JP3754193B2 - Volume control valve for variable capacity compressor - Google Patents

Volume control valve for variable capacity compressor Download PDF

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Publication number
JP3754193B2
JP3754193B2 JP27151697A JP27151697A JP3754193B2 JP 3754193 B2 JP3754193 B2 JP 3754193B2 JP 27151697 A JP27151697 A JP 27151697A JP 27151697 A JP27151697 A JP 27151697A JP 3754193 B2 JP3754193 B2 JP 3754193B2
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Japan
Prior art keywords
pressure
valve
sensitive member
control valve
chamber
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Expired - Fee Related
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JP27151697A
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Japanese (ja)
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JPH11107929A (en
Inventor
清 寺内
幸彦 田口
俊之 小倉
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Sanden Holdings Corp
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Sanden Corp
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Publication date
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Priority to JP27151697A priority Critical patent/JP3754193B2/en
Priority to EP19980118560 priority patent/EP0907021B1/en
Priority to DE1998603732 priority patent/DE69803732T2/en
Publication of JPH11107929A publication Critical patent/JPH11107929A/en
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Publication of JP3754193B2 publication Critical patent/JP3754193B2/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—Crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1859—Suction pressure

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Description

【０００１】
【発明の属する技術分野】
本案は特に自動車用空調装置に使用する可変容量圧縮機に関する。
【０００２】
【従来の技術】
従来の可変容量圧縮機のための容量制御弁としては、例えば図６に示すように、クランク室の圧力を調整することによりピストンのストロークを制御するものがある。その容量制御弁は、ベローズ１で吸入室の圧力を感知し、これに応じてボール弁２を開閉してクランク室に導入する吐出室からのガス量を調整するようにしている。これは、所謂内部制御タイプのベローズ弁構造である。このベローズ弁構造をベースとし、さらにボール弁２の上部に電磁アクチュエータ３を配置し、電磁力がボール弁２に作用するように構成している。したがって図７に示す様に電磁アクチュエータへの通電量によりベローズ弁の動作点、つまり吸入室の圧力制御点を変化させることが可能となる。
【０００３】
【発明が解決しようとする課題】
図６の容量制御弁ではボ−ル弁が吐出室圧力を受ける構造となっているため、図７に示すように電磁アクチュエーターへの通電量が一定でも吐出室圧力Ｐｄ１，Ｐｄ２，Ｐｄ３，…により吸入室圧力制御点が変化してしまう。つまり電磁アクチュエーターの通電量に対して吸入室圧力制御点が一義的に決まらず、最適な吐出容量制御を行わせるための制御方法が複雑になるという問題がある。
【０００４】
図６の構造では可変容量圧縮機の吸入室の圧力に上限があり、例えば図７では吸入室の圧力を３．７ｋｇ／ｃｍ２Ｇ以上で制御させることができない。
【０００５】
通常の車両走行時では吸入室の圧力は２ｋｇ／ｃｍ２Ｇ前後に維持制御されている場合が多いため問題はない。一方、車両加速時等には加速性能を高めるために吐出容量を減少させようとする場合がある。その場合には、吐出容量が減少して吸入室の圧力が上昇する。吸入室の圧力が３．７ｋｇ／ｃｍ２Ｇまで上昇すると、この圧力を維持するように吐出容量が制御され、運転条件によっては最小容量が維持できない場合が発生し、車両の走行性能に重大な影響を与えかねない。
【０００６】
それ故に本発明の課題は、電磁アクチュエータの通電量に対して吸入室圧力制御点が一義的に決まるようにし、かつ通電しない状態では可変容量圧縮機を強制的に最小容量に維持できるように構成した容量制御弁を提供することにある。
【０００７】
【課題を解決するための手段】
本発明によれば、可変容量圧縮機の吸入室又はクランク室の圧力を感知して伸縮する感圧部材と、前記感圧部材の伸縮に応答して開閉され、前記可変容量圧縮機の吐出室からクランク室に導入するガス量を調整する弁機構と、前記弁機構に外部信号により付勢力を与え、前記弁機構の実質的な開度を調整する外力付勢機構とを備え、前記クランク室の圧力を調整することにより前記可変容量圧縮機のピストンのストロークを制御する容量制御弁において、前記弁機構の弁体の弁座に当接する側とは反対側の面に前記クランク室又は前記吸入室の圧力を受けるように構成し、前記感圧部材は弁ケーシングに収容されており、前記感圧部材と前記弁ケーシングとの間に前記感圧部材を開弁方向に付勢するばね部材を介在させたことを特徴とする容量制御弁が得られる。
【０００８】
好ましくは、前記弁体の弁座に当接する側とは反対側の面の受圧面積は、前記弁体の弁座に当接する側で前記弁体が弁座と当接している状態での前記クランク室の圧力の受圧面積と同等に設定される。
【００１０】
前記弁機構は前記感圧部材の一端側に配置されており、前記感圧部材の他端は前記ケーシングに対して移動可能なように支持されているとよい。
【００１１】
【発明の実施の形態】
図１は本発明の実施の一形態に係る容量制御弁を示し、（ａ）は可変容量圧縮機の通常運転時の状態であり、（ｂ）は最小容量の状態である。
【００１２】
この容量制御弁は可変容量圧縮機の圧縮容量を制御するためのものであり、弁ケーシング１１と、この弁ケーシング１１内に配設され、内部を真空にしてばねを配置したベローズ１２と、このベローズ１２の図中下端を受け、弁ケーシング１１に移動可能なように支持されたガイド１３と、このガイド１３を図中上方に付勢するばね１４と、ベローズ１２の伸縮量を調整し、弁ケーシング１１の一部を構成する調整ネジ１５と、ベローズ１２の図中上端に当接して弁ケーシング１１に移動可能なように支持された伝達ロッド１６と、この伝達ロッド１６の他端に当接し、ベローズ１２の伸縮に応じて可変容量圧縮機の吐出室とクランク室との間の連通路１７を開閉する弁体１８と、この弁体１８をプランジャー１９及び伝達ロッド２０を介して閉弁方向に付勢する電磁力を発生させる電磁コイル２１とから横成される。
【００１３】
また弁体１８の弁座に当接する当接面１８ａとは反対側の面１８ｂは導圧路２２によってクランク室の圧力を受圧するように構成されている。尚、弁体１８の当接面１８ａ側のクランク室圧力受圧面積とこれとは反対側の面１８ｂのクランク室圧力受圧面積とは同等に設定されている。また弁体１８の側面１８ｃは弁ケーシング１１に移動可能なように支持され、かつ側面１８ｃと弁ケーシング１１側の挿入部との隙間は極小となるように設定されている。
【００１４】
次に図２をも参照して図１の容量制御弁の動作について説明する。
【００１５】
電磁コイル２１に通電しない状態では電磁力は発生しないため、圧力バランス状態では弁体１８を閉弁方向に付勢する力は無く、また可変容量圧縮機の吸入室の圧力が高い場合にはベロ−ズ１２は収縮するが、ばね１４によって図中上方に付勢されているため、弁体１８は常時開弁している。この状態で圧縮機を起動した場合、吐出室のガスが常時クランク室に導入されクランク室と吸入室との圧力差が増加するため、最小容量に維持される。
【００１６】
尚、ばね１４の付勢力は小さく、例えば電磁コイル２１に通電された電流値ｉ０（Ａ）にて発生する電磁力より小さく設定されている。このためｉ０（Ａ）以上の電流領域では弁体１８は閉弁することが可能である。
【００１７】
例えば圧力が６ｋｇ／ｃｍ２Ｇでバランスしている状態から圧縮機を起動し、吸入室圧力が２ｋｇ／ｃｍ２Ｇになるように電磁コイル２１への通電量を電流値ｉ３（Ａ）に調整すると、電磁コイル２１により発生する電磁力がばね１４の付勢力より大きいため弁体１８は閉弁し、これによりクランク室の圧力が低下し吸入室の圧力と同等になるため、圧縮機は最大容量に維持され、吸入室の圧力が徐々に低下する。吸入室の圧力が低下するに従いベローズ１２が伸長し、ガイド１３の図中下端が調整ネジ１５に当接するため、ばね１４の機能が消失する。この時弁体１８に作用するクランク室圧力による力は面１８ａ側と面１８ｂ側で相殺され、また吐出室圧力は弁体１８の軸方向には作用しないため、弁体１８は電磁力とベローズ１２に作用する吸入室圧力に応じて開閉制御される。つまり、吸入室の圧力が２ｋｇ／ｃｍ２Ｇまで低下するとベローズ１２が伸長し、弁体１８が開く方向に動作するため、吐出室のガスがクランク室に導入され、クランク室と吸入室との圧力差の増加により吐出容量が減少する。これにより吸入室の圧力が上昇するとベローズ１２が収縮し、弁体１８が閉じる方向に動作するため、クランク室の圧力が低下し、クランク室と吸入室との圧力差の減少により、吐出容量が増加する。
【００１８】
このようにして吸入室の圧力が所定値になるように弁体１８の開度が調整され、吐出容量が制御される。したがって図２に示すように電流値により吸入室圧力制御点が一義的に決まる。この状態から電流値をゼロにすると、ベロ−ズ１２が伸長し弁体１８が全開となり、クランク室と吸入室との圧力差が著しく増加するため最小容量に移行する。これにより吸入室の圧力が上昇し図２で３．５ｋｇ／ｃｍ２Ｇ以上に上昇し、ベローズ１２が収縮するような状態になっても、弁体１８はばね１４により図中上方に付勢されているため、弁体１８は常時開弁し、最小容量に維持される。
【００１９】
なお図３〜図５に本発明の実施の他の形態に係る容量制御弁をそれぞれ示すように、様々な変形が可能なことは言うまでもない。
【００２０】
【発明の効果】
請求項１記載の発明では、弁体の弁座に当接する側とは反対側の面がクランク室又は吸入室の圧力を受けているため、弁体に作用する吐出室の圧力による力を小さくすることができ、吐出室の圧力にほとんど影響しない吸入室圧力制御特性が得られる。
【００２１】
請求項２記載の発明では、弁体の弁座に当接する側とは反対側の面の受圧面積を、弁体が弁座に当接している状態でのクランク室の圧力の受圧面積と同等に設定しているため、弁体に作用する吐出室の圧力による力を無くすことができ、吐出室の圧力に影響しない吸入室圧力制御特性が得られる。
【００２２】
請求項３記載の発明では、電磁アクチエーターへの通電をゼロとした場合、ばね部材により感圧部材が図中上方にシフトし、弁体が開弁するため、常時最小容量が維持される。
【００２３】
請求項４記載の発明では、ベロ−ズの弁機構とは反対側の端部がケーシングに対して移動可能なように支持されているため、ベロ−ズの軸ずれが防止でき、制御機能及び耐久信頼性向上に寄与する。
【図面の簡単な説明】
【図１】本発明の実施の一形態に係る容量制御弁を示し、（ａ）は可変容量圧縮機の通常運転時の状態の縦断面図であり、（ｂ）は最小容量の状態の縦断面図である。
【図２】図１の容量制御弁の圧力制御特性を示すグラフである。
【図３】本発明の実施の他の形態に係る容量制御弁の縦断面図である。
【図４】本発明の実施のさらに他の形態に係る容量制御弁の縦断面図である。
【図５】本発明の実施のさらに他の形態に係る容量制御弁の縦断面図である。
【図６】従来の容量制御弁の縦断面図である。
【図７】図６の容量制御弁の圧力制御特性を示すグラフである。
【符号の説明】
１１ 弁ケーシング
１２ ベローズ
１３ ガイド
１４ ばね
１５ 調整ネジ
１６ 伝達ロッド
１７ 連通路
１８ 弁体
１８ａ 弁座に当接する当接面
１８ｂ 反対側の面
１８ｃ 側面
１９ プランジャー
２０ 伝達ロッド
２１ 電磁コイル
２２ 導圧路[0001]
BACKGROUND OF THE INVENTION
The present invention particularly relates to a variable capacity compressor used in an automobile air conditioner.
[0002]
[Prior art]
As a conventional capacity control valve for a variable capacity compressor, for example, as shown in FIG. 6, there is one that controls the stroke of the piston by adjusting the pressure in the crank chamber. The capacity control valve senses the pressure in the suction chamber with the bellows 1 and adjusts the amount of gas from the discharge chamber introduced into the crank chamber by opening and closing the ball valve 2 accordingly. This is a so-called internal control type bellows valve structure. The bellows valve structure is used as a base, and an electromagnetic actuator 3 is disposed above the ball valve 2 so that an electromagnetic force acts on the ball valve 2. Therefore, as shown in FIG. 7, the operating point of the bellows valve, that is, the pressure control point of the suction chamber can be changed by the amount of current supplied to the electromagnetic actuator.
[0003]
[Problems to be solved by the invention]
6 has a structure in which the ball valve receives the discharge chamber pressure. Therefore, as shown in FIG. 7, the discharge chamber pressures Pd1, Pd2, Pd3,. The suction chamber pressure control point changes. That is, there is a problem that the suction chamber pressure control point is not uniquely determined with respect to the energization amount of the electromagnetic actuator, and the control method for performing optimal discharge capacity control becomes complicated.
[0004]
6 has an upper limit on the pressure in the suction chamber of the variable capacity compressor. For example, in FIG. 7, the pressure in the suction chamber cannot be controlled at 3.7 kg / cm 2 G or more.
[0005]
During normal vehicle travel, there is no problem because the pressure in the suction chamber is often maintained and controlled at around 2 kg / cm 2 G. On the other hand, when the vehicle is accelerated, there is a case where the discharge capacity is to be decreased in order to improve acceleration performance. In that case, the discharge capacity decreases and the pressure in the suction chamber increases. When the pressure in the suction chamber rises to 3.7 kg / cm 2 G, the discharge capacity is controlled so as to maintain this pressure, and the minimum capacity may not be maintained depending on the driving conditions, which is critical for the running performance of the vehicle. May have an impact.
[0006]
Therefore, the problem of the present invention is that the suction chamber pressure control point is uniquely determined with respect to the energization amount of the electromagnetic actuator, and that the variable capacity compressor can be forcibly maintained at the minimum capacity without energization. Is to provide a capacity control valve.
[0007]
[Means for Solving the Problems]
According to the present invention, the pressure-sensitive member that expands and contracts by sensing the pressure in the suction chamber or the crank chamber of the variable capacity compressor, and the discharge chamber of the variable capacity compressor that is opened and closed in response to the expansion and contraction of the pressure-sensitive member. A valve mechanism that adjusts the amount of gas introduced into the crank chamber, and an external force urging mechanism that applies an urging force to the valve mechanism by an external signal and adjusts a substantial opening of the valve mechanism. In the displacement control valve that controls the stroke of the piston of the variable displacement compressor by adjusting the pressure of the crank chamber or the suction port on the surface opposite to the side that contacts the valve seat of the valve body of the valve mechanism The pressure sensitive member is accommodated in a valve casing, and a spring member that urges the pressure sensitive member in the valve opening direction is provided between the pressure sensitive member and the valve casing. Description characterized in that interposed Control valve can be obtained.
[0008]
Preferably, the pressure receiving area of the surface of the valve body opposite to the side in contact with the valve seat is such that the valve body is in contact with the valve seat on the side in contact with the valve seat of the valve body. It is set equal to the pressure receiving area of the crank chamber pressure.
[0010]
The valve mechanism may be disposed on one end side of the pressure-sensitive member, and the other end of the pressure-sensitive member may be supported so as to be movable with respect to the casing.
[0011]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 shows a capacity control valve according to an embodiment of the present invention, in which (a) shows a state during normal operation of the variable capacity compressor, and (b) shows a minimum capacity state.
[0012]
This capacity control valve is for controlling the compression capacity of the variable capacity compressor, and includes a valve casing 11, a bellows 12 disposed in the valve casing 11, and having a vacuum inside and a spring disposed therein, A guide 13 that receives the lower end of the bellows 12 in the figure and is supported by the valve casing 11 so as to be movable, a spring 14 that biases the guide 13 upward in the figure, and an expansion / contraction amount of the bellows 12 is adjusted. An adjustment screw 15 that constitutes a part of the casing 11, a transmission rod 16 that abuts on the upper end of the bellows 12 in the drawing and is supported so as to be movable on the valve casing 11, and abuts on the other end of the transmission rod 16. The valve body 18 opens and closes the communication passage 17 between the discharge chamber and the crank chamber of the variable capacity compressor according to the expansion and contraction of the bellows 12, and the valve body 18 is connected via the plunger 19 and the transmission rod 20. It made laterally from the electromagnetic coil 21 for generating an electromagnetic force for biasing in the valve closing direction.
[0013]
Further, the surface 18 b opposite to the contact surface 18 a that contacts the valve seat of the valve body 18 is configured to receive the pressure of the crank chamber by the pressure guide path 22. The crank chamber pressure receiving area on the contact surface 18a side of the valve body 18 and the crank chamber pressure receiving area on the opposite surface 18b are set to be equal. The side surface 18c of the valve body 18 is supported by the valve casing 11 so as to be movable, and the clearance between the side surface 18c and the insertion portion on the valve casing 11 side is set to be minimal.
[0014]
Next, the operation of the capacity control valve of FIG. 1 will be described with reference to FIG.
[0015]
Since no electromagnetic force is generated when the electromagnetic coil 21 is not energized, there is no force for urging the valve body 18 in the valve closing direction in the pressure balance state, and when the pressure in the suction chamber of the variable capacity compressor is high, the velocity is low. Although the valve 12 contracts, it is biased upward in the drawing by the spring 14, so that the valve body 18 is always open. When the compressor is started in this state, the gas in the discharge chamber is always introduced into the crank chamber and the pressure difference between the crank chamber and the suction chamber increases, so that the minimum capacity is maintained.
[0016]
The urging force of the spring 14 is small, for example, set to be smaller than the electromagnetic force generated at the current value i0 (A) energized in the electromagnetic coil 21. For this reason, the valve element 18 can be closed in a current region of i0 (A) or more.
[0017]
For example, the compressor is started from a state where the pressure is balanced at 6 kg / cm 2 G, and the energization amount to the electromagnetic coil 21 is adjusted to the current value i3 (A) so that the suction chamber pressure becomes 2 kg / cm 2 G. Then, since the electromagnetic force generated by the electromagnetic coil 21 is larger than the urging force of the spring 14, the valve body 18 is closed, thereby lowering the pressure in the crank chamber and equaling the pressure in the suction chamber. The capacity is maintained, and the pressure in the suction chamber gradually decreases. As the pressure in the suction chamber decreases, the bellows 12 expands, and the lower end of the guide 13 in the drawing contacts the adjustment screw 15, so that the function of the spring 14 is lost. At this time, the force due to the crank chamber pressure acting on the valve body 18 is canceled by the surface 18a side and the surface 18b side, and the discharge chamber pressure does not act in the axial direction of the valve body 18. The opening / closing control is performed in accordance with the suction chamber pressure acting on 12. That is, when the pressure in the suction chamber decreases to 2 kg / cm 2 G, the bellows 12 extends and the valve body 18 operates in the opening direction, so that the gas in the discharge chamber is introduced into the crank chamber, and the crank chamber and the suction chamber The discharge capacity decreases due to the increase in pressure difference. As a result, when the pressure in the suction chamber rises, the bellows 12 contracts and the valve body 18 moves in the closing direction, so that the pressure in the crank chamber decreases, and the discharge capacity is reduced due to a decrease in the pressure difference between the crank chamber and the suction chamber. To increase.
[0018]
In this way, the opening degree of the valve body 18 is adjusted so that the pressure in the suction chamber becomes a predetermined value, and the discharge capacity is controlled. Therefore, as shown in FIG. 2, the suction chamber pressure control point is uniquely determined by the current value. When the current value is reduced to zero from this state, the bellows 12 is extended and the valve body 18 is fully opened, and the pressure difference between the crank chamber and the suction chamber is remarkably increased, so that the capacity is shifted to the minimum capacity. As a result, the pressure in the suction chamber rises and rises to 3.5 kg / cm 2 G or more in FIG. 2, and even if the bellows 12 contracts, the valve body 18 is biased upward in the figure by the spring 14. Therefore, the valve body 18 is always opened and maintained at the minimum capacity.
[0019]
It is needless to say that various modifications are possible as shown in FIGS. 3 to 5 for the capacity control valve according to another embodiment of the present invention.
[0020]
【The invention's effect】
In the first aspect of the invention, since the surface of the valve body opposite to the side in contact with the valve seat receives the pressure of the crank chamber or the suction chamber, the force due to the pressure of the discharge chamber acting on the valve body is reduced. Thus, a suction chamber pressure control characteristic that hardly affects the pressure of the discharge chamber can be obtained.
[0021]
In the invention according to claim 2, the pressure receiving area of the surface of the valve body opposite to the side in contact with the valve seat is equal to the pressure receiving area of the pressure in the crank chamber when the valve body is in contact with the valve seat. Therefore, the force due to the pressure of the discharge chamber acting on the valve body can be eliminated, and a suction chamber pressure control characteristic that does not affect the pressure of the discharge chamber can be obtained.
[0022]
According to the third aspect of the present invention, when energization to the electromagnetic actuator is zero, the pressure sensitive member is shifted upward in the drawing by the spring member, and the valve body is opened, so that the minimum capacity is always maintained.
[0023]
In the invention according to claim 4, since the end opposite to the valve mechanism of the bellows is supported so as to be movable with respect to the casing, the shaft misalignment of the bellows can be prevented, and the control function and Contributes to improved durability and reliability.
[Brief description of the drawings]
1A and 1B show a capacity control valve according to an embodiment of the present invention, wherein FIG. 1A is a longitudinal sectional view of a variable capacity compressor during normal operation, and FIG. 1B is a longitudinal section of a minimum capacity state; FIG.
FIG. 2 is a graph showing pressure control characteristics of the capacity control valve of FIG. 1;
FIG. 3 is a longitudinal sectional view of a capacity control valve according to another embodiment of the present invention.
FIG. 4 is a longitudinal sectional view of a capacity control valve according to still another embodiment of the present invention.
FIG. 5 is a longitudinal sectional view of a capacity control valve according to still another embodiment of the present invention.
FIG. 6 is a longitudinal sectional view of a conventional capacity control valve.
7 is a graph showing a pressure control characteristic of the capacity control valve of FIG. 6;
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 11 Valve casing 12 Bellows 13 Guide 14 Spring 15 Adjustment screw 16 Transmission rod 17 Communication path 18 Valve body 18a Contact surface 18b contacted with a valve seat Opposite surface 18c Side surface 19 Plunger 20 Transmission rod 21 Electromagnetic coil 22 Induction path

Claims (3)

可変容量圧縮機の吸入室又はクランク室の圧力を感知して伸縮する感圧部材と、前記感圧部材の伸縮に応答して開閉され、前記可変容量圧縮機の吐出室からクランク室に導入するガス量を調整する弁機構と、前記弁機構に外部信号により付勢力を与え、前記弁機構の実質的な開度を調整する外力付勢機構とを備え、前記クランク室の圧力を調整することにより前記可変容量圧縮機のピストンのストロークを制御する容量制御弁において、前記弁機構の弁体の弁座に当接する側とは反対側の面に前記クランク室又は前記吸入室の圧力を受けるように構成し、前記感圧部材は弁ケーシングに収容されており、前記感圧部材と前記弁ケーシングとの間に前記感圧部材を開弁方向に付勢するばね部材を介在させたことを特徴とする容量制御弁。A pressure-sensitive member that expands and contracts by sensing the pressure in the suction chamber or crank chamber of the variable capacity compressor, and opens and closes in response to expansion and contraction of the pressure-sensitive member, and is introduced into the crank chamber from the discharge chamber of the variable capacity compressor A valve mechanism that adjusts the amount of gas; and an external force urging mechanism that applies an urging force to the valve mechanism by an external signal and adjusts a substantial opening of the valve mechanism, and adjusts the pressure in the crank chamber. In the displacement control valve for controlling the stroke of the piston of the variable displacement compressor, the pressure of the crank chamber or the suction chamber is received on the surface of the valve mechanism opposite to the side in contact with the valve seat. The pressure-sensitive member is housed in a valve casing, and a spring member that biases the pressure-sensitive member in the valve opening direction is interposed between the pressure-sensitive member and the valve casing. And capacity control valve. 前記弁体の弁座に当接する側とは反対側の面の受圧面積は、前記弁体の弁座に当接する側で前記弁体が弁座と当接している状態での前記クランク室の圧力の受圧面積と同等に設定されている請求項１記載の容量制御弁。  The pressure receiving area of the surface of the valve body opposite to the side in contact with the valve seat is such that the valve body is in contact with the valve seat on the side in contact with the valve seat of the valve body. The capacity control valve according to claim 1, wherein the capacity control valve is set to be equal to a pressure receiving area. 前記弁機構は前記感圧部材の一端側に配置されており、前記感圧部材の他端は前記ケーシングに対して移動可能なように支持されている請求項１又は２記載の容量制御弁。The capacity control valve according to claim 1 or 2, wherein the valve mechanism is disposed on one end side of the pressure-sensitive member, and the other end of the pressure-sensitive member is supported so as to be movable with respect to the casing.
JP27151697A 1997-10-03 1997-10-03 Volume control valve for variable capacity compressor Expired - Fee Related JP3754193B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP27151697A JP3754193B2 (en) 1997-10-03 1997-10-03 Volume control valve for variable capacity compressor
EP19980118560 EP0907021B1 (en) 1997-10-03 1998-10-01 Displacement control valve for use in a variable displacement compressor
DE1998603732 DE69803732T2 (en) 1997-10-03 1998-10-01 Stroke control valve for use in a variable displacement compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP27151697A JP3754193B2 (en) 1997-10-03 1997-10-03 Volume control valve for variable capacity compressor

Publications (2)

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JPH11107929A JPH11107929A (en) 1999-04-20
JP3754193B2 true JP3754193B2 (en) 2006-03-08

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JP2000009033A (en) * 1998-06-18 2000-01-11 Sanden Corp Volume control valve for variable displacement compressor
JP4118414B2 (en) 1998-10-29 2008-07-16 サンデン株式会社 Control circuit for capacity control valve of variable capacity compressor
JP2000283029A (en) * 1999-03-26 2000-10-10 Sanden Corp Capacity control valve and variable displacement compressor
JP4162419B2 (en) 2002-04-09 2008-10-08 サンデン株式会社 Variable capacity compressor
JP4118587B2 (en) 2002-04-09 2008-07-16 サンデン株式会社 Variable capacity compressor
JP4695032B2 (en) * 2006-07-19 2011-06-08 サンデン株式会社 Volume control valve for variable capacity compressor
JP4861900B2 (en) 2007-02-09 2012-01-25 サンデン株式会社 Capacity control system for variable capacity compressor
JP5270890B2 (en) 2007-09-26 2013-08-21 サンデン株式会社 Capacity control system for variable capacity compressor
JP5075682B2 (en) 2008-03-05 2012-11-21 サンデン株式会社 Capacity control system for variable capacity compressor
JP4930440B2 (en) * 2008-04-09 2012-05-16 株式会社デンソー Refrigeration cycle equipment

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JP2567947B2 (en) * 1989-06-16 1996-12-25 株式会社豊田自動織機製作所 Variable capacity compressor
KR910004933A (en) * 1989-08-09 1991-03-29 미다 가쓰시게 Variable displacement swash plate compressor
SG30647G (en) * 1991-01-28 1995-09-01 Sanden Corp Slant plate type compressor with variable displacement mechanism
JP3178631B2 (en) * 1993-01-11 2001-06-25 株式会社豊田自動織機製作所 Control valve for variable displacement compressor
JP3355002B2 (en) * 1993-10-15 2002-12-09 株式会社豊田自動織機 Control valve for variable displacement compressor
JP3255008B2 (en) * 1996-04-17 2002-02-12 株式会社豊田自動織機 Variable displacement compressor and control method thereof
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EP0907021A2 (en) 1999-04-07
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DE69803732D1 (en) 2002-03-21
JPH11107929A (en) 1999-04-20
EP0907021A3 (en) 1999-09-08

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