JP3862380B2 - Volume control valve for variable capacity compressor - Google Patents

Volume control valve for variable capacity compressor Download PDF

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Publication number
JP3862380B2
JP3862380B2 JP27297297A JP27297297A JP3862380B2 JP 3862380 B2 JP3862380 B2 JP 3862380B2 JP 27297297 A JP27297297 A JP 27297297A JP 27297297 A JP27297297 A JP 27297297A JP 3862380 B2 JP3862380 B2 JP 3862380B2
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JP
Japan
Prior art keywords
valve
pressure
sensitive member
control valve
capacity
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.)
Expired - Fee Related
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JP27297297A
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Japanese (ja)
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JPH11107930A (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 JP27297297A priority Critical patent/JP3862380B2/en
Priority to EP19980118877 priority patent/EP0908624B1/en
Priority to DE1998602885 priority patent/DE69802885T2/en
Publication of JPH11107930A publication Critical patent/JPH11107930A/en
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Publication of JP3862380B2 publication Critical patent/JP3862380B2/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
    • F04B2027/1854—External parameters
    • 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

Description

【０００１】
【発明の属する技術分野】
本発明は自動車用空調装置に使用する可変容量圧縮機に関し、特に圧縮容量を制御するための容量制御弁に関する。
【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５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６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。なお図６において、吐出室の圧力は一定とする。
【０００３】
【発明が解決しようとする課題】
図５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６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。
【０００４】
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。
【０００５】
それ故に本発明の課題は、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。
【０００６】
【課題を解決するための手段】
本発明によれば、弁ケーシングに収容され、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前記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閉弁方向の付勢力を与え、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、前記感圧部材を前記弁機構からみて前記外力付勢機構とは反対側に配置し、前記感圧部材の一端側には前記弁機構が配置されており、前記感圧部材の他端は、前記弁ケーシングに対して移動可能であるが、前記弁ケーシングの一部に当接した状態で支持されており、前記感圧部材と前記弁ケーシングとの間に、前記外力付勢機構による付勢力よりも小さい力で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。
【０００７】
前記感圧部材の一端側には前記弁機構が配置されており、前記感圧部材の他端は前記弁ケーシングに対して移動可能に支持されているとよい。
【０００８】
【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。
【０００９】
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、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。
【００１０】
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。なお吐出室の圧力は一定とする。
【００１１】
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。
【００１２】
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。
【００１３】
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の機能が消失し、これにより図５に示す従来の容量制御弁と同じ機能が得られる。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。
【００１４】
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。この状態から電流値をゼロにすると、ベローズ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は常開弁し、最小容量に維持される。
【００１５】
図３は本発明の実施の他の形態に係る容量制御弁を示す。この容量制御弁では、ばね１４が調整ネジ１５に当接するのに対し、ガイド１３は弁ケーシング１１の本体部分に軸方向で当接する構造となっている。この構造によれば、調整ネジ１５を操作することにより、ばね１４の付勢力を任意に調節できできる。なお図３の容量制御弁も図１の容量制御弁と同様な動作を行う。
【００１６】
図４は本発明の実施のさらに他の形態に係る容量制御弁を示す。この容量制御弁では、ガイド１３がベローズ１２の図中上端に固着されている。図４の容量制御弁も図１の容量制御弁と同様な動作を行う。
【００１７】
【発明の効果】
請求項１記載の発明では、ベローズとケーシングの間にばねを介在させ、電磁アクチュエーターへの通電を遮断した時に開弁するように構成しているため、吐出室のガスが常時クランク室に導入され、最小容量に維持することが可能となる。
【００１８】
請求項２記載の発明では、ベロー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、ベロー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】従来の容量制御弁の縦断面図である。
【図６】図５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
１９ プランジャー
２０ 伝達ロッド
２１ 電磁コイル[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a variable capacity compressor used for an air conditioner for automobiles, and more particularly to a capacity control valve for controlling the compression capacity.
[0002]
[Prior art]
As a conventional displacement control valve for a variable displacement compressor, for example, as shown in FIG. 5, there is a valve that controls the stroke of a piston by adjusting the pressure in a 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. 6, the operating point of the bellows valve, that is, the pressure control point of the suction chamber can be changed by the energization amount to the electromagnetic actuator. In FIG. 6, the discharge chamber pressure is constant.
[0003]
[Problems to be solved by the invention]
5 has an upper limit on the pressure in the suction chamber of the variable capacity compressor. For example, in FIG. 6, the pressure in the suction chamber cannot be controlled at 3.7 kg / cm 2 G or more.
[0004]
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.
[0005]
SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a capacity control valve configured so that a variable capacity compressor can be forcibly maintained at a minimum capacity.
[0006]
[Means for Solving the Problems]
According to the present invention, the pressure-sensitive member housed in the valve casing and which expands and contracts by sensing the pressure in the suction chamber or the crank chamber of the variable capacity compressor, and 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 from the discharge chamber of the capacity compressor into the crank chamber, and an urging force in the valve closing direction is applied to the valve mechanism by an external signal to adjust the substantial opening of the valve mechanism. A displacement control valve that controls the stroke of the piston of the variable displacement compressor by adjusting the pressure in the crank chamber, and the external force biasing mechanism as viewed from the valve mechanism. The valve mechanism is disposed on one end side of the pressure-sensitive member, and the other end of the pressure-sensitive member is movable with respect to the valve casing. In contact with a part of Are supported, between the valve casing and said pressure sensing member that, by interposing a spring member for urging in the valve opening direction the pressure sensing member in a force smaller than the urging force of the external force urging mechanism Is obtained.
[0007]
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 valve casing.
[0008]
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.
[0009]
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 urges the guide 13 upward in the figure, and an amount of expansion and contraction of the bellows 12 are adjusted. 11, an adjustment screw 15 that constitutes a part of the belt 11, a transmission rod 16 that is in contact with the upper end of the bellows 12 in the figure and supported so as to be movable on the valve casing 11, and abuts on the other end of the transmission rod 16, A valve body 18 that 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 this valve body 18 through a plunger 19 and a transmission rod 20. It made laterally from the electromagnetic coil 21 for generating an electromagnetic force for urging the valve direction.
[0010]
Next, the operation of the capacity control valve of FIG. 1 will be described with reference to FIG. The pressure in the discharge chamber is constant.
[0011]
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.
[0012]
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.
[0013]
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 contact with the adjustment screw 15 disappears, so that the function of the spring 14 is lost, which is the same as the conventional capacity control valve shown in FIG. Function is obtained. 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.
[0014]
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. When the current value is reduced to zero from this state, the bellows 12 is extended and the valve element 18 is fully opened, and the pressure difference between the crank chamber and the suction chamber is remarkably increased. As a result, even when the pressure in the suction chamber rises to 3.5 kg / cm 2 G or more in FIG. 2 and the bellows 12 contracts, the valve body 18 is urged upward in the figure by the spring 14. Therefore, the valve body 18 is normally opened and is maintained at the minimum capacity.
[0015]
FIG. 3 shows a capacity control valve according to another embodiment of the present invention. In this capacity control valve, the spring 14 is in contact with the adjusting screw 15, while the guide 13 is in contact with the main body portion of the valve casing 11 in the axial direction. According to this structure, the urging force of the spring 14 can be arbitrarily adjusted by operating the adjustment screw 15. The displacement control valve in FIG. 3 performs the same operation as the displacement control valve in FIG.
[0016]
FIG. 4 shows a capacity control valve according to still another embodiment of the present invention. In this capacity control valve, the guide 13 is fixed to the upper end of the bellows 12 in the figure. The displacement control valve of FIG. 4 performs the same operation as the displacement control valve of FIG.
[0017]
【The invention's effect】
According to the first aspect of the present invention, the spring is interposed between the bellows and the casing so that the valve is opened when the electromagnetic actuator is de-energized. Therefore, the gas in the discharge chamber is always introduced into the crank chamber. It becomes possible to maintain the minimum capacity.
[0018]
In the second aspect of the invention, since the end of the bellows opposite to the valve mechanism 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 durability reliability are improved. Contribute to.
[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 conventional capacity control valve.
6 is a graph showing a pressure control characteristic of the capacity control valve of FIG. 5;
[Explanation of symbols]
11 Valve casing 12 Bellows 13 Guide 14 Spring 15 Adjustment screw 16 Transmission rod 17 Communication path 18 Valve element 19 Plunger 20 Transmission rod 21 Electromagnetic coil

Claims (1)

弁ケーシングに収容され、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前記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閉弁方向の付勢力を与え、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、前記感圧部材を前記弁機構からみて前記外力付勢機構とは反対側に配置し、前記感圧部材の一端側に前記弁機構が配置されており、前記感圧部材の他端は、前記弁ケーシングに対して移動可能であるが、前記弁ケーシングの一部に当接した状態で支持されており、前記感圧部材と前記弁ケーシングとの間に、前記外力付勢機構による付勢力よりも小さい力で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 housed in the valve casing, which expands and contracts by sensing the pressure of the suction chamber or crank chamber of the variable capacity compressor, and is opened and closed in response to the expansion and contraction of the pressure sensitive member, and the discharge chamber of the variable capacity compressor A valve mechanism that adjusts the amount of gas introduced into the crank chamber, and an external force biasing mechanism that applies a biasing force in the valve closing direction to the valve mechanism by an external signal and adjusts a substantial opening of the valve mechanism A displacement control valve that controls the stroke of the piston of the variable displacement compressor by adjusting the pressure in the crank chamber, and the pressure sensitive member is disposed on the opposite side of the external force biasing mechanism as viewed from the valve mechanism The valve mechanism is disposed on one end side of the pressure-sensitive member, and the other end of the pressure-sensitive member is movable with respect to the valve casing, but is in contact with a part of the valve casing. It is supported by the state, A capacity characterized in that a spring member for biasing the pressure sensitive member in the valve opening direction with a force smaller than the biasing force by the external force biasing mechanism is interposed between the pressure sensitive member and the valve casing. Control valve.
JP27297297A 1997-10-06 1997-10-06 Volume control valve for variable capacity compressor Expired - Fee Related JP3862380B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP27297297A JP3862380B2 (en) 1997-10-06 1997-10-06 Volume control valve for variable capacity compressor
EP19980118877 EP0908624B1 (en) 1997-10-06 1998-10-06 Displacement control valve for use in a variable displacement compressor
DE1998602885 DE69802885T2 (en) 1997-10-06 1998-10-06 Stroke control valve for use in a variable displacement compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP27297297A JP3862380B2 (en) 1997-10-06 1997-10-06 Volume control valve for variable capacity compressor

Publications (2)

Publication Number Publication Date
JPH11107930A JPH11107930A (en) 1999-04-20
JP3862380B2 true JP3862380B2 (en) 2006-12-27

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Country Status (3)

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JP (1) JP3862380B2 (en)
DE (1) DE69802885T2 (en)

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Publication number Priority date Publication date Assignee Title
KR100340606B1 (en) * 1999-09-10 2002-06-15 이시카와 타다시 Control valve for variable capacity compressor
JP4121785B2 (en) * 2002-06-12 2008-07-23 サンデン株式会社 Control device for variable capacity compressor
US7063511B2 (en) * 2003-07-28 2006-06-20 Delphi Technologies, Inc. Integrated control valve for a variable capacity compressor
JP2006200435A (en) * 2005-01-20 2006-08-03 Fuji Koki Corp Control valve for variable displacement compressor
JP2008274756A (en) 2007-04-25 2008-11-13 Sanden Corp Control device of variable displacement compressor

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JP2661121B2 (en) * 1988-03-31 1997-10-08 日産自動車株式会社 Vehicle air conditioners and variable displacement compressors
JPH0331581A (en) * 1989-06-28 1991-02-12 Sanden Corp Variable-capacity swash plate type compressor
JPH04342883A (en) * 1991-05-17 1992-11-30 Sanden Corp Variable delivery swash plate type compressor
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

Also Published As

Publication number Publication date
EP0908624A2 (en) 1999-04-14
JPH11107930A (en) 1999-04-20
EP0908624A3 (en) 1999-09-08
EP0908624B1 (en) 2001-12-12
DE69802885T2 (en) 2002-08-01
DE69802885D1 (en) 2002-01-24

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