JP2861478B2 - Piston displacement mechanism in oscillating swash plate compressor - Google Patents
Piston displacement mechanism in oscillating swash plate compressorInfo
- Publication number
- JP2861478B2 JP2861478B2 JP3133014A JP13301491A JP2861478B2 JP 2861478 B2 JP2861478 B2 JP 2861478B2 JP 3133014 A JP3133014 A JP 3133014A JP 13301491 A JP13301491 A JP 13301491A JP 2861478 B2 JP2861478 B2 JP 2861478B2
- Authority
- JP
- Japan
- Prior art keywords
- swash plate
- displacement
- piston
- mediating
- headed piston
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
- F04B27/0886—Piston shoes
Landscapes
- Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、回転軸に傾動可能に支
持された斜板の両面と片頭ピストンの首部との間に介在
された変位媒介部材を介して斜板の回転運動を片頭ピス
トンの往復直線運動に変換すると共に、クランク室内の
圧力と吸入圧との片頭ピストンを介した差により斜板の
傾角を制御する可変容量型の揺動斜板式圧縮機における
ピストン変位機構に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a single-headed piston which rotates the swash plate through a displacement mediating member interposed between both sides of a swash plate supported on a rotating shaft and a neck of a single-headed piston. The present invention relates to a piston displacement mechanism in a variable displacement type swash plate type compressor that controls the inclination angle of a swash plate by a difference between a pressure in a crank chamber and a suction pressure through a single-headed piston, while converting the pressure into a reciprocating linear motion. .
【０００２】[0002]
【従来の技術】特開昭６０ー１７５７８３号公報に開示
されるこの種の圧縮機では、半球状のシューの球面部が
片頭ピストンの首部の球面凹部に嵌まり込み支持されて
いると共に、その端面部が斜板面に接している。このよ
うなシュー支持構造によって斜板の回転に伴って片頭ピ
ストンが回転軸方向に往復動可能である。回転軸に傾動
可能かつ回転軸と一体的に回転可能に支持された回転板
上に斜板を相対回転可能に支持すると共に、斜板と片頭
ピストンとをピストンロッドで連結した揺動斜板式圧縮
機においては斜板回り止め機構が必要であるが、特開昭
６０ー１７５７８３号公報の揺動斜板式圧縮機では回転
板及び斜板回り止め機構が不要となり、機構の簡素化が
著しい。2. Description of the Related Art In a compressor of this type disclosed in Japanese Patent Application Laid-Open No. 60-175783, a spherical portion of a hemispherical shoe is fitted into and supported by a spherical concave portion of a neck of a single-headed piston. The end face is in contact with the swash plate surface. With such a shoe support structure, the single-headed piston can reciprocate in the rotation axis direction with the rotation of the swash plate. Oscillating swash plate compression system in which a swash plate is rotatably supported on a rotating plate that is tiltable to a rotating shaft and rotatably supported integrally with the rotating shaft, and a swash plate and a single-headed piston are connected by a piston rod. Although a swash plate anti-rotation mechanism is required in the compressor, the swinging swash plate type compressor disclosed in Japanese Patent Application Laid-Open No. Sho 60-177583 does not require a rotating plate and a swash plate anti-rotation mechanism, and the mechanism is significantly simplified.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、斜板の
回転によって片頭ピストンがシューを介して斜板から側
方への荷重を受け、シリンダボアと片頭ピストンとの間
で片当たりが生じる。そのため、片頭ピストンとシリン
ダボアとの片当たり部位で摩耗が生じたり、あるいは焼
付けを起こしたりするおそれがある。However, the rotation of the swash plate causes the single-headed piston to receive a load from the swash plate to the side via the shoe, thereby causing a one-sided contact between the cylinder bore and the single-headed piston. For this reason, there is a possibility that abrasion may occur at a contact portion between the single-headed piston and the cylinder bore, or seizure may occur.
【０００４】本発明は片頭ピストンが斜板から受ける側
方への荷重を低減し得るピストン変位機構を提供するこ
とを目的とする。[0004] It is an object of the present invention to provide a piston displacement mechanism which can reduce a lateral load received by a single-headed piston from a swash plate.
【０００５】[0005]
【課題を解決するための手段】そのために本発明では、
斜板の片面と片頭ピストンとの間に一対の変位媒介部材
を介在し、斜板の片面には第１の変位媒介部材を周方向
へのみ相対変位可能に支持する環状支持条を回転軸の周
りに設けると共に、片頭ピストンの首部には第２の変位
媒介部材を斜板の半径方向へのみ変位案内可能な変位ガ
イド条を設け、両変位媒介部材を斜板の半径方向へ摺動
可能に嵌合した。According to the present invention, there is provided:
A pair of displacement mediating members are interposed between one surface of the swash plate and the single-headed piston, and an annular support member that supports the first displacement mediating member so as to be relatively displaceable only in the circumferential direction is provided on one surface of the swash plate. Around the single-ended piston, a displacement guide member is provided at the neck of the single-headed piston to guide the second displacement mediating member only in the radial direction of the swash plate so that both displacement mediating members can slide in the radial direction of the swash plate. Mated.
【０００６】[0006]
【作用】斜板の回転に伴って第２の変位媒介部材が第１
の変位媒介部材を介して斜板から側方への荷重を受け
る。これにより第２の変位媒介部材が片頭ピストン側の
変位ガイド条に沿って斜板の半径方向へ変位し、片頭ピ
ストンが斜板から受ける側方への荷重が第２の変位媒介
部材の半径方向への変位によって吸収緩和される。With the rotation of the swash plate, the second displacement mediating member moves to the first position.
The load is applied laterally from the swash plate via the displacement mediating member. As a result, the second displacement mediating member is displaced in the radial direction of the swash plate along the displacement guide strip on the single-headed piston side, and the lateral load received by the single-headed piston from the swash plate is reduced in the radial direction of the second displacement mediating member. Is absorbed and relaxed by the displacement to
【０００７】[0007]
【実施例】以下、本発明を具体化した一実施例を第１〜
４図に基づいて説明する。圧縮機全体のハウジングの一
部となるシリンダブロック１の前後にはフロントハウジ
ング２及びリヤハウジング３が接合固定されており、シ
リンダブロック１及びフロントハウジング２には回転軸
４が回転可能に支持されている。フロントハウジング２
内にて回転軸４には回転支持体５が止着されており、そ
の先端側には長孔５ａが透設されている。DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, one embodiment of the present invention will be described with reference to the first to first embodiments.
This will be described with reference to FIG. A front housing 2 and a rear housing 3 are joined and fixed to the front and rear of a cylinder block 1 which is a part of a housing of the entire compressor. A rotary shaft 4 is rotatably supported on the cylinder block 1 and the front housing 2. I have. Front housing 2
A rotary support 5 is fixed to the rotary shaft 4 inside, and an elongate hole 5a is provided at the tip side thereof.
【０００８】回転軸４には球状のブッシュ６がスライド
可能に支持されており、ブッシュ６には斜板７が回転軸
４方向へ回動可能に支持されている。斜板７には連結片
７ａが取着されており、連結片７ａの先端部にはピン７
ｂが取付られている。ピン７ｂは長孔５ａに係合してお
り、長孔５ａは斜板７の傾動をピン７ｂを介して案内す
る。これにより斜板７がブッシュ６を中心に回転軸４方
向へ揺動可能かつ回転軸４と一体的に回転可能であり、
長孔５ａとピン７ｂとのスライドガイド作用、ブッシュ
６のスライド作用及びブッシュ６の支持作用により斜板
７の傾動が案内される。[0008] A spherical bush 6 is slidably supported on the rotating shaft 4, and a swash plate 7 is supported on the bush 6 so as to be rotatable in the direction of the rotating shaft 4. A connecting piece 7a is attached to the swash plate 7, and a pin 7 is attached to the tip of the connecting piece 7a.
b is attached. The pin 7b is engaged with the long hole 5a, and the long hole 5a guides the tilt of the swash plate 7 through the pin 7b. Thereby, the swash plate 7 can swing about the bush 6 in the direction of the rotation shaft 4 and can rotate integrally with the rotation shaft 4.
The tilting of the swash plate 7 is guided by the slide guide action of the elongated hole 5a and the pin 7b, the slide action of the bush 6, and the support action of the bush 6.
【０００９】クランク室２ａ、リヤハウジング３内の吸
入室３ａ及び吐出室３ｂを接続するようにシリンダブロ
ック１に貫設されたシリンダボア１ａ内には片頭ピスト
ン８が収容されている。片頭ピストン８の首部９には斜
板通過溝９ａが設けられており、斜板通過溝９ａの両側
端面上には変位ガイド溝９ｂが斜板７の半径方向に沿っ
て設けられている。斜板通過溝９ａ内を通過する斜板７
の外周部両面には環状の支持レール７ｃが形成されてお
り、その半径中心が回転軸４の軸線Ｌ1 上に設定されて
いる。A single-headed piston 8 is accommodated in a cylinder bore 1a provided through the cylinder block 1 so as to connect the crank chamber 2a, the suction chamber 3a and the discharge chamber 3b in the rear housing 3. A swash plate passage groove 9a is provided in the neck portion 9 of the single-headed piston 8, and displacement guide grooves 9b are provided along the radial direction of the swash plate 7 on both end surfaces of the swash plate passage groove 9a. Swash plate 7 passing through swash plate passage groove 9a
The outer periphery side of an annular support rail 7c is formed, the center of radius is set on the axis L 1 of the rotating shaft 4.
【００１０】第２図に示すように複数の片頭ピストン８
が回転軸４の周りに等間隔角度一に配列されており、各
片頭ピストン８の首部９と環状支持レール７ｃとの間に
は一対の変位媒介部材１０，１１が介在されている。第
１の変位媒介部材１０は第３図に示すように半円柱形状
であり、その矩形端面側が環状支持レール７ｃに摺接可
能に嵌合支持されている。第２の変位媒介部材１１は断
面円弧形状の変位ガイド溝９ｂに嵌まり込み、かつ第１
の変位媒介部材１０の周面部を嵌合支持している。[0010] As shown in FIG.
Are arranged at equal intervals around the rotation shaft 4, and a pair of displacement mediating members 10, 11 are interposed between the neck 9 of each single-headed piston 8 and the annular support rail 7c. As shown in FIG. 3, the first displacement mediating member 10 has a semi-cylindrical shape, and its rectangular end face is slidably fitted and supported on the annular support rail 7c. The second displacement mediating member 11 fits into the displacement guide groove 9b having an arc-shaped cross section, and
Of the displacement mediating member 10 is fitted and supported.
【００１１】半円柱形状の第１の変位媒介部材１０の周
面軸線Ｌ2 は前後一対の環状支持レール７ｃ間の中心上
に設定されており、断面円弧形状の変位ガイド溝９ｂの
円弧中心軸線Ｌ3 は軸線Ｌ2 上に設定されている。従っ
て、両変位媒介部材１０，１１は斜板回転角度に関係な
く斜板通過溝９ａ内に常に隙間無く嵌まり込み支持さ
れ、斜板７の回転に伴う第１の変位媒介部材１０の回転
軸線Ｌ1 からの距離変動が変位ガイド溝９ｂに沿った第
２の変位媒介部材１１のスライド変位によって許容され
る。従って、斜板７の回転運動が両変位媒介部材１０，
１１を介して片頭ピストン８の前後往復動に変換され、
片頭ピストン８がシリンダボア１ａ内を前後動する。こ
れにより吸入室３ａからシリンダボア１ａ内へ吸入され
た冷媒ガスが圧縮されつつ吐出室３ｂへ吐出されるが、
クランク室２ａ内の圧力とシリンダボア１ａ内の吸入圧
との片頭ピストン８を介した差圧に応じて片頭ピストン
８のストロークが変わり、圧縮容量を左右する斜板７の
傾角が変化する。クランク室２ａ内の圧力はシリンダブ
ロック１内の電磁制御弁機構１９により制御される。[0011] peripheral surface axis L 2 of the first displacement-mediated member 10 of the semi-cylindrical shape is set on the center between the front and rear pair of annular support rails 7c, arc center axis of the displacement guide groove 9b of the circular arc cross sectional shape L 3 is set on the axis L 2. Therefore, the two displacement mediating members 10 and 11 are always fitted and supported without any gap in the swash plate passage groove 9a regardless of the swash plate rotation angle, and the rotation axis of the first displacement mediating member 10 accompanying the rotation of the swash plate 7 is supported. distance variation from L 1 is allowed by the sliding displacement of the second displacement-mediated member 11 along the displacement guide groove 9b. Therefore, the rotational movement of the swash plate 7 is caused by the two displacement mediating members 10,
11 is converted into a back and forth reciprocation of the single-headed piston 8,
The single-headed piston 8 moves back and forth in the cylinder bore 1a. Thereby, the refrigerant gas sucked into the cylinder bore 1a from the suction chamber 3a is discharged to the discharge chamber 3b while being compressed.
The stroke of the single-headed piston 8 changes according to the pressure difference between the pressure in the crank chamber 2a and the suction pressure in the cylinder bore 1a through the single-headed piston 8, and the inclination angle of the swash plate 7, which affects the compression capacity, changes. The pressure in the crank chamber 2a is controlled by an electromagnetic control valve mechanism 19 in the cylinder block 1.
【００１２】第１の変位媒介部材１０の回転軸線Ｌ1 か
らの距離変動の許容は斜板７の回転に伴う片頭ピストン
８の首部９に対する側方への荷重の低減作用をもたら
す。第４図のグラフは片頭ピストン８が斜板７から受け
る側方への荷重を表す、鎖線曲線Ｃ1 は従来の揺動斜板
式圧縮機における側方への荷重曲線を表し、実線曲線Ｃ
2 は本実施例の側方への荷重曲線を表す。両曲線Ｃ1,Ｃ
2 から明らかなように本実施例の側方への荷重低減作用
は顕著であり、このような大きな抑制効果は第２の変位
媒介部材１１の斜板半径方向のスライドによって得られ
る。The rotation axis L of the first displacement mediating member 101Or
The one-head piston accompanying the rotation of the swash plate 7
8 has the effect of reducing the lateral load on the neck 9
You. In the graph of FIG. 4, the single-headed piston 8 is received from the swash plate 7.
Chain line C representing the lateral load1Is a conventional rocking swash plate
Represents the load curve to the side in the compressor of the type shown in FIG.
TwoRepresents a lateral load curve of the present embodiment. Both curves C1,C
TwoAs is clear from FIG.
Is remarkable, and such a large suppression effect is caused by the second displacement.
Obtained by sliding the intermediate member 11 in the swash plate radial direction.
You.
【００１３】又、片頭ピストン８に対する第２の変位媒
介部材１１のスライド方向が斜板７の半径方向に限られ
ると共に、第１の変位媒介部材１０のスライド方向が斜
板７の周方向に限られるため、片頭ピストン８が斜板７
の回転に伴ってローリングを起こすことはない。従っ
て、片頭ピストン８の首部９と斜板７の周縁とが干渉す
ることはなく、片頭ピストン８に対するローリング阻止
機構を別に設ける必要はない。Further, the sliding direction of the second displacement mediating member 11 with respect to the single-headed piston 8 is limited to the radial direction of the swash plate 7, and the sliding direction of the first displacement mediating member 10 is limited to the circumferential direction of the swash plate 7. Swash plate 7
Rolling does not occur with the rotation of. Therefore, there is no interference between the neck 9 of the single-headed piston 8 and the peripheral edge of the swash plate 7, and there is no need to separately provide a rolling prevention mechanism for the single-headed piston 8.
【００１４】本発明は勿論前期実施例にのみ限定される
ものではなく、例えば第５〜１１図に示す実施例も可能
である。第５図の実施例では環状支持レール１２を断面
半円形状にし、第６図の実施例では環状支持レールに代
えて環状支持溝１３としたものである。第７図の実施例
でば前記各実施例における斜板７の前後の一対の変位媒
介部材を一体化した変位媒介部材１４を用いている。The present invention is, of course, not limited to the first embodiment, but may be, for example, the embodiments shown in FIGS. In the embodiment of FIG. 5, the annular support rail 12 has a semicircular cross section, and in the embodiment of FIG. 6, the annular support rail is replaced by an annular support groove 13. In the embodiment shown in FIG. 7, a displacement mediating member 14 in which a pair of displacement mediating members before and after the swash plate 7 in each of the above embodiments is integrated is used.
【００１５】第８図の実施例では片頭ピストン８の斜板
通過溝９ａの領域外に環状支持レール７ｃを設けてお
り、変位媒介部材１１と同タイプの変位媒介部材１７の
足１７ａが環状支持レール７ｃに嵌合支持される。これ
により環状支持レール７ｃの断面積拡大が可能となり、
耐荷重性能が向上する。第９図の実施例では第１の変位
媒介部材１５が半球形状であり、第２の変位媒介部材１
６と第１の変位媒介部材１５とは球面嵌合する。従っ
て、片頭ピストン８の首部９における変位ガイド溝９ｃ
は第２の変位媒介部材１６を斜板７の半径方向へのみ摺
動案内可能な形状であれば良く、変位ガイド溝９ｃと第
２の変位媒介部材１６との間には摺接回動のためのガイ
ド関係は不要となる。In the embodiment shown in FIG. 8, an annular support rail 7c is provided outside the area of the swash plate passage groove 9a of the single-headed piston 8, so that the foot 17a of the displacement mediating member 17 of the same type as the displacement mediating member 11 has an annular support rail. The fitting is supported by the rail 7c. This makes it possible to increase the sectional area of the annular support rail 7c,
The load bearing performance is improved. In the embodiment of FIG. 9, the first displacement mediating member 15 has a hemispherical shape, and the second displacement mediating member 1
6 and the first displacement mediating member 15 are spherically fitted. Therefore, the displacement guide groove 9c in the neck 9 of the single-headed piston 8
Any shape may be used as long as the second displacement mediating member 16 can be slid and guided only in the radial direction of the swash plate 7. A guide relationship is unnecessary.
【００１６】なお、第２の変位媒介部材１６の形状とし
ては第１０図に示すものも可能である。第１１図の実施
例では第９，１０図の第１の変位媒介部材１５と第３図
の第２の変位媒介部材１１のタイプとを組み合わせてい
る。The shape of the second displacement mediating member 16 may be as shown in FIG. In the embodiment shown in FIG. 11, the first displacement mediating member 15 shown in FIGS. 9 and 10 is combined with the type of the second displacement mediating member 11 shown in FIG.
【００１７】[0017]
【発明の効果】以上詳述したように本発明は、一対の変
位媒介部材を組み合わせると共に、片頭ピストンに対し
て接合関係にある一方の変位媒介部材を斜板半径方向へ
スライドできるようにしたので、片頭ピストンが斜板か
ら受ける側方への荷重を一方の変位媒介部材の斜板半径
方向へのスライド変位によってかなりの部分吸収でき、
側方への荷重に起因する片頭ピストンとシリンダボアと
の間の摩耗あるいは焼きつきを防止し得るという優れた
効果を奏する。As described above in detail, according to the present invention, a pair of displacement mediating members are combined, and one of the displacement mediating members which is connected to the single-headed piston can be slid in the radial direction of the swash plate. The side load that the single-headed piston receives from the swash plate can be considerably partially absorbed by the sliding displacement of one displacement mediating member in the swash plate radial direction,
An excellent effect of preventing wear or seizure between the single-headed piston and the cylinder bore due to a lateral load can be achieved.
【図１】圧縮機全体の側断面図である。FIG. 1 is a side sectional view of the entire compressor.
【図２】第１図のＡーＡ線断面図である。FIG. 2 is a sectional view taken along line AA of FIG. 1;
【図３】第３図は要部分解斜視図である。FIG. 3 is an exploded perspective view of a main part.
【図４】第４図は側方への荷重のグラフである。FIG. 4 is a graph of a lateral load.
【図５】別例を示す要部側断面図である。FIG. 5 is a sectional side view of a main part showing another example.
【図６】別例を示す要部側断面図である。FIG. 6 is a sectional side view of a main part showing another example.
【図７】別例を示す要部側断面図である。FIG. 7 is a sectional side view of a main part showing another example.
【図８】別例を示す要部側断面図である。FIG. 8 is a sectional side view of a main part showing another example.
【図９】別例を示す要部分解斜視図である。FIG. 9 is an exploded perspective view of a main part showing another example.
【図１０】別例を示す要部分解斜視図である。FIG. 10 is an exploded perspective view of a main part showing another example.
【図１１】別例を示す要部分解斜視図である。FIG. 11 is an exploded perspective view of a main part showing another example.
７ 斜板、７ｃ 環状支持条としての支持レール、１
２，１３ 環状支持溝、８片頭ピストン、９ｂ，９ｃ
変位ガイド条としての変位ガイド溝、１０，１４，１５
第１の変位媒介部材、１１，１６ 第２の変位媒介部
材である。7 swash plate, 7c support rail as annular support strip, 1
2,13 annular support groove, 8 single-ended pistons, 9b, 9c
Displacement guide grooves as displacement guide strips, 10, 14, 15
First displacement mediating member, 11, 16 A second displacement mediating member.
Claims (1)
各室を接続するシリンダボアを区画形成し、シリンダボ
ア内に片頭ピストンを往復直線運動可能に収容するハウ
ジング内の回転軸上に斜板を傾動可能に支持すると共
に、回転軸上の回転支持体に斜板を傾動可能に連係し、
斜板の両面と片頭ピストンの首部との間に介在された変
位媒介部材を介して斜板の回転運動を片頭ピストンの往
復直線運動に変換すると共に、クランク室内の圧力と吸
入圧との片頭ピストンを介した差により斜板の傾角を制
御する揺動斜板式圧縮機において、斜板の片面と片頭ピ
ストンとの間には一対の変位媒介部材を介在し、斜板の
片面には第１の変位媒介部材を周方向へのみ相対変位可
能に支持する環状支持条を回転軸の周りに設けると共
に、片頭ピストンの首部には第２の変位媒介部材を斜板
の半径方向へのみ変位案内可能な変位ガイド条を設け、
両変位媒介部材を斜板の半径方向へ摺動可能に嵌合した
揺動斜板式圧縮機におけるピストン変位機構。A swash plate is tilted on a rotary shaft in a housing which defines a crank chamber, a suction chamber, a discharge chamber, and a cylinder bore connecting these chambers, and accommodates a single-headed piston in the cylinder bore so as to reciprocate linearly. Swash plate is tiltably linked to the rotating support on the rotating shaft,
The rotary motion of the swash plate is converted into a reciprocating linear motion of the single-head piston via a displacement mediating member interposed between both surfaces of the swash plate and the neck of the single-head piston, and the single-head piston of the pressure in the crank chamber and the suction pressure is converted. In a swinging swash plate type compressor in which the inclination angle of the swash plate is controlled by a difference through the swash plate, a pair of displacement mediating members are interposed between one side of the swash plate and the single-headed piston, and the first surface of the swash plate is An annular support member for supporting the displacement mediating member so as to be relatively displaceable only in the circumferential direction is provided around the rotation axis, and the second displacement mediating member can be displaced and guided only in the radial direction of the swash plate at the neck of the single-ended piston. A displacement guide strip is provided,
A piston displacement mechanism in an oscillating swash plate type compressor in which both displacement mediating members are slidably fitted in a radial direction of a swash plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3133014A JP2861478B2 (en) | 1991-06-04 | 1991-06-04 | Piston displacement mechanism in oscillating swash plate compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3133014A JP2861478B2 (en) | 1991-06-04 | 1991-06-04 | Piston displacement mechanism in oscillating swash plate compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04228882A JPH04228882A (en) | 1992-08-18 |
| JP2861478B2 true JP2861478B2 (en) | 1999-02-24 |
Family
ID=15094782
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3133014A Expired - Lifetime JP2861478B2 (en) | 1991-06-04 | 1991-06-04 | Piston displacement mechanism in oscillating swash plate compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2861478B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112012007009T5 (en) | 2012-10-12 | 2015-07-02 | Mitsubishi Electric Corporation | Automatic engine stop / restart device and automatic engine stop / restart procedure |
-
1991
- 1991-06-04 JP JP3133014A patent/JP2861478B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04228882A (en) | 1992-08-18 |
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