concave groove 16A. To position. At this time, the flow rates of the flow channel AB and the flow channel CD are about 50% of the flow rate in the fully open state. FIG. 12B is a diagram showing the refrigerant flow at this point. As shown in FIG. 12B, the refrigerant that has flowed into the notch 20A2 from the through hole 11Ba flows out to the fully open port 19Cb via the first concave groove 16A1. The refrigerant supplied from the fully open port 19Cc flows out from the fully open port 19Cd through the communication groove 20A1 and the second concave groove 16A2.

  When the voltage applied to the stepping motor becomes 20 pulses, as shown in FIG. 11 (d), the first concave groove 16A1 is covered with the seal surface 20B of the main valve portion 20A, and then in the flow rate characteristics of the flow path AB. The linear range ends. On the other hand, one end 20Y of the communication groove 20A1 is located on the fully open port 19Cd, and the flow rate of the flow path CD becomes the maximum value in the linear range.

  When the voltage applied to the stepping motor reaches 20 pulses, as shown in FIGS. 11 (e) and 12 (c), the first concave groove 16A1 is closed by the sealing surface 20B of the main valve portion 20A, and the fully open port 19Cb. The refrigerant cannot be discharged from the flow path, and the flow rate of the flow path AB becomes zero. Further, since the fully open port 19Cc is also closed by the seal surface 20B of the main valve portion 20A, the flow path CD is also blocked and the flow rate of the flow path CD becomes zero.

  According to the cooling system of the second embodiment, the groove widths of the first concave groove 16A1 and the second concave groove 16A2 are narrowed in opposite directions, so that the flow paths AB and CD of the motor-operated valve are reduced. As shown in FIG. 10, when the refrigerant is supplied to one cooler, it becomes possible to stop or restrict the supply of the refrigerant to the other cooler as shown in FIG. 10, and the three-way valve is deleted. It becomes possible to do. As a result, the installation space can be further reduced as compared with the cooling system of the first embodiment, and the cost can be improved.

  In addition, when the cooling operation is performed by alternately switching the flow path with the three-way valve, the refrigerant does not flow to the refrigerating room cooler during the cooling of the freezing room, and the temperature of the refrigerating room gradually increases. According to the cooling system of the second embodiment, a small amount of refrigerant also flows through the refrigerating room cooler during cooling of the freezing room, and the freezing room is brought to a more appropriate temperature while suppressing the temperature rise of the refrigerating room as much as possible. Can be controlled. Similarly, when cooling the refrigerator compartment, a small amount of refrigerant flows through the freezer cooler, and the refrigerator compartment can be controlled to a more appropriate temperature while suppressing the temperature rise of the refrigerator compartment. As a result, energy saving of the cooling system can be realized.

  Next, an electric valve according to a third embodiment will be described. Since the third embodiment is a modification of the second embodiment, portions different from the second embodiment will be described in detail, and descriptions of overlapping portions will be omitted. FIG. 14 is a view of a valve body that is rotated by a divided rotational motion of a stepping motor, as viewed from above, in an electric valve according to a third embodiment.

  As shown in FIG. 14A, in the third embodiment, the first concave groove 16A1, the second concave groove 16A2, and the communication groove 20A1 are not arranged on the same circumference. A groove 16A2 and a communication groove 20A1 are formed outside the first concave groove 16A1. Accordingly, the communication groove 20A1 is formed to be long.

  Next, in the cooling system of the third embodiment, a change in the flow rate characteristic when the valve body 20 is driven to be divided and rotated will be described. First, as shown in FIG. 14A, when the valve body 20 in the 0-pulse state is at the base point position, the fully open port 19Cb is in a half-open state, so that the flow rate of the flow path AB is maximum as shown in FIG. It becomes. In the third embodiment, the refrigerant flowing into the valve chamber 13 from the through hole 11Ba communicates with a space 20P formed in the upper surface portion 20E of the valve body 20 and the step 20L (see FIG. 4) ( (Not shown) reaches the fully open port 19Cb via the space 20P. On the other hand, since the second concave groove 16A2 is closed by the seal surface 20B of the main valve portion 20A, the flow rate of the flow path CD in the zero pulse state becomes zero.

  When the voltage applied to the stepping motor becomes 5 pulses, as shown in FIG. 14B, the seal surface 20B of the main valve portion 20A begins to partially cover the first concave groove 16A1, and the first concave groove 16A1 Flow control is started. That is, as shown in FIG. 15, the flow rate characteristic of the flow path AB shifts to the linear range. For this reason, the flow rate of the flow path AB at this time is the maximum flow rate in the linear range. Note that the fully open port 19Cd is still closed by the seal surface 20B of the main valve portion 20A, so the flow rate of the flow path CD remains zero.

  When the voltage applied to the stepping motor becomes 20 pulses, as shown in FIG. 14C, the first concave groove 16A1 and the second concave groove 16A2 are each half-closed by the sealing surface 20B of the main valve portion 20A. For this reason, the flow rates of the flow channel AB and the flow channel CD are each about 50% of the flow rate in the fully open state.

  When the voltage applied to the stepping motor becomes 35 pulses, as shown in FIG. 14 (d), the first concave groove 16A1 is covered with the seal surface 20B of the main valve portion 20A, and thereafter, in the flow rate characteristics of the flow path AB. The linear range ends. On the other hand, the fully open port 19Cc and the fully open port 19Cd are connected by the communication groove 20A1, and the flow rate of the flow path CD becomes the maximum value in the linear range.

  When the voltage applied to the stepping motor reaches 37 pulses, as shown in FIG. 14 (e), the first concave groove 16A1 is closed by the seal surface 20B of the main valve portion 20A, and the refrigerant is discharged from the fully open port 19Cb. The flow rate of the flow path AB becomes 0. Further, since the fully open port 19Cc is also closed by the seal surface 20B of the main valve portion 20A, the flow path CD is also blocked and the flow rate of the flow path CD becomes zero.

  According to the motor-operated valve of the third embodiment, the second groove 16A2 and the communication groove 20A1 are formed outside the first groove 16A1, and the length can be increased to control the flow rate. Since this range can be widened, precise temperature control can be performed.

  In the third embodiment, the position of the first groove 16A1 and the position of the second groove 16A2 are switched, and the first groove 16A1 is positioned outside the second groove 16A2 as shown in FIG. You may make it do. Also in this case, as shown in FIGS. 16A to 16E, the flow rate control similar to that of the electric valve of the third embodiment can be performed.

  In each of the above-described embodiments, the communication groove 20A1 does not necessarily have to be formed with a uniform depth and the same width. In each of the above-described embodiments, the concave groove 16A has a maximum groove at one end when the groove depth is gradually changed in the extending direction instead of the groove width or together with the groove width. When the groove depth portion, the groove width, and the groove depth are all gradually changed in the extending direction, a configuration may be adopted in which the maximum width at one end and the maximum depth portion communicate with the fully open port 19C.

  As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, specific configurations and materials are not limited to these embodiments, and the design does not depart from the gist of the present invention. Any change or the like is included in the present invention.

  For example, the disk-shaped bottom cover member 11 does not necessarily have a disk shape. Further, the pipe joint 14 does not necessarily have to be connected below the bottom cover member 11. For example, the bottom lid member 11 may be a cylindrical member, and the pipe joint 14 may be connected to a through hole formed on the side surface of the cylinder.

10 Motorized valve 11 Bottom cover member 11Ba Through hole (first inlet port)
11Bb Through hole (first outlet port)
11Bc Through hole (second inlet port)
11Bd Through hole (second outlet port)
14 Pipe joint 16A1 First concave groove 16A2 Second concave groove 17 Intermediate plate 17C Notch portion 17D Communication opening 17G Stopper piece 19 Valve seat 19C Fully open port 19G Valve seat surface 20 Valve body 20A Main valve portion 20B Seal surface 20A1 Communication groove 20A2 Notch 20P space

Claims (7)

An electric valve that controls a throttle flow rate by rotating a single valve element disposed opposite to a valve seat surface around an axis,
The valve seat surface is formed with a first groove and a second groove that extend in an arc shape in the same direction as the rotation direction of the valve body, and the groove width gradually changes.
On the valve seat surface side of the valve body, a main valve portion is disposed that communicates the first inlet port and the first outlet port communicating with the first concave groove via the first concave groove,
A communication groove that extends in a circular arc shape in the same direction as the rotation direction of the valve body and communicates with the second inlet port and the second outlet port that communicates with the second concave groove on the seal surface of the main valve portion. The motor-operated valve characterized by being formed. The main valve portion is
A notch formed in an outer diameter for communicating the first inlet port and the first outlet port through the first concave groove;
2. The motor-operated valve according to claim 1, further comprising at least one of a space provided in the center for communicating the first inlet port and the first outlet port via the first concave groove.   The motor-operated valve according to claim 1 or 2, wherein the groove width of the first groove and the groove width of the second groove are gradually changed in the same direction.   3. The motor-operated valve according to claim 1, wherein the groove width of the first groove and the groove width of the second groove are gradually changed in opposite directions.   The motor-operated valve according to any one of claims 1 to 4, wherein the first concave groove and the second concave groove are formed on the same circumference.   The motor-operated valve according to any one of claims 1 to 4, wherein the first concave groove and the second concave groove are formed on circumferences having different diameters.   The cooling system using the motor operated valve as described in any one of Claims 1-6.

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