JP2005156146A - Expansion valve - Google Patents

Expansion valve Download PDF

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Publication number
JP2005156146A
JP2005156146A JP2004318491A JP2004318491A JP2005156146A JP 2005156146 A JP2005156146 A JP 2005156146A JP 2004318491 A JP2004318491 A JP 2004318491A JP 2004318491 A JP2004318491 A JP 2004318491A JP 2005156146 A JP2005156146 A JP 2005156146A
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Prior art keywords
valve
spool
head
expansion
hole
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Japanese (ja)
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Peter Horstmann
ペーター　ホルストマン
Peter Satzger
ペーター　ザッツガー
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
    • 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
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
    • F16K3/267—Combination of a sliding valve and a lift valve
    • 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
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift 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
    • 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
    • F25B41/345—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids
    • F25B41/347—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids with the valve member being opened and closed cyclically, e.g. with pulse width modulation
    • 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
    • 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
    • F25B2500/12—Sound
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To solve problems of a noise in a valve seat and leakage in a spool valve. <P>SOLUTION: One end part of a hollow cylindrical valve spool 52 movable along an axial direction in a valve chest 50 for restricting or blocking a flow rate passing an expansion valve 24 between a flow-in part 34 and a flow-out part 36 is arranged to be closed by an end face wall 60, a circumferential face of the valve spool has a control hole 54 to be cooperated with a flow-in hole 42, a valve head 64 is provided in an opened end face side of the valve spool, the valve head is arranged to be coupled to the valve spool 52 via a valve stem 62, the valve head is directed to the valve seat 46, the valve seat is arranged to surround a flow-out opening 44 of a valve housing 38, and the control hole 54 is arranged to close the flow-in hole 42 already before the valve head 64 is mounted on the valve seat 46, relatively to the valve head 64 along the axial direction. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、膨張弁であって、弁ハウジングに設けられた弁室内で軸方向に移動可能な絞り体が設けられており、該絞り体がアクチュエータによって弁ばねの力に抗して運転パラメータおよび周辺パラメータに関連して調節され得ることにより、前記絞り体が流入部と流出部との間で当該膨張弁を通る通流量を絞るか、または遮断するようになっている形式のものに関する。   The present invention is an expansion valve, and is provided with a throttle body that is movable in the axial direction within a valve chamber provided in a valve housing. It can be adjusted in relation to the peripheral parameters, so that the throttle body is adapted to throttle or block the flow through the expansion valve between the inlet and outlet.

欧州特許出願公開第０９４５２９１号明細書に基づき、自動車の有効室の暖房および冷房のための装置および方法が公知である。冷媒は暖房運転時ではコンプレッサにより圧縮されて、３ポート２位置弁を介して室内熱交換器へ流入し、この室内熱交換器において冷媒は、圧縮により形成された熱の一部を、低温の車両室内空気へ引き渡す。室内熱交換器から冷媒は膨張装置へ流入し、この膨張装置において冷媒は、後続配置されたエバポレータ（蒸発器）において周辺空気から熱を吸収し得るようになる程度にまで冷却される。膨張装置は少なくとも１つの膨張弁を有している。   An apparatus and method for heating and cooling an automobile's effective room is known from EP-A-0945291. During the heating operation, the refrigerant is compressed by the compressor and flows into the indoor heat exchanger through the three-port two-position valve. In this indoor heat exchanger, the refrigerant removes a part of the heat formed by the compression at a low temperature. Delivered to vehicle interior air. The refrigerant flows from the indoor heat exchanger into the expansion device, and in this expansion device, the refrigerant is cooled to such an extent that heat can be absorbed from the surrounding air in an evaporator (evaporator) arranged subsequently. The expansion device has at least one expansion valve.

ドイツ連邦共和国特許第１０１２５７８９号明細書に基づき、膨張弁を備えた弁装置が公知である。この膨張弁には高圧側で冷媒が流入し、低圧側ではこの膨張弁から冷媒が流出する。高圧側から低圧側への通流量は絞り体によって制御される。この絞り体はハウジング固定の弁座と協働し、かつ作動装置によって軸方向に移動可能である。操作ユニットを備えた膨張弁は極めて複雑に形成されていて、大きな手間がかかる。弁が完全に閉鎖された状態における座弁の高いシール性は有利である。これによって原理的には、最小の容積流においてなお規定された高圧を入力制御することも可能となる。遮断機能は、たとえば安全上の理由から望ましいとされており、これにより、管路破断時に膨張弁の下流側で過度に大量の冷媒が流出してしまうことが回避される。しかし、特に振動時に絞り体が弁座に衝突すると、座弁はしばしば不都合な騒音を発生させる。   A valve device with an expansion valve is known from DE 10125789. The refrigerant flows into the expansion valve on the high pressure side, and the refrigerant flows out from the expansion valve on the low pressure side. The flow rate from the high pressure side to the low pressure side is controlled by the throttle body. This throttle body cooperates with a valve seat fixed to the housing and can be moved axially by means of an actuating device. The expansion valve provided with the operation unit is extremely complicated and takes a lot of time and effort. The high sealing performance of the seat valve when the valve is completely closed is advantageous. In principle, this also makes it possible to control the input of the high pressure that is still defined with a minimum volume flow. The shut-off function is desirable for safety reasons, for example, and this prevents an excessive amount of refrigerant from flowing out downstream of the expansion valve when the pipe line is broken. However, when the throttle body collides with the valve seat, particularly during vibration, the seat valve often generates inconvenient noise.

さらに、騒音の少ない運転を有するスプール弁が知られている。しかし、スプール弁は一般に完全に密には閉鎖されない。なぜならば、とりわけ冷媒として二酸化炭素が使用されるエアコンディショナにおいて発生するような特に高い圧力差において、弁スプールとハウジングとの間の運動ギャップを介して冷媒が流出してしまうからである。この冷媒体積流量はエアコンディショナの運転のためには大き過ぎてしまう。さらに、このような漏れに基づき、低い圧力では、エアコンディショナを効率および出力に関して好都合な運転領域において運転するために十分な圧力を形成することができなくなる。
欧州特許出願公開第０９４５２９１号明細書 ドイツ連邦共和国特許第１０１２５７８９号明細書 Furthermore, spool valves having a low noise operation are known. However, the spool valve is generally not completely tightly closed. This is because the refrigerant flows out through the motion gap between the valve spool and the housing, especially at a particularly high pressure difference, such as occurs in an air conditioner where carbon dioxide is used as the refrigerant. This refrigerant volume flow is too large for the operation of the air conditioner. Furthermore, based on such leaks, low pressures do not allow sufficient pressure to be created to operate the air conditioner in an operating region that is advantageous with respect to efficiency and power.
European Patent Application No. 0945291 German Patent No. 10125789

本発明の課題は、冒頭で述べた形式の膨張弁を改良して、座弁の持つ騒音問題と、スプール弁の持つ漏れ問題とが十分に解消されるような膨張弁を提供することである。   An object of the present invention is to provide an expansion valve that sufficiently improves the noise problem of the seat valve and the leakage problem of the spool valve by improving the expansion valve of the type described at the beginning. .

この課題を解決するために本発明の構成では、前記絞り体が中空円筒状の弁スプールであり、該弁スプールの一方の端部が端面壁により閉鎖されており、前記弁スプールの周面が少なくとも１つの制御孔を有しており、該制御孔が、弁ハウジングに設けられた少なくとも１つの流入孔と協働するようになっており、前記弁スプールの開いた方の端面側に皿形の弁ヘッドが設けられており、該弁ヘッドが弁ステムを介して前記弁スプールに結合されており、さらに前記弁ヘッドが弁座に向けられており、該弁座が、弁ハウジングに設けられた流出開口を取り囲んでおり、ただし前記制御孔は軸方向で前記弁ヘッドに対して相対的に、前記弁ヘッドが前記弁座に載着する前に前記流入孔が既に閉鎖されているように配置されているようにした。   In order to solve this problem, in the configuration of the present invention, the throttle body is a hollow cylindrical valve spool, one end of the valve spool is closed by an end face wall, and the peripheral surface of the valve spool is At least one control hole, and the control hole cooperates with at least one inflow hole provided in the valve housing. The valve head is coupled to the valve spool via a valve stem, the valve head is directed to the valve seat, and the valve seat is disposed on the valve housing. The control hole is axially relative to the valve head, so that the inflow hole is already closed before the valve head is mounted on the valve seat. It was arranged.

本発明によれば、スプール弁と座弁とを組み合わせることにより、膨張弁を一方では密に閉鎖し、他方では弁スプールによって比例的な開放のために使用することが可能となる。この場合、皿形の弁ヘッドと弁スプールとは、同じアクチュエータによって同時に操作される。アクチュエータが作動させられていない状態で膨張弁を開放しておきたいのか、または閉鎖しておきたいのかに応じて、弁ばねは弁スプールを、ひいてはそれと同時に弁ヘッドを開放方向または閉鎖方向に負荷することができる。重要となるのは、弁ばねと駆動装置とが、弁ヘッドにおける圧力差に基づいた力を克服し得るように弁ばねと駆動装置とが設計されかつ互いに調和されていることである。さらに、弁ヘッドが閉鎖する前に、弁スプールが既に閉鎖されていることが望ましい。この場合、流入孔に対する弁スプールの十分に大きなオーバラップが配慮されなければならない。これにより、振動および騒音を回避することができる。なぜならば、弁スプールに存在する、ほとんど閉鎖された環状ギャップに基づき、弁ヘッドを取り囲む流れはもはやほとんど存在しなくなり、したがって弁ヘッドにおいて、もはや騒音は形成されなくなるからである。弁ヘッドはほぼ騒音なしに弁座に載着する。   According to the invention, the combination of the spool valve and the seat valve allows the expansion valve to be closed tightly on the one hand and on the other hand to be used for proportional opening by the valve spool. In this case, the dish-shaped valve head and the valve spool are simultaneously operated by the same actuator. Depending on whether the expansion valve is to be opened or closed when the actuator is not actuated, the valve spring loads the valve spool and thus simultaneously the valve head in the opening or closing direction. can do. What is important is that the valve spring and the drive device are designed and harmonized with each other so that the valve spring and the drive device can overcome the force based on the pressure difference in the valve head. Furthermore, it is desirable that the valve spool is already closed before the valve head is closed. In this case, a sufficiently large overlap of the valve spool with respect to the inlet hole must be taken into account. Thereby, vibration and noise can be avoided. This is because, based on the almost closed annular gap present in the valve spool, there is no longer any flow surrounding the valve head and therefore no more noise is formed in the valve head. The valve head rests on the valve seat with almost no noise.

弁座のシール面としては、たとえば円形ゴムリング（Ｏリング）、金属製パッキン等のようなシール技術を種々のバリエーションで使用することができる。騒音特性に関しては、弁座が弾性的なエレメントによって形成されていると有利である。   As a sealing surface of the valve seat, for example, a sealing technique such as a circular rubber ring (O-ring), metal packing or the like can be used in various variations. With regard to noise characteristics, it is advantageous if the valve seat is formed by an elastic element.

さらに、本発明の有利な構成では、アクチュエータが電磁石であり、該電磁石のアーマチュアがアーマチュアプランジャを介して前記弁スプールもしくは前記弁ステムに作用するようになっている。電磁石はパルス幅変調された信号により制御され得ると有利である。この信号は特定の信号領域において弁スプールを比例弁として運動させ、その他の信号領域においては膨張弁の閉鎖を生ぜしめる。特定の閉鎖度が超えられると、弁スプールと弁ヘッドとは弁座における圧力差により自動的に閉鎖される。   Furthermore, in an advantageous configuration of the invention, the actuator is an electromagnet, and the armature of the electromagnet acts on the valve spool or the valve stem via an armature plunger. Advantageously, the electromagnet can be controlled by a pulse width modulated signal. This signal causes the valve spool to move as a proportional valve in certain signal regions and causes the expansion valve to close in other signal regions. When a certain degree of closure is exceeded, the valve spool and the valve head are automatically closed due to the pressure difference in the valve seat.

弁スプールの軸方向の運動により、弁ハウジングとピストンスプールの端面壁との間に封入されている容積が変化する。端面壁の両側の圧力が補償され得るようにするために、この端面壁には補償孔が設けられている。   The axial movement of the valve spool changes the volume enclosed between the valve housing and the end wall of the piston spool. In order to be able to compensate the pressure on both sides of the end face wall, the end face wall is provided with compensation holes.

弁ヘッドの閉鎖範囲では、この弁ヘッドに一方では高圧側の圧力が作用し、他方では低圧側の圧力が作用する。電磁石の所要の作動力を小さく保持するためには、弁ヘッドと弁スプールとに作用する圧力を少なくとも部分的に補償することが有利である。このためには、弁ハウジング内に、アクチュエータ寄りの側で第２の弁室が設けられている。この第２の弁室は接続開口を介して第１の弁室に接続されている。この接続開口は流出開口と同時に第２の弁ヘッドによって閉鎖される。この第２の弁ヘッドは閉鎖された状態で、第１の弁ヘッドと同じ有効面積を有している。第２の弁室と膨張弁の流出部との間の接続管路の働きにより、第１の弁ヘッドに作用する定圧側の圧力は、逆方向で第２の弁ヘッドに作用し、これにより相殺される。閉鎖された状態で両弁ヘッドが同じ有効面積を有している限り、同じく、第１の弁室内部で両弁ヘッドに作用する圧力も互いに相殺される。有効面積が互いに異なっていると、面積差に相当する合成力が一方の方向または他方の方向へ生ぜしめられる。   In the closed range of the valve head, the pressure on the high pressure side acts on this valve head on the one hand and the pressure on the low pressure side acts on the other. In order to keep the required actuation force of the electromagnet small, it is advantageous to at least partially compensate for the pressure acting on the valve head and the valve spool. For this purpose, a second valve chamber is provided in the valve housing on the side closer to the actuator. The second valve chamber is connected to the first valve chamber via a connection opening. This connection opening is closed by the second valve head simultaneously with the outflow opening. The second valve head is closed and has the same effective area as the first valve head. Due to the action of the connecting line between the second valve chamber and the outflow part of the expansion valve, the constant pressure side pressure acting on the first valve head acts on the second valve head in the reverse direction, thereby Offset. As long as both valve heads have the same effective area in the closed state, the pressure acting on both valve heads in the first valve chamber is also canceled out. When the effective areas are different from each other, a resultant force corresponding to the area difference is generated in one direction or the other direction.

本発明のその他の利点は以下の実施例の説明から明らかになる。図面には本発明の実施例が図示されている。図面、発明の詳細な説明および特許請求の範囲には、多数の特徴が組み合わされた形で含まれている。当業者であれば、これらの特徴を有利には個々に考察して、別の有利な組合せを形成することもできる。   Other advantages of the present invention will become apparent from the description of the following examples. The drawings illustrate embodiments of the invention. The drawings, the detailed description, and the claims include numerous features in combination. Those skilled in the art can advantageously consider these features individually to form other advantageous combinations.

以下に、本発明を実施するための最良の形態を図面につき詳しく説明する。   In the following, the best mode for carrying out the invention will be described in detail with reference to the drawings.

空調設備もしくはエアコンディショナ１０では、コンプレッサ（圧縮機）１２が矢印１４の方向で冷媒を搬送し、そしてこのときに冷媒の圧力および温度を増大させる。この冷媒はオイルセパレータ３２を介してガスクーラ１６に流入し、このガスクーラ１６内では冷媒が、圧縮時に発生した熱の一部を周辺環境へ放出する。この場合、ブロワ２０が空気流１８を空気側でガスクーラ１６に通して搬送する。その後に、この冷媒は内部熱交換器２２を通流し、この内部熱交換器２２では、コンプレッサ１２に戻る冷たい冷媒に熱が伝達される。冷却された冷媒は流入部３４を介して膨張弁２４に流入する。この膨張弁２４では、膨張によって冷媒からさらに熱が取り出される。膨張弁２４の流出部３６はエバポレータ（蒸発器）２６に接続されている。このエバポレータ２６内では、冷媒が周辺環境から熱を吸収する。このためには、別のブロワ２８が空気流３０を空気側でエバポレータ２６を通じて搬送する。エバポレータ２６から冷媒は内部熱交換器２２を介してコンプレッサ１２の吸込側に戻り、これによりこの冷凍回路は閉じられている。   In the air conditioner or the air conditioner 10, the compressor (compressor) 12 conveys the refrigerant in the direction of the arrow 14, and at this time, increases the pressure and temperature of the refrigerant. The refrigerant flows into the gas cooler 16 through the oil separator 32, and the refrigerant releases part of heat generated during compression to the surrounding environment in the gas cooler 16. In this case, the blower 20 carries the air stream 18 through the gas cooler 16 on the air side. Thereafter, the refrigerant flows through the internal heat exchanger 22, and heat is transferred to the cold refrigerant that returns to the compressor 12 in the internal heat exchanger 22. The cooled refrigerant flows into the expansion valve 24 through the inflow portion 34. In the expansion valve 24, heat is further extracted from the refrigerant by expansion. The outflow portion 36 of the expansion valve 24 is connected to an evaporator (evaporator) 26. In the evaporator 26, the refrigerant absorbs heat from the surrounding environment. For this purpose, another blower 28 carries the air stream 30 through the evaporator 26 on the air side. The refrigerant returns from the evaporator 26 to the suction side of the compressor 12 through the internal heat exchanger 22, thereby closing the refrigeration circuit.

図２に示した膨張弁２４は弁ハウジング３８を有している。この弁ハウジング３８はその周面に設けられた少なくとも１つの流入部３４と、カバー４０に設けられた流出部３６とを有している。カバー４０は弁ハウジング３８内に設けられた円筒状の弁室５０を閉鎖している。弁室５０内には、中空円筒状の弁スプール５２が支承されている。この弁スプール５２の周面は少なくとも１つの制御孔５４を有している。この制御孔５４は弁ハウジング３８に設けられた流入孔４２と協働して、膨張弁２４を通る通流量を制御する。弁スプール５２の一方の端面側は端面壁６０によって閉鎖されており、この端面壁６０には圧力補償孔５８が設けられている。弁スプール５２は弁ばね５６によって開放方向に負荷されており、この場合、弁ばね５６は一方ではカバー４０に、他方では端面壁６０にそれぞれ支持されている。膨張弁２４の開放された状態では、流入部３４が流入孔４２と制御孔５４とによって完全に開放されている。   The expansion valve 24 shown in FIG. 2 has a valve housing 38. The valve housing 38 has at least one inflow portion 34 provided on the peripheral surface thereof and an outflow portion 36 provided on the cover 40. The cover 40 closes a cylindrical valve chamber 50 provided in the valve housing 38. A hollow cylindrical valve spool 52 is supported in the valve chamber 50. The peripheral surface of the valve spool 52 has at least one control hole 54. The control hole 54 controls the flow rate through the expansion valve 24 in cooperation with the inflow hole 42 provided in the valve housing 38. One end face side of the valve spool 52 is closed by an end face wall 60, and the end face wall 60 is provided with a pressure compensation hole 58. The valve spool 52 is loaded in the opening direction by a valve spring 56. In this case, the valve spring 56 is supported on the one hand by the cover 40 and on the other hand by the end wall 60, respectively. When the expansion valve 24 is opened, the inflow portion 34 is completely opened by the inflow hole 42 and the control hole 54.

弁スプール５２の開いた端面側には、皿形の弁ヘッド６４が設けられている。この弁ヘッド６４は弁ステム６２によって弁スプール５２に結合されている。この弁ヘッド６４はカバー４０に設けられた流出孔４４に向けられており、この流出孔４４は流出部３６に通じている。弁室５０の側でカバー４０には環状溝４８が設けられており、この環状溝４８は流出孔４４を取り囲んでいる。さらに環状溝４８内には、円形ゴムリング（Ｏリング）が嵌め込まれている。   On the open end face side of the valve spool 52, a dish-shaped valve head 64 is provided. The valve head 64 is coupled to the valve spool 52 by a valve stem 62. The valve head 64 is directed to an outflow hole 44 provided in the cover 40, and the outflow hole 44 communicates with the outflow portion 36. An annular groove 48 is provided in the cover 40 on the valve chamber 50 side, and the annular groove 48 surrounds the outflow hole 44. Further, a circular rubber ring (O-ring) is fitted in the annular groove 48.

電磁石の形のアクチュエータ６６により、弁スプール５２と弁ヘッド６４とは同時に移動調節される。アクチュエータ６６はアーマチュア７０を有しており、このアーマチュア７０は電磁コイル６８の磁界により移動させられて、アーマチュアプランジャ７２を介して弁スプール５２もしくは弁ステム６２に作用する。アーマチュアプランジャ７２は弁スプール５２または弁ステム６２に固く結合されていてよいか、またはこれらの構成部分にルーズに接触していてもよい。その場合、弁ばね５６がこれらの構成部分の間の接触を生ぜしめる。   The valve spool 52 and the valve head 64 are moved and adjusted simultaneously by an actuator 66 in the form of an electromagnet. The actuator 66 has an armature 70, which is moved by the magnetic field of the electromagnetic coil 68 and acts on the valve spool 52 or the valve stem 62 via the armature plunger 72. The armature plunger 72 may be rigidly coupled to the valve spool 52 or the valve stem 62, or may loosely contact these components. In that case, the valve spring 56 makes contact between these components.

電磁コイル６８は制御ユニット（図示しない）によって、有利にはパルス幅変調された信号により制御されて、弁スプール５２を弁ヘッド６４と共に弁特性線８８（図５）に相応して移動させる。このときに、流入部３４はまず流入孔４２と制御孔５４とで絞られ、この場合、流入部３４は、弁スプール５２が流入孔４２を覆い隠し、弁スプール５２と弁ハウジング３８との間の運動ギャップを介して最小容積流だけしか流出部３６に到達しなくなるまで絞られる。この段階の間、電磁コイル６８は、弁ストロークｈと信号量Ｓ（％）との関係を示す弁特性線８８が比例範囲８４と、この比例範囲８４に移行範囲を介して続いた閉鎖範囲８６とを有するように制御される。閉鎖範囲８６では、弁ヘッド６４が弁座もしくは円形ゴムリング４６に接触し、そして弁ばね５６と、アクチュエータ６６と、流入部３４と流出部３６との間の圧力差とからの合成力により、この弁座に保持される。膨張弁２４はこの状態で密に閉鎖されている。この膨張弁２４は、弁座への弁ヘッド６４の載着時に騒音を発生させない。なぜならば、通流量が極めて小さく、したがって振動が回避されるからである。さらに、円形ゴムリング４６の弾性材料が、弁ヘッド６４の載着運動を緩衝する。弁スプール５２の軸方向運動時では、端面壁６０と弁ハウジング３８との間に封入された容積が変化する。補償孔５８を介して、相応する量補償および圧力補償が行われる。   The electromagnetic coil 68 is controlled by a control unit (not shown), preferably with a pulse width modulated signal, to move the valve spool 52 with the valve head 64 in accordance with the valve characteristic line 88 (FIG. 5). At this time, the inflow portion 34 is first throttled by the inflow hole 42 and the control hole 54. In this case, the inflow portion 34 covers the inflow hole 42 between the valve spool 52 and the valve housing 38. Through the motion gap, only the minimum volume flow is throttled until it reaches the outflow portion 36. During this stage, the electromagnetic coil 68 has a proportional range 84 with a valve characteristic line 88 indicating the relationship between the valve stroke h and the signal amount S (%), and a closed range 86 in which the proportional range 84 continues via the transition range. It is controlled to have. In the closed range 86, the valve head 64 contacts the valve seat or the circular rubber ring 46, and due to the combined force from the valve spring 56, the actuator 66, and the pressure difference between the inflow 34 and outflow 36, It is held by this valve seat. The expansion valve 24 is tightly closed in this state. The expansion valve 24 does not generate noise when the valve head 64 is mounted on the valve seat. This is because the flow rate is very small and therefore vibrations are avoided. Further, the elastic material of the circular rubber ring 46 cushions the mounting movement of the valve head 64. During the axial movement of the valve spool 52, the volume enclosed between the end wall 60 and the valve housing 38 changes. Corresponding amount compensation and pressure compensation are performed via the compensation hole 58.

図２に示した構成は、無電流状態の電磁コイル６８において開放されている膨張弁を示している。それに対して、図４に示した構成では、無電流状態の電磁コイル６８において膨張弁２４が閉鎖されている。この場合には、弁スプール５２を弁ヘッド６４と共に弁ばね５６の力に抗して開放するために、アクチュエータ６６が作動されなければならない。   The configuration shown in FIG. 2 shows an expansion valve that is opened in the electromagnetic coil 68 in a non-current state. On the other hand, in the configuration shown in FIG. 4, the expansion valve 24 is closed in the electromagnetic coil 68 in a non-current state. In this case, the actuator 66 must be actuated to open the valve spool 52 with the valve head 64 against the force of the valve spring 56.

図３に示した変化実施例は、アクチュエータ側に位置する第２の弁室７４が設けられている点で、図２に示した実施例とは異なっている。第２の弁室７４は接続開口８０を介して第１の弁室５０に接続されている。接続開口８０はアクチュエータ側で弁座７６によって取り囲まれる。この弁座７６は弁座４６と同様に形成されていてよく、皿形の弁ヘッド７８と協働する。この弁ヘッド７８は第１の弁ヘッド６４と結合されているので、第１の弁ヘッド６４が流出孔４４を閉鎖すると同時に弁ヘッド７８は接続開口８０を閉鎖する。弁ヘッド６４の有効面積と弁ヘッド７８の有効面積とは等しいので、両弁ヘッド６４，７８に作用する押圧力は互いに相殺される。外部から両弁ヘッド６４，７８に作用する押圧力も互いに相殺されるようにするためには、流出部３６の低圧側が接続管路８２によって第２の弁室７４に接続されている。弁スプール５２もしくは弁ヘッド６４，７８における圧力補償に基づき、小さな作動力しか生ぜしめられないので、電磁石６６を小さく設計することができる。   The modified embodiment shown in FIG. 3 is different from the embodiment shown in FIG. 2 in that a second valve chamber 74 located on the actuator side is provided. The second valve chamber 74 is connected to the first valve chamber 50 via the connection opening 80. The connection opening 80 is surrounded by a valve seat 76 on the actuator side. The valve seat 76 may be formed similar to the valve seat 46 and cooperates with a dish-shaped valve head 78. Since the valve head 78 is coupled to the first valve head 64, the valve head 78 closes the connection opening 80 at the same time as the first valve head 64 closes the outflow hole 44. Since the effective area of the valve head 64 and the effective area of the valve head 78 are equal, the pressing forces acting on both valve heads 64 and 78 cancel each other. In order to cancel out the pressing forces acting on the valve heads 64 and 78 from the outside, the low pressure side of the outflow portion 36 is connected to the second valve chamber 74 by a connection pipe line 82. Based on the pressure compensation in the valve spool 52 or the valve heads 64 and 78, only a small operating force can be generated, so that the electromagnet 66 can be designed to be small.

本発明による膨張弁を備えたエアコンディショナを示す概略的な回路図である。It is a schematic circuit diagram which shows the air conditioner provided with the expansion valve by this invention.

本発明による膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve by this invention.

図２に示した実施例に対する変化実施例を示す縦断面図である。It is a longitudinal cross-sectional view which shows the change Example with respect to the Example shown in FIG.

図２に示した実施例に対する別の変化実施例を示す縦断面図である。It is a longitudinal cross-sectional view which shows another change Example with respect to the Example shown in FIG.

本発明による膨張弁の弁特性線を示す線図である。It is a diagram which shows the valve characteristic line of the expansion valve by this invention.

符号の説明Explanation of symbols

１０ エアコンディショナ
１２ コンプレッサ
１６ ガスクーラ
１８ 空気流
２０ ブロワ
２２ 内部熱交換器
２４ 膨張弁
２６ エバポレータ
２８ ブロワ
３０ 空気流
３２ オイルセパレータ
３４ 流入部
３６ 流出部
３８ 弁ハウジング
４０ カバー
４２ 流入孔
４４ 流出孔
４６ 円形ゴムリング
４８ 環状溝
５０ 弁室
５２ 弁スプール
５４ 制御孔
５６ 弁ばね
５８ 圧力補償孔
６０ 端面壁
６２ 弁ステム
６４ 弁ヘッド
６６ アクチュエータ
６８ 電磁コイル
７０ アーマチュア
７２ アーマチュアプランジャ
７４ 第２の弁室
７６ 弁座
７８ 弁ヘッド
８０ 接続開口
８２ 接続管路
８４ 比例範囲
８６ 閉鎖範囲
８８ 弁特性線 DESCRIPTION OF SYMBOLS 10 Air conditioner 12 Compressor 16 Gas cooler 18 Air flow 20 Blower 22 Internal heat exchanger 24 Expansion valve 26 Evaporator 28 Blower 30 Air flow 32 Oil separator 34 Inflow part 36 Outflow part 38 Valve housing 40 Cover 42 Inflow hole 44 Outflow hole 46 Circular shape Rubber ring 48 Annular groove 50 Valve chamber 52 Valve spool 54 Control hole 56 Valve spring 58 Pressure compensation hole 60 End face wall 62 Valve stem 64 Valve head 66 Actuator 68 Electromagnetic coil 70 Armature 72 Armature plunger 74 Second valve chamber 76 Valve seat 78 Valve head 80 Connection opening 82 Connection line 84 Proportional range 86 Closed range 88 Valve characteristic line

Claims (5)

膨張弁（２４）であって、弁ハウジング（３８）に設けられた弁室（５０）内で軸方向に移動可能な絞り体（５２）が設けられており、該絞り体（５２）がアクチュエータ（６６）によって弁ばね（５６）の力に抗して運転パラメータおよび周辺パラメータに関連して調節され得ることにより、前記絞り体（５２）が流入部（３４）と流出部（３６）との間で当該膨張弁（２４）を通る通流量を絞るか、または遮断するようになっている形式のものにおいて、前記絞り体（５２）が中空円筒状の弁スプール（５２）であり、該弁スプール（５２）の一方の端部が端面壁（６０）により閉鎖されており、前記弁スプール（５２）の周面が少なくとも１つの制御孔（５４）を有しており、該制御孔（５４）が、弁ハウジング（３８）に設けられた少なくとも１つの流入孔（４２）と協働するようになっており、前記弁スプール（５２）の開いた方の端面側に皿形の弁ヘッド（６４）が設けられており、該弁ヘッド（６４）が弁ステム（６２）を介して前記弁スプール（５２）に結合されており、さらに前記弁ヘッド（６４）が弁座（４６）に向けられており、該弁座（４６）が、弁ハウジング（３８）に設けられた流出開口（４４）を取り囲んでおり、ただし前記制御孔（５４）は軸方向で前記弁ヘッド（６４）に対して相対的に、前記弁ヘッド（６４）が前記弁座（４６）に載着する前に前記流入孔（４２）が既に閉鎖されているように配置されていることを特徴とする膨張弁。   The expansion valve (24) is provided with a throttle body (52) movable in the axial direction within a valve chamber (50) provided in the valve housing (38), and the throttle body (52) is an actuator. (66) can be adjusted in relation to operating parameters and peripheral parameters against the force of the valve spring (56), so that the throttle body (52) is connected to the inflow part (34) and the outflow part (36). In which the flow rate through the expansion valve (24) is throttled or blocked, the throttle body (52) is a hollow cylindrical valve spool (52), One end of the spool (52) is closed by the end wall (60), and the peripheral surface of the valve spool (52) has at least one control hole (54), and the control hole (54 ) Provided in the valve housing (38) It cooperates with at least one inflow hole (42), and a dish-shaped valve head (64) is provided on the open end face side of the valve spool (52). (64) is coupled to the valve spool (52) via a valve stem (62), and the valve head (64) is directed to the valve seat (46), the valve seat (46) Enclosing an outflow opening (44) provided in the valve housing (38), wherein the control hole (54) is axially relative to the valve head (64). The expansion valve is arranged such that the inflow hole (42) is already closed before mounting on the valve seat (46). 前記弁座（４６）が、弾性的なエレメントにより形成されている、請求項１記載の膨張弁。   The expansion valve according to claim 1, wherein the valve seat is formed by an elastic element. アクチュエータ（６６）が電磁石（６８，７０）であり、該電磁石（６８，７０）のアーマチュア（７０）がアーマチュアプランジャ（７２）を介して前記弁スプール（５２）もしくは前記弁ステム（６２）に作用する、請求項１または２記載の膨張弁。   The actuator (66) is an electromagnet (68, 70), and the armature (70) of the electromagnet (68, 70) acts on the valve spool (52) or the valve stem (62) via the armature plunger (72). The expansion valve according to claim 1 or 2. 前記弁スプール（５２）の端面壁（６０）に補償孔（５８）が設けられている、請求項１から３までのいずれか１項記載の膨張弁。   The expansion valve according to any one of claims 1 to 3, wherein a compensation hole (58) is provided in an end wall (60) of the valve spool (52). 弁ハウジング（３８）内に、アクチュエータ（６６）寄りの側で第２の弁室（７４）が設けられており、該第２の弁室（７４）が接続開口（８０）を介して第１の弁室（５０）に接続されており、該接続開口（８０）が前記流出開口（４４）と同時に、皿形の第２の弁ヘッド（７８）によって閉鎖されるようになっており、該第２の弁ヘッド（７８）が第１の弁ヘッド（６４）に結合されていて、閉鎖された状態で第１の弁ヘッド（６４）と同じ有効面積を有しており、さらに前記流出部（３６）が接続管路（８２）を介して第２の弁室（７４）に接続されている、請求項１から４までのいずれか１項記載の膨張弁。   A second valve chamber (74) is provided in the valve housing (38) on the side closer to the actuator (66), and the second valve chamber (74) is connected to the first valve via the connection opening (80). The connection opening (80) is closed simultaneously with the outflow opening (44) by the dish-shaped second valve head (78), A second valve head (78) is coupled to the first valve head (64) and has the same effective area as the first valve head (64) in the closed state, and further the outlet The expansion valve according to any one of claims 1 to 4, wherein (36) is connected to the second valve chamber (74) via a connecting line (82).
JP2004318491A 2003-11-20 2004-11-01 Expansion valve Withdrawn JP2005156146A (en)

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DE102006001142B3 (en) * 2006-01-09 2007-06-28 Thomas Magnete Gmbh Air conditioning circuit control valve has a resilient axially sliding actuator with radial holes by which refrigerant may flow through bores in the housing according to its axial position
EP2004428B1 (en) * 2006-04-12 2011-09-21 Miro Gudzulic On-off valve
PT2708782E (en) 2012-09-14 2015-03-02 Gce Holding Ab Ignition reducing shut-off valve
DE102014217375A1 (en) 2014-09-01 2016-03-03 Robert Bosch Gmbh Electromagnetically actuated expansion valve
AU2018243466B2 (en) * 2017-03-31 2021-04-29 D.T. Davis Enterprises, Ltd. (D.B.A. Hovertech International) Flow control valve
DE102017107296A1 (en) * 2017-04-05 2018-10-11 Hanon Systems Shut-off valve and fluid shut-off device of a refrigerant compressor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01155164A (en) * 1987-09-01 1989-06-19 Misawa Homes Co Ltd Control valve
JPH09265322A (en) * 1996-03-29 1997-10-07 Osaka Gas Co Ltd Valve structure for pressure governor
DE19813674C1 (en) 1998-03-27 1999-04-15 Daimler Chrysler Ag Air conditioner for motor vehicle interior
DE10125789C1 (en) 2001-05-26 2003-06-12 Danfoss As Valve arrangement with expansion valve
JP3977066B2 (en) * 2001-12-03 2007-09-19 株式会社テージーケー Solenoid proportional valve
DE10219667A1 (en) * 2002-05-02 2003-11-13 Egelhof Fa Otto Expansion valve with electronic controller, for motor vehicle air conditioning systems using carbon dioxide as coolant, has two throttle points in series, with the passage cross-section of second point adjustable to the first point

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FR2862738A1 (en) 2005-05-27
FR2862738B1 (en) 2006-09-29
DE10354229A1 (en) 2005-06-23

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