JPH089432Y2 - Variable capacity compressor - Google Patents
Variable capacity compressorInfo
- Publication number
- JPH089432Y2 JPH089432Y2 JP1989118084U JP11808489U JPH089432Y2 JP H089432 Y2 JPH089432 Y2 JP H089432Y2 JP 1989118084 U JP1989118084 U JP 1989118084U JP 11808489 U JP11808489 U JP 11808489U JP H089432 Y2 JPH089432 Y2 JP H089432Y2
- Authority
- JP
- Japan
- Prior art keywords
- suction
- chamber
- partition
- ribs
- swash plate
- 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 - Lifetime
Links
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Description
【考案の詳細な説明】 ［産業上の利用分野］ 本考案は吸入室と吐出室とクランク室とを備え、クラ
ンク室内に駆動軸の回転をシリンダボア内に収容された
ピストンの往復動に変換する作用をなす斜板を設け、ク
ランク室圧力と吸入圧力との差圧に応じて前記斜板の傾
斜角が変化することによりピストンのストロークが変更
されて圧縮容量を制御するようにした可変容量圧縮機に
関するものである。DETAILED DESCRIPTION OF THE INVENTION [Industrial application] The present invention includes a suction chamber, a discharge chamber and a crank chamber, and converts the rotation of a drive shaft into the crank chamber into reciprocating motion of a piston housed in a cylinder bore. A variable displacement compression is provided in which a swash plate that operates is provided, and the stroke of the piston is changed by changing the inclination angle of the swash plate in accordance with the pressure difference between the crank chamber pressure and the suction pressure to control the compression capacity. It is about machines.
［従来の技術］ この種の可変容量圧縮機、例えば揺動斜板式圧縮機
（ワッブル式圧縮機）においては、第３図に示すよう
に、ピストン41が往復摺動可能に収容されるシリンダボ
ア42が形成されたシリンダブロック43の端面にバルブプ
レート44を介してリヤハウジング45がボルト（図示せ
ず）により接合固定されている。バルブプレート44には
リヤハウジング45に形成された吸入室46及び吐出室47を
前記シリンダボア42と連通させる吸入孔48及び吐出孔49
がそれぞれ形成されるとともに、シリンダブロック43側
に前記吸入孔48を開閉する吸入弁50が、吐出室47側に前
記吐出孔49を開閉する吐出弁51がそれぞれ設けられてい
る。そして、吸入弁50及び吐出弁51が必要以上に開放側
に撓むのを防止するため、吐出弁51の背面側にはリテー
ナ52が配設され、シリンダボア42の端部には吸入弁50の
先端を係止する係止凹部53が形成されている。又、外部
冷却回路からの帰還冷媒ガスが吸入室46に開口する吸入
ポート54から吸入室46に直接導入されるようになってい
る。[Prior Art] In a variable displacement compressor of this type, for example, an oscillating swash plate type compressor (wobble type compressor), as shown in FIG. 3, a cylinder bore 42 in which a piston 41 is reciprocally slidably housed is accommodated. A rear housing 45 is joined and fixed to the end surface of the cylinder block 43 formed with the valve plate 44 with a bolt (not shown). The valve plate 44 has a suction hole 48 and a discharge hole 49 for communicating a suction chamber 46 and a discharge chamber 47 formed in the rear housing 45 with the cylinder bore 42.
And a suction valve 50 that opens and closes the suction hole 48 on the cylinder block 43 side, and a discharge valve 51 that opens and closes the discharge hole 49 on the discharge chamber 47 side. Then, in order to prevent the intake valve 50 and the discharge valve 51 from flexing to the open side more than necessary, a retainer 52 is provided on the back side of the discharge valve 51, and the intake valve 50 is provided at the end of the cylinder bore 42. A locking recess 53 for locking the tip is formed. Further, the return refrigerant gas from the external cooling circuit is directly introduced into the suction chamber 46 from the suction port 54 opening to the suction chamber 46.
［考案が解決しようとする課題］ 前記従来の構成では駆動軸の低速回転時、すなわちピ
ストン41の移動速度が遅い場合、吸入弁50はその先端部
が開き始めてから係止凹部53に当接するまでの間に自励
振動を生じ、この自励振動により特有の周波数を持つ吸
入脈動が発生する。そして、前記のように外部冷却回路
からの帰還冷媒ガスが吸入ポート54から吸入室46に直接
導入される構成では、吸入ポート54と外部冷却回路の蒸
発器とを連結する管路を介して前記吸入脈動が減衰され
ずに蒸発器に伝達され、前記特有の周波数を持つ吸入脈
動により蒸発器が共振して異音を発生するという不都合
があった。係止凹部53の深さを浅くすればこの不都合を
解消することができるが、吸入抵抗となって吸入性能が
低下し、冷房効率が低下するという問題が生じる。[Problems to be Solved by the Invention] In the above-described conventional configuration, when the drive shaft rotates at a low speed, that is, when the moving speed of the piston 41 is slow, the suction valve 50 starts contacting with the locking recess 53 from the beginning of its opening. A self-excited vibration is generated during this period, and this self-excited vibration causes an intake pulsation having a specific frequency. Then, in the configuration in which the return refrigerant gas from the external cooling circuit is directly introduced from the suction port 54 into the suction chamber 46 as described above, the suction port 54 and the evaporator of the external cooling circuit are connected via a pipe line. The suction pulsation is transmitted to the evaporator without being damped, and the suction pulsation having the above-mentioned specific frequency causes the evaporator to resonate and generate abnormal noise. This inconvenience can be eliminated by making the depth of the locking recess 53 shallow, but there arises a problem that suction resistance becomes a reduction in suction performance and cooling efficiency decreases.
本考案は前記の問題点に鑑みてなされたものであっ
て、その目的は吸入弁の自励振動に起因する蒸発器の共
振を防止して、異音発生を低減することができる可変容
量圧縮機を提供することにある。The present invention has been made in view of the above problems, and an object thereof is to prevent the resonance of the evaporator caused by the self-excited vibration of the suction valve and reduce the generation of abnormal noise. To provide a machine.
［課題を解決するための手段］ 前記の目的を達成するため、本考案は、吸入室と吐出
室とクランク室とを備え、クランク室内に駆動軸の回転
をシリンダボア内に収容されたピストンの往復動に変換
する作用をなす斜板を設け、クランク室圧力と吸入圧力
との差圧に応じて前記斜板の傾斜角が変化することによ
りピストンのストロークが変更されて圧縮容量を制御す
るようにした可変容量圧縮機において、外側に環状の吸
入室を、内側に吐出室を区画形成する環状隔壁を有する
ハウジングに前記収入室に連通する吸入ポートを形成す
るとともに、該ハウジングの周壁内面に第１隔壁リブを
複数箇所に突設して、各第１隔壁リブと前記環状隔壁の
外周面との間に冷媒ガスの流路面積が一時的に小さくな
る第１絞り部をそれぞれ設け、前記環状隔壁の外周面に
第２隔壁リブを複数箇所に突設して、各第２隔壁リブと
前記ハウジングの周壁内面との間に冷媒ガスの流路面積
が一時的に小さくなる第２絞り部をそれぞれ設け、さら
に、前記第１及び第２の隔壁リブの間にそれぞれ形成さ
れた複数の吸入小室を各シリンダボアに連通する吸入孔
と対応した。[Means for Solving the Problems] In order to achieve the above object, the present invention includes a suction chamber, a discharge chamber, and a crank chamber, and the rotation of a drive shaft in the crank chamber reciprocates a piston housed in a cylinder bore. A swash plate having a function of converting into motion is provided, and the stroke of the piston is changed by changing the inclination angle of the swash plate according to the pressure difference between the crank chamber pressure and the suction pressure, so that the compression capacity is controlled. In the variable displacement compressor described above, a suction port communicating with the income chamber is formed in a housing having an annular suction chamber on the outer side and an annular partition wall defining a discharge chamber on the inner side, and a first inner surface of the peripheral wall of the housing. The partition ribs are provided at a plurality of locations, and first throttle portions each having a temporarily reduced flow passage area of the refrigerant gas are provided between the respective first partition ribs and the outer peripheral surface of the annular partition. A plurality of second partition ribs are provided on the outer peripheral surface of the housing so as to project a plurality of second throttle portions between the second partition ribs and the inner surface of the peripheral wall of the housing to temporarily reduce the flow passage area of the refrigerant gas. Further, the plurality of suction small chambers formed between the first and second partition ribs correspond to the suction holes that communicate with each cylinder bore.
［作用］ 圧縮機が運転されてピストンの往動によりシリンダボ
アに形成される圧縮室内の圧力が低下すると、吸入弁が
開いて圧縮室への冷媒ガスの吸入が行われる。このとき
吸入弁は従来装置と同様に自励振動を生じ、該吸入弁近
傍の冷媒ガスに吸入弁の自励振動による特有の周波数を
持った振動が伝達される。吸入孔と吸入ポートとを連通
する冷媒ガスの流路の途中に、つまり吸入室に、その流
路面積を一時的に小さくする第１及び第２の絞り部があ
るため、前記振動が伝播する流路の面積が第１及び第２
の絞り部の前後で大幅に変化し、かつ方向転換を強いら
れて、ガス流路が長くなり、従って、両絞り部を通過す
ることにより特有の周波数をもった振動の減衰効果が促
進され蒸発器の共振が防止されて異音の発生がなくな
る。[Operation] When the compressor is operated and the forward movement of the piston lowers the pressure in the compression chamber formed in the cylinder bore, the suction valve opens and the refrigerant gas is sucked into the compression chamber. At this time, the suction valve causes self-excited vibration as in the conventional device, and the vibration having a specific frequency due to the self-excited vibration of the suction valve is transmitted to the refrigerant gas near the suction valve. Since the first and second throttle portions that temporarily reduce the flow passage area are provided in the middle of the flow passage of the refrigerant gas that communicates the suction hole and the suction port, that is, in the suction chamber, the vibration propagates. The area of the flow path is the first and second
Before and after the throttle part, the gas flow path is lengthened by the change of direction and the change of direction is forced. Therefore, by passing through both throttle parts, the damping effect of vibration with a unique frequency is promoted and vaporized. Resonance of the vessel is prevented and abnormal noise is eliminated.
［実施例１］ 以下、本考案を揺動斜板式圧縮機に具体化した第１実
施例を第１、２図に従って説明する。[First Embodiment] A first embodiment in which the present invention is embodied in a swing swash plate type compressor will be described below with reference to FIGS.
シリンダブロック１の前端面には内部にクランク室２
が形成されたフロントハウジング３が接合固定され、後
端面には吸入室４及び吐出室５が形成されたリヤハウジ
ング６がバルブプレート７を介して接合固定されてい
る。バルブプレート７には前記吸入室４及び吐出室５を
前記シリンダブロック１に形成されたシリンダボア1aと
連通させる吸入孔８及び吐出孔９がそれぞれ形成されて
いる。バルブプレート７のシリンダブロック１側には吸
入孔８を開閉する吸入弁10が、吐出室５側には吐出孔９
を開閉する吐出弁11がそれぞれ設けられている。そし
て、吸入弁10及び吐出弁11が必要以上に開放側に撓むの
を防止するため、吐出弁11の背面側にはリテーナ12が配
設され、シリンダボア1aの端部には吸入弁10の先端を係
止する係止凹部13が形成されている。The front of the cylinder block 1 has a crank chamber 2 inside.
The front housing 3 in which is formed is joined and fixed, and the rear housing 6 in which the suction chamber 4 and the discharge chamber 5 are formed is joined and fixed to the rear end surface via the valve plate 7. The valve plate 7 is formed with a suction hole 8 and a discharge hole 9 for communicating the suction chamber 4 and the discharge chamber 5 with the cylinder bore 1a formed in the cylinder block 1, respectively. A suction valve 10 for opening and closing a suction hole 8 is provided on the cylinder block 1 side of the valve plate 7, and a discharge hole 9 is provided on the discharge chamber 5 side.
Discharge valves 11 for opening and closing are respectively provided. Then, in order to prevent the intake valve 10 and the discharge valve 11 from flexing to the open side more than necessary, a retainer 12 is arranged on the back side of the discharge valve 11, and the intake valve 10 is provided at the end of the cylinder bore 1a. A locking recess 13 for locking the tip is formed.
シリンダブロック１とフロントハウジング３との間に
は駆動軸18が回転自在に支持され、該駆動軸18に一体回
転可能に嵌着固定された回転体19には回転駆動板20が連
結ピン21を介して一体回転可能かつ傾動可能に取付けら
れている。前記駆動軸18上にはスライダ22が軸線方向へ
摺動可能に嵌挿され、スライダ22の対称位置に突設され
た一対のピン23に対して前記回転駆動板20がその支持筒
部20aにおいて傾動可能に支持されている。そして、回
転駆動板20の支持筒部20aには、揺動斜板24が相対回転
可能かつ同期傾動可能に支持されている。揺動斜板24は
前記シリンダブロック１に形成されたシリンダボア1a内
に収容されたピストン25に対してピストンロッド26を介
して連結されるとともに、シリンダブロック１とフロン
トハウジング３との間に横架された案内ロッド27により
回転が規制されている。又、スライダ22はバネ28により
揺動斜板24の傾斜角を増大させる方向（第１図の左方
向）に付勢されている。A drive shaft 18 is rotatably supported between the cylinder block 1 and the front housing 3, and a rotary drive plate 20 is provided with a connecting pin 21 on a rotary body 19 fitted and fixed to the drive shaft 18 so as to be integrally rotatable. It is attached so as to be integrally rotatable and tiltable via the. A slider 22 is slidably fitted on the drive shaft 18 in the axial direction, and the rotary drive plate 20 is supported by a pair of pins 23 projecting at symmetrical positions of the slider 22 at its supporting cylinder portion 20a. It is supported so that it can tilt. A swing swash plate 24 is supported by the support cylinder portion 20a of the rotary drive plate 20 so as to be relatively rotatable and synchronously tiltable. The swing swash plate 24 is connected to a piston 25 housed in a cylinder bore 1a formed in the cylinder block 1 via a piston rod 26, and is horizontally mounted between the cylinder block 1 and the front housing 3. The rotation is restricted by the guide rod 27 that is formed. Further, the slider 22 is urged by a spring 28 in a direction to increase the inclination angle of the swing swash plate 24 (leftward in FIG. 1).
第２図に示すように吸入室４と吐出室５とを区画する
環状隔壁6aを有するリヤハウジング６の周壁内面に第１
隔壁リブ29が３個突設され、前記環状隔壁6aの外周面に
第２隔壁リブ29′が３個突設されている。そして、前記
両隔壁リブ29,29′により吸入室４が各シリンダボア1a
と対応する複数個（この実施例では６個）の小室4aに区
画され、各小室4aは吸入孔８を介してシリンダボア1aに
連通可能となっている。そして、第１隔壁リブ29の先端
と環状隔壁6aの外周面との間が冷媒ガスの流路面積を一
時的に小さくする第１絞り部30となっている。又、第２
隔壁リブ29′の先端とリヤハウジング６の周壁内面との
間が冷媒ガスの流路面積を一時的に小さくする第２絞り
部30′となっている。As shown in FIG. 2, on the inner surface of the peripheral wall of the rear housing 6 having an annular partition wall 6a which divides the suction chamber 4 and the discharge chamber 5, the first
Three partition ribs 29 are provided so as to project, and two second partition ribs 29 'are provided on the outer peripheral surface of the annular partition 6a. Then, the suction chamber 4 is moved to each cylinder bore 1a by the both partition ribs 29, 29 '.
Is divided into a plurality of (6 in this embodiment) small chambers 4a, and each small chamber 4a can communicate with the cylinder bore 1a through the suction hole 8. Further, a space between the tip of the first partition rib 29 and the outer peripheral surface of the annular partition 6a is a first throttle portion 30 that temporarily reduces the flow passage area of the refrigerant gas. Also, the second
A portion between the tip of the partition rib 29 'and the inner surface of the peripheral wall of the rear housing 6 serves as a second throttle portion 30' for temporarily reducing the flow passage area of the refrigerant gas.
なお、図示しないがリヤハウジング６にはクランク室
２内の圧力を制御する制御弁が設けられている。Although not shown, the rear housing 6 is provided with a control valve for controlling the pressure in the crank chamber 2.
次に前記のように構成された装置の作用を説明する。 Next, the operation of the device configured as described above will be described.
圧縮機が運転されると、駆動軸18の回転に伴い回転駆
動板20が駆動軸18と一体的に回転する。一方、揺動斜板
24は案内ロッド27との係合により回転が規制されるた
め、回転駆動板20の回転に伴い揺動斜板24が回転駆動板
20と共に揺動し、ピストンロッド26を介してピストン25
が往復動されて冷媒ガスの圧縮動作が行われる。又、ク
ランク室２内の圧力が制御弁により制御され、クランク
室圧力と吸入圧力との差圧に応じて揺動斜板24の傾斜角
が変化してピストン25のストロークすなわち圧縮容量が
変更される。When the compressor is operated, the rotary drive plate 20 rotates integrally with the drive shaft 18 as the drive shaft 18 rotates. On the other hand, the swing swash plate
Since the rotation of 24 is restricted by the engagement with the guide rod 27, the swing swash plate 24 is rotated by the rotation of the rotation drive plate 20.
Oscillates with the piston 20 through the piston rod 26
Are reciprocated to perform the compression operation of the refrigerant gas. Further, the pressure in the crank chamber 2 is controlled by the control valve, and the tilt angle of the swing swash plate 24 is changed according to the differential pressure between the crank chamber pressure and the suction pressure to change the stroke of the piston 25, that is, the compression capacity. It
圧縮機の運転中、ピストン25が上死点から下死点へ向
かって移動する吸入行程すなわち第１図の状態からピス
トン25が左方へ移動する行程において、圧縮室内の圧力
が吸入室４の圧力よりも低くなると、吸入室４内の冷媒
ガスが吸入弁10をその弾性に抗して圧縮機（シリンダボ
ア1a）側へ撓ませながら圧縮室内に吸入される。このと
き、吸入弁10はその先端が係止凹部13に係止される位置
に移動配置されるまでの間に自励振動を生じ、この自励
振動による特有の周波数を持った振動（吸入脈動９が収
入室４、吸入ポート16及び管路を経て蒸発器まで伝達さ
れる。During the operation of the compressor, in the suction stroke in which the piston 25 moves from the top dead center to the bottom dead center, that is, in the stroke in which the piston 25 moves leftward from the state shown in FIG. When the pressure becomes lower than the pressure, the refrigerant gas in the suction chamber 4 is sucked into the compression chamber while bending the suction valve 10 toward the compressor (cylinder bore 1a) side against its elasticity. At this time, the suction valve 10 generates self-excited vibration until its tip is moved to a position where it is locked in the locking recess 13, and vibration (suction pulsation) having a specific frequency due to this self-excited vibration is generated. 9 is transmitted to the evaporator through the income chamber 4, the suction port 16 and the pipe.
この実施例では第１及び第２の隔壁リブ29,29′で区
画された小室4aがマフラーの役割を果たす。吸入ポート
16から離れた位置の小室4aに対応して設けられた吸入弁
10の自励振動により生じた特有の周波数を持った振動
は、振動が吸入ポート16に到達する前にマフラーの役割
を果たす小室4aを通過するので、吸入ポート16に到達す
る前に減衰される。又、吸入ポート16の両側に位置する
小室4aに対応して設けられた吸入弁10の自励振動により
生じた特有の周波数を持った振動は、マフラーの役割を
果たす小室4aを通過することはないが、吸入ポート16と
対向する位置に設けられた第２絞り部30′の作用により
若干減衰される。従って、圧縮機全体としては吸入弁10
の自励振動により生じた特有の周波数を持った振動によ
り蒸発器が共振して異音を発生することが防止される。In this embodiment, the small chamber 4a defined by the first and second partition ribs 29, 29 'functions as a muffler. Inhalation port
Suction valve provided corresponding to small chamber 4a located away from 16
The vibration having a specific frequency generated by the self-excited vibration of 10 passes through the small chamber 4a that functions as a muffler before reaching the suction port 16, so is damped before reaching the suction port 16. . Further, the vibration having a specific frequency generated by the self-excited vibration of the suction valve 10 provided corresponding to the small chambers 4a located on both sides of the suction port 16 does not pass through the small chamber 4a which plays the role of the muffler. Although not provided, it is slightly damped by the action of the second throttle portion 30 'provided at the position facing the suction port 16. Therefore, the intake valve 10
It is possible to prevent the evaporator from resonating and generating abnormal noise due to the vibration having a specific frequency generated by the self-excited vibration of the.
又、この実施例では第１及び第２の隔壁リブ29,29′
が吸入弁10や吐出弁11を形成するための弁形成プレート
を押圧するので、シール性が良くなる。Also, in this embodiment, the first and second partition ribs 29, 29 'are
Presses the valve forming plate for forming the suction valve 10 and the discharge valve 11, so that the sealing property is improved.
なお、本考案は前記実施例に限定されるものではな
く、例えば、隔壁リブ29を非対称位置に設けてもよい。
又、揺動斜板式圧縮機以外に特開昭61−171886号公報に
開示された構成の可変容量圧縮機に適用してもよい。The present invention is not limited to the above embodiment, and the partition ribs 29 may be provided at asymmetrical positions, for example.
Further, in addition to the swing swash plate type compressor, it may be applied to a variable capacity compressor having a configuration disclosed in Japanese Patent Laid-Open No. 61-171886.
［考案の効果］ 以上詳述したように、この考案は吸入弁の自励振動に
起因する蒸発器の共振を防止して、騒音発生を低減する
ことができる。又、この考案はハウジング、環状隔壁及
び第1,第２の隔壁リブ等の一体成型が可能となり、この
ため部品点数を低減し、構造を簡素化して組付作業を容
易に行い、コストダウンを図ることができる。さらに、
圧縮機の軸線方向と直交する方向に隔壁を設ける構造と
比較して圧縮機の軸線方向への小型化を図ることもでき
る。[Advantages of the Invention] As described in detail above, the present invention can prevent the resonance of the evaporator due to the self-excited vibration of the intake valve and reduce the noise generation. In addition, the present invention enables the housing, the annular partition wall, and the first and second partition wall ribs to be integrally molded. Therefore, the number of parts is reduced, the structure is simplified, the assembly work is facilitated, and the cost is reduced. Can be planned. further,
It is also possible to reduce the size of the compressor in the axial direction as compared with the structure in which the partition wall is provided in the direction orthogonal to the axial direction of the compressor.
第１図は本考案を具体化した一実施例を示す中央部縦断
面図、第２図は第１図のＩ−Ｉ線断面図、第３図は従来
例を示す断面図である。 シリンダボア1a、クランク室２、吸入室４、小室4a、吐
出室５、リヤハウジング６、環状隔壁6a、吸入ポート1
6、駆動軸18、揺動斜板24、ピストン25、第１及び第２
の隔壁リブ29,29′、第１及び第２の絞り部30,30′。FIG. 1 is a longitudinal sectional view of a central portion showing an embodiment embodying the present invention, FIG. 2 is a sectional view taken along the line II of FIG. 1, and FIG. 3 is a sectional view showing a conventional example. Cylinder bore 1a, crank chamber 2, suction chamber 4, small chamber 4a, discharge chamber 5, rear housing 6, annular partition wall 6a, suction port 1
6, drive shaft 18, swing swash plate 24, piston 25, first and second
Partition ribs 29, 29 ', first and second throttle portions 30, 30'.
───────────────────────────────────────────────────── フロントページの続き (72)考案者 竹市 亨 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 (72)考案者 小林 久和 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 (56)参考文献 特開 昭54−31611（ＪＰ，Ａ) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takeichi Toru, Aichi Prefecture, Kariya City, 2-chome, 1-chome Toyota Industries Corporation (72) Inventor Hisawa Kobayashi, Aichi Prefecture, 2-chome, Toyota-cho Stock company Toyota Automatic Loom Works (56) References JP 54-31611 (JP, A)
Claims (1)
ランク室内に駆動軸の回転をシリンダボア内に収容され
たピストンの往復動に変換する作用をなす斜板を設け、
クランク室圧力と吸入圧力との差圧に応じて前記斜板の
傾斜角が変化することによりピストンのストロークが変
更されて圧縮容量を制御するようにした可変容量圧縮機
において、 外側に環状の吸入室を、内側に吐出室を区画形成する環
状隔壁を有するハウジングに前記収入室に連通する吸入
ポートを形成するとともに、該ハウジングの周壁内面に
第１隔壁リブを複数箇所に突設して、各第１隔壁リブと
前記環状隔壁の外周面との間に冷媒ガスの流路面積が一
時的に小さくなる第１絞り部をそれぞれ設け、前記環状
隔壁の外周面に第２隔壁リブを複数箇所に突設して、各
第２隔壁リブと前記ハウジングの周壁内面との間に冷媒
ガスの流路面積が一時的に小さくなる第２絞り部をそれ
ぞれ設け、さらに、前記第１及び第２の隔壁リブの間に
それぞれ形成された複数の吸入小室を各シリンダボアに
連通する吸入孔と対応した可変容量圧縮機。1. A swash plate provided with a suction chamber, a discharge chamber, and a crank chamber, the swash plate having a function of converting rotation of a drive shaft into reciprocating motion of a piston housed in a cylinder bore,
In the variable displacement compressor in which the stroke of the piston is changed by controlling the inclination angle of the swash plate according to the pressure difference between the crank chamber pressure and the suction pressure, the suction capacity is annular outside The chamber is provided with an inlet port communicating with the income chamber in a housing having an annular partition wall that defines a discharge chamber inside, and first partition ribs are provided at a plurality of locations on the inner surface of the peripheral wall of the housing so as to project. First narrowed portions are provided between the first partition ribs and the outer peripheral surface of the annular partition so as to temporarily reduce the flow passage area of the refrigerant gas, and second partition ribs are provided at a plurality of locations on the outer peripheral surface of the annular partition. Protrudingly provided second throttle portions between the respective second partition ribs and the inner surface of the peripheral wall of the housing to temporarily reduce the flow passage area of the refrigerant gas, and further, the first and second partition walls. Between the ribs A variable capacity compressor corresponding to the suction holes that connect the formed small suction chambers to the respective cylinder bores.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989118084U JPH089432Y2 (en) | 1989-10-06 | 1989-10-06 | Variable capacity compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989118084U JPH089432Y2 (en) | 1989-10-06 | 1989-10-06 | Variable capacity compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0356887U JPH0356887U (en) | 1991-05-31 |
| JPH089432Y2 true JPH089432Y2 (en) | 1996-03-21 |
Family
ID=31666269
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1989118084U Expired - Lifetime JPH089432Y2 (en) | 1989-10-06 | 1989-10-06 | Variable capacity compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH089432Y2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011081381A3 (en) * | 2009-12-28 | 2011-11-10 | 두원공과대학교 | Reciprocating compressor |
| WO2011081427A3 (en) * | 2009-12-30 | 2011-11-10 | 두원공과대학교 | Reciprocating compressor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002021725A (en) * | 2000-07-06 | 2002-01-23 | Zexel Valeo Climate Control Corp | Reciprocating compressor |
| JP2003065225A (en) * | 2001-08-28 | 2003-03-05 | Zexel Valeo Climate Control Corp | Reciprocating coolant compressor |
| JP2009257149A (en) * | 2008-04-15 | 2009-11-05 | Sanden Corp | Intake flow path changing adaptor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5431611A (en) * | 1977-08-12 | 1979-03-08 | Sentoraru Jidoushiya Kougiyou | Cooling medium compressor |
-
1989
- 1989-10-06 JP JP1989118084U patent/JPH089432Y2/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011081381A3 (en) * | 2009-12-28 | 2011-11-10 | 두원공과대학교 | Reciprocating compressor |
| WO2011081427A3 (en) * | 2009-12-30 | 2011-11-10 | 두원공과대학교 | Reciprocating compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0356887U (en) | 1991-05-31 |
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