JP2002122367A - Control valve - Google Patents
Control valveInfo
- Publication number
- JP2002122367A JP2002122367A JP2000316809A JP2000316809A JP2002122367A JP 2002122367 A JP2002122367 A JP 2002122367A JP 2000316809 A JP2000316809 A JP 2000316809A JP 2000316809 A JP2000316809 A JP 2000316809A JP 2002122367 A JP2002122367 A JP 2002122367A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- refrigerant
- flow rate
- valve port
- equal
- 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.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 75
- 238000005192 partition Methods 0.000 claims description 14
- 238000011144 upstream manufacturing Methods 0.000 claims description 14
- 230000007423 decrease Effects 0.000 claims description 7
- 238000000638 solvent extraction Methods 0.000 claims description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 29
- 230000001965 increasing effect Effects 0.000 description 6
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 4
- MWUXSHHQAYIFBG-UHFFFAOYSA-N Nitric oxide Chemical compound O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 3
- 238000010257 thawing Methods 0.000 description 3
- 229910002092 carbon dioxide Inorganic materials 0.000 description 2
- 239000001569 carbon dioxide Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- OTMSDBZUPAUEDD-UHFFFAOYSA-N Ethane Chemical compound CC OTMSDBZUPAUEDD-UHFFFAOYSA-N 0.000 description 1
- VGGSQFUCUMXWEO-UHFFFAOYSA-N Ethene Chemical compound C=C VGGSQFUCUMXWEO-UHFFFAOYSA-N 0.000 description 1
- 239000005977 Ethylene Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000001939 inductive effect Effects 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
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
- F25B41/30—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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Magnetically Actuated Valves (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Lift Valve (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、高圧側の冷媒圧力
が冷媒の臨界圧力以上となる超臨界サイクルに適用され
る流量制御用の制御弁であって、例えば超臨界ヒートポ
ンプにて温水を生成する給湯器に用いて有効である。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control valve for controlling a flow rate applied to a supercritical cycle in which a refrigerant pressure on a high pressure side is equal to or higher than a critical pressure of the refrigerant. It is effective for use in hot water heaters.
【０００２】[0002]
【従来の技術及び発明が解決しようとする課題】超臨界
ヒートポンプでは高圧側の冷媒圧力が高いので、循環す
る冷媒の密度が高く、体積流量が小さくても大きな質量
流量を得ることができる。このため、室外器にて大気中
から熱を吸収して温水を生成するヒートポンプ運転時に
おいては、フロン等を冷媒とする未臨界ヒートポンプに
比べて、少ない体積流量にて必要とする熱量（質量流
量）を得ることができる。2. Description of the Related Art In a supercritical heat pump, since the refrigerant pressure on the high pressure side is high, a high mass flow rate can be obtained even if the circulating refrigerant has a high density and a small volume flow rate. For this reason, when operating a heat pump in which an outdoor unit absorbs heat from the atmosphere to generate hot water, the required amount of heat (mass flow rate) is smaller than that of a subcritical heat pump using fluorocarbon or the like as a refrigerant. ) Can be obtained.
【０００３】したがって、体積流量（以下、単に流量と
呼ぶときには、体積流量を意味する。）変化量に対す
る、高圧側の冷媒圧力（圧縮機の吐出圧）及び質量流量
の変化量が、未臨界ヒートポンプに比べて大きくなって
しまうので、バルブ開度を小さくした（絞った）とき
に、必要以上に流量が低下して高圧側の冷媒圧力が過度
に上昇してしまうといった問題が発生し易く、流量が比
較的少ないときにおける流量制御が難しい。[0003] Therefore, the change in the refrigerant pressure (discharge pressure of the compressor) and the mass flow on the high pressure side with respect to the change in the volume flow (hereinafter, simply referred to as the flow) means the change in the subcritical heat pump. Therefore, when the valve opening is reduced (throttled), a problem that the flow rate is unnecessarily reduced and the refrigerant pressure on the high pressure side is excessively increased easily occurs. Is difficult to control when the flow rate is relatively small.
【０００４】本発明は、上記点に鑑み、バルブ開度を小
さくした（絞った）ときに、必要以上に流量が低下して
高圧側の冷媒圧力が過度に上昇してしまうことを防止す
ることを目的とする。SUMMARY OF THE INVENTION In view of the above, it is an object of the present invention to prevent the flow rate from decreasing more than necessary and the refrigerant pressure on the high pressure side from excessively increasing when the valve opening is reduced (throttled). With the goal.
【０００５】[0005]
【課題を解決するための手段】本発明は、上記目的を達
成するために、請求項１に記載の発明では、高圧側の冷
媒圧力が冷媒の臨界圧力以上となる超臨界サイクルに適
用され、冷媒流量を制御する制御弁であって、冷媒流路
（３１１）を上流側空間（３１１ａ）と下流側空間（３
１１ｂ）とに仕切る隔壁部（３１２）、及び隔壁部（３
１２）に形成され、上流側空間（３１１ａ）と下流側空
間（３１１ｂ）と連通させる弁口（３１３）を有するバ
ルブボディ（３１０）と、弁口（３１３）を流通する冷
媒流量を調節する弁体（３１４）とを備え、弁口（３１
３）に対する弁体（３１４）の相対位置によって決定す
るバルブ開度によらず、所定以上の流量を流通させるこ
とができる冷媒漏れ流路（３１３ｄ）が設けられている
ことを特徴とする。According to the present invention, in order to achieve the above object, the present invention is applied to a supercritical cycle in which the refrigerant pressure on the high pressure side is equal to or higher than the critical pressure of the refrigerant, A control valve for controlling a refrigerant flow rate, wherein a refrigerant flow path (311) is provided in an upstream space (311a) and a downstream space (311).
11b) and the partition (312) and the partition (3
12) a valve body (310) having a valve port (313) communicating with the upstream space (311a) and the downstream space (311b); and a valve for adjusting the flow rate of the refrigerant flowing through the valve port (313). (314) and a valve port (31).
A refrigerant leakage flow path (313d) through which a flow rate equal to or more than a predetermined flow rate is provided regardless of the valve opening determined by the relative position of the valve element (314) with respect to 3) is provided.
【０００６】これにより、バルブ開度を小さくした（絞
った）ときに、必要以上に流量が低下して高圧側の冷媒
圧力が過度に上昇してしまうことを未然に防止できるの
で、比較的流量が少ないときであっても、流量を容易に
制御することができる。Accordingly, when the valve opening is reduced (closed), it is possible to prevent the flow rate from unnecessarily lowering and the refrigerant pressure on the high pressure side from excessively increasing. Even when the amount is small, the flow rate can be easily controlled.
【０００７】なお、冷媒漏れ流路は、請求項２に記載の
発明のごとく、弁口（３１３）及び弁体（３１４）のう
ち、少なくともいずれか一方に溝部（３１３ｄ）を設け
ることにより形成してもよい。The coolant leakage passage is formed by providing a groove (313d) in at least one of the valve port (313) and the valve body (314), as in the second aspect of the present invention. You may.
【０００８】請求項３に記載の発明では、高圧側の冷媒
圧力が冷媒の臨界圧力以上となる超臨界サイクルに適用
され、冷媒流量を制御する制御弁であって、冷媒流路
（３１１）を上流側空間（３１１ａ）と下流側空間（３
１１ｂ）とに仕切る隔壁部（３１２）、及び隔壁部（３
１２）に形成され、上流側空間（３１１ａ）と下流側空
間（３１１ｂ）と連通させる弁口（３１３）を有するバ
ルブボディ（３１０）と、弁口（３１３）を流通する冷
媒流量を調節する弁体（３１４）とを備え、弁体（３１
４）のうち弁口（３１３）側には、弁口（３１３）側に
向かうほど断面積が縮小する第１、２テーパ部（３１４
ａ、３１４ｂ）、及び第１、２テーパ部（３１４ａ、３
１４ｂ）の間に形成されて断面積が一定となった円柱部
（３１４ｆ）とが設けられていることを特徴とする。According to the third aspect of the present invention, the control valve is applied to a supercritical cycle in which the refrigerant pressure on the high pressure side is equal to or higher than the critical pressure of the refrigerant, and controls the flow rate of the refrigerant. The upstream space (311a) and the downstream space (3
11b) and the partition (312) and the partition (3
12) a valve body (310) having a valve port (313) communicating with the upstream space (311a) and the downstream space (311b); and a valve for adjusting the flow rate of the refrigerant flowing through the valve port (313). And a valve body (314).
4), the first and second tapered portions (314) whose cross-sectional area decreases toward the valve port (313).
a, 314b) and the first and second tapered portions (314a, 314b).
14b) and a columnar portion (314f) having a constant cross-sectional area.
【０００９】これにより、弁体（３１４）が変位してバ
ルブ開度（弁口（３１３）に対する弁体３１４の相対位
置）が次第に小さくなっていくときに、円柱部（３１４
ｆ）の存在によって、バルブ開度によらず、実質的な冷
媒が流通することができる開口面積が一定となる状態が
発生し、弁口（３１３）円柱部（３１４ｆ）の側面との
間に冷媒の漏れ流路が形成されるので、バルブ開度によ
らず所定以上の流量を流通させることができる。As a result, when the valve element (314) is displaced and the valve opening (the relative position of the valve element 314 with respect to the valve port (313)) gradually decreases, the cylindrical portion (314) is displaced.
Due to the presence of f), a state occurs in which the opening area through which the substantial refrigerant can flow is constant irrespective of the valve opening degree, and between the valve port (313) and the side surface of the cylindrical portion (314f). Since a refrigerant leakage channel is formed, a flow rate equal to or higher than a predetermined value can be circulated regardless of the valve opening.
【００１０】したがって、バルブ開度を小さくした（絞
った）ときに、必要以上に流量が低下して高圧側の冷媒
圧力が過度に上昇してしまうことを未然に防止できるの
で、比較的流量が少ないときであっても、流量を容易に
制御することができる。Therefore, when the valve opening is reduced (closed), it is possible to prevent the flow rate from unnecessarily decreasing and the refrigerant pressure on the high pressure side from excessively increasing. Even when the amount is small, the flow rate can be easily controlled.
【００１１】請求項４に記載の発明では、高圧側の冷媒
圧力が冷媒の臨界圧力以上となる超臨界サイクルに適用
され、冷媒流量を制御する制御弁であって、冷媒流路
（３１１）を上流側空間（３１１ａ）と下流側空間（３
１１ｂ）とに仕切る隔壁部（３１２）、及び隔壁部（３
１２）に形成され、上流側空間（３１１ａ）と下流側空
間（３１１ｂ）と連通させる弁口（３１３）を有するバ
ルブボディ（３１０）と、弁口（３１３）を流通する冷
媒流量を調節する弁体（３１４）と、電気制御信号に応
じて弁体（３１４）を変位させる電気式のアクチュエー
タ（３２０）とを備え、電気制御信号値が所定値以下の
場合には、その電気制御信号値によらず、所定以上の流
量を流通させることができる冷媒漏れ流路（３１３ｄ）
が設けられていることを特徴とする。According to a fourth aspect of the present invention, the control valve is applied to a supercritical cycle in which the refrigerant pressure on the high pressure side is equal to or higher than the critical pressure of the refrigerant, and controls a refrigerant flow rate. The upstream space (311a) and the downstream space (3
11b) and the partition (312) and the partition (3
12) a valve body (310) having a valve port (313) communicating with the upstream space (311a) and the downstream space (311b); and a valve for adjusting the flow rate of the refrigerant flowing through the valve port (313). A body (314), and an electric actuator (320) for displacing the valve body (314) in response to the electric control signal. When the electric control signal value is equal to or less than a predetermined value, the electric control signal value Independently, a refrigerant leakage flow path (313d) capable of flowing a flow rate equal to or more than a predetermined flow rate
Is provided.
【００１２】これにより、バルブ開度を小さくした（絞
った）ときに、必要以上に流量が低下して高圧側の冷媒
圧力が過度に上昇してしまうことを未然に防止できるの
で、比較的流量が少ないときであっても、流量を容易に
制御することができる。Thus, when the valve opening is reduced (throttled), it is possible to prevent the flow rate from unnecessarily decreasing and the refrigerant pressure on the high pressure side from excessively increasing. Even when the amount is small, the flow rate can be easily controlled.
【００１３】また、電気制御信号値が所定値以下の場合
には、その電気制御信号値によらず、所定以上の流量を
流通させるので、制御弁の製造バラツキによらず、バル
ブ開度を小さくした（絞った）ときに、所定以上の流量
を確実に確保することができる。When the electric control signal value is equal to or less than a predetermined value, a flow rate equal to or more than a predetermined value is circulated regardless of the electric control signal value. When the flow rate is reduced (squeezed), a flow rate equal to or higher than a predetermined value can be ensured.
【００１４】したがって、本発明によれば、制御弁の製
造バラツキを吸収しつつ、比較的流量が少ないときであ
っても、流量を容易に制御することができる。Therefore, according to the present invention, it is possible to easily control the flow rate even when the flow rate is relatively small while absorbing the manufacturing variation of the control valve.
【００１５】因みに、上記各手段の括弧内の符号は、後
述する実施形態に記載の具体的手段との対応関係を示す
一例である。Incidentally, the reference numerals in parentheses of the above means are examples showing the correspondence with specific means described in the embodiments described later.
【００１６】[0016]
【発明の実施の形態】（第１実施形態）本実施形態は、
本発明に係る制御弁を、超臨界ヒートポンプサイクルに
て温水を生成する給湯器に適用したものであって、図１
は本実施形態に係る給湯器の模式図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment)
The control valve according to the present invention is applied to a water heater that generates hot water in a supercritical heat pump cycle.
FIG. 1 is a schematic diagram of a water heater according to the present embodiment.
【００１７】図１中、一転鎖線で囲まれた機器が超臨界
ヒートポンプを構成するものであり、１００は冷媒（本
実施形態では、二酸化炭素）を吸入圧縮する圧縮機であ
り、本実施形態では、圧縮機構と圧縮機構を駆動する電
動モータ（駆動手段）とが一体となった電動式の圧縮機
を採用している。In FIG. 1, a device surrounded by a chain line constitutes a supercritical heat pump, and a compressor 100 sucks and compresses a refrigerant (carbon dioxide in the present embodiment). In addition, an electric compressor in which a compression mechanism and an electric motor (drive means) for driving the compression mechanism are integrated is adopted.
【００１８】２００は圧縮機１００から吐出した高温・
高圧の冷媒と給湯水とを熱交換して給湯水を加熱する給
湯用熱交換器（ガスクーラ）であり、本実施形態では、
冷媒流れと給湯水流れとを対向流れとすることにより、
給湯水と冷媒との熱交換効率を高めている。Reference numeral 200 denotes a high temperature discharged from the compressor 100.
This is a hot water supply heat exchanger (gas cooler) that heats hot water by exchanging heat between high-pressure refrigerant and hot water. In the present embodiment,
By making the refrigerant flow and the hot water flow counter flow,
The heat exchange efficiency between the hot water and the refrigerant is improved.
【００１９】３００は、バルブ開度を調節することによ
り、超臨界サイクル内を循環する冷媒流量及び圧縮機１
００の吐出圧（高圧側圧力）を制御するとともに、冷媒
を減圧する制御弁であり、４００は制御弁３００にて減
圧された低温・低圧の冷媒を蒸発させて外気（大気）か
ら熱を吸収する室外器（蒸発器）である。なお、制御弁
３００の詳細は後述する。Reference numeral 300 designates the flow rate of the refrigerant circulating in the supercritical cycle and the compressor 1 by adjusting the valve opening.
The control valve 400 controls the discharge pressure (high-pressure side pressure) of 00 and decompresses the refrigerant, and 400 absorbs heat from the outside air (atmosphere) by evaporating the low-temperature and low-pressure refrigerant depressurized by the control valve 300. Outdoor unit (evaporator). The details of the control valve 300 will be described later.
【００２０】５００は室外器４００から流出する冷媒を
液相冷媒と気相冷媒とに分離して気相冷媒を圧縮機１０
０の吸入側に流出させるとともに、超臨界サイクル中の
余剰冷媒を蓄えるアキュムレータである。The reference numeral 500 designates a refrigerant which flows out of the outdoor unit 400 and is separated into a liquid-phase refrigerant and a gas-phase refrigerant.
This is an accumulator that allows the refrigerant to flow out to the suction side and store excess refrigerant during the supercritical cycle.
【００２１】また、６００は給湯用熱交換器２００にて
生成された高温の温水（給湯水）を保温貯蔵する保温タ
ンクであり、７００は給湯水を循環ささせるポンプであ
る。Reference numeral 600 denotes a heat retention tank for keeping the high-temperature hot water (hot water) generated by the hot water supply heat exchanger 200 warm and stored, and 700 a pump for circulating the hot water.
【００２２】次に、制御弁３００について述べる。Next, the control valve 300 will be described.
【００２３】図２は制御弁３００の断面図であり、３１
０は、冷媒流路３１１を上流側空間３１１ａと下流側空
間３１１ｂとに仕切る隔壁部３１２が形成されたステン
レス製のバルブボディであり、この隔壁部３１２には、
上流側空間３１１ａと下流側空間３１１ｂと連通させる
弁口３１３が設けられている。FIG. 2 is a sectional view of the control valve 300, and FIG.
Numeral 0 is a stainless steel valve body in which a partition wall 312 for partitioning the refrigerant flow passage 311 into an upstream space 311a and a downstream space 311b is formed.
A valve port 313 communicating with the upstream space 311a and the downstream space 311b is provided.
【００２４】３１４は弁口３１３の開度（バルブ開度）
を調節する柱状のニードル弁体（以下、弁体と略す。）
であり、この弁体３１４の弁口３１３側端部には、図３
に示すように、弁口３１３側に向かうほど断面積が縮小
する第１、２テーパ部３１４ａ、３１４ｂが形成されて
いる。Reference numeral 314 denotes the opening of the valve port 313 (valve opening).
The needle valve element (hereinafter abbreviated as valve element)
The end of the valve body 314 on the valve port 313 side is
As shown in FIG. 7, first and second tapered portions 314a and 314b whose cross-sectional area decreases toward the valve port 313 side are formed.
【００２５】なお、本実施形態では、第１テーパ部３１
４ａのテーパ比Ｃ（ＪＩＳ Ｂ ０６１２参照）が、第
２テーパ部３１４ｂのテーパ比Ｃより大きくなるように
段付き状のテーパ部としている。In this embodiment, the first tapered portion 31
The second tapered portion 314b has a stepped taper portion so that the taper ratio C of 4a (see JIS B 0612) is larger than the taper ratio C of the second tapered portion 314b.
【００２６】一方、弁口３１３のうち弁体３１４側の端
部には、弁体３１４側に向かうほど弁口３１３の開口面
積が増大する第１テーパ部３１３ａが形成され、弁口３
１３のうち弁体３１４と反対側（下流側空間３１１ｂ
側）の端部には、下流側に向かうほど弁口３１３の開口
面積が増大する第２テーパ部３１３ｂが形成され、両テ
ーパ部３１３ａ、１３１ｂ間を繋ぐ部分３１３ｃ（以
下、この部分をオリフィス部３１３ｃと呼ぶ。）は開口
面積が一定となるように円筒状となっている。On the other hand, at the end of the valve port 313 on the valve element 314 side, there is formed a first tapered portion 313a in which the opening area of the valve port 313 increases toward the valve element 314 side.
13 (the downstream space 311b)
A second tapered portion 313b whose opening area increases toward the downstream side is formed at the end of the second tapered portion 313b, and a portion 313c connecting the tapered portions 313a and 131b (hereinafter referred to as an orifice portion) is formed. 313c) is cylindrical so that the opening area is constant.
【００２７】因みに、弁口３１３の第１テーパ部３１３
ａは、図４に示すように、弁口３１３を弁体３１４によ
り閉じた際に、弁体３１４の第１テーパ部３１４ａに接
触して弁体３１４の座りを良くする弁座をとして機能す
るものである。Incidentally, the first tapered portion 313 of the valve port 313
As shown in FIG. 4, when the valve port 313 is closed by the valve body 314, a functions as a valve seat that contacts the first tapered portion 314a of the valve body 314 to improve the seating of the valve body 314. Things.
【００２８】また、弁口３１３の第１テーパ部３１３ａ
の一部には、図４、５に示すように、バルブ開度によら
ず、所定以上の流量を流通させることができる冷媒漏れ
流路を構成する溝部３１３ｄが形成されている。The first tapered portion 313a of the valve port 313
As shown in FIGS. 4 and 5, a groove 313d that forms a refrigerant leakage flow path through which a flow rate equal to or more than a predetermined flow rate can be formed irrespective of the valve opening degree is formed in a part of the groove.
【００２９】ここで、バルブ開度とは、弁口３１３に対
する弁体３１４の相対位置によって決定するもので、弁
体３１４の第２テーパ部３１４ｂが弁口３１３の中（オ
リフィス部３１３ｃ内）に入り込むほど、バルブ開度が
小さくなり、逆に第２テーパ部３１４ｂが弁口３１３の
外（オリフィス部３１３ｃ外）側に移動するほど、バル
ブ開度が大きくなる。Here, the valve opening is determined by the relative position of the valve element 314 with respect to the valve port 313, and the second tapered portion 314b of the valve element 314 is located in the valve port 313 (in the orifice section 313c). The valve opening degree becomes smaller as it enters, and conversely, the valve opening degree becomes larger as the second tapered portion 314b moves toward the outside of the valve port 313 (outside the orifice portion 313c).
【００３０】また、図２中、３２０は弁体３１４をその
長手方向に可動させるアクチュエータ部であり、このア
クチュエータ部３２０は、バルブボディ３１０に対して
回転することにより弁体３１４を可動させるロータ部３
２１、及びロータ部３２１周りに所定の回転磁界を誘起
することによりロータ部３２１を回転させる励磁コイル
部３２２、ロータ部３２１の回転運動を弁体３１４の長
手方向の直線運動に変換する送りネジ部材３２３等から
なるステッピングモータ式のものである。In FIG. 2, reference numeral 320 denotes an actuator section for moving the valve body 314 in the longitudinal direction. The actuator section 320 rotates the valve body 314 by rotating with respect to the valve body 310. 3
21, an exciting coil unit 322 for rotating the rotor unit 321 by inducing a predetermined rotating magnetic field around the rotor unit 321; a feed screw member for converting the rotational movement of the rotor unit 321 into a linear movement in the longitudinal direction of the valve body 314; 323 and the like.
【００３１】ここで、ロータ部３２１は、アルミニウム
にて成形された略円柱状のスリーブ３２１ａ、及びこの
スリーブ３２１ａの外周側に接着された円筒状の永久磁
石（マグネット）３２１ｂからなるものである。Here, the rotor portion 321 includes a substantially cylindrical sleeve 321a formed of aluminum, and a cylindrical permanent magnet (magnet) 321b adhered to the outer periphery of the sleeve 321a.
【００３２】そして、スリーブ３２１ａの略中央部に
は、円筒状の送りネジ部材３２３の外周部に形成された
ネジ部にネジ嵌合するネジ部が軸方向に延びて形成さ
れ、一方、送りネジ部３２３はバルブボディ３１０にカ
シメ固定されている。このため、ロータ部３２１が回転
すると、ロータ部３２１は回転しながら送りネジ部材３
２１の長手方向に直線的に移動する。At approximately the center of the sleeve 321a, a screw portion is formed extending in the axial direction to be screw-fitted to a screw portion formed on the outer peripheral portion of the cylindrical feed screw member 323. The portion 323 is caulked and fixed to the valve body 310. For this reason, when the rotor portion 321 rotates, the rotor portion 321 rotates while the feed screw member 3 rotates.
21 linearly moves in the longitudinal direction.
【００３３】また、弁体３１４は、スリーブ３２１ａ内
をその軸方向に貫通するようにスリーブ３２１ａに配設
された状態で、第１、２テーパ部３１４ａ、３１４ｂと
反対側の端部に装着された止め輪３１４ｃにより係止さ
れるようにスリーブ３２１ａに吊り下げられている。The valve body 314 is mounted on the end opposite to the first and second tapered portions 314a and 314b in a state of being disposed on the sleeve 321a so as to penetrate the sleeve 321a in the axial direction. It is suspended from the sleeve 321a so as to be locked by the retaining ring 314c.
【００３４】また、３１４ｄは、止め輪３１４ｃとスリ
ーブ３２１ａとの接触面圧が上昇する向き（弁体３１４
を弁口３１３側に押し付ける向き）の弾性力を弁体３１
４に作用させるコイルバネ（弾性体）であり、このコイ
ルバネ３１４ｄ（の弾性力）により、ロータ部３２１が
回転しながら弁口３１３側に移動する際に、弁体３１４
をロータ部３２１に追従させて弁口３１３側に移動させ
ることができる。The direction 314d is such that the contact surface pressure between the retaining ring 314c and the sleeve 321a increases (the valve element 314d).
To the valve body 313).
4 is a coil spring (elastic body) that acts on the valve element 314d when the rotor part 321 moves toward the valve port 313 while rotating.
Can be moved to the valve port 313 side by following the rotor portion 321.
【００３５】なお、励磁コイル部３２２は、第１、２コ
イル３２２ａ、３２２ｂ、磁路を構成する金属製のヨー
ク３２２ｃ、及び第１、２コイル３２２ａ、３２２ｂに
パルス電流を供給する端子部３２２ｄ等からなるもの
で、これれら３２２ａ〜３２２ｄは樹脂にてモールド固
定されている。The excitation coil section 322 includes first and second coils 322a and 322b, a metal yoke 322c forming a magnetic path, and a terminal section 322d for supplying a pulse current to the first and second coils 322a and 322b. 322a to 322d are molded and fixed with resin.
【００３６】因みに、３２２ｅは、バルブボディ３１０
に形成された位置決め用の穴部３１０ａに勘合する突起
部３２２ｆが形成されたバネ特性を有すＬ字状の位置決
めバネであり、この位置決めバネ３２２ｅは、Ｐネジに
て励磁コイル部３２２に固定されている。Incidentally, 322e is the valve body 310.
An L-shaped positioning spring having a spring characteristic is provided with a projection 322f that fits into the positioning hole 310a formed in the positioning hole 310a. The positioning spring 322e is fixed to the exciting coil portion 322 with a P screw. Have been.
【００３７】また、３３０はロータ部３２１と励磁コイ
ル部３２２との間に所定の磁気ギャップを形成するとと
もに、ロータ部３２１側を収納する圧力隔壁を構成する
ステンレス製のカバーであり、このカバー３３０はバル
ブボディ３１０に溶接されている。Reference numeral 330 denotes a stainless steel cover which forms a predetermined magnetic gap between the rotor section 321 and the exciting coil section 322 and forms a pressure partition for accommodating the rotor section 321 side. Are welded to the valve body 310.
【００３８】３３１、３３２はロータ部３２１がバルブ
ボディ３１０側に移動した際の最大移動量を規制するス
トッパであり、ロータ部３２１（スリーブ３２１ａ）に
圧入されたストッパ３３１とバルブボディ３１０に圧入
されたストッパ３３２とが衝突することによりロータ部
３２１の最大移動量が規制される。Reference numerals 331 and 332 denote stoppers for restricting the maximum amount of movement when the rotor portion 321 moves toward the valve body 310. The stopper 331 is press-fitted into the rotor portion 321 (sleeve 321a) and the stopper 331 is press-fitted into the valve body 310. When the stopper 332 collides, the maximum movement amount of the rotor portion 321 is regulated.
【００３９】そして、本実施形態では、弁体３１４の可
動可能な全ストローク寸法が、弁体３１４の第２テーパ
部３１４ｂの長さより大きくなるように設定されてい
る。なお、第２テーパ部３１４ｂの長さとは、第２テー
パ部３１４ｂのうち弁体３１４の長手方向と平行な方向
に測った寸法（テーパ比の分母寸法）である。In the present embodiment, the entire movable stroke dimension of the valve element 314 is set to be larger than the length of the second tapered portion 314b of the valve element 314. The length of the second tapered portion 314b is a dimension (a denominator dimension of the taper ratio) of the second tapered portion 314b measured in a direction parallel to the longitudinal direction of the valve element 314.
【００４０】次に、本実施形態に係る給湯器及び制御弁
３００の概略作動を述べる。Next, the general operation of the water heater and the control valve 300 according to this embodiment will be described.
【００４１】１．給湯器が停止しているとき、又は流量
が所定流量以下のとき 給湯器が停止しているときには、圧縮機１００及びポン
プ７００を停止させるとともに、図４に示すように、弁
体３１４の第１テーパ部３１４ａを弁口３１３の第１テ
ーパ部３１３ａに密着させるようにして弁口３１３を閉
じる。1. When the water heater is stopped, or when the flow rate is equal to or less than the predetermined flow rate. When the water heater is stopped, the compressor 100 and the pump 700 are stopped, and as shown in FIG. The valve port 313 is closed so that the tapered portion 314a is in close contact with the first tapered portion 313a of the valve port 313.
【００４２】このとき、第１テーパ部３１３ａの一部に
は溝部３１３ｄが形成されているので、バルブ開度によ
らず、所定流量以上の冷媒が流通することができるよう
になっている。At this time, since the groove portion 313d is formed in a part of the first tapered portion 313a, a refrigerant having a predetermined flow rate or more can flow regardless of the valve opening.
【００４３】２．給湯器を稼動させて温水を生成すると
き（通常流量調節領域） 励磁コイル部３２２に所定数のパルス電流を与えること
により、ロータ部３２１がそのパルス数に応じた回転角
度だけ回転するので、弁体３１４がその長手方向に移動
する。このため、弁体３１４の移動量（パルス数）に応
じたバルブ開度となるので、バルブ開度（パルス数）に
応じた冷媒流量となる。2. When hot water is operated to generate hot water (normal flow rate control region) By applying a predetermined number of pulse currents to excitation coil portion 322, rotor portion 321 rotates by a rotation angle corresponding to the number of pulses. The body 314 moves in its longitudinal direction. For this reason, the valve opening degree is determined according to the amount of movement (pulse number) of the valve element 314, and the refrigerant flow rate is determined according to the valve opening degree (pulse number).
【００４４】なお、このとき、バルブ開度は、給湯用熱
交換器２００に流入する給湯水の温度と給湯用熱交換器
２００から流出する冷媒の温度との差が所定の温度差Δ
Ｔ（本実施形態では、約１０℃）となるように、弁体３
１４の先端３１４ｅ（図４参照）が、弁口３１３の第１
テーパ部３１３ａのうち最も開口面積が小さくなる部位
３１３ｅ（図３参照）よりバルブ開度が縮小する側に位
置する範囲内で制御される。At this time, the difference between the temperature of the hot water flowing into the hot water supply heat exchanger 200 and the temperature of the refrigerant flowing out of the hot water supply heat exchanger 200 is determined by a predetermined temperature difference Δ
T (in the present embodiment, about 10 ° C.)
14 is connected to the first end 314e of the valve port 313 (see FIG. 4).
The control is performed within a range in which the valve opening is smaller than a portion 313e (see FIG. 3) of the tapered portion 313a having the smallest opening area.
【００４５】３．除霜運転時（最大流量領域） 給湯器を稼動させて温水を生成しているときに、室外器
４００の表面に霜が付着したときには、ポンプ７００を
停止させるとともに、図３に示すように、弁体３１４の
先端３１４ｅが、弁口３１３の第１テーパ部３１３ａの
うち最も開口面積が小さくなる部位３１３ｅよりバルブ
開度が拡大する側に位置する部位まで移動させる。3. At the time of defrosting operation (maximum flow rate region) When the hot water heater is operated to generate hot water, when frost adheres to the surface of the outdoor unit 400, the pump 700 is stopped, and as shown in FIG. The distal end 314e of the valve body 314 is moved to a portion of the first tapered portion 313a of the valve port 313 that is located on the side where the valve opening is enlarged from the portion 313e where the opening area is smallest.
【００４６】これにより、弁口３１３を流通する冷媒流
量が、バルブ開度（弁体３１４の移動量）によらず、弁
口３１３の開口面積によって決定する最大流量まで上昇
するとともに、圧縮機１００から吐出した冷媒が、制御
弁３００にて大きく減圧されることなく室外器４００に
流入するので、室外器４００の表面に付着した霜を融解
除去する。As a result, the flow rate of the refrigerant flowing through the valve port 313 rises to the maximum flow rate determined by the opening area of the valve port 313 regardless of the valve opening (movement amount of the valve element 314). Is discharged into the outdoor unit 400 without being greatly reduced in pressure by the control valve 300, so that the frost attached to the surface of the outdoor unit 400 is melted and removed.
【００４７】なお、本実施形態では、外気温と室外器出
口冷媒温度との温度差が所定温度差より大きく、かつ、
外気温と室外器出口冷媒温度との温度差が所定温度差よ
り大きい状態が所定時間以上継続したときに霜が室外器
４００の表面に付着したものとみなして、除霜運転を所
定時間だけ実行する。In this embodiment, the temperature difference between the outside air temperature and the outdoor unit outlet refrigerant temperature is larger than the predetermined temperature difference, and
When a state in which the temperature difference between the outside air temperature and the outdoor unit outlet refrigerant temperature is larger than the predetermined temperature difference continues for a predetermined time or more, it is considered that frost has adhered to the surface of the outdoor unit 400, and the defrosting operation is performed for a predetermined time. I do.
【００４８】次に、本実施形態の特徴を述べる。Next, the features of this embodiment will be described.
【００４９】図６は弁体３１４のパルス比（全ストロー
ク寸法に対応するパルス数に対する比率）と流量比（最
大流量に対する比率）との関係を示すグラフであり、Ａ
に示す領域が給湯器が停止しているとき又は流量が所定
流量以下のとき（微少流量制御領域）のパルス比を示し
ており、Ｂに示す領域が給湯器を稼動させて温水を生成
するとき（通常流量調節領域）のパルス比を示してお
り、Ｃに示す領域が除霜運転時（最大流量領域）のパル
ス比を示している。FIG. 6 is a graph showing the relationship between the pulse ratio of the valve element 314 (the ratio to the number of pulses corresponding to the entire stroke size) and the flow ratio (the ratio to the maximum flow).
The area indicated by B indicates the pulse ratio when the water heater is stopped or when the flow rate is equal to or less than the predetermined flow rate (small flow rate control area), and the area indicated by B indicates when the water heater is operated to generate hot water. The pulse ratio in the (normal flow control region) is shown, and the region indicated by C indicates the pulse ratio during the defrosting operation (the maximum flow region).
【００５０】そして、このグラフからも明らかなよう
に、微少流量制御領域Ａにおいては、、パルス比（バル
ブ開度）によらず、所定以上の流量を確保することがで
き、通常流量調節領域Ｂにおいては、パルス比（バルブ
開度）に応じて流量比が増減し、最大流量領域Ｃにおい
ては、パルス比（バルブ開度）の増減によらず、流量比
が最大流量比となることが判る。As is clear from this graph, in the minute flow rate control region A, a flow rate equal to or higher than a predetermined value can be secured regardless of the pulse ratio (valve opening degree). In, the flow ratio increases or decreases in accordance with the pulse ratio (valve opening), and in the maximum flow region C, the flow ratio becomes the maximum flow ratio regardless of the increase or decrease in the pulse ratio (valve opening). .
【００５１】したがって、バルブ開度を小さくした（絞
った）ときに、必要以上に流量が低下して高圧側の冷媒
圧力が過度に上昇してしまうことを未然に防止できるの
で、比較的流量が少ないときであっても、流量を容易に
制御することができる。Therefore, when the valve opening is reduced (closed), it is possible to prevent the flow rate from unnecessarily lowering and the refrigerant pressure on the high pressure side from excessively increasing. Even when the amount is small, the flow rate can be easily controlled.
【００５２】また、パルス比（電気制御信号値）が所定
値以下の場合には、そのパルス比によらず、所定以上の
流量を流通させるので、制御弁３００の製造バラツキに
よらず、バルブ開度を小さくした（絞った）ときに、所
定以上の流量を確実に確保することができる。したがっ
て、制御弁３００の製造バラツキを吸収しつつ、比較的
流量が少ないときであっても、流量を容易に制御するこ
とができる。When the pulse ratio (electric control signal value) is equal to or less than a predetermined value, the flow rate is equal to or higher than a predetermined value regardless of the pulse ratio. When the degree is reduced (squeezed), a flow rate equal to or higher than a predetermined value can be reliably ensured. Therefore, it is possible to easily control the flow rate even when the flow rate is relatively small while absorbing the manufacturing variation of the control valve 300.
【００５３】（第２実施形態）第１実施形態では、第１
テーパ部３１３ａの一部に溝部３１３ｄを形成すること
により、パルス比が所定値以下となってバルブ開度によ
らず所定以上の流量を流通させることができる冷媒漏れ
流路を構成したが、本実施形態は、図７に示すように、
弁体３１４の第１、２テーパ部３１４ａ、３１４ｂの間
に断面積が一定となった円柱部３１４ｆを設けて冷媒漏
れ流路を構成したものである。(Second Embodiment) In the first embodiment, the first
By forming the groove portion 313d in a part of the tapered portion 313a, the pulse ratio becomes equal to or less than a predetermined value, thereby forming a refrigerant leakage flow path capable of flowing a flow rate equal to or more than a predetermined value regardless of the valve opening degree. In the embodiment, as shown in FIG.
A cylindrical portion 314f having a constant cross-sectional area is provided between the first and second tapered portions 314a and 314b of the valve element 314 to form a refrigerant leakage flow path.
【００５４】これにより、弁体３１４の第２テーパ部３
１４ｂがオリフィス部３１３ｃ内に入り込んでいってバ
ルブ開度が次第に小さくなっていくときに、バルブ開度
（弁口３１３に対する弁体３１４の相対位置）によら
ず、開口面積が一定となって弁口３１３と円柱部３１４
ｆの側面との間に冷媒が流通するので、バルブ開度によ
らず所定以上の流量を流通させることができる。すなわ
ち、弁口３１３と円柱部３１４ｆの側面との間に冷媒の
漏れ流路が形成されることなる。Thus, the second tapered portion 3 of the valve element 314
When the valve opening gradually decreases as the valve 14b enters the orifice portion 313c, the opening area becomes constant regardless of the valve opening (the relative position of the valve body 314 with respect to the valve port 313). Mouth 313 and column 314
Since the refrigerant circulates between the side surface f and the side surface f, a predetermined flow rate or more can be circulated regardless of the valve opening. That is, a refrigerant leakage flow path is formed between the valve port 313 and the side surface of the cylindrical portion 314f.
【００５５】なお、円柱部３１４ｆの直径寸法は、オリ
フィス部３１３ｃの直径寸法より小さく、その寸法差
は、所定以上の流量を確保するに必要な開口面積を確保
することができる程度の大きさである。The diameter of the cylindrical portion 314f is smaller than the diameter of the orifice portion 313c, and the difference between the diameters is large enough to secure an opening area required to secure a flow rate equal to or more than a predetermined value. is there.
【００５６】因みに、第１、２テーパ部３１４ａ、３１
４ｂの間に円柱部３１４ｆが設けられているので、パル
ス比と流量比との関係はは、図８に示すようになる。Incidentally, the first and second tapered portions 314a, 314
Since the cylindrical portion 314f is provided between 4b, the relationship between the pulse ratio and the flow rate ratio is as shown in FIG.
【００５７】（その他の実施形態）上述の実施形態で
は、本発明に係る制御弁を給湯器に適用したが、本発明
はこれに限定されるものでなはく、空調装置にも適用す
ることができる。(Other Embodiments) In the above embodiment, the control valve according to the present invention is applied to a water heater, but the present invention is not limited to this, and may be applied to an air conditioner. Can be.
【００５８】また、熱を取り出すヒートポンプのみなら
ず、冷却のみを行う冷凍機にも適用することができる。The present invention can be applied not only to a heat pump for extracting heat but also to a refrigerator for cooling only.
【００５９】また、上述の実施形態では、冷媒として二
酸化炭素を採用したが、本発明はこれに限定されるもの
ではなく、例えばエチレン、エタン、酸化窒素等であっ
てもよい。In the above embodiment, carbon dioxide is employed as the refrigerant, but the present invention is not limited to this, and may be, for example, ethylene, ethane, nitrogen oxide, or the like.
【００６０】また、上述の実施形態では、弁口３１３に
溝部３１３ｄを設けたが、弁体３１４（第２テーパ部３
１４ｂ）に溝部３１３ｄを設けてもよい。同様に、弁口
３１３及び弁体３１４に溝部３１３ｄを設けてもよい。In the above-described embodiment, the groove 313d is provided in the valve port 313, but the valve element 314 (the second tapered part 3) is provided.
A groove 313d may be provided in 14b). Similarly, a groove 313d may be provided in the valve port 313 and the valve body 314.
【００６１】また、上述の実施形態では、パルス数によ
りアクチュエータ３２０の作動量を制御したが、本発明
はこれに限定されるものではなく、電流値や電圧値等の
その他の電気制御信号値によりアクチュエータ３２０を
制御してもよい。In the above-described embodiment, the operation amount of the actuator 320 is controlled by the number of pulses. However, the present invention is not limited to this, and is controlled by other electric control signal values such as a current value and a voltage value. The actuator 320 may be controlled.
【図１】本発明の第１実施形態に係る給湯器の模式図で
ある。FIG. 1 is a schematic diagram of a water heater according to a first embodiment of the present invention.
【図２】本発明の第１実施形態に係る制御弁の断面図で
ある。FIG. 2 is a sectional view of the control valve according to the first embodiment of the present invention.
【図３】本発明の第１実施形態に係る最大流量域におけ
る制御弁の絞り部分の拡大図である。FIG. 3 is an enlarged view of a throttle portion of a control valve in a maximum flow rate range according to the first embodiment of the present invention.
【図４】本発明の第１実施形態に係る微少流量域におけ
る制御弁の絞り部分の拡大図である。FIG. 4 is an enlarged view of a throttle portion of a control valve in a minute flow rate range according to the first embodiment of the present invention.
【図５】本発明の第１実施形態に係る制御弁の弁口部分
の拡大図である。FIG. 5 is an enlarged view of a valve port of the control valve according to the first embodiment of the present invention.
【図６】本発明の第１実施形態に係るパルス比（全スト
ローク寸法に対応するパルス数に対する比率）と流量比
（最大流量に対する比率）との関係を示すグラフであ
る。FIG. 6 is a graph showing a relationship between a pulse ratio (a ratio to the number of pulses corresponding to the entire stroke size) and a flow ratio (a ratio to a maximum flow) according to the first embodiment of the present invention.
【図７】本発明の第２実施形態に係る制御弁の絞り部分
の拡大図である。FIG. 7 is an enlarged view of a throttle portion of a control valve according to a second embodiment of the present invention.
【図８】本発明の第２実施形態に係るパルス比と流量比
との関係を示すグラフである。FIG. 8 is a graph showing a relationship between a pulse ratio and a flow ratio according to a second embodiment of the present invention.
３００…制御弁、３１０…バルブボディ、３１３…弁
口、３１３ａ…第１テーパ部、３１３ｂ…第２テーパ
部、３１３ｄ…溝部、３１４…弁体、３１４ａ…第１テ
ーパ部、３１４ｂ…第２テーパ部。300 control valve, 310 valve body, 313 valve opening, 313a first taper portion, 313b second taper portion, 313d groove portion, 314 valve body, 314a first taper portion, 314b second taper Department.
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ１６Ｋ 31/06 ３０５ Ｆ１６Ｋ 31/06 ３０５Ｍ Ｆ２４Ｈ 1/00 ６１１ Ｆ２４Ｈ 1/00 ６１１Ｃ Ｆ２５Ｂ 1/00 ３９５ Ｆ２５Ｂ 1/00 ３９５Ｚ Ｆターム(参考） 3H052 AA01 BA03 CB03 CC03 DA03 EA11 3H106 DA05 DA23 DB32 DB34 DC02 DC17 DD03 DD05 DD18 EE04 EE36 GB19 GB21 GC02 HH04 HH06 KK23 ──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. 7 Identification symbol FI Theme coat ゛ (Reference) F16K 31/06 305 F16K 31/06 305M F24H 1/00 611 F24H 1/00 611C F25B 1/00 395 F25B 1 / 00395Z F term (reference) 3H052 AA01 BA03 CB03 CC03 DA03 EA11 3H106 DA05 DA23 DB32 DB34 DC02 DC17 DD03 DD05 DD18 EE04 EE36 GB19 GB21 GC02 HH04 HH06 KK23
Claims (4)
となる超臨界サイクルに適用され、冷媒流量を制御する
制御弁であって、 冷媒流路（３１１）を上流側空間（３１１ａ）と下流側
空間（３１１ｂ）とに仕切る隔壁部（３１２）、及び前
記隔壁部（３１２）に形成され、前記上流側空間（３１
１ａ）と前記下流側空間（３１１ｂ）と連通させる弁口
（３１３）を有するバルブボディ（３１０）と、 前記弁口（３１３）を流通する冷媒流量を調節する弁体
（３１４）とを備え、 前記弁口（３１３）に対する前記弁体（３１４）の相対
位置によって決定するバルブ開度によらず、所定以上の
流量を流通させることができる冷媒漏れ流路（３１３
ｄ）が設けられていることを特徴とする制御弁。1. A control valve applied to a supercritical cycle in which a refrigerant pressure on a high pressure side is equal to or higher than a critical pressure of a refrigerant, and controls a refrigerant flow rate, wherein a refrigerant flow path (311) is connected to an upstream space (311a). A partition (312) partitioning from the downstream space (311b) and the partition (312) are formed and the upstream space (31
1a), a valve body (310) having a valve port (313) communicating with the downstream space (311b), and a valve element (314) for adjusting a flow rate of a refrigerant flowing through the valve port (313). A refrigerant leakage flow path (313) through which a flow rate equal to or more than a predetermined flow rate can flow regardless of the valve opening determined by the relative position of the valve element (314) with respect to the valve port (313).
d) a control valve, characterized in that:
３）及び前記弁体（３１４）のうち、少なくともいずれ
か一方に溝部（３１３ｄ）を設けることにより形成され
ていることを特徴とする請求項１に記載の制御弁。2. The refrigerant leakage flow path is connected to the valve port (31).
The control valve according to claim 1, wherein the control valve is formed by providing a groove (313d) in at least one of 3) and the valve body (314).
となる超臨界サイクルに適用され、冷媒流量を制御する
制御弁であって、 冷媒流路（３１１）を上流側空間（３１１ａ）と下流側
空間（３１１ｂ）とに仕切る隔壁部（３１２）、及び前
記隔壁部（３１２）に形成され、前記上流側空間（３１
１ａ）と前記下流側空間（３１１ｂ）と連通させる弁口
（３１３）を有するバルブボディ（３１０）と、 前記弁口（３１３）を流通する冷媒流量を調節する弁体
（３１４）とを備え、 前記弁体（３１４）のうち前記弁口（３１３）側には、
前記弁口（３１３）側に向かうほど断面積が縮小する第
１、２テーパ部（３１４ａ、３１４ｂ）、及び前記第
１、２テーパ部（３１４ａ、３１４ｂ）の間に形成され
て断面積が一定となった円柱部（３１４ｆ）が設けられ
ていることを特徴とする制御弁。3. A control valve which is applied to a supercritical cycle in which a refrigerant pressure on a high pressure side is equal to or higher than a critical pressure of a refrigerant and controls a refrigerant flow rate, wherein a refrigerant flow path (311) is connected to an upstream space (311a). A partition (312) partitioning from the downstream space (311b) and the partition (312) are formed and the upstream space (31
1a), a valve body (310) having a valve port (313) communicating with the downstream space (311b), and a valve element (314) for adjusting a flow rate of a refrigerant flowing through the valve port (313). On the valve port (313) side of the valve element (314),
The first and second tapered portions (314a, 314b) whose cross-sectional area decreases toward the valve port (313) and the first and second tapered portions (314a, 314b) are formed to have a constant cross-sectional area. A control valve characterized by having a cylindrical portion (314f).
となる超臨界サイクルに適用され、冷媒流量を制御する
制御弁であって、 冷媒流路（３１１）を上流側空間（３１１ａ）と下流側
空間（３１１ｂ）とに仕切る隔壁部（３１２）、及び前
記隔壁部（３１２）に形成され、前記上流側空間（３１
１ａ）と前記下流側空間（３１１ｂ）と連通させる弁口
（３１３）を有するバルブボディ（３１０）と、 前記弁口（３１３）を流通する冷媒流量を調節する弁体
（３１４）と、 電気制御信号に応じて前記弁体（３１４）を変位させる
電気式のアクチュエータ（３２０）とを備え、 前記電気制御信号値が所定値以下の場合には、その電気
制御信号値によらず、所定以上の流量を流通させること
ができる冷媒漏れ流路（３１３ｄ）が設けられているこ
とを特徴とする制御弁。4. A control valve which is applied to a supercritical cycle in which a refrigerant pressure on a high pressure side is equal to or higher than a critical pressure of a refrigerant and controls a refrigerant flow rate, wherein a refrigerant flow path (311) is connected to an upstream space (311a). A partition (312) partitioning from the downstream space (311b) and the partition (312) are formed and the upstream space (31
1a) a valve body (310) having a valve port (313) communicating with the downstream space (311b); a valve element (314) for adjusting a flow rate of refrigerant flowing through the valve port (313); An electric actuator (320) for displacing the valve element (314) in response to a signal, wherein when the electric control signal value is equal to or smaller than a predetermined value, the electric control signal value is equal to or higher than a predetermined value regardless of the electric control signal value. A control valve provided with a refrigerant leakage channel (313d) through which a flow rate can flow.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000316809A JP2002122367A (en) | 2000-10-17 | 2000-10-17 | Control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000316809A JP2002122367A (en) | 2000-10-17 | 2000-10-17 | Control valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002122367A true JP2002122367A (en) | 2002-04-26 |
Family
ID=18795704
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000316809A Pending JP2002122367A (en) | 2000-10-17 | 2000-10-17 | Control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002122367A (en) |
Cited By (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002147901A (en) * | 2000-11-15 | 2002-05-22 | Saginomiya Seisakusho Inc | Motorized valve |
| JP2005069599A (en) * | 2003-08-26 | 2005-03-17 | Denso Corp | Ejector system pressure reducing device |
| JP2005114655A (en) * | 2003-10-10 | 2005-04-28 | Komatsu Seiki Kk | Flowmeter |
| WO2006093149A1 (en) * | 2005-02-28 | 2006-09-08 | Daikin Industries, Ltd. | Expansion valve and refrigeration device |
| JP2006266663A (en) * | 2005-02-25 | 2006-10-05 | Mitsubishi Heavy Ind Ltd | Expansion valve and air conditioner |
| JP2006266634A (en) * | 2005-03-25 | 2006-10-05 | Fuji Koki Corp | Solenoid expansion valve |
| JP2007205565A (en) * | 2006-01-05 | 2007-08-16 | Fuji Koki Corp | Motor operated valve |
| JP2008517244A (en) * | 2004-10-21 | 2008-05-22 | ダンフォス アクチーセルスカブ | Valves used in cooling systems |
| JP2009036346A (en) * | 2007-08-03 | 2009-02-19 | Nidec Sankyo Corp | Flow control valve |
| DE102008039641A1 (en) | 2007-08-27 | 2009-04-30 | Denso Corp., Kariya-shi | Refrigeration cycle device |
| JP2009162366A (en) * | 2008-01-10 | 2009-07-23 | Fuji Koki Corp | Motor-operated valve and its assembling method |
| JP2009293560A (en) * | 2008-06-06 | 2009-12-17 | Nikkiso Co Ltd | Air bleed valve of hydraulic diaphragm pump |
| JP2010169181A (en) * | 2009-01-22 | 2010-08-05 | Kayaba Ind Co Ltd | Electromagnetic proportional throttle valve, and power steering device |
| JP2012177470A (en) * | 2011-01-31 | 2012-09-13 | Saginomiya Seisakusho Inc | Throttle valve device |
| CN103940159A (en) * | 2014-03-25 | 2014-07-23 | 浙江三花股份有限公司 | Electronic expansion valve |
| CN104396793A (en) * | 2014-11-22 | 2015-03-11 | 蚌埠依爱电子科技有限责任公司 | Poultry water drinking device with adjustable water flow |
| CN106352100A (en) * | 2015-07-17 | 2017-01-25 | 株式会社鹭宫制作所 | Pressure operating valve and frozen cycle |
| CN106352139A (en) * | 2015-07-17 | 2017-01-25 | 株式会社鹭宫制作所 | Electric valve and refrigeration cycle |
| CN106870750A (en) * | 2015-12-10 | 2017-06-20 | 浙江三花智能控制股份有限公司 | Two-period form electric expansion valve |
| JP2018059526A (en) * | 2016-09-30 | 2018-04-12 | 株式会社富士通ゼネラル | Throttle device and refrigeration cycle device |
| CN110836269A (en) * | 2018-08-17 | 2020-02-25 | 浙江盾安禾田金属有限公司 | Electronic expansion valve and air conditioning system using same |
| JP2020091038A (en) * | 2016-03-28 | 2020-06-11 | 株式会社不二工機 | Motor-operated valve |
| JP2020204407A (en) * | 2020-09-08 | 2020-12-24 | 株式会社不二工機 | Motor-operated valve |
| JP2021073419A (en) * | 2021-02-12 | 2021-05-13 | 株式会社不二工機 | Motor-operated valve |
| JP2021080982A (en) * | 2019-11-18 | 2021-05-27 | 株式会社鷺宮製作所 | Motor valve and refrigeration cycle system |
| CN113324054A (en) * | 2016-09-30 | 2021-08-31 | 株式会社鹭宫制作所 | Electric valve |
| JP2022046636A (en) * | 2020-09-08 | 2022-03-23 | 株式会社不二工機 | Motor-operated valve |
| JP2023003224A (en) * | 2021-06-23 | 2023-01-11 | ダイキン工業株式会社 | Air conditioning apparatus |
| EP4215781A1 (en) * | 2022-01-19 | 2023-07-26 | Fujikoki Corporation | Electric-operated valve |
-
2000
- 2000-10-17 JP JP2000316809A patent/JP2002122367A/en active Pending
Cited By (47)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002147901A (en) * | 2000-11-15 | 2002-05-22 | Saginomiya Seisakusho Inc | Motorized valve |
| JP2005069599A (en) * | 2003-08-26 | 2005-03-17 | Denso Corp | Ejector system pressure reducing device |
| JP2005114655A (en) * | 2003-10-10 | 2005-04-28 | Komatsu Seiki Kk | Flowmeter |
| JP2008517244A (en) * | 2004-10-21 | 2008-05-22 | ダンフォス アクチーセルスカブ | Valves used in cooling systems |
| JP2006266663A (en) * | 2005-02-25 | 2006-10-05 | Mitsubishi Heavy Ind Ltd | Expansion valve and air conditioner |
| WO2006093149A1 (en) * | 2005-02-28 | 2006-09-08 | Daikin Industries, Ltd. | Expansion valve and refrigeration device |
| US7832653B2 (en) | 2005-02-28 | 2010-11-16 | Daikin Industries, Ltd. | Expansion valve having a grooved valve member and refrigeration device including the same |
| JP2006266634A (en) * | 2005-03-25 | 2006-10-05 | Fuji Koki Corp | Solenoid expansion valve |
| JP4594142B2 (en) * | 2005-03-25 | 2010-12-08 | 株式会社不二工機 | Solenoid expansion valve |
| JP2007205565A (en) * | 2006-01-05 | 2007-08-16 | Fuji Koki Corp | Motor operated valve |
| KR101303536B1 (en) * | 2006-01-05 | 2013-09-03 | 가부시기가이샤 후지고오키 | Electric valve |
| JP2009036346A (en) * | 2007-08-03 | 2009-02-19 | Nidec Sankyo Corp | Flow control valve |
| DE102008039641A1 (en) | 2007-08-27 | 2009-04-30 | Denso Corp., Kariya-shi | Refrigeration cycle device |
| JP2009162366A (en) * | 2008-01-10 | 2009-07-23 | Fuji Koki Corp | Motor-operated valve and its assembling method |
| JP2009293560A (en) * | 2008-06-06 | 2009-12-17 | Nikkiso Co Ltd | Air bleed valve of hydraulic diaphragm pump |
| JP2010169181A (en) * | 2009-01-22 | 2010-08-05 | Kayaba Ind Co Ltd | Electromagnetic proportional throttle valve, and power steering device |
| JP2012177470A (en) * | 2011-01-31 | 2012-09-13 | Saginomiya Seisakusho Inc | Throttle valve device |
| JP2013139882A (en) * | 2011-01-31 | 2013-07-18 | Saginomiya Seisakusho Inc | Throttle valve apparatus |
| JP2014059063A (en) * | 2011-01-31 | 2014-04-03 | Saginomiya Seisakusho Inc | Throttle valve device |
| CN103940159A (en) * | 2014-03-25 | 2014-07-23 | 浙江三花股份有限公司 | Electronic expansion valve |
| CN104396793A (en) * | 2014-11-22 | 2015-03-11 | 蚌埠依爱电子科技有限责任公司 | Poultry water drinking device with adjustable water flow |
| CN106352139A (en) * | 2015-07-17 | 2017-01-25 | 株式会社鹭宫制作所 | Electric valve and refrigeration cycle |
| JP2017025974A (en) * | 2015-07-17 | 2017-02-02 | 株式会社鷺宮製作所 | Motor valve and refrigeration cycle |
| JP2017025975A (en) * | 2015-07-17 | 2017-02-02 | 株式会社鷺宮製作所 | Pressure operation valve and refrigeration cycle |
| CN106352100A (en) * | 2015-07-17 | 2017-01-25 | 株式会社鹭宫制作所 | Pressure operating valve and frozen cycle |
| CN106352139B (en) * | 2015-07-17 | 2018-11-20 | 株式会社鹭宫制作所 | Motor-driven valve and refrigerating circulation system |
| CN106352100B (en) * | 2015-07-17 | 2019-02-01 | 株式会社鹭宫制作所 | Pressure-operated valve and refrigerating circulation system |
| CN106870750A (en) * | 2015-12-10 | 2017-06-20 | 浙江三花智能控制股份有限公司 | Two-period form electric expansion valve |
| JP2020091038A (en) * | 2016-03-28 | 2020-06-11 | 株式会社不二工機 | Motor-operated valve |
| CN113324054A (en) * | 2016-09-30 | 2021-08-31 | 株式会社鹭宫制作所 | Electric valve |
| CN113324054B (en) * | 2016-09-30 | 2024-02-13 | 株式会社鹭宫制作所 | Electric valve |
| JP2018059526A (en) * | 2016-09-30 | 2018-04-12 | 株式会社富士通ゼネラル | Throttle device and refrigeration cycle device |
| CN113418014A (en) * | 2016-09-30 | 2021-09-21 | 株式会社鹭宫制作所 | Electric valve |
| CN113418014B (en) * | 2016-09-30 | 2023-10-17 | 株式会社鹭宫制作所 | Electric valve |
| CN110836269A (en) * | 2018-08-17 | 2020-02-25 | 浙江盾安禾田金属有限公司 | Electronic expansion valve and air conditioning system using same |
| JP2021080982A (en) * | 2019-11-18 | 2021-05-27 | 株式会社鷺宮製作所 | Motor valve and refrigeration cycle system |
| JP7242511B2 (en) | 2019-11-18 | 2023-03-20 | 株式会社鷺宮製作所 | Electric valve and refrigeration cycle system |
| JP7332191B2 (en) | 2020-09-08 | 2023-08-23 | 株式会社不二工機 | electric valve |
| JP2020204407A (en) * | 2020-09-08 | 2020-12-24 | 株式会社不二工機 | Motor-operated valve |
| JP7006981B2 (en) | 2020-09-08 | 2022-01-24 | 株式会社不二工機 | Solenoid valve |
| JP2022046636A (en) * | 2020-09-08 | 2022-03-23 | 株式会社不二工機 | Motor-operated valve |
| JP7129113B2 (en) | 2021-02-12 | 2022-09-01 | 株式会社不二工機 | electric valve |
| JP2021073419A (en) * | 2021-02-12 | 2021-05-13 | 株式会社不二工機 | Motor-operated valve |
| JP7248922B2 (en) | 2021-06-23 | 2023-03-30 | ダイキン工業株式会社 | air conditioner |
| JP2023003224A (en) * | 2021-06-23 | 2023-01-11 | ダイキン工業株式会社 | Air conditioning apparatus |
| EP4215781A1 (en) * | 2022-01-19 | 2023-07-26 | Fujikoki Corporation | Electric-operated valve |
| JP7440107B2 (en) | 2022-01-19 | 2024-02-28 | 株式会社不二工機 | electric valve |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2002122367A (en) | Control valve | |
| US9803770B2 (en) | Motor operated valve | |
| JP5022120B2 (en) | Motorized valves for air conditioning systems | |
| JP6194157B2 (en) | Motorized valve | |
| US20050262873A1 (en) | Refrigeration cycle | |
| EP2700853B1 (en) | Control valve | |
| WO2015040850A1 (en) | Ejector-type refrigeration cycle | |
| US7637115B2 (en) | Expansion device for an air conditioning system | |
| JP2010249246A (en) | Motor-operated valve and refrigeration cycle using the same | |
| JP2008064301A (en) | Pilot type control valve | |
| JP4570484B2 (en) | Composite valve, heat pump type air conditioner and control method thereof | |
| JP4336866B2 (en) | Heat pump cycle | |
| EP2685143B1 (en) | Control valve | |
| JP2010249247A (en) | Motor-operated valve and refrigeration cycle using the same | |
| JP4043076B2 (en) | Flow control valve | |
| JP2002340213A (en) | Flow control valve | |
| JP6194403B2 (en) | Motorized valve | |
| JPH0519717Y2 (en) | ||
| JP2002130507A (en) | Fluid control valve | |
| JP7299178B2 (en) | Electric valve and refrigeration cycle system | |
| JP7254678B2 (en) | Electric valve and refrigeration cycle system | |
| JP6572745B2 (en) | Ejector refrigeration cycle | |
| JP2023084804A (en) | Motor-operated valve and refrigeration cycle system | |
| JP4351561B2 (en) | Refrigeration cycle apparatus and electric control valve | |
| KR20230091413A (en) | Electric valve device for refrigerant control capable of multi stage control |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20061129 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20081022 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20081104 |
|
| A521 | Request for written amendment filed |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20081223 |
|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20090317 |