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WO2018038528A1 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

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Publication number
WO2018038528A1
WO2018038528A1 PCT/KR2017/009205 KR2017009205W WO2018038528A1 WO 2018038528 A1 WO2018038528 A1 WO 2018038528A1 KR 2017009205 W KR2017009205 W KR 2017009205W WO 2018038528 A1 WO2018038528 A1 WO 2018038528A1
Authority
WO
WIPO (PCT)
Prior art keywords
outlet
valve body
valve
adjustment groove
outlet port
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/KR2017/009205
Other languages
English (en)
Korean (ko)
Inventor
세오타츠야
마츠자키타카시
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Samsung Electronics Co Ltd
Original Assignee
Samsung Electronics Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2017140384A external-priority patent/JP2018112305A/ja
Application filed by Samsung Electronics Co Ltd filed Critical Samsung Electronics Co Ltd
Priority to KR1020187032973A priority Critical patent/KR102403519B1/ko
Priority to US16/327,752 priority patent/US11828502B2/en
Priority to EP17843948.5A priority patent/EP3486581B1/fr
Publication of WO2018038528A1 publication Critical patent/WO2018038528A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/30—Details
    • F16K3/314—Forms or constructions of slides; Attachment of the slide to the spindle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/062—Capillary expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to, for example, a valve structure used in a refrigeration refrigerator and a refrigerator using the same.
  • valve seat 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.
  • the said valve body In order to control the refrigerant flow rate of the refrigerant
  • 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.
  • this invention is made
  • 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.
  • tip part is a concept in which the movement trace of the front-end
  • the tip end portion of the adjustment groove overlaps at an angle shifted from the front directly with respect to the outlet port.
  • 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.
  • 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.
  • the distal end of the adjusting groove 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.
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • the outer edge of the said widening part moves away from the rotation trajectory of the said front end part.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • the overlapping area can be secured even when the area where the adjustment groove and the outlet overlaps becomes the lower limit (minimum).
  • 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.
  • 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.
  • 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.
  • 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.
  • the compressor 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. .
  • the rotation range of the valve body is less than 360 degrees, for example, by a stopper for starting point correction or position recognition.
  • manufacturing conditions are limited in order to make a valve structure small and simple, it is very difficult to form each area mentioned above.
  • 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.
  • 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.
  • 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.
  • valve structure which concerns on this invention is used as a four-way valve.
  • 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.
  • 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.
  • 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
  • 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.
  • the compressor 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. .
  • valve structure which can form a fully open area
  • 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.
  • a switching valve 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.
  • the flow rate adjusting width is expanded by switching a plurality of capillary tubes having different tube diameters to the switching valve.
  • 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.
  • 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.
  • 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.
  • each flow rate adjustment range can be widened in the refrigeration cycle for switching a plurality of evaporators.
  • 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.
  • 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.
  • 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.
  • 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. 2 is a schematic diagram showing a refrigerant circuit of the freezer refrigerator according to the embodiment.
  • FIG. 7 is a plan view illustrating the valve seat and the valve body according to the embodiment.
  • FIG. 9 is a view for explaining the operation of the valve structure and the flow of the refrigerant in the embodiment.
  • valve 10 is experimental data in which a valve structure in the same embodiment is compared with a conventional valve structure.
  • FIG. 11 is a Moriel diagram of a refrigeration cycle in the embodiment.
  • FIG. 12B is a layout view of a refrigerant circuit of the freezer refrigerator according to the second embodiment.
  • FIG. 19 is a view for explaining the operation of the valve structure and the flow of refrigerant in the embodiment.
  • 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.
  • the valve structure according to the first embodiment is used as a so-called four-way valve.
  • valve structure 20 which concerns on this embodiment is used for the refrigerator refrigerator 100, for example.
  • 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.
  • 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.
  • the refrigerator evaporator 231, the freezer compartment evaporator 232, the variable temperature room evaporator 233 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.
  • 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.
  • 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.
  • a capillary tube 243 for alternating temperature is provided in series as a pressure reducing means for the chamber.
  • 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.
  • 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).
  • the return pipe L and the capillary tubes 241, 242, 243 are connected by soldering or the like, for example.
  • 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 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.
  • 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,
  • the drive mechanism which rotates the valve body 4 is carried out.
  • 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.
  • 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.
  • 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.
  • 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.
  • the end portion formed between the upper portion 31 and the lower portion 32 has a lower surface of the lid body 62.
  • 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.
  • 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.
  • the 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)
  • 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.
  • the 1st valve seat 3A and the 2nd valve seat 3B are disk shapes of the same diameter dimension mutually.
  • first outlet 3a1 and second outlet 3a2 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.
  • first outlet 3a1 is connected to the inlet side of the refrigerating chamber evaporator 231 by the first outlet pipe 81
  • 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
  • One outlet 3a (hereinafter, this outlet 3a is called 3rd outlet 3a3) is formed in the 2nd valve seat 3B.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • the tip portion 4b is shaped to have a width dimension of 0.2 mm or more.
  • the semicircular portion of a circle having a diameter of 0.2 mm or more is used as the tip portion 4b.
  • the width dimension here is a dimension along the direction perpendicular
  • 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.
  • 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.
  • the center O of the outlet port 3a is displaced from the rotational trajectory of the tip portion 4b of the adjustment groove 4a.
  • 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.
  • 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
  • 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
  • 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.
  • 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.
  • valve structure 20 Next, the operation of the valve structure 20 and the flow of the refrigerant will be described.
  • 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
  • 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.
  • region is an area
  • region of this embodiment is an area
  • 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.
  • 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.
  • 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
  • the first outlet 3a1, the second outlet 3a2, and the second outlet are provided as spare sections.
  • region in which all 3 outflow openings 3a3 become a fully closed state is provided.
  • 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.
  • 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.
  • 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.
  • the valve body 4 rotates and the front end 4x of the adjustment groove 4a overlaps with the outlet port 3a, since the magnitude
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • corresponds to two valve seats 3 (1st valve seat 3A and 2nd valve seat 3B), and each of these valve seats 3, respectively.
  • two valve bodies 4 the first valve body 4A and the second valve body 4B
  • 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.
  • the first outlet 3a1 is connected to the inlet side of the refrigerating chamber evaporator 231 by the first outlet pipe 81
  • the second outlet 3a2 is the second outlet pipe 82. Is connected to the inlet side of the freezer evaporator 232.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • channel 4f is comprised so that it may overlap with the whole outflow opening 3a1.
  • 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.
  • 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.
  • valve structure 20 Next, the operation of the valve structure 20 and the flow of the refrigerant will be described.
  • the valve structure 20 of this embodiment is a fully closed area
  • 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.
  • region is an area
  • 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.
  • the flow rate of the refrigerant flowing out from the first outlet 3a1 and the second outlet 3a2 is gradually increased.
  • 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.
  • region to become is provided.
  • 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
  • the valve body 4 is provided with the 2nd full opening groove
  • the second fully open groove 4f is configured to overlap the entirety of the other outlet 3a, so that a pair of valves
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • this invention is not limited to 1st Embodiment and 2nd 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.
  • tip 4x of the adjustment groove 4a is in contact with the outer edge of the outlet 3a. It is formed to.
  • valve opening degree rotation angle at which refrigerant starts to flow
  • 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
  • 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.
  • the outlet port 3a of a reference position was arrange
  • the outlet 3a is arrange
  • 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.
  • 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.
  • 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).
  • 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
  • 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).
  • 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.
  • the internal combustion 4h2 may be parallel to the rotation trajectory P of the tip 4x.
  • the narrow part 4g is formed in parallel with the rotation trace P of the front-end
  • the flow volume can gradually increase after a coolant starts to flow to some extent, and it will adjust.
  • 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.
  • 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.
  • valve structure 20 of the present embodiment 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Multiple-Way Valves (AREA)

Abstract

La présente invention concerne une structure de soupape capable de commander avec haute précision un débit au moment où le fluide commence à s'écouler. La structure de soupape (20) comprend : un siège de soupape (3) dans lequel deux orifices de sortie (3a) pour décharger un fluide sont formés; et un corps de soupape (4) qui est prévu pour pouvoir tourner par rapport au siège de soupape (3) afin de régler le degré d'ouverture des orifices de sortie (3a). Le corps de soupape (4) comporte une rainure de commande d'écoulement (4d) le long de la direction circonférentielle dans laquelle la zone de chevauchement du corps de soupape (4) avec les orifices de sortie (3a) est modifiée par rotation, et le centre (O) des orifices de sortie (3a) est déplacée à partir d'une trace de rotation d'une extrémité avant (4b) de la rainure de commande d'écoulement (4d) qui commence à se chevaucher avec les orifices de sortie (3a) par une rotation du corps de soupape (4).
PCT/KR2017/009205 2016-08-24 2017-08-23 Réfrigérateur Ceased WO2018038528A1 (fr)

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US16/327,752 US11828502B2 (en) 2016-08-24 2017-08-23 Refrigerator
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KR20250146092A (ko) * 2024-03-29 2025-10-13 삼성전자주식회사 체크밸브 및 이를 포함하는 냉장고

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JP2015014294A (ja) * 2013-07-03 2015-01-22 日立アプライアンス株式会社 流量制御弁及び流量制御弁を備えた機器
KR20150063930A (ko) * 2013-12-02 2015-06-10 삼성전자주식회사 냉각 장치

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