JP4119720B2 - Electric valve and refrigeration cycle equipment for refrigeration / refrigerator - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
  TECHNICAL FIELD The present invention relates to an electric valve and a refrigeration cycle apparatus for a refrigeration / refrigerator, and in particular, is used as an expansion valve for a refrigeration cycle apparatus for a refrigeration / refrigerator of the type that defrosts an evaporator by heat of refrigerant discharge gas. The present invention relates to a motor operated valve and a refrigeration cycle apparatus for a refrigeration / refrigerator.
[0002]
[Prior art]
  Instead of using a heater to remove frost that has formed on the evaporator of a household refrigerator (freezer / refrigerator), the high-temperature refrigerant discharge gas discharged from the compressor is directly applied to the evaporator. It has already been proposed to use the heat of the refrigerant discharged gas. Since the defrosting by the refrigerant discharge gas heat is heaterless, it is suitable for a refrigeration / refrigerator of a vapor compression refrigeration cycle apparatus using HC refrigerant (R6000a) or the like, and energy saving is also achieved.
[0003]
[Patent Document 1]
         JP 2002-162124 A
[Patent Document 2]
          JP-A-10-62035
[0004]
[Problems to be solved by the invention]
  In a vapor compression refrigeration cycle apparatus using HC refrigerant (R6000a) or the like, in order to effectively obtain the evaporator capacity, the refrigerant pressure flowing into the evaporator is lowered and the refrigerant evaporates as compared with the refrigerant refrigerant. In order to lower the temperature, it is necessary to precisely perform the refrigerant throttling with a small flow rate.
[0005]
  On the other hand, in the case where the defrosting is performed by the refrigerant discharge gas heat, the refrigerant discharge gas is required to flow through the evaporator at the maximum flow rate during the defrosting operation so that the defrosting is efficiently performed in a short time. The
[0006]
  The present invention has been made to solve the above-described problems, and performs defrosting by the refrigerant discharge gas heat, accurately performs a small flow rate restriction during normal cooling operation, and at the maximum during defrosting operation, An object of the present invention is to provide an electric valve having a composite function such as an expansion valve with a fully open function capable of obtaining a flow rate, and a refrigeration cycle apparatus for a refrigeration / refrigerator using the electric valve.
[0007]
[Means for Solving the Problems]
  In order to achieve the above-described object, an electric valve according to the present invention includes a valve body that is rotationally driven by a stepping motor, and a case that accommodates the valve body so as to rotate and move in the axial direction.A spring that biases the valve body toward the valve seat surface, a first pressure chamber that exerts a primary pressure on one end surface of the valve body in a primary pressure atmosphere, and the other of the valve body A second pressure chamber for exerting pressure on the end face;A valve seat surface formed with a throttle flow metering portion and a fully open port is provided on the case side,There is a pilot passage that is closed in the first motor rotation angle range and is in communication in the second motor rotation angle range and introduces a secondary pressure lower than the primary pressure into the second pressure chamber. Provided in the valve body,The valve body is movable between a first axial position seated on the valve seat surface and a second axial position spaced from the valve seat surface, and in a first motor rotation angle range,In the closed state of the pilot passage, the second pressure chamber is in a primary pressure atmosphere, and the valve body is positioned at the first axial position by the spring force of the spring,By rotationally displacing the valve seat surface at the first axial position, the throttle flow rate of the throttle flow rate measuring unit is quantitatively set according to the rotation angle with the fully opened port closed. In a second motor rotation angle range that is larger than the first motor rotation angle range,In the communication state of the pilot passage, the valve body resists the spring force of the spring by the differential pressure between the pressure of the first pressure chamber and the pressure of the second pressure chamber.It moves in the axial direction to the second axial position and opens the fully open port.
[0008]
  In this electric valve, in the first motor rotation angle range,In the closed state of the pilot passage, the second pressure chamber is in the primary pressure atmosphere, the valve element is positioned at the first axial position by the spring force of the spring, and the valve seat surface is positioned at the first axial position. With the rotational displacement, the fully open port is closed,The throttle flow rate of the throttle flow rate metering section is quantitatively variably set according to the rotation angle of the valve body, and a small flow rate throttle is performed, which functions as an electric expansion valve. In the second motor rotation angle range,The valve body resists the spring force of the spring by the differential pressure between the pressure in the first pressure chamber and the pressure in the second pressure chamber in the communication state of the pilot passage.When the valve body moves in the axial direction and moves away from the valve seat surface, the fully open port is opened, and the maximum flow rate can be obtained.
[0009]
  In the motor-operated valve according to the present invention, the throttle flow rate measuring portion has a concave groove portion that extends in an arc shape in the same direction as the rotation direction of the valve body, and the groove width gradually changes in the extending direction. The position where the slit formed in the body aligns with the concave groove portion according to the rotational displacement of the valve body changes in the extending direction of the concave groove portion, so that the throttle flow rate according to the rotation angle of the valve body The throttle flow rate of the metering unit can be set quantitatively, and highly accurate small flow rate throttle control can be performed.
[0010]
  Further, a refrigeration cycle apparatus for a refrigeration / refrigerator according to the present invention includes a compressor, a condenser, an evaporator, and a refrigeration cycle apparatus for a refrigeration / refrigerator including a refrigerant passage connecting them. → Evaporator → Compressor cooling operation circuit and compressor → Evaporator → Compressor defrosting operation circuit with flow path switching means for switching the flow path. Is provided as an electrically driven expansion valve with a fully open function.
[0011]
  According to the refrigeration cycle apparatus for refrigeration / refrigerator according to the present invention, the motor operated valve is used in the first motor rotation angle range during the cooling operation to reduce the small flow rate, and during the defrosting operation, the motor operated valve is rotated to the second motor. The motor-operated valve can be fully opened using the angular range, and the refrigerant discharge gas can flow to the evaporator at the maximum flow rate.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
  Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
(Electric valve implementation formstate)
  1 ~FIG.Motorized valve according to the present inventionStateShow.
[0013]
  As shown in FIG. 1, the motor-operated valve 10 includes a disk-shaped bottom lid member 11 and a can-shaped case 12 that is airtightly welded or brazed onto the bottom lid member 11. The case 12 cooperates with the bottom lid member 11 to form a valve chamber / rotor chamber 13 having an airtight chamber structure inside.
[0014]
  A primary port 14 and a secondary port 15 are formed through the bottom lid member 11. The primary port 14 is in a position shifted laterally from the center position of the bottom cover member 11 and is in direct communication (always communicating) with the valve chamber / rotor chamber 13. A joint pipe 16 is connected to the primary side port 14. The secondary side port 15 is in the center position of the bottom cover member 11, and another joint pipe 17 is connected to the secondary side port 15.
[0015]
  In FIG.As shown, the base plate 18 is positioned and brazed on the bottom lid member 11 (valve chamber / rotor chamber 13 side) by fitting the alignment embosses 11A and 18A. The base plate 18 is formed with a central hole 19 having an extended portion 19 </ b> A and communicating with the secondary port 15, and a notch opening 20 aligned with the primary port 14.
[0016]
  The base plate 18, onA stopper piece 22 having a shape rising upward is integrally formed.
[0017]
  On the base plate 18, the valve seat plate 23 is positioned by fitting the alignment 18A and the positioning hole 23A, and bonded and adhered by a refrigerant-resistant adhesive. The upper surface of the valve seat plate 23 is a valve seat surface 23B, and a fully open port 24 is formed through the center position. The fully open port 24 has a large diameter D that can obtain the maximum flow rate on the system, and communicates with the secondary port 15 through the central hole 19. Further, the valve seat plate 23 is formed with a notch opening 25 that is aligned with the notch opening 20.
[0018]
  A throttling control fully open port 26 is formed at a position shifted laterally from the center position of the valve seat plate 23. The aperture control fully-open port 26 has a small diameter d for aperture control, and communicates with the secondary port 15 via the expanded portion 19A of the central hole 19.
[0019]
  On the valve seat surface 23 </ b> B of the valve seat plate 23, as a throttle flow rate metering unit (small flow rate control unit), it extends in an arc shape in the same direction as the rotation direction of a valve body 30 described later, that is, substantially around the central axis. The groove portion 27 extends in the rotation angle range (first motor rotation angle range) of 270 degrees, and the groove width gradually changes in the extending direction.
[0020]
  The concave groove portion 27 is formed by half etching or the like, and has a uniform depth h.The mostThe throttle control fully open port 26 is communicated with the maximum width portion (starting end) 27A due to a large Wm, and the groove width gradually decreases as it advances in the counterclockwise direction in the figure, and reaches the end (valve opening point) 27B. It is narrow Wo.
[0021]
  As shown in FIG. 1, the valve body 30 is provided on the valve seat surface 23 </ b> B of the valve seat plate 23 so as to be rotatable around the central axis and movable in the axial direction. The valve body 30 is in the valve chamber / rotor chamber 13,In FIG.As shown, the first axial position (which is seated on the valve seat surface 23B with the lower bottom surface 30A (FIG.a) see)In FIG.As shown, the lower bottom surface 30A is separated from the valve seat surface 23B by a second axial position (FIG. 6 (d)It is possible to move between.
[0022]
  In the state where the valve body 30 is located at the first axial position, the fully open port 24 is blocked by the lower bottom surface 30A of the valve body 30, and the valve body 30 is located at the second axial position. The fully open port 24 is opened. The fully open area Af when the fully open port 24 is opened is the valve lift amount L (See Figure 5Af = D · π · L, and the maximum flow rate on the system is obtained by the fully open area Af.
[0023]
  The valve body 30 includesIn FIG.As shown in the figure, a slit 31 for controlling the throttle flow rate is formed, and the position aligned with the concave groove 27 according to the rotational displacement of the valve body 30 at the first axial position is the extension of the concave groove 27. By changing in the present direction, the throttle flow rate is quantitatively set in accordance with the rotation angle of the valve body 30. The groove width of the concave groove portion 27 at the portion where the slit 31 is aligned is set to Wi.When,The opening area Ai of the throttle passage is represented by Ai = Wi · h, and the control groove width Wi continuously changes from the fully closed to the minimum width Wo and the maximum width Wm according to the rotation angle of the valve body 30.
[0024]
  The valve body 30 is connected in a torque transmission relationship by the engagement of a rotor 51 of a stepping motor 50 described later and a half-engaged engagement portion 30B, 51B, and rotates integrally with the rotor 51.
[0025]
  As shown in FIG. 1, a rotor 51 of a stepping motor 50 is rotatably provided in the valve chamber / rotor chamber 13. The rotor 51 isIn FIG.As shown in the drawing, the outer peripheral portion 51C is a multi-pole magnetized plastics magnet, and the central shaft 53 passes through the central portion of the boss portion 51A. A bearing member 54 is insert-molded at the upper end of the central shaft 53.
[0026]
  As shown in FIG. 1, the bearing member 54 engages with a bearing recess 12 </ b> A formed in the ceiling portion of the case 12 by the upper protrusion 54 </ b> A and is supported rotatably from the case 12. The center shaft 53 is bearing-fitted into the center hole 30D of the valve body 30 at the lower end.
[0027]
  A compression coil spring 36 is provided between the boss 51A of the rotor 51 and the valve body 30 to urge the valve body 30 toward the valve seat surface 23B.
[0028]
  A stator assembly 55 of the stepping motor 50 is positioned and fixed to the outer periphery of the case 12. The stator assembly 55 includes upper and lower two-stage stator coils 56, a plurality of magnetic pole teeth 57, and the like, and the inside of the cover 58 is liquid-tightly sealed with a potting resin 60 as a whole.
[0029]
  The stator assembly 55 is phase-matched when the positioning piece 59 provided with the stator assembly 55 is engaged with a plurality of positioning recesses 11 </ b> B formed on the outer peripheral portion of the bottom cover member 11.
[0030]
  Embodiment of the inventionStateIn such a motor-operated valve 10,Figure 1As shown, an inner shell 37 is hermetically welded inside the case 12. The valve body 30 is fitted to the cylindrical portion 37A of the inner shell 37, and is supported so as to be rotatable from the inner shell 37 and movable in the axial direction.
[0031]
  The inner shell 37 causes the primary pressure to be exerted upward on the lower bottom surface (one end surface) 30A of the valve body 30 in the primary pressure atmosphere by always communicating with the primary side port 14 in the valve shell / rotor chamber 13. The pressure chamber 13A is divided into a first pressure chamber 13A and a second pressure chamber 13B that exerts a pressure downward on the upper surface (the other end surface) 30E of the valve body 30.
[0032]
  The valve body 30 is formed with one stopper piece 38 protruding therefrom. When the stopper piece 38 comes into contact with the stopper piece 22 (only one) of the base plate 18, the rotation of the valve body 30 is limited to approximately one rotation.
[0033]
  A pilot passage 39 is formed through the valve body 30 between the lower bottom surface 30A and the upper surface 30E. The pilot passage 39 is used for throttle control in a first motor rotation angle range (for example, 64/72 pulse range) in which throttle flow rate control is performed by matching the slit 31 of the valve body 30 and the concave groove portion 27 of the valve seat plate 23. In the second motor rotation angle range (for example, 72 pulses), it is in communication with the throttle control fully open port 26 in a position away from the fully open port 26, and is in a communication state. The secondary pressure is introduced into the second pressure chamber 13B.
[0034]
  In a state where the pilot passage 39 is closed, the primary pressure in the first pressure chamber 13A is transmitted to the second pressure chamber 13B through the fitting portion gap 37B between the valve body 30 and the cylindrical portion 37A of the inner shell 37. Therefore, the second pressure chamber 13B becomes a primary pressure atmosphere having the same pressure as the first pressure chamber A, and the valve element 30 is caused by the spring force of the compression coil spring 36.In FIG.As shown, it is located at a first axial position.
[0035]
  When the pilot passage 39 is in the communication state, the secondary pressure is introduced into the second pressure chamber 13B by the pilot passage 39, and the pressure in the second pressure chamber 13B becomes lower than the pressure in the first pressure chamber 13A. Due to the differential pressure between the pressure in the chamber 13A and the pressure in the second pressure chamber 13B, the valve body 30 isIn FIG.As shown, it moves to a second axial position against the spring force of the compression coil spring 36..
[0036]
  Next, the embodiment with the above configurationStateThe operation of the motor operated valve 10 will be described.
(Complete valve closure = initialization)
  The stator coil 56 of the stepping motor 50 is excited with a specified number of pulses with the valve closing direction (clockwise direction) as the rotational direction. This makes the rotor51 rotates in the clockwise direction, and the valve body 30 integrally rotates with the rotor 51 in the clockwise direction.As shown in a), the slit 31 of the valve body 30 is located at a rotational position separated from both the aperture control full opening port 26 and the concave groove 27. The pilot passage 39 is also located at a position away from the throttle control fully open port 26.
[0037]
  This clockwise rotation is performed until the stopper piece 38 of the valve body 30 comes into contact with one end face of the stopper piece 22 of the base member 18.
[0038]
  In this state, the valve body 30 is pushed to the first axial position by the spring force of the compression coil spring 36, and the lower bottom surface 30A of the valve body 30 is seated on the valve seat surface 23B (See Figure 4The fully open port 24 is closed.
[0039]
  As a result, a complete valve closed state is obtained, and the base point position (phase) of the valve body 30 is obtained with the A-phase 0 pulse.
[0040]
(Throttle flow control range)
  The stator coil 56 of the stepping motor 50 is excited with a specified number of pulses with the valve opening direction (counterclockwise direction) as the rotational direction. As a result, the rotor 51 rotates counterclockwise, and the valve body 30 integrally rotates with the rotor 51 counterclockwise. For example, with A-phase 4 pulses,FIG.b), the slit 31 of the valve element 30 is located at the valve opening point 27B of the concave groove 27, and the throttle passage by the opening area of Ai = Wo · h is formed on the primary side port 14 (valve chamber · It is established between the rotor chamber 13) and the secondary port 15.
[0041]
  The opening area of the throttle passage is changed from the minimum Ai = Wo · h to the maximum Ai by changing the position where the slit 31 aligns with the concave groove portion 27 in accordance with the increase in the counterclockwise rotation angle of the valve body 30. = Continuously increases in the range of Wm · h. Thereby, the minute flow control is performed with high accuracy.
[0042]
  In the variable throttle passage obtained by the alignment of the slit 31 and the concave groove portion 27, the fluid throttled there also flows in the extending direction of the concave groove portion 27, so that the structure is strong against dust clogging in micro flow control.
[0043]
  For example, with A-phase 64 pulses,FIG.As shown in c), the slit 31 of the valve body 30 is aligned with the throttle control fully open port 26, and the throttle is fully opened. Since one rotation of the rotor is 80 pulses, the range of 64/80 pulses is the first motor rotation angle range, and this motor rotation angle range is the throttle flow rate control region.
[0044]
  In this 64/80 pulse range (first motor rotation angle range), the pilot passage 39 is in a closed state away from the throttle control fully open port 26, and the valve body 30 and the cylindrical portion 37A of the inner shell 37 are fitted. Since the primary pressure of the first pressure chamber 13A is transmitted to the second pressure chamber 13B through the gap 37B, the second pressure chamber 13B becomes a primary pressure atmosphere having the same pressure as the first pressure chamber A, and is compressed. The valve body 30 is moved by the spring force of the coil spring 36.In FIG.As shown, the lower bottom surface 30A is maintained in a first axial position for seating on the valve seat surface 23B.
[0045]
(Maximum flow fully open)
  Further, the stator coil 56 of the stepping motor 50 is excited with a specified number of pulses with the valve opening direction (counterclockwise direction) as the rotation direction. As a result, the rotor 51 further rotates the second motor rotation angle range in the counterclockwise direction. For example,FIG.As shown in d), the stopper piece 38 of the valve body 30 comes into contact with the other end face of the stopper piece 22 of the base member 18, and the rotation of the rotor 51 in the counterclockwise direction is stopped.
[0046]
  At this time, the pilot passage 39 is aligned with the throttle control fully-open port 26, and the pilot passage 39 is in a communication state. As a result, the secondary pressure is introduced into the second pressure chamber 13B by the pilot passage 39, the pressure in the second pressure chamber 13B becomes lower than the pressure in the first pressure chamber 13A, and the pressure in the first pressure chamber 13A As shown in FIG. 5, the valve body 30 moves to the second axial position against the spring force of the compression coil spring 36 by the pressure difference from the pressure of the two pressure chambers 13 </ b> B.
[0047]
  ThisIn FIG.As shown, the valve body 30 is located at the second axial position, the fully open port 24 is opened, and the maximum flow rate on the system is obtained by the fully open area Af = D · π · L.
[0048]
  When obtaining this maximum flow rate, there is no suction noise or water hammer phenomenon as in an electromagnetic valve, so that quietness can be obtained.
[0049]
  In this embodiment, the maximum flow rate fully open state → throttle flow rate control state → complete valve closed state is reversibly obtained by the reverse operation of the above-described operation.
[0050]
(Embodiment 1 of a refrigeration cycle apparatus for refrigerator / refrigerator using an electric valve)
  Next, Embodiment 1 of the refrigeration cycle apparatus for a refrigeration / refrigerator in which the motor-operated valve 10 having the above-described configuration is incorporated,7 andAndFigure 8The description will be given with reference.
[0051]
  A refrigeration cycle apparatus for a refrigeration / refrigerator includes a compressor 101, a condenser 102, an electric valve 10 as an electric expansion valve with a fully open function, an evaporator 103, a three-way switching valve 104, and a refrigerant passage that connects them. A vapor compression refrigeration cycle apparatus including 105 to 109 and using HC refrigerant (R6000a) or the like is configured. The motor-operated valve 10 may be either the first embodiment or the second embodiment described above. The freezer / refrigerator has a freezer compartment 121, a refrigerator compartment 122, and a vegetable compartment 123.
[0052]
  The high pressure side port D of the three-way switching valve 104 is connected to the discharge port 101d of the compressor 101, the first flow path switching port C is connected to the condenser 102 by the refrigerant passage 105, and the second flow path switching port E is the bypass refrigerant. Each passage 109 is connected to the primary side port 14 of the motor-operated valve 10. The bypass refrigerant passage 109 bypasses the condenser 102 and connects the second flow path switching port E to the inlet side of the motor-operated valve 10. The secondary port 15 of the motor-operated valve 10 is connected to the inlet of the evaporator 103 by the refrigerant passage 107.
[0053]
  When the three-way switching valve 104 is in the first switching state,In FIG.As shown, the discharge port 101d of the compressor 101 is connected to the condenser 102 by the refrigerant passage 105, and the circulation path (cooling) of the compressor 101 → the condenser 102 → the motor operated valve 10 → the evaporator 103 → the compressor 101. Operation circuit) is established.
[0054]
  At this time, the motor-operated valve 10 is controlled in the first motor rotation angle range, so that fine throttle flow control (small-flow throttle) is performed, and the motor-operated valve 10 operates effectively as an electric expansion valve. Thereby, even if HC refrigerant | coolant (R6000a) etc. are used, the capability of the evaporator 103 can be obtained effectively and efficient cooling operation is performed.
[0055]
  During this cooling operation, cool air is sent from the evaporator 103 to the freezer compartment 121 by the fan 124, and cool air is sent to the refrigerating chamber 122 by opening and closing the damper 125.
[0056]
  When the three-way switching valve 104 switches to the second switching state,Figure 8As shown, the discharge port 101d of the compressor 101 bypasses the condenser 102 by the bypass refrigerant passage 109 and is directly connected to the primary port 14 of the motor-operated valve 10, and the compressor 101 → the motor-operated valve 10 → evaporation. The circulation path (defrosting operation circuit) between the compressor 103 and the compressor 101 is established.
[0057]
  At this time, the motor-operated valve 10 is controlled in the second motor rotation angle range so that the maximum flow rate on the system can be obtained.
[0058]
  As a result, the high-temperature and high-pressure refrigerant from the compressor 101 flows directly to the evaporator 103 with the maximum flow rate by the bypass refrigerant passage 109, and the defrosting (defrost) of the evaporator 103 is efficiently performed by the discharged refrigerant gas heat.
[0059]
  As described above, the motor-operated valve 10 according to the present invention functions as a small flow rate expansion valve corresponding to the evaporator capacity of a domestic refrigeration / refrigerator during the cooling operation, and is large according to the defrost capacity during the defrosting operation. A fully open flow characteristic is obtained.
[0060]
  In the home refrigeration / refrigerator according to the present invention, the refrigerant flow direction of the evaporator 103 is the same during the cooling operation and the defrosting operation, and the electric valve 10 is not used as a reversible flow. It is not necessary to configure a reverse pressure resistant type compatible with reversible flow. Moreover, the frost that has formed on the main body portion and the coil portion of the motor-operated valve 10 is also defrosted during the defrosting operation of the evaporator 103 by the discharge gas flowing.
[0061]
(Embodiment 2 of a refrigeration cycle apparatus for a refrigeration / refrigerator using an electric valve)
  Next, Embodiment 2 of the refrigeration cycle apparatus for a refrigeration / refrigerator in which the motor-operated valve 10 having the above-described configuration is incorporated,9 andAndFigure 10The description will be given with reference. In addition,9 andAndIn FIG.Leave7 andAndFigure 8The corresponding part is7 andAndFigure 8The same reference numerals as in the attached reference numerals are used, and the description thereof is omitted.
[0062]
  This refrigeration / refrigeration refrigeration cycle apparatus has an evaporator 103F for a freezer compartment and an evaporator 103R for a refrigerator compartment separately, a separate capillary tube 110 for the refrigerator compartment, and another three-way switching valve. 111, circuit switching can be performed between the refrigerant circuit of the refrigerant passage 112, the capillary tube 110, the refrigerant passage 112, and the evaporator 103R, and the refrigerant circuit of the refrigerant passage 106, the motor-operated valve 10, the refrigerant passage 107, and the evaporator 103F. It is like that. The refrigerator 103R for the refrigerator compartment and the evaporator 103F for the freezer compartment are connected by a refrigerant passage 115 including a check valve 114.
[0063]
  Also in the second embodiment, the high-pressure side port D of the three-way switching valve 104 is connected to the discharge port 101d of the compressor 101, the first flow path switching port C is connected to the condenser 102 by the refrigerant passage 105, and the second flow path. The switching port E is connected to the primary port 14 of the motor-operated valve 10 by a bypass refrigerant passage 109.
[0064]
  When the three-way switching valve 104 is in the first switching state and the three-way switching valve 111 causes the refrigerant to flow into the refrigerant circuit of the refrigerant passage 106, the electric valve 10, the refrigerant passage 107, and the evaporator 103F,In FIG.As shown, the discharge port 101d of the compressor 101 is connected to the condenser 102 by the refrigerant passage 105, and the compressor 101 → the condenser 102 → the three-way switching valve 111 → the motor operated valve 10 → the evaporator 103F → the compressor 101. The circulation path (cooling operation circuit) is established.
[0065]
  At this time, the motor-operated valve 10 is controlled in the first motor rotation angle range, so that fine throttle flow control (small-flow throttle) is performed, and the motor-operated valve 10 operates effectively as an electric expansion valve. Thereby, even if HC refrigerant | coolant (R6000a) etc. are used, the capability of the evaporator 103F is obtained effectively and efficient cooling operation is performed.
[0066]
  When the three-way switching valve 104 switches to the second switching state,In FIG.As shown, the discharge port 101d of the compressor 101 bypasses the condenser 102 by the bypass refrigerant passage 109 and is directly connected to the primary port 14 of the motor-operated valve 10, and the compressor 101 → the motor-operated valve 10 → evaporation. The circulation path (defrosting operation circuit) of the compressor 103F → the compressor 101 is established.
[0067]
  At this time, the motor-operated valve 10 is controlled in the second motor rotation angle range so that the maximum flow rate on the system can be obtained.
[0068]
  As a result, the high-temperature and high-pressure refrigerant from the compressor 101 flows directly to the evaporator 103F through the bypass refrigerant passage 109 with the maximum flow rate, and the defrosting (defrost) of the evaporator 103F is efficiently performed by the discharged refrigerant gas heat.
[0069]
  As described above, also in this embodiment, the motor-operated valve 10 according to the present invention functions as a small flow rate expansion valve corresponding to the evaporator capacity of a domestic refrigeration / refrigerator during cooling operation, and defrosting during defrosting operation. A fully open characteristic with a large flow rate corresponding to the capacity can be obtained.
[0070]
  Also in this embodiment, the refrigerant flow direction of the evaporator 103F is the same during the cooling operation and the defrosting operation, and the motor-operated valve 10 is not used as a reversible flow. It is no longer necessary to configure the device with a reverse pressure resistance specification. Moreover, the frost that has formed on the main body portion and the coil portion of the motor-operated valve 10 is also defrosted during the defrosting operation of the evaporator 103F by the discharge gas flowing.
[0071]
【The invention's effect】
  As understood from the above description, according to the motor operated valve according to the present invention, the throttle flow rate of the throttle flow rate measuring unit is quantitatively variably set in accordance with the rotation angle of the valve body in the first motor rotation angle range. In the second motor rotation angle range, since the valve element moves in the axial direction and moves away from the valve seat surface, the fully open port is opened and the maximum flow rate can be obtained. With the use of a refrigeration cycle system for refrigeration and refrigerators that defrosts by discharge gas heat, a small flow rate restriction is accurately performed during normal cooling operation, and the maximum flow rate can be obtained during defrosting operation. It is effectively used as a composite function valve such as an expansion valve.
[Brief description of the drawings]
1 is an embodiment of a motor-operated valve according to the present invention;StateIt is a longitudinal cross-sectional view shown.
[Figure 2] Implementation formStateAccording to the motorized valvePerspective view of valve seatFIG.
[Figure 3] ImplementationStateAccording to the motorized valveDisassembly of main partsIt is a perspective view.
[Fig. 4] ImplementationStateAccording to the motorized valveLongitudinal section of the main part showing operationFIG.
FIG. 5 Implementation formStateAccording to the motorized valveShow behaviorIt is a longitudinal cross-sectional view of the principal part.
[Fig. 6](A) to (d)ImplementationStateOf the main part showing the operation of the motorized valvePlaneFIG.
FIG. 7 is a refrigerant circuit diagram showing a first embodiment of a refrigeration cycle apparatus for a refrigeration / refrigerator according to the present invention.
FIG. 8 is a refrigerant circuit diagram showing Embodiment 1 of the refrigeration cycle apparatus for a refrigeration / refrigerator according to the present invention.
FIG. 9 is a refrigerant circuit diagram showing a second embodiment of a refrigeration cycle apparatus for refrigeration according to the present invention.
FIG. 10 is a refrigerant circuit diagram showing a second embodiment of a refrigeration cycle apparatus for refrigeration according to the present invention.
[Explanation of symbols]
  10 Motorized valve
  11 Bottom cover member
  12 cases
  13 Valve chamber / rotor chamber
  13A 1st pressure chamber
  13B Second pressure chamber
  14 Primary port
  15 Secondary port
  18 baseBoard
23 Valve seat plate
  24 Fully open port
  26 Open port for aperture control
  27 Groove
  30 Disc
  31 SlipG
36 Compression coil spring
  39 Pilot Passage
  50 Stepping motor
  51 rotor
  55 Stator assembly
  101 Compressor
  102 Condenser
  103, 103F, 103R Evaporator
  104 three-way valve
  109 Bypass refrigerant passage

Claims (3)

A valve body that is rotationally driven by a stepping motor, a case that accommodates the valve body so as to rotate and move in the axial direction, a spring that biases the valve body toward the valve seat surface, and a primary pressure atmosphere A first pressure chamber that exerts a primary pressure on one end face of the valve body, and a second pressure chamber that exerts pressure on the other end face of the valve body ,
A valve seat surface formed with a throttle flow rate metering part and a fully open port is provided on the case side, and is closed in the first motor rotation angle range and in a communication state in the second motor rotation angle range. A pilot passage for introducing a secondary side pressure lower than the primary side pressure into the second pressure chamber is provided in the valve body;
The valve body is movable between a second axial position spaced from the valve seat surface and the first axial position to be seated on the valve seat surface, in the first motor rotation angle range, the In a closed state of the pilot passage, the second pressure chamber is in a primary pressure atmosphere, the valve body is positioned at the first axial position by the spring force of the spring, and the first axial position is By rotationally displacing with respect to the valve seat surface, the throttle flow rate of the throttle flow rate measuring unit is quantitatively set according to the rotation angle with the fully opened port closed, and the first motor rotation angle range is set. In a larger second motor rotation angle range, the valve body resists the spring force of the spring due to the pressure difference between the pressure in the first pressure chamber and the pressure in the second pressure chamber in the communication state of the pilot passage. and axially moved to the second axial position, the whole Electric valve, characterized in that open port. The throttle flow rate metering portion extends in an arc shape in the same direction as the rotation direction of the valve body, has a concave groove portion whose groove width gradually changes in the extending direction, and the slit formed in the valve body has the slit The position of alignment with the concave groove portion changes in the extending direction of the concave groove portion according to the rotational displacement of the valve body, so that the throttle flow rate of the throttle flow rate measuring portion is quantitatively determined according to the rotation angle of the valve body. electric valve according to claim 1 Symbol mounting, characterized in that it is set. In a refrigeration cycle apparatus for a refrigeration / refrigerator including a compressor, a condenser, an evaporator, and a refrigerant passage connecting them,
It has a flow path switching means for switching the flow path between the compressor → condenser → evaporator → compressor cooling operation circuit and the compressor → evaporator → compressor defrost operation circuit,
A refrigeration cycle apparatus for a refrigeration / refrigerator, wherein the motor-operated valve according to claim 1 or 2 is provided as an electric expansion valve with a fully open function on the inlet side of the evaporator.

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