JPH09166086A - Capacity controller of capacity variable compressor - Google Patents
Capacity controller of capacity variable compressorInfo
- Publication number
- JPH09166086A JPH09166086A JP7324940A JP32494095A JPH09166086A JP H09166086 A JPH09166086 A JP H09166086A JP 7324940 A JP7324940 A JP 7324940A JP 32494095 A JP32494095 A JP 32494095A JP H09166086 A JPH09166086 A JP H09166086A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- side valve
- pressure side
- chamber
- refrigerant
- 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.)
- Granted
Links
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
【０００１】[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。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a capacity control device for a capacity variable compressor used for compressing a refrigerant in a refrigeration cycle of an air conditioner for an automobile.
【０００２】[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。2. Description of the Related Art A compressor used in a refrigeration cycle of a vehicle air conditioner cannot directly control the number of revolutions because it is directly connected to an engine by a belt. Therefore, a variable capacity compressor capable of changing the capacity (discharge amount) of the refrigerant is used in order to obtain an appropriate cooling capacity without being restricted by the engine speed.
【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。In such a variable displacement compressor, generally, an oscillating plate provided with a variable tilt angle in an airtightly formed crank chamber is driven by the rotational motion of a rotary shaft to oscillate, and A piston that reciprocates due to the oscillating motion of the oscillating plate sucks the refrigerant in the suction chamber into the cylinder, compresses it, and then discharges it into the discharge chamber.The difference between the pressure in the crank chamber and the pressure in the suction chamber causes the oscillating plate to move. The discharge amount of the refrigerant is changed by changing the inclination angle.
【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。In such a variable displacement compressor, in order to change the inclination angle of the oscillating plate as necessary, the high pressure side valve portion for opening and closing the communication between the discharge chamber and the crank chamber, the suction chamber and the crank. An electromagnetic solenoid opens and closes the low-pressure side valve portion that opens and closes the communication with the chamber so that the opening and closing relationship of both valve portions is reversed.
【０００５】[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。In the displacement control device for the variable displacement compressor as described above, when the electromagnetic solenoid is used to open and close both valve parts, the differential pressure between the pressure in the discharge chamber and the pressure in the crank chamber is used. , And the pressure difference between the pressure in the crank chamber and the pressure in the suction chamber, both must be driven.
【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。However, the discharge chamber from which the compressed refrigerant is discharged may have a high pressure of, for example, about 30 atmospheres. Therefore, in order to open the high pressure side valve portion communicating with the discharge chamber against the high pressure, It is necessary to supply a considerably large current to the electromagnetic coil of the driving electromagnetic solenoid.
【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。As a result, the electromagnetic coil of the electromagnetic solenoid may remarkably generate heat, which may cause problems such as deterioration of the sealing O-ring and leakage of the refrigerant.
【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。Therefore, the present invention relates to a variable capacity compressor which can open and close the valve portion with a small force, requires only a small current to the electromagnetic solenoid for driving the valve, and can suppress the heat generation of the coil. An object is to provide a capacity control device.
【０００９】[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。In order to achieve the above object, the capacity control device for a variable capacity compressor according to the present invention is provided in an airtightly formed crank chamber with a variable inclination angle with respect to a rotary shaft. An oscillating body driven by the rotational movement of the rotary shaft to oscillate, and reciprocatingly connected to the oscillating body to suck and compress the refrigerant in the suction chamber into the cylinder, and then discharge the refrigerant to the discharge chamber. A displacement variable compressor having a piston and adapted to change the discharge amount of the refrigerant by changing the inclination angle of the oscillating body by the difference between the pressure in the crank chamber and the pressure in the suction chamber. And a high-pressure side valve section that opens and closes the communication between the discharge chamber and the crank chamber, and a low-pressure side valve section that opens and closes the communication between the crank chamber and the suction chamber. And the high pressure side valve section In the one provided with an electromagnetic solenoid that simultaneously opens and closes the low pressure side valve section so that the opening and closing relationship of both valve sections is reversed, the differential pressure between the pressure in the discharge chamber and the pressure in the crank chamber is the high pressure. The effective pressure receiving area acting in the opening direction of the side valve portion and the effective pressure receiving area acting in the closing direction are formed to be equal, and the differential pressure between the pressure in the crank chamber and the pressure in the suction chamber reduces the low pressure side valve portion. It is characterized in that the effective pressure receiving area acting in the opening direction and the effective pressure receiving area acting in the closing direction are formed to be equal.
【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。At least one of the high-pressure side valve portion and the low-pressure side valve portion is formed at one end of a rod-shaped valve body, and the end and the side surface at a position distant therefrom. A refrigerant passage hole that opens to the above may be formed in the rod-shaped valve body, and the diameter of the rod-shaped valve body and the effective diameter of the valve portion may be formed to be equal.
【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。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 is provided on the outer peripheral portion of the rod-shaped member. Good.
【００１２】[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。Embodiments of the present invention will be described with reference to the drawings. 1 and 2 show a variable capacity compressor 10 used in a refrigeration cycle of an automobile air conditioner and a capacity control device 30 thereof. FIG. 1 shows a maximum capacity state and FIG. 2 shows a minimum capacity state. .
【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。Reference numeral 11 denotes a crank chamber 12 which is airtight.
An oscillating plate 14 disposed inside the crank chamber 12 that is inclined with respect to the rotating shaft 11 and is rotatably driven by the drive pulley 13 oscillates as the rotating shaft 11 rotates. To do.
【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１
４とが連結されている。A piston 17 is reciprocally arranged in a cylinder 15 arranged in the peripheral portion of the crank chamber 12, and the piston 17 and the oscillating plate 1 are connected by a rod 18.
4 are connected.
【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１
５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。Therefore, when the rocking plate 14 rocks, the piston 17 reciprocates in the cylinder 15 and the cylinder 1
5, the refrigerant is sucked into the cylinder 15 from the suction chamber 20 formed on the upstream side, compressed in the cylinder 15, and then discharged to the discharge chamber 21 on the downstream side.
【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。The block 31 surrounding the capacity control device 30 is
It is formed of the same block as the variable capacity compressor 10,
The body cylinder 32 is fitted in the coaxial multi-stage hole formed therein. Reference numeral 33 is an O-ring for sealing the fitting portion and other fitting portions.
【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。A rod-shaped high-pressure side valve element 34 and a rod-shaped low-pressure side valve element 35 formed slightly thicker than the rod-shaped high-pressure side valve element 34 are axially movable back and forth in a through hole formed at the axial position of the main body cylinder 32. It is arranged straight on the coaxial line.
【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３
６（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。The high pressure side valve element 34 has a flexible diaphragm 3 for preventing refrigerant from leaking from the discharge chamber 21 side to the crank chamber 12 side along the outer peripheral surface thereof.
6 (seal film member) is attached to the outer peripheral portion. 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】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。In order to attach the diaphragm 36, the high pressure side valve body 34 is formed by being divided into two parts 34a and 34b, but it may be formed by one part. Further, the high pressure side valve body 34 and the low pressure side valve body 35 may be formed as one component.
【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。In the high pressure side valve element 34, a bottomed refrigerant passage hole 38 is formed at an axial position from the end portion on the side communicating with the discharge chamber 21. One end of the refrigerant passage hole 38 is open to the end of the high-pressure side valve body 34, and the other end is at a position prior to 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. It is opened to the side surface of the high pressure side valve body 34 and communicates with a pressurizing flow path 38 communicating with the crank chamber 12.
【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。A valve seat 39 is fixedly attached to the main body cylinder 32 so as to face the end of the high pressure side valve element 34 where the refrigerant passage hole 38 opens, and the end of the high pressure side valve element 34 is A high-pressure side valve portion 44 opens and closes a communication passage between a high-pressure communication passage 40 communicating with the high-pressure (Pd) discharge chamber 21 and a pressurizing flow passage 41 communicating with the crank chamber 12.
【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。When the high pressure side valve portion 44 is opened, the discharge chamber 21 is opened.
The pressure (Pc) in the crank chamber 12 is increased by communicating with the inside of the crank chamber 12. Reference numeral 45 denotes a compression coil spring that biases the high pressure side valve body 34 in a direction in which the high pressure side valve portion 44 opens. A filter 46 for removing dust and the like is covered on an inlet portion to the high pressure side valve portion 44.
【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。A refrigerant passage hole 51 is formed in the low pressure side valve element 35 at an axial position from an end portion on the side communicating with the suction chamber 20. The refrigerant passage hole 51 has one end opening to the end of the low pressure side valve body 35, and the other end at a position prior to 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. Low pressure side valve body 35
Is open to the side surface of the crankcase 12 and communicates with the pressure-reducing flow path 52 communicating with the crank chamber 12.
【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。A valve seat formed on an end surface of a movable iron core 61 of an electromagnetic solenoid 60, which will be described later, is located so as to face the end of the low pressure side valve body 35 where the refrigerant passage hole 51 opens.
An end portion of the low pressure side valve body 35 serves as a low pressure side valve portion 55 that opens and closes a communication passage between a low pressure communication passage 53 communicating with the low pressure (Ps) suction chamber 20 and a pressure reducing flow passage 52 communicating with the crank chamber 12. Has become.
【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。When the low pressure side valve portion 55 is opened, the suction chamber 20
And the inside of the crank chamber 12 communicate with each other, and the pressure (Pc) in the crank chamber 12 decreases. Reference numeral 57 denotes a compression coil spring that biases the low pressure side valve body 35 in a direction in which the low pressure side valve portion 55 opens, and 58.
Is a stopper for restricting the movement of the low pressure side valve body 35 in the axial direction within a certain range.
【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。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 arranged 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 face thereof.
【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。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 which integrally advance and retreat 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】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、Ｐ
ｄ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。In the apparatus constructed as described above, as shown in FIG.
As shown in, 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,
It is set to A = B. Therefore, the differential pressure between the pressure (Pd) in the discharge chamber 21 and the pressure (Pc) in the crank chamber 12 has an effective pressure receiving area that acts in the opening direction and an effective pressure receiving area that acts in the closing direction. Equal, so P
The differential pressure between d and Pc is canceled and does not act on the opening / closing force of the high pressure side valve portion 44.
【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、Ｐ
ｃ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。When the effective diameter of the low pressure side valve portion 55 is C and the diameter of the fitting portion between the low pressure side valve body 35 and the main body cylinder 32 is D,
It is set to C = D. Therefore, the crank chamber 12
Since the differential pressure between the internal pressure (Pc) and the internal pressure (Ps) of the suction chamber 20 is equal to the effective pressure receiving area acting in the opening direction of the low pressure side valve portion 55, the effective pressure receiving area acting in the closing direction is equal to P
The differential pressure between c and Pd is canceled and does not act on the opening / closing force of the low pressure side valve portion 55.
【００３０】その結果、高圧側弁体３４と低圧側弁体３
５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。As a result, the high pressure side valve body 34 and the low pressure side valve body 3
When opening and closing 5 and 5 by the electromagnetic solenoid 60, only the biasing forces of the two compression coil springs 45 and 57 act on the electromagnetic solenoid 60, and the refrigerant pressure does not act at all.
【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。Therefore, a large force is not required to open and close both valve portions 44 and 55, both valve portions 44 and 55 can be opened and closed without causing a large current to flow through the electromagnetic coil 62, and the electromagnetic coil 62 generates much heat. do not do.
【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。By adjusting the amount of electricity to the electromagnetic coil 62, the high pressure side valve element 34 and the low pressure side valve element 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. Then, the oscillating plate 14 can be set to a tilt angle corresponding to it, and the capacity (discharge amount) of the variable capacity compressor 10 can be controlled arbitrarily.
【００３３】[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。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 opening direction of the high pressure side valve portion and the effective pressure receiving area acting in the closing direction. In addition, since the differential pressure between the pressure in the crank chamber and the pressure in the suction chamber equalizes the effective pressure receiving area acting in the opening direction of the low pressure side valve section and the effective pressure receiving area acting in the closing direction, Since the pressure of the refrigerant that acts on the opening and closing is canceled to almost zero, the current supplied to the electromagnetic solenoid for driving the valve can be small, and the heat generation of the electromagnetic coil can be greatly suppressed, resulting in heat generation. It is possible to prevent the occurrence of defects.
【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。FIG. 1 is a sectional view of a maximum capacity state according to an embodiment of the present invention.
【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。FIG. 2 is a sectional view of the minimum capacity state according to the embodiment of the present invention.
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 10 Capacity Variable 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 Body 35 Low Pressure Side Valve Body 44 High Pressure Side Valve Section 55 Low Pressure Side Valve Section 60 Electromagnetic Solenoid 62 Electromagnetic coil
Claims (3)
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
ことを特徴とする容量可変圧縮機の容量制御装置。1. An oscillating body, which is provided in an airtightly formed crank chamber with a variable inclination angle with respect to a rotating shaft and is oscillated by being driven by the rotational movement of the rotating shaft, and is connected to the oscillating body. By reciprocating the suction chamber to suck the refrigerant in the suction chamber into the cylinder, compress the refrigerant, and then discharge the refrigerant into the discharge chamber.The piston of the rocking body is moved by the difference between the pressure in the crank chamber and the pressure in the suction chamber. A displacement control device for controlling the displacement of a variable displacement compressor, which is configured to change the discharge amount of the refrigerant by changing the inclination angle, and opens and closes the communication between the discharge chamber and the crank chamber. The high-pressure side valve section, the low-pressure side valve section that opens and closes the communication between the crank chamber and the suction chamber, and the high-pressure side valve section and the low-pressure side valve section have opposite open / close relationships. Solenoid that opens and closes at the same time The pressure difference between the pressure in the discharge chamber and the pressure in the crank chamber is equal to the effective pressure receiving area acting in the opening direction of the high pressure side valve portion and the effective pressure receiving area acting in the closing direction. At the same time, the differential pressure between the pressure in the crank chamber and the pressure in the suction chamber forms the effective pressure receiving area acting in the opening direction of the low pressure side valve portion and the effective pressure receiving area acting in the closing direction thereof. The characteristic capacity control device of the variable capacity compressor.
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
る請求項１記載の容量可変圧縮機の容量制御装置。2. At least one of the high-pressure side valve portion and the low-pressure side valve portion is formed at one end of a rod-shaped valve body, and the end and a side surface at a position apart from the end are formed. 2. The displacement control device for a variable displacement compressor according to claim 1, wherein a refrigerant passage hole that opens in the opening is formed in the rod-shaped valve body, and the diameter of the rod-shaped valve body and the effective diameter of the valve portion are formed to be equal.
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
られている請求項２記載の容量可変圧縮機の容量制御装
置。3. 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 is provided on the outer peripheral portion of the rod-shaped member. The capacity control device for the variable capacity compressor according to claim 2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32494095A JP3678824B2 (en) | 1995-12-14 | 1995-12-14 | Capacity controller for variable capacity compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32494095A JP3678824B2 (en) | 1995-12-14 | 1995-12-14 | Capacity controller for variable capacity compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09166086A true JPH09166086A (en) | 1997-06-24 |
| JP3678824B2 JP3678824B2 (en) | 2005-08-03 |
Family
ID=18171328
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP32494095A Expired - Fee Related JP3678824B2 (en) | 1995-12-14 | 1995-12-14 | Capacity controller for variable capacity compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3678824B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1113235A1 (en) * | 1999-12-27 | 2001-07-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Air-conditioning system |
| EP1014016A3 (en) * | 1998-12-21 | 2002-01-16 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Air conditioning systems |
| US6394761B1 (en) * | 1999-04-27 | 2002-05-28 | Tgk Co., Inc. | Capacity controller of capacity variable compressor |
| US6585494B1 (en) | 1999-06-24 | 2003-07-01 | Zexel Valeo Climate Control Corporation | Variable-capacity control for refrigerating cycle without using a large pressure control valve |
-
1995
- 1995-12-14 JP JP32494095A patent/JP3678824B2/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1014016A3 (en) * | 1998-12-21 | 2002-01-16 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Air conditioning systems |
| US6394761B1 (en) * | 1999-04-27 | 2002-05-28 | Tgk Co., Inc. | Capacity controller of capacity variable compressor |
| US6585494B1 (en) | 1999-06-24 | 2003-07-01 | Zexel Valeo Climate Control Corporation | Variable-capacity control for refrigerating cycle without using a large pressure control valve |
| EP1113235A1 (en) * | 1999-12-27 | 2001-07-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Air-conditioning system |
| US6449971B1 (en) | 1999-12-27 | 2002-09-17 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Air-conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3678824B2 (en) | 2005-08-03 |
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