JPH06307336A - Compressor with variable capacity - Google Patents
Compressor with variable capacityInfo
- Publication number
- JPH06307336A JPH06307336A JP5092638A JP9263893A JPH06307336A JP H06307336 A JPH06307336 A JP H06307336A JP 5092638 A JP5092638 A JP 5092638A JP 9263893 A JP9263893 A JP 9263893A JP H06307336 A JPH06307336 A JP H06307336A
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- crank chamber
- suction
- pressure
- suction chamber
- 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)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両空調用に供して好
適な圧縮機に係り、詳しくは吸入室、吐出室及びクラン
ク室を備え、吸入室圧力とクランク室圧力との差圧を調
節して回転斜板の傾角（ピストンストローク）を変える
ことにより、吐出容量を制御するようにした可変容量型
圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor suitable for air conditioning of a vehicle, and more particularly to a compressor provided with a suction chamber, a discharge chamber and a crank chamber for adjusting the differential pressure between the suction chamber pressure and the crank chamber pressure. The present invention relates to a variable displacement compressor in which the discharge capacity is controlled by changing the tilt angle (piston stroke) of the rotary swash plate.
【０００２】[0002]
【従来の技術】従来、この種の可変容量型圧縮機とし
て、例えば特開昭６２ー２０３９８０号公報に示された
構成のものが知られている。この圧縮機には、吐出室と
クランク室とを連通する給気通路と、その給気通路を開
閉するための開閉制御弁と、吸入室とクランク室とを常
時連通する抽気通路とが設けられ、吸入室圧力が設定値
以下になったときは、その圧力に応答する開閉制御弁が
給気通路を開放し、同吸入室圧力が設定値以上になった
ときは、同開閉制御弁が給気通路を閉鎖するようになさ
れている。2. Description of the Related Art Conventionally, as a variable capacity type compressor of this type, one having a structure disclosed in, for example, JP-A-62-203980 is known. This compressor is provided with an air supply passage that connects the discharge chamber and the crank chamber, an opening / closing control valve that opens and closes the air supply passage, and an extraction passage that constantly connects the suction chamber and the crank chamber. When the suction chamber pressure falls below the set value, the on-off control valve that responds to that pressure opens the air supply passage, and when the suction chamber pressure rises above the set value, the on-off control valve feeds. It is designed to close the air passage.
【０００３】したがって、開閉制御弁が給気通路を閉鎖
した圧縮機の全容量運転時には、圧縮室からクランク室
へブローバイされる冷媒ガスは抽気通路を経て常に吸入
室へ還流され、クランク室圧力と吸入室圧力との差圧は
ごく小さな値に保たれて、回転斜板は最大傾角に維持さ
れている。そして熱負荷の低下とともに吸入室圧力が設
定値を下回ると、開閉制御弁が開かれて吐出室からクラ
ンク室へ高圧の冷媒ガスが供給され、クランク室圧力を
上昇させる。すなわち、クランク室圧力と吸入室圧力と
の差圧が大きくなって回転斜板の傾角は、次第に縮小さ
れ、圧縮機の吐出容量は低減される。その後、かかる低
容量運転の継続によって熱負荷が再び上昇に転じ、吸入
室圧力が設定値を上回るのに伴って開閉制御弁が閉鎖さ
れると、上記抽気通路を経由する冷媒ガスの還流により
クランク室圧力の低下、つまり回転斜板の傾角が復活さ
れる。Therefore, during full-capacity operation of the compressor in which the opening / closing control valve closes the air supply passage, the refrigerant gas blow-by from the compression chamber to the crank chamber is constantly recirculated to the suction chamber through the bleed passage and the pressure in the crank chamber increases. The differential pressure from the suction chamber pressure is kept at a very small value, and the rotary swash plate is kept at the maximum tilt angle. Then, when the suction chamber pressure falls below the set value as the heat load decreases, the opening / closing control valve is opened and high-pressure refrigerant gas is supplied from the discharge chamber to the crank chamber to raise the crank chamber pressure. That is, the differential pressure between the crank chamber pressure and the suction chamber pressure increases, and the tilt angle of the rotating swash plate is gradually reduced, so that the discharge capacity of the compressor is reduced. After that, when the low load operation continues, the heat load starts to rise again, and when the suction chamber pressure exceeds the set value and the on-off control valve is closed, the crank gas is returned by the refrigerant gas passing through the extraction passage. The chamber pressure is reduced, that is, the inclination of the rotating swash plate is restored.
【０００４】[0004]
【発明が解決しようとする課題】さて、上述したよう
に、熱負荷に応答して圧縮機の容量復帰を敏感に行うた
めには、クランク室圧力を速やかに低下させることが必
要である。ところが、一般に吸入室の形状は設計上の制
約などから複雑なものとなることが多く、吸入室に開口
する吸入孔の近傍位置と、同開口から最も離隔した位置
とでは、ガス流れに伴う圧力損失により意外と大きな圧
力差が生じ、例えば３．０００ｒ．ｐ．ｍの回転数にお
いて、その値は０．５〜１ｋｇ／ｃｍ2 にも達する。こ
のため、吸入室に連通される上記抽気通路の開口位置如
何によっては、クランク室圧力の低下速度、つまり圧縮
機の容量復帰速度にもかなりの不同が生じることにな
る。As described above, in order to sensitively restore the capacity of the compressor in response to heat load, it is necessary to quickly reduce the crank chamber pressure. However, in general, the shape of the suction chamber is often complicated due to design restrictions, and the pressure due to the gas flow is different between the position near the suction hole that opens in the suction chamber and the position most distant from the opening. The loss causes an unexpectedly large pressure difference, and for example, 3.000 r.p.m. p. At a rotational speed of m, the value reaches 0.5 to 1 kg / cm 2 . For this reason, depending on the opening position of the bleed passage communicating with the suction chamber, a considerable disparity may occur in the rate of decrease of the crank chamber pressure, that is, the capacity return rate of the compressor.
【０００５】勿論、単純にクランク室から吸入室へのガ
ス流動を促すという一面からみれば、該抽気通路の断面
積を大きく設定することで十分足りるはずであるが、上
述した低容量運転への移行時のように、クランク室へ積
極的に吐出冷媒ガスを供給する制御方式を採用したもの
では、逆に抽気通路の断面積に比例して供給ガス量が増
大し、結果的には動力損失を招くといった不具合が避け
られない。Of course, from a point of view of simply promoting gas flow from the crank chamber to the suction chamber, it should be sufficient to set the cross-sectional area of the extraction passage to a large value, but it is sufficient for the above-mentioned low capacity operation. In the case of adopting the control system that positively supplies the discharged refrigerant gas to the crank chamber as in the transition, the supply gas amount increases in proportion to the cross-sectional area of the extraction passage, resulting in power loss. Inevitable problems such as inviting
【０００６】本発明の解決課題は、熱負荷に対する容量
制御の応答性を確実に向上させることである。A problem to be solved by the present invention is to surely improve the responsiveness of the capacity control to the heat load.
【０００７】[0007]
【課題を解決するための手段】本発明は上記課題解決の
ため、複数のボアを並設したシリンダブロックと、クラ
ンク室を形成して該シリンダブロックの一端を閉塞する
フロントハウジングと、吸入孔及び吐出孔にそれぞれ接
続された吸入室及び吐出室とを有し、弁板を介して該シ
リンダブロックの他端を閉塞するリヤハウジングと、該
クランク室内に延在する駆動軸と、クランク室内で該駆
動軸と共に回転し、かつ傾角変位可能な回転斜板と、該
回転斜板に連係され、その回転揺動に基づいて各ボア内
を直動するピストンと、上記クランク室と上記吸入室と
を連通する抽気通路を介して両室の差圧を調節し、上記
回転斜板の傾角変位と共に吐出容量を変化させる制御弁
とを装備した可変容量型圧縮機において、上記抽気通路
が吸入室内の上記吸入孔開口部より最も離隔した領域に
開口されているという新規な構成を採用している。In order to solve the above problems, the present invention provides a cylinder block having a plurality of bores arranged side by side, a front housing which forms a crank chamber and closes one end of the cylinder block, a suction hole, and A rear housing having an intake chamber and a discharge chamber respectively connected to the discharge holes and closing the other end of the cylinder block via a valve plate, a drive shaft extending into the crank chamber, and a drive shaft extending in the crank chamber. A rotary swash plate that rotates together with the drive shaft and is capable of tilt displacement, a piston that is linked to the rotary swash plate, and that linearly moves in each bore based on the rotational swing thereof, the crank chamber, and the suction chamber. In a variable displacement compressor equipped with a control valve that adjusts the differential pressure between the two chambers via a communicating bleed passage and changes the discharge capacity along with the tilt displacement of the rotary swash plate, the bleed passage is in the suction chamber. It employs a novel configuration that is open to the farthest region from the entry apertures opening.
【０００８】本発明の好適な形態として、上記制御弁は
吐出室とクランク室とを結ぶ給気通路に配設されて、該
クランク室への積極的な給気を制御するものであるが、
これが上記抽気通路に配設されて、該クランク室からの
抽気を制御するものであっても本発明の適用は可能であ
る。As a preferred embodiment of the present invention, the control valve is arranged in an air supply passage connecting the discharge chamber and the crank chamber to control positive air supply to the crank chamber.
The present invention can be applied even if it is arranged in the bleed passage to control the bleed air from the crank chamber.
【０００９】[0009]
【作用】クランク室と吸入室とを連通する抽気通路を、
吸入室内の吸入孔開口部より最も離隔した領域（圧力低
下の大なる領域）に開口させたので、容量復帰時のクラ
ンク室と吸入室との圧力勾配が大きくなって、クランク
室圧力を可及的速やかに低下させることができる。ま
た、低容量への移行時には、容量低下に伴う吸入室内の
ガス流量の減少につれて、圧力損失による差圧も当然に
小さくなるので、上記開口の特定による実質的に有害な
動力損失は生じない。[Operation] The bleed passage that connects the crank chamber and the suction chamber is
Since the opening is made in the region farthest from the opening of the suction hole in the suction chamber (the region where the pressure drop is large), the pressure gradient between the crank chamber and the suction chamber at the time of capacity restoration becomes large, and the crank chamber pressure can be increased. It can be lowered promptly. In addition, at the time of shifting to a low capacity, the differential pressure due to the pressure loss naturally decreases as the gas flow rate in the suction chamber decreases due to the decrease in capacity, so that substantially harmful power loss due to the specification of the opening does not occur.
【００１０】[0010]
【実施例】以下、図１及び図２に基づいて本発明の実施
例を具体的に説明する。図において、圧縮機の外郭の一
部を構成するシリンダブロック１の前端にはフロントハ
ウジング２が結合され、同後端には吸入室５及び吐出室
６が形成されたリヤハウジング３が弁板４を介して結合
されている。そしてフロントハウジング２内に形成され
たクランク室７には、動力源に連結された駆動軸８が挿
通され、該駆動軸８はシリンダブロック１及びフロント
ハウジング２に回転自在に支承されている。クランク室
７内の駆動軸８上には回転支持体９が固着され、該回転
支持体９の後面側に延出した支持アーム１０の先端部に
は長孔１０ａが貫設されている。そして該長孔１０ａに
はピン１１がスライド可能に嵌入されており、同ピン１
１には回転斜板１２が傾動可能に連結されている。Embodiments of the present invention will be specifically described below with reference to FIGS. 1 and 2. In the figure, a front housing 2 is coupled to a front end of a cylinder block 1 which constitutes a part of an outer shell of a compressor, and a rear housing 3 having a suction chamber 5 and a discharge chamber 6 is formed at a rear end of the cylinder block 1 and a valve plate 4. Are connected through. A drive shaft 8 connected to a power source is inserted into a crank chamber 7 formed in the front housing 2, and the drive shaft 8 is rotatably supported by the cylinder block 1 and the front housing 2. A rotation support 9 is fixed to the drive shaft 8 in the crank chamber 7, and a long hole 10a is formed at the tip of a support arm 10 extending to the rear surface side of the rotation support 9. A pin 11 is slidably fitted in the elongated hole 10a.
A rotary swash plate 12 is tiltably connected to the shaft 1.
【００１１】回転支持体９の後端に隣接して駆動軸８上
にはスリーブ１３が遊嵌され、コイルばね１４により常
に回転支持体９側へ付勢されるとともに、スリーブ１３
の左右両側に突設された枢軸１３ａ（一方のみ図示）が
回転斜板１２の図示しない係合孔に嵌入されて、該回転
斜板１２は枢軸１３ａの周りを揺動しうるように支持さ
れている。A sleeve 13 is loosely fitted on the drive shaft 8 adjacent to the rear end of the rotary support 9, and is constantly biased toward the rotary support 9 by a coil spring 14, and at the same time, the sleeve 13 is provided.
Pivot shafts 13a (only one of which is shown) projecting from the left and right sides of the rotary swash plate 12 are fitted into engaging holes (not shown) of the rotary swash plate 12, and the rotary swash plate 12 is supported so as to swing around the pivot shaft 13a. ing.
【００１２】回転斜板１２の後面側には揺動板１５が相
対回転可能に支持され、かつ外縁部に設けた案内部１５
ａが通しボルト１６と係合することにより自転が拘束さ
れるとともに、シリンダブロック１に貫設されたボア１
７内のピストン１８と該揺動板１５とはコンロッド１９
により連節されている。したがって、駆動軸８の回転運
動が回転斜板１２を介して揺動板１５の前後揺動に変換
され、ピストン１８がボア１７内を往復動することによ
り吸入室５からボア１７内へ吸入された冷媒ガスが圧縮
されつつ吐出室６へ吐出される。そしてクランク室圧力
と吸入室圧力との差圧に応じてピストン１８のストロー
ク及び揺動板１５の傾角が変化し、吐出容量が制御され
る。なお、クランク室圧力は以下に述べる開閉制御弁２
０により冷房負荷に基づいて制御される。A swing plate 15 is supported on the rear surface side of the rotary swash plate 12 so as to be relatively rotatable, and a guide portion 15 provided at an outer edge portion.
Rotation is restrained by engaging a with the through bolt 16 and the bore 1 penetrating the cylinder block 1 is provided.
The piston 18 and the oscillating plate 15 inside the connecting rod 19
Has been articulated by. Therefore, the rotary motion of the drive shaft 8 is converted into the back-and-forth swing of the swing plate 15 via the rotary swash plate 12, and the piston 18 reciprocates in the bore 17 to be sucked from the suction chamber 5 into the bore 17. The refrigerant gas is discharged into the discharge chamber 6 while being compressed. Then, the stroke of the piston 18 and the tilt angle of the oscillating plate 15 change according to the pressure difference between the crank chamber pressure and the suction chamber pressure, and the discharge capacity is controlled. The crank chamber pressure is controlled by the on-off control valve 2 described below.
0 controls on the basis of the cooling load.
【００１３】すなわち、リヤハウジング３に内装された
開閉制御弁２０には、吸入圧室２１と吐出圧室２２が対
峙して設けられ、吸入圧室２１は通孔２３を介して吸入
室５と、また、吐出圧室２２は通孔２４を介して吐出室
６とそれぞれ連通せしめられている。そして吸入圧室２
１には中心部に配置された大気圧室２５を囲繞するよう
に伸縮自在なベローズ２６が設けられ、該ベローズ２６
はばね２７を介して常時伸長方向（吐出圧室２２方向）
に付勢されている。一方、吐出圧室２２には吸入圧室２
１寄りの一端に弁孔２８が設けられ、該弁孔２８に連な
って画設されたポート２９は、給気通路３０を経由して
クランク室７に連通されている。また、上記ベローズ２
６には弁杆３１の基端が連結されて吐出圧室２２方向に
延び、その先端はポート２９及び弁孔２８を貫通して吐
出圧室２２内に臨むように設けられている。そして該弁
杆３１の先端には弁孔２８と対向させて弁体３２が取付
けられ、該弁体３２はベローズ２６の伸縮作用を介して
開閉作動可能に構成されるとともに、吐出圧室２２に介
装されたばね３３により常に弁孔２８方向（閉じ方向）
に付勢されている。したがって、吸入圧室２１に導入さ
れる吸入室圧力が設定値よりも低下すると、ベローズ２
６の伸長と共に弁杆３１は進動して弁体３２を開弁さ
せ、弁孔２８からポート２９及び給気通路３０を経由し
てクランク室７には吐出冷媒ガスが供給される。That is, the opening / closing control valve 20 provided in the rear housing 3 is provided with a suction pressure chamber 21 and a discharge pressure chamber 22 facing each other, and the suction pressure chamber 21 is connected to the suction chamber 5 via a through hole 23. The discharge pressure chamber 22 is communicated with the discharge chamber 6 through the through hole 24. And suction pressure chamber 2
1 is provided with a bellows 26 which is expandable and contractable so as to surround an atmospheric pressure chamber 25 arranged at the center.
Always extends through spring 27 (direction of discharge pressure chamber 22)
Is urged by. On the other hand, the discharge pressure chamber 22 has a suction pressure chamber 2
A valve hole 28 is provided at one end closer to the port 1, and a port 29 that is continuous with the valve hole 28 is connected to the crank chamber 7 via an air supply passage 30. In addition, the bellows 2
A base end of a valve rod 31 is connected to 6 and extends in the direction of the discharge pressure chamber 22. The tip of the valve rod 31 penetrates through the port 29 and the valve hole 28 and faces the discharge pressure chamber 22. A valve body 32 is attached to the tip of the valve rod 31 so as to face the valve hole 28. The valve body 32 is configured to be opened and closed through expansion and contraction of the bellows 26, and to the discharge pressure chamber 22. The inserted spring 33 always keeps the valve hole 28 (closed direction).
Is urged by. Therefore, when the suction chamber pressure introduced into the suction pressure chamber 21 falls below the set value, the bellows 2
6, the valve rod 31 advances to open the valve element 32, and the discharged refrigerant gas is supplied from the valve hole 28 to the crank chamber 7 via the port 29 and the air supply passage 30.
【００１４】次いで、本発明の特徴的構成要素である抽
気通路４０について説明する。抽気通路４０は、クラン
ク室７からシリンダブロック１及び弁板４を貫通して吸
入室５に連通され、その流量は固定絞り４１によって所
定の値に設定されている。図２に示すように、吸入室５
は、軸心部を含んで形成された吐出室６を囲包する形態
で画設されており、該吸入室５は吸入孔５ａ及びこれに
連なる図示しない配管を経由して蒸発器に接続され、一
方、吐出室６も吐出孔６ａに連なる同様の配管を経由し
て凝縮器に接続されている。Next, the extraction passage 40, which is a characteristic component of the present invention, will be described. The extraction passage 40 communicates with the suction chamber 5 from the crank chamber 7 through the cylinder block 1 and the valve plate 4, and the flow rate thereof is set to a predetermined value by the fixed throttle 41. As shown in FIG. 2, the suction chamber 5
Is defined so as to surround the discharge chamber 6 formed including the axial center portion, and the suction chamber 5 is connected to the evaporator through the suction hole 5a and a pipe (not shown) connected to the suction hole 5a. On the other hand, the discharge chamber 6 is also connected to the condenser via a similar pipe connected to the discharge hole 6a.
【００１５】そして図から明らかなように、吸入室５は
吐出室６の所要スペース、通しボルト１６の結合孔、接
続フランジの設定位置など幾多の設計上の制約から、か
なり複雑化した形状を強いられることもあって、例えば
吸入孔５ａの開口近傍の吸入口５ｂに流れる冷媒ガス
と、該開口部から最も離隔した吸入口５ｂ′に流れる冷
媒ガスとでは、圧力損失に伴う大きな圧力差が生じてい
る。上記クランク室７と吸入室５とを連通する抽気通路
４０は、吸入孔５ａの開口部から最も離隔した領域、つ
まり吸入室５内において最も低圧となる領域に開口４０
ａすべく構成されている。As is clear from the figure, the suction chamber 5 is strongly complicated due to various design restrictions such as the required space of the discharge chamber 6, the connecting hole of the through bolt 16 and the setting position of the connecting flange. As a result, for example, a large pressure difference occurs due to the pressure loss between the refrigerant gas flowing through the suction port 5b near the opening of the suction hole 5a and the refrigerant gas flowing through the suction port 5b 'that is farthest from the opening. ing. The bleed passage 40 that connects the crank chamber 7 and the suction chamber 5 to each other is opened in a region farthest from the opening of the suction hole 5a, that is, in a region where the pressure is the lowest in the suction chamber 5.
a).
【００１６】したがって、圧縮機の低容量運転の継続に
より熱負荷が上昇に転じ、吸入室圧力が設定値を上回る
のに伴って開閉制御弁２０が閉鎖されると、抽気通路４
０を経由して吸入室５に至る冷媒ガスの還流によりクラ
ンク室圧力は低下されるが、該抽気通路４０は吸入室５
内の吸入孔５ａ開口部より最も離隔した領域（最低圧領
域）に開口４０ａされているので、クランク室７と吸入
室５との圧力勾配が大きくなって、クランク室圧力は可
及的速やかに低下され、熱負荷に応答した素早い容量復
帰が行われる。Therefore, when the heat load starts to increase due to the continued low capacity operation of the compressor and the opening / closing control valve 20 is closed as the suction chamber pressure exceeds the set value, the bleed passage 4
Although the crank chamber pressure is reduced by the circulation of the refrigerant gas to the suction chamber 5 via 0, the extraction passage 40 is
Since the opening 40a is formed in the region (the lowest pressure region) farthest from the opening of the suction hole 5a, the pressure gradient between the crank chamber 7 and the suction chamber 5 becomes large, and the crank chamber pressure is as fast as possible. The capacity is lowered to provide a quick capacity recovery in response to the heat load.
【００１７】また、圧縮機の低容量運転への移行時に
は、吸入室圧力の低下が開閉制御弁２０の開通、クラン
ク室圧力の上昇、容量の低下並びに吸入室５内のガス流
量の低下を伴って圧力損失を減少させるので、上記抽気
通路４０の開口４０ａが占める領域の他の領域に対する
相対的圧力は上昇し、過剰抽気を過剰給気で補うといっ
た不合理な動力の浪費は生じない。Further, when the compressor is shifted to a low capacity operation, the suction chamber pressure is decreased by opening the on-off control valve 20, the crank chamber pressure is increased, the capacity is decreased, and the gas flow rate in the suction chamber 5 is decreased. Since the pressure loss is reduced by this, the relative pressure of the region occupied by the opening 40a of the bleed passage 40 to the other region increases, and irrational power consumption such as supplementing the excess bleed with excess air does not occur.
【００１８】なお、上述の実施例は、クランク室圧力と
吸入室圧力との差圧調節による容量制御を、吐出室とク
ランク室とを結ぶ給気通路に制御弁を配設して、該制御
弁によるクランク室への積極的な給気制御と、抽気通路
を介したクランク室からの定量抽気とを複合させて行う
方式の圧縮機について説明したが、本発明は必ずしもか
かる制御方式に限定されるものではない。In the above embodiment, the capacity control by adjusting the differential pressure between the crank chamber pressure and the suction chamber pressure is performed by disposing a control valve in the air supply passage connecting the discharge chamber and the crank chamber. Although the compressor of the system that combines the positive air supply control to the crank chamber by the valve and the quantitative extraction from the crank chamber through the extraction passage has been described, the present invention is not necessarily limited to such a control system. Not something.
【００１９】すなわち、クランク室圧力の上昇手段とし
て、単にクランク室に漏入するブローバイガスのみを利
用するか、若しくは吐出室とクランク室とを結ぶ固定絞
り通路を設けて補助的な給気を行うようにし、一方、抽
気通路が形成されるシリンダブロック又はリヤハウジン
グには抽気流量を調整する制御弁を配設して、これら定
量給気と可変抽気制御とを複合させた制御方式、さらに
は給気、抽気の双方を制御する弁機構を備えた制御方式
の圧縮機であっても、本発明の適用が可能であることは
勿論である。That is, as a means for increasing the crank chamber pressure, only blow-by gas that leaks into the crank chamber is used, or a fixed throttle passage that connects the discharge chamber and the crank chamber is provided to perform supplementary air supply. On the other hand, on the other hand, a control valve for adjusting the extraction flow rate is provided in the cylinder block or the rear housing in which the extraction passage is formed, and a control system that combines these constant amount air supply and variable air extraction control Needless to say, the present invention can be applied to a control type compressor including a valve mechanism that controls both air and bleed air.
【００２０】[0020]
【発明の効果】以上、詳述したように本発明は、クラン
ク室と吸入室とを連通する抽気通路を吸入室内の吸入孔
開口部より最も離隔した領域に開口させたものであるか
ら、吸入室内に生起する圧力損失の有効活用により、容
量復帰時におけるクランク室と吸入室との圧力勾配を大
きくしえて、クランク室圧力を迅速に低下させることが
でき、一方、容量低減時には吸入室内のガス流量の減少
につれて圧力損失も自動的に縮小されるので、動力の浪
費を伴うことなくクランク室圧力を円滑に上昇させるこ
とができる。As described above in detail, according to the present invention, the bleed passage that connects the crank chamber and the suction chamber is opened in the region that is farthest from the suction hole opening in the suction chamber. By effectively utilizing the pressure loss that occurs in the room, the pressure gradient between the crank chamber and the suction chamber at the time of capacity restoration can be increased, and the crank chamber pressure can be quickly reduced. Since the pressure loss is automatically reduced as the flow rate decreases, the crank chamber pressure can be smoothly increased without wasting power.
【図１】本発明の実施例に係る圧縮機の全容を示す断面
図。FIG. 1 is a cross-sectional view showing the entire structure of a compressor according to an embodiment of the present invention.
【図２】吸入室と抽気通路との関係を示す断面側面図。FIG. 2 is a sectional side view showing the relationship between the suction chamber and the extraction passage.
１はシリンダブロック、３はリヤハウジング、５は吸入
室、５ａは吸入孔、６は吐出室、７はクランク室、８は
駆動軸、１２は回転斜板、２０は開閉制御弁、３０は給
気通路、４０は抽気通路、４０ａは開口1 is a cylinder block, 3 is a rear housing, 5 is a suction chamber, 5a is a suction hole, 6 is a discharge chamber, 7 is a crank chamber, 8 is a drive shaft, 12 is a rotary swash plate, 20 is an opening / closing control valve, and 30 is a supply valve. Air passage, 40 is extraction passage, 40a is opening
───────────────────────────────────────────────────── フロントページの続き (72)発明者 日高 茂之 愛知県刈谷市豊田町２丁目１番地 株式会 社豊田自動織機製作所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Shigeyuki Hidaka, 2-chome, Toyota-cho, Kariya city, Aichi Prefecture Toyota Industries Corporation
Claims (3)
と、クランク室を形成して該シリンダブロックの一端を
閉塞するフロントハウジングと、吸入孔及び吐出孔にそ
れぞれ接続された吸入室及び吐出室とを有し、弁板を介
して該シリンダブロックの他端を閉塞するリヤハウジン
グと、該クランク室内に延在する駆動軸と、クランク室
内で該駆動軸と共に回転し、かつ傾角変位可能な回転斜
板と、該回転斜板に連係され、その回転揺動に基づいて
各ボア内を直動するピストンと、上記クランク室と上記
吸入室とを連通する抽気通路を介して両室の差圧を調節
し、上記回転斜板の傾角変位と共に吐出容量を変化させ
る制御弁とを装備した可変容量型圧縮機において、上記
抽気通路は吸入室内の上記吸入孔開口部より最も離隔し
た領域に開口されていることを特徴とする可変容量型圧
縮機。1. A cylinder block having a plurality of bores arranged in parallel, a front housing forming a crank chamber to close one end of the cylinder block, and a suction chamber and a discharge chamber respectively connected to the suction hole and the discharge hole. A rear housing that closes the other end of the cylinder block via a valve plate, a drive shaft that extends into the crank chamber, and a rotary tilt that rotates together with the drive shaft in the crank chamber and that is capable of tilt displacement. A plate, a piston that is linked to the rotary swash plate, and that directly moves in each bore based on its rotational oscillation, and a differential pressure between the two chambers via a bleed passage that connects the crank chamber and the suction chamber. In a variable displacement compressor equipped with a control valve that adjusts and changes the displacement of the rotary swash plate with the tilt displacement of the rotary swash plate, the bleed passage is opened in a region farthest from the suction hole opening in the suction chamber. A variable capacity compressor characterized in that
ぶ給気通路に配設されて、該クランク室への積極的な給
気を制御するものである請求項１記載の可変容量型圧縮
機。2. The variable displacement type according to claim 1, wherein the control valve is arranged in an air supply passage connecting the discharge chamber and the crank chamber to control positive air supply to the crank chamber. Compressor.
て、クランク室からの抽気を制御するものである請求項
１記載の可変容量型圧縮機。3. The variable displacement compressor according to claim 1, wherein the control valve is arranged in the bleed passage to control bleed air from the crank chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05092638A JP3092765B2 (en) | 1993-04-20 | 1993-04-20 | Variable displacement compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05092638A JP3092765B2 (en) | 1993-04-20 | 1993-04-20 | Variable displacement compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06307336A true JPH06307336A (en) | 1994-11-01 |
| JP3092765B2 JP3092765B2 (en) | 2000-09-25 |
Family
ID=14059997
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05092638A Expired - Fee Related JP3092765B2 (en) | 1993-04-20 | 1993-04-20 | Variable displacement compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3092765B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014043822A (en) * | 2012-08-28 | 2014-03-13 | Sanden Corp | Compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101568964B1 (en) | 2015-07-10 | 2015-11-12 | 신혜원 | A Flooring For Arrest Of Noise |
-
1993
- 1993-04-20 JP JP05092638A patent/JP3092765B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014043822A (en) * | 2012-08-28 | 2014-03-13 | Sanden Corp | Compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3092765B2 (en) | 2000-09-25 |
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