JP3678824B2 - Capacity controller for variable capacity compressor - Google Patents

Capacity controller for variable capacity compressor Download PDF

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Publication number
JP3678824B2
JP3678824B2 JP32494095A JP32494095A JP3678824B2 JP 3678824 B2 JP3678824 B2 JP 3678824B2 JP 32494095 A JP32494095 A JP 32494095A JP 32494095 A JP32494095 A JP 32494095A JP 3678824 B2 JP3678824 B2 JP 3678824B2
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pressure side
side valve
valve body
pressure
rod
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JPH09166086A (en
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久寿 広田
直之 伊藤
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TGK Co Ltd
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TGK Co Ltd
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Description

【０００１】
【発明の属する技術分野】
この発明は、自動車用空調装置などの冷凍サイクル中で冷媒を圧縮するために用いられる容量可変圧縮機の容量制御装置に関する。
【０００２】
【従来の技術】
自動車用空調装置の冷凍サイクルに用いられる圧縮機は、エンジンにベルトで直結されているので回転数制御を行うことができない。そこで、エンジンの回転数に制約されることなく適切な冷房能力を得るために、冷媒の容量（吐出量）を変えることのできる容量可変圧縮機が用いられている。
【０００３】
そのような容量可変圧縮機においては、一般に、気密に形成されたクランク室内で傾斜角可変に設けられた揺動板が回転軸の回転運動によって駆動されて揺動運動をし、その揺動板の揺動運動により往復動するピストンが吸入室の冷媒をシリンダ内に吸入して圧縮したあと吐出室に吐出し、クランク室内の圧力と吸入室内の圧力との差によって揺動板の傾斜角度を変化させることによって冷媒の吐出量が変化するようになっている。
【０００４】
そのような容量可変圧縮機において、必要に応じて揺動板の傾斜角を変えるために、吐出室とクランク室との間の連通を開閉する高圧側弁部と、吸入室とクランク室との間の連通を開閉する低圧側弁部とを、両弁部の開閉関係が逆になるように電磁ソレノイドによって開閉させている。
【０００５】
【発明が解決しようとする課題】
上述のような容量可変圧縮機の容量制御装置において、電磁ソレノイドで両弁部を開閉駆動する際には、吐出室内の圧力とクランク室内の圧力との差圧、及びクランク室内と吸入室内の圧力との差圧の、両方の差圧に抗して駆動しなければならない。
【０００６】
しかし、圧縮後の冷媒が吐出される吐出室は、例えば３０気圧程度という高圧になる場合があるので、吐出室に連通する高圧側弁部をその高圧に抗して開くためには、駆動用の電磁ソレノイドの電磁コイルに相当の大電流を通電する必要がある。
【０００７】
その結果、電磁ソレノイドの電磁コイルが著しく発熱をして、例えばシール用のＯリングが劣化して冷媒漏れが発生する等の不具合発生の原因になる場合がある。
【０００８】
そこで本発明は、弁部を小さい力で開閉させることができて、弁駆動用の電磁ソレノイドへの通電電流が小さくて済み、コイルの発熱を抑制することができる容量可変圧縮機の容量制御装置を提供することを目的とする。
【０００９】
【課題を解決するための手段】
上記の目的を達成するため、本発明の容量可変圧縮機の容量制御装置は、気密に形成されたクランク室内で回転軸に対して傾斜角可変に設けられて上記回転軸の回転運動によって駆動されて揺動運動をする揺動体と、上記揺動体に連結されて往復動することにより吸入室の冷媒をシリンダ内に吸入して圧縮したあと吐出室に吐出するピストンとを有し、上記クランク室内の圧力と上記吸入室内の圧力との差によって上記揺動体の傾斜角度を変化させて上記冷媒の吐出量を変化させるようにした容量可変圧縮機の容量を制御するための容量制御装置であって、上記吐出室と上記クランク室との間の連通を開閉する高圧側弁部と、上記クランク室と上記吸入室との間の連通を開閉する低圧側弁部と、上記高圧側弁部と上記低圧側弁部とを両弁部の開閉関係が逆になるように同時に開閉駆動する電磁ソレノイドとを設けたものにおいて、上記吐出室内の圧力と上記クランク室内の圧力との差圧が上記高圧側弁部を開く方向に作用する有効受圧面積と閉じる方向に作用する有効受圧面積とを等しく形成すると共に、上記クランク室内の圧力と上記吸入室内の圧力との差圧が上記低圧側弁部を開く方向に作用する有効受圧面積と閉じる方向に作用する有効受圧面積とを等しく形成したことを特徴とする。
【００１０】
なお、上記高圧側弁部と上記低圧側弁部の少なくとも一方が、棒状に形成された弁体の一方の端部に形成されて、その端部とそこから離れた位置の側面とに開口する冷媒通過孔が上記棒状弁体に形成されていて、上記棒状弁体の直径と弁部の有効径とが等しく形成されていてもよい。
【００１１】
また、冷媒が上記棒状部材の外周面に沿って上記吐出室側から上記クランク室側にリークするのを防止するためのシール膜部材が、上記棒状部材の外周部に設けられていてもよい。
【００１２】
【発明の実施の形態】
図面を参照して、本発明の実施の形態を説明する。
図１及び図２は、自動車用空調装置の冷凍サイクル中に用いられる容量可変圧縮機１０と、その容量制御装置３０を示しており、図１は最大容量状態、図２は最小容量状態である。
【００１３】
１１は、気密に構成されたクランク室１２内に配置され、駆動プーリ１３によって回転駆動される回転軸であり、回転軸１１に対して傾斜してクランク室１２内に配置された揺動板１４が、回転軸１１の回転にしたがって揺動する。
【００１４】
クランク室１２内の周辺部に配置されたシリンダ１５内には、ピストン１７が往復動自在に配置されており、ロッド１８によってピストン１７と揺動板１４とが連結されている。
【００１５】
したがって、揺動板１４が揺動すると、ピストン１７がシリンダ１５内で往復動して、シリンダ１５の上流側に形成された吸入室２０からシリンダ１５内に冷媒を吸入し、その冷媒をシリンダ１５内で圧縮した後、下流側の吐出室２１に吐出する。
【００１６】
容量制御装置３０を囲むブロック３１は、容量可変圧縮機１０と同じブロックで形成されており、そこに形成された同軸多段状の孔内に、本体筒３２が嵌め込まれている。３３は、その嵌合部及びその他の嵌合部をシールするためのＯリングである。
【００１７】
本体筒３２の軸線位置に形成された貫通孔内には、棒状の高圧側弁体３４とそれよりやや太く形成された棒状の低圧側弁体３５とが、軸方向に進退自在に同軸線上に真っ直ぐに配置されている。
【００１８】
なお、高圧側弁体３４には、その外周面に沿って冷媒が吐出室２１側からクランク室１２側にリークするのを防止するための可撓性のあるダイアフラム３６（シール膜部材）が外周部に取り付けられている。したがって、吐出室２１からクランク室１２に流れる冷媒は、必ず後述の高圧側弁部４４を通ることになる。
【００１９】
ダイアフラム３６を取り付けるために、高圧側弁体３４は二つの部品３４ａ，３４ｂに分けて形成されているが、一部品で形成してもよい。また、高圧側弁体３４と低圧側弁体３５とを一部品で形成してもよい。
【００２０】
高圧側弁体３４には、吐出室２１に通じる側の端部から有底の冷媒通過孔３８が軸線位置に穿設されている。冷媒通過孔３８は一端が高圧側弁体３４の端部に開口しており、他端は、高圧側弁体３４の外周面と本体筒３２側の孔との嵌合部分より先の位置で高圧側弁体３４の側面に開口していて、クランク室１２に通じる加圧用流路３８に通じている。
【００２１】
その冷媒通過孔３８が開口する高圧側弁体３４の端部に対向して、弁座３９が本体筒３２に固定的に取り付けられており、高圧側弁体３４の端部が、高圧（Ｐｄ）の吐出室２１に通じる高圧連通路４０とクランク室１２に通じる加圧用流路４１との間の連通路を開閉する高圧側弁部４４になっている。
【００２２】
この高圧側弁部４４が開くと、吐出室２１とクランク室１２内とが通じてクランク室１２内の圧力（Ｐｃ）が高められる。４５は、高圧側弁部４４が開く方向に高圧側弁体３４を付勢する圧縮コイルバネである。高圧側弁部４４への入口部分には、ゴミ等を除去するためのフィルタ４６が被せられている。
【００２３】
低圧側弁体３５には、吸入室２０に通じる側の端部から冷媒通過孔５１が軸線位置に穿設されている。冷媒通過孔５１は一端が低圧側弁体３５の端部に開口しており、他端は、低圧側弁体３５の外周面と本体筒３２側の孔との嵌合部分より先の位置で低圧側弁体３５の側面に開口していて、クランク室１２に通じる減圧用流路５２に通じている。
【００２４】
その冷媒通過孔５１が開口する低圧側弁体３５の端部に対向して、後述する電磁ソレノイド６０の可動鉄心６１の端面に形成された弁座が位置しており、低圧側弁体３５の端部が、低圧（Ｐｓ）の吸入室２０に通じる低圧連通路５３とクランク室１２に通じる減圧用流路５２との間の連通路を開閉する低圧側弁部５５になっている。
【００２５】
この低圧側弁部５５が開くと、吸入室２０とクランク室１２内とが通じてクランク室１２内の圧力（Ｐｃ）が低下する。５７は、低圧側弁部５５が開く方向に低圧側弁体３５を付勢する圧縮コイルバネ、５８は、低圧側弁体３５の軸線方向の動きを一定範囲に規制するためのストッパである。
【００２６】
電磁ソレノイド６０は、高圧側弁体３４と低圧側弁体３５とを軸線方向に駆動するための電磁ソレノイドであり、６２はその電磁コイルである。可動鉄心６１は高圧側弁体３４及び低圧側弁体３５と同軸線上に配置されていて、その端面に圧縮コイルバネ５７の一端が当接している。
【００２７】
高圧側弁部４４と低圧側弁部５５は、前述のように軸線方向に一体的に進退する高圧側弁体３４と低圧側弁体３５の端部に形成されている。したがって、高圧側弁部４４が閉じると低圧側弁部５５が開き、高圧側弁部４４が開くと低圧側弁部５５が閉じる。
【００２８】
このように構成された装置において、図２に示されるように、高圧側弁部４４の有効径をＡ、高圧側弁体３４と本体筒３２との嵌合部の径をＢとすると、Ａ＝Ｂに設定されている。したがって、吐出室２１内の圧力（Ｐｄ）とクランク室１２内の圧力（Ｐｃ）との差圧が高圧側弁部４４を開く方向に作用する有効受圧面積と閉じる方向に作用する有効受圧面積が等しいので、ＰｄとＰｃとの差圧はキャンセルされて高圧側弁部４４の開閉力に作用しない。
【００２９】
また、低圧側弁部５５の有効径をＣ、低圧側弁体３５と本体筒３２との嵌合部の径をＤとすると、Ｃ＝Ｄに設定されている。したがって、クランク室１２内の圧力（Ｐｃ）と吸入室２０内の圧力（Ｐｓ）との差圧が低圧側弁部５５を開く方向に作用する有効受圧面積と閉じる方向に作用する有効受圧面積が等しいので、ＰｃとＰｄとの差圧はキャンセルされて低圧側弁部５５の開閉力に作用しない。
【００３０】
その結果、高圧側弁体３４と低圧側弁体３５とを電磁ソレノイド６０で開閉駆動する際には、電磁ソレノイド６０には二つの圧縮コイルバネ４５，５７の付勢力が作用するだけで、冷媒の圧力は全く作用しない。
【００３１】
したがって、両弁部４４，５５の開閉に大きな力は必要とせず、電磁コイル６２に大電流を流すことなく両弁部４４，５５を開閉させることができ、電磁コイル６２があまり発熱しない。
【００３２】
そして、電磁コイル６２への通電量を加減することによって、高圧側弁部４４と低圧側弁部５５が両方とも開いた中間状態で高圧側弁体３４と低圧側弁体３５を停止させて、揺動板１４をそれに応じた傾斜角にセットし、容量可変圧縮機１０の容量（吐出量）を任意に制御することができる。
【００３３】
【発明の効果】
本発明によれば、吐出室内の圧力とクランク室内の圧力との差圧が高圧側弁部を開く方向に作用する有効受圧面積と閉じる方向に作用する有効受圧面積とを等しくし、且つクランク室内の圧力と吸入室内の圧力との差圧が低圧側弁部を開く方向に作用する有効受圧面積と閉じる方向に作用する有効受圧面積とを等しくしたことにより、両弁部の開閉に対して作用する冷媒の圧力が各々キャンセルされてほぼゼロになるので、弁駆動用の電磁ソレノイドへの通電電流が小さくて済み、電磁コイルの発熱を大幅に抑制して、発熱に起因する不具合の発生を防止することができる。
【図面の簡単な説明】
【図１】本発明の実施の形態の最大容量状態の断面図である。
【図２】本発明の実施の形態の最小容量状態の断面図である。
【符号の説明】
１０ 容量可変圧縮機
１２ クランク室
１４ 揺動板
１５ シリンダ
１７ ピストン
２０ 吸入室
２１ 吐出室
３０ 容量制御装置
３４ 高圧側弁体
３５ 低圧側弁体
４４ 高圧側弁部
５５ 低圧側弁部
６０ 電磁ソレノイド
６２ 電磁コイル[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a capacity control device for a variable capacity compressor used for compressing refrigerant in a refrigeration cycle such as an air conditioner for automobiles.
[0002]
[Prior art]
Since the compressor used in the refrigeration cycle of the air conditioner for automobiles is directly connected to the engine with a belt, the rotational speed cannot be controlled. Therefore, in order to obtain an appropriate cooling capacity without being restricted by the engine speed, a variable capacity compressor capable of changing the refrigerant capacity (discharge amount) is used.
[0003]
In such a variable capacity compressor, generally, an oscillating plate provided with a variable inclination angle in an airtight crank chamber is driven by an oscillating motion of a rotary shaft, and oscillating the oscillating plate. The piston that reciprocates due to the rocking motion sucks the refrigerant in the suction chamber into the cylinder, compresses it, discharges it to the discharge chamber, and the inclination angle of the rocking plate is adjusted by the difference between the pressure in the crank chamber and the pressure in the suction chamber. By changing it, the discharge amount of the refrigerant is changed.
[0004]
In such a variable capacity compressor, in order to change the inclination angle of the swing plate as necessary, a high-pressure side valve portion that opens and closes communication between the discharge chamber and the crank chamber, and a suction chamber and a crank chamber The low pressure side valve portion that opens and closes the communication between them is opened and closed by an electromagnetic solenoid so that the open / close relationship of both valve portions is reversed.
[0005]
[Problems to be solved by the invention]
In the capacity control device for the variable capacity compressor as described above, when the both solenoid valves are driven to open and close by the electromagnetic solenoid, the pressure difference between the pressure in the discharge chamber and the pressure in the crank chamber, and the pressure in the crank chamber and the suction chamber Must be driven against both differential pressures.
[0006]
However, the discharge chamber into which the compressed refrigerant is discharged may have a high pressure of, for example, about 30 atm. Therefore, in order to open the high-pressure side valve portion communicating with the discharge chamber against the high pressure, the drive chamber It is necessary to apply a considerable current to the electromagnetic coil of the electromagnetic solenoid.
[0007]
As a result, the electromagnetic coil of the electromagnetic solenoid may generate a significant amount of heat, which may cause problems such as deterioration of the sealing O-ring and refrigerant leakage.
[0008]
Accordingly, the present invention provides a capacity control device for a variable capacity compressor that can open and close the valve part with a small force, requires a small energization current to the solenoid solenoid for driving the valve, and suppresses heat generation of the coil. The purpose is to provide.
[0009]
[Means for Solving the Problems]
In order to achieve the above object, a capacity control device for a variable capacity compressor according to the present invention is provided with a variable inclination angle with respect to a rotary shaft in an airtight crank chamber and is driven by the rotary motion of the rotary shaft. An oscillating body that oscillates and a piston that is connected to the oscillating body and reciprocates to suck and compress the refrigerant in the suction chamber into the cylinder and then discharge the refrigerant into the discharge chamber. A capacity control device for controlling the capacity of a variable capacity compressor that changes the discharge amount of the refrigerant by changing the inclination angle of the oscillator according to the difference between the pressure of the suction chamber and the pressure in the suction chamber. A high pressure side valve portion that opens and closes communication between the discharge chamber and the crank chamber, a low pressure side valve portion that opens and closes communication between the crank chamber and the suction chamber, the high pressure side valve portion, and the The low pressure side valve part An effective pressure receiving pressure in which a differential pressure between the pressure in the discharge chamber and the pressure in the crank chamber acts in the direction to open the high-pressure side valve portion, provided with an electromagnetic solenoid that opens and closes simultaneously so that the closing relationship is reversed The area and the effective pressure receiving area acting in the closing direction are formed equally, and the differential pressure between the pressure in the crank chamber and the pressure in the suction chamber acts in the direction to open the low pressure side valve portion and the closing direction. The effective pressure receiving area that acts on the same is formed equally.
[0010]
Note that at least one of the high-pressure side valve portion and the low-pressure side valve portion is formed at one end portion of a rod-shaped valve body and opens to the end portion and a side surface at a position away from the end portion. The refrigerant passage hole may be formed in the rod-shaped valve body, and the diameter of the rod-shaped valve body may be equal to the effective diameter of the valve portion.
[0011]
Further, a seal film member for preventing the refrigerant from leaking from the discharge chamber side to the crank chamber side along the outer peripheral surface of the rod-shaped member may be provided on the outer periphery of the rod-shaped member.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described with reference to the drawings.
1 and 2 show a variable capacity compressor 10 and its capacity control device 30 used during the refrigeration cycle of an automotive air conditioner. FIG. 1 shows a maximum capacity state, and FIG. 2 shows a minimum capacity state. .
[0013]
Reference numeral 11 denotes a rotating shaft that is disposed in an airtight crank chamber 12 and is rotationally driven by a driving pulley 13. The swing plate 14 is disposed in the crank chamber 12 so as to be inclined with respect to the rotating shaft 11. Swings in accordance with the rotation of the rotating shaft 11.
[0014]
A piston 17 is disposed in a reciprocating manner in a cylinder 15 disposed in the periphery of the crank chamber 12, and the piston 17 and the swing plate 14 are connected by a rod 18.
[0015]
Therefore, when the swing plate 14 swings, the piston 17 reciprocates in the cylinder 15 to suck the refrigerant into the cylinder 15 from the suction chamber 20 formed on the upstream side of the cylinder 15. After being compressed inside, it is discharged into the discharge chamber 21 on the downstream side.
[0016]
A block 31 surrounding the capacity control device 30 is formed of the same block as the variable capacity compressor 10, and a main body cylinder 32 is fitted in a coaxial multistage hole formed therein. 33 is an O-ring for sealing the fitting part and other fitting parts.
[0017]
In the through hole formed at the axial position of the main body cylinder 32, a rod-shaped high-pressure side valve body 34 and a rod-shaped low-pressure side valve body 35 formed slightly thicker are coaxially movable in the axial direction. It is placed straight.
[0018]
The high pressure side valve body 34 has a flexible diaphragm 36 (seal film member) for preventing the refrigerant from leaking from the discharge chamber 21 side to the crank chamber 12 side along the outer peripheral surface thereof. It is attached to the part. Therefore, the refrigerant flowing from the discharge chamber 21 to the crank chamber 12 always passes through the high pressure side valve portion 44 described later.
[0019]
In order to attach the diaphragm 36, the high-pressure side valve body 34 is divided into two parts 34a and 34b, but may be formed as one part. Moreover, you may form the high pressure side valve body 34 and the low pressure side valve body 35 by one component.
[0020]
The high-pressure side valve body 34 is provided with a bottomed refrigerant passage hole 38 at an axial position from an end portion that leads to the discharge chamber 21. One end of the refrigerant passage hole 38 opens at the end of the high pressure side valve body 34, and the other end is a position ahead of the fitting portion between the outer peripheral surface of the high pressure side valve body 34 and the hole on the main body cylinder 32 side. The high pressure side valve body 34 is open to the side surface and communicates with a pressurizing flow path 38 that leads to the crank chamber 12.
[0021]
The valve seat 39 is fixedly attached to the main body cylinder 32 so as to face the end of the high-pressure side valve body 34 where the refrigerant passage hole 38 is opened, and the end of the high-pressure side valve body 34 has a high pressure (Pd ) Is a high pressure side valve portion 44 that opens and closes the communication path between the high pressure communication path 40 leading to the discharge chamber 21 and the pressurizing flow path 41 leading to the crank chamber 12.
[0022]
When the high-pressure side valve portion 44 is opened, the discharge chamber 21 and the crank chamber 12 are connected to increase the pressure (Pc) in the crank chamber 12. Reference numeral 45 denotes a compression coil spring that urges the high-pressure side valve body 34 in the direction in which the high-pressure side valve portion 44 opens. A filter 46 for removing dust and the like is put on the inlet portion to the high-pressure side valve portion 44.
[0023]
A refrigerant passage hole 51 is formed in the low pressure side valve body 35 at an axial position from an end portion on the side communicating with the suction chamber 20. One end of the refrigerant passage hole 51 opens at the end of the low-pressure side valve body 35, and the other end is a position ahead of the fitting portion between the outer peripheral surface of the low-pressure side valve body 35 and the hole on the main body cylinder 32 side. It opens to the side surface of the low pressure side valve body 35 and communicates with a pressure reducing flow path 52 that leads to the crank chamber 12.
[0024]
A valve seat formed on an end surface of a movable iron core 61 of an electromagnetic solenoid 60 (described later) is located opposite to the end of the low pressure side valve body 35 where the refrigerant passage hole 51 is opened. The end portion is a low pressure side valve portion 55 that opens and closes a communication path between the low pressure communication path 53 that communicates with the low pressure (Ps) suction chamber 20 and the decompression flow path 52 that communicates with the crank chamber 12.
[0025]
When the low-pressure side valve portion 55 is opened, the suction chamber 20 and the crank chamber 12 communicate with each other, and the pressure (Pc) in the crank chamber 12 decreases. 57 is a compression coil spring that urges the low-pressure side valve body 35 in the direction in which the low-pressure side valve section 55 opens, and 58 is a stopper for restricting the axial movement of the low-pressure side valve body 35 to a certain range.
[0026]
The electromagnetic solenoid 60 is an electromagnetic solenoid for driving the high pressure side valve body 34 and the low pressure side valve body 35 in the axial direction, and 62 is an electromagnetic coil thereof. The movable iron core 61 is disposed coaxially with the high-pressure side valve body 34 and the low-pressure side valve body 35, and one end of the compression coil spring 57 is in contact with the end surface.
[0027]
The high-pressure side valve portion 44 and the low-pressure side valve portion 55 are formed at the end portions of the high-pressure side valve body 34 and the low-pressure side valve body 35 that advance and retract integrally in the axial direction as described above. Therefore, when the high pressure side valve portion 44 is closed, the low pressure side valve portion 55 is opened, and when the high pressure side valve portion 44 is opened, the low pressure side valve portion 55 is closed.
[0028]
In the apparatus configured in this manner, as shown in FIG. 2, when the effective diameter of the high-pressure side valve portion 44 is A and the diameter of the fitting portion between the high-pressure side valve body 34 and the main body cylinder 32 is B, A = B is set. Therefore, an effective pressure receiving area in which the differential pressure between the pressure (Pd) in the discharge chamber 21 and the pressure (Pc) in the crank chamber 12 acts in the direction to open the high-pressure side valve portion 44 and the effective pressure receiving area in the closing direction. Therefore, the differential pressure between Pd and Pc is canceled and does not act on the opening / closing force of the high-pressure side valve portion 44.
[0029]
Further, C = D, where C is the effective diameter of the low pressure side valve portion 55 and D is the diameter of the fitting portion between the low pressure side valve body 35 and the main body cylinder 32. Therefore, the effective pressure receiving area that acts in the direction in which the differential pressure between the pressure (Pc) in the crank chamber 12 and the pressure (Ps) in the suction chamber 20 opens in the direction of opening the low pressure side valve portion 55 and the direction in which it closes. Therefore, the differential pressure between Pc and Pd is canceled and does not act on the opening / closing force of the low pressure side valve portion 55.
[0030]
As a result, when the high pressure side valve body 34 and the low pressure side valve body 35 are driven to open and close by the electromagnetic solenoid 60, the urging force of the two compression coil springs 45 and 57 acts on the electromagnetic solenoid 60, so No pressure is applied.
[0031]
Therefore, a large force is not required to open and close both the valve portions 44 and 55, the both valve portions 44 and 55 can be opened and closed without flowing a large current through the electromagnetic coil 62, and the electromagnetic coil 62 does not generate much heat.
[0032]
Then, by adjusting the energization amount to the electromagnetic coil 62, the high pressure side valve body 34 and the low pressure side valve body 35 are stopped in an intermediate state in which both the high pressure side valve portion 44 and the low pressure side valve portion 55 are open, The swing plate 14 is set at an inclination angle corresponding to the swing plate 14, and the capacity (discharge amount) of the variable capacity compressor 10 can be arbitrarily controlled.
[0033]
【The invention's effect】
According to the present invention, the differential pressure between the pressure in the discharge chamber and the pressure in the crank chamber equalizes the effective pressure receiving area acting in the direction of opening the high pressure side valve portion and the effective pressure receiving area acting in the closing direction, and The pressure difference between the pressure in the suction chamber and the pressure in the suction chamber acts on the opening and closing of both valve parts by making the effective pressure receiving area acting in the direction of opening the low pressure side valve part equal to the effective pressure receiving area acting in the closing direction. Since the pressure of the refrigerant to be canceled is almost zero, the energization current to the solenoid solenoid for driving the valve can be reduced, greatly suppressing the heat generation of the electromagnetic coil and preventing the occurrence of problems caused by the heat generation can do.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a maximum capacity state according to an embodiment of the present invention.
FIG. 2 is a sectional view of a minimum capacity state according to the embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 10 Variable displacement compressor 12 Crank chamber 14 Oscillating plate 15 Cylinder 17 Piston 20 Suction chamber 21 Discharge chamber 30 Capacity control device 34 High pressure side valve element 35 Low pressure side valve element 44 High pressure side valve part 55 Low pressure side valve part 60 Electromagnetic solenoid 62 Electromagnetic coil

Claims (3)

気密に形成されたクランク室内で回転軸に対して傾斜角可変に設けられて上記回転軸の回転運動によって駆動されて揺動運動をする揺動体と、上記揺動体に連結されて往復動することにより吸入室の冷媒をシリンダ内に吸入して圧縮したあと吐出室に吐出するピストンとを有し、上記クランク室内の圧力と上記吸入室内の圧力との差によって上記揺動体の傾斜角度を変化させて上記冷媒の吐出量を変化させるようにした容量可変圧縮機の容量を制御するための容量制御装置であって、
上記吐出室と上記クランク室との間の連通を開閉する高圧側弁部と、上記クランク室と上記吸入室との間の連通を開閉する低圧側弁部と、上記高圧側弁部と上記低圧側弁部とを両弁部の開閉関係が逆になるように同時に開閉駆動する電磁ソレノイドとを設けたものにおいて、
上記高圧側弁部と上記低圧側弁部の少なくとも一方が、棒状に形成された弁体の一方の端部に形成されると共に、その端部とそこから離れた位置の側面とに開口する冷媒通過孔が上記棒状の弁体に形成されていて、上記棒状の弁体の直径とその弁体の端部の弁部の有効径とが等しく形成されていることを特徴とする容量可変圧縮機の容量制御装置。An oscillating body that is provided with a variable inclination angle with respect to the rotating shaft in an airtight crank chamber and that is driven by the rotating motion of the rotating shaft to perform an oscillating motion, and reciprocatingly connected to the oscillating body. A piston that sucks and compresses the refrigerant in the suction chamber into the cylinder and then discharges it into the discharge chamber, and changes the inclination angle of the oscillator according to the difference between the pressure in the crank chamber and the pressure in the suction chamber. A capacity control device for controlling the capacity of the variable capacity compressor configured to change the discharge amount of the refrigerant,
A high pressure side valve portion that opens and closes communication between the discharge chamber and the crank chamber, a low pressure side valve portion that opens and closes communication between the crank chamber and the suction chamber, the high pressure side valve portion and the low pressure side In an electromagnetic solenoid that opens and closes the side valve part at the same time so that the opening and closing relationship of both valve parts is reversed,
At least one of the high-pressure side valve portion and the low-pressure side valve portion is formed at one end portion of a rod-shaped valve body, and opens to the end portion and a side surface at a position away from the end portion. A variable displacement compressor characterized in that a passage hole is formed in the rod-shaped valve body, and the diameter of the rod-shaped valve body is equal to the effective diameter of the valve portion at the end of the valve body. Capacity controller. 上記高圧側弁部と上記低圧側弁部が個々に、棒状に形成された弁体の一方の端部に形成されると共に、その端部とそこから離れた位置の側面とに開口する冷媒通過孔が上記各棒状の弁体に形成されていて、上記各棒状の弁体の直径とその弁体の端部の弁部の有効径とが各々等しく形成され、上記高圧側弁部が形成された棒状の弁体と上記低圧側弁部が形成された棒状の弁体とが上記電磁ソレノイドによって軸線方向に一体的に進退駆動される請求項１記載の容量可変圧縮機の容量制御装置。The high-pressure side valve portion and the low-pressure side valve portion are individually formed at one end of a rod-shaped valve body, and the refrigerant passes through the end and a side surface away from the end. A hole is formed in each of the rod-shaped valve bodies, and the diameter of each of the rod-shaped valve bodies and the effective diameter of the valve portion at the end of the valve body are each formed to form the high-pressure side valve section. 2. The capacity control device for a variable displacement compressor according to claim 1, wherein the rod-shaped valve body and the rod-shaped valve body on which the low-pressure side valve portion is formed are integrally driven forward and backward in the axial direction by the electromagnetic solenoid . 上記高圧側弁部が形成された棒状の弁体の外周面に沿って上記吐出室側から上記クランク室側に冷媒がリークするのを防止するためのシール膜部材が、上記高圧側弁部が形成された棒状の弁体の外周部に設けられている請求項２記載の容量可変圧縮機の容量制御装置。Sealing membrane member for preventing along the outer peripheral surface of the valve body of the rod-like the high-pressure-side valve portion is formed from the discharge chamber side to leak refrigerant to the crank chamber side, the high-pressure-side valve portion 3. The capacity control device for a variable capacity compressor according to claim 2, wherein the capacity control apparatus is provided on an outer peripheral portion of the formed rod-shaped valve body .
JP32494095A 1995-12-14 1995-12-14 Capacity controller for variable capacity compressor Expired - Fee Related JP3678824B2 (en)

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000177375A (en) * 1998-12-21 2000-06-27 Toyota Autom Loom Works Ltd Air conditioner
JP3886290B2 (en) * 1999-04-27 2007-02-28 株式会社テージーケー Capacity control device for variable capacity compressor
JP4392631B2 (en) 1999-06-24 2010-01-06 株式会社ヴァレオサーマルシステムズ Variable capacity controller for refrigeration cycle
JP3906432B2 (en) 1999-12-27 2007-04-18 株式会社豊田自動織機 Air conditioner

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