JP2019173614A - Compressor and equipment including the same - Google Patents

Compressor and equipment including the same Download PDF

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JP2019173614A
JP2019173614A JP2018061093A JP2018061093A JP2019173614A JP 2019173614 A JP2019173614 A JP 2019173614A JP 2018061093 A JP2018061093 A JP 2018061093A JP 2018061093 A JP2018061093 A JP 2018061093A JP 2019173614 A JP2019173614 A JP 2019173614A
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piston
piston pin
recess
compressor
small end
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JP6893487B2 (en
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賢一 押久保
Kenichi Oshikubo
賢一 押久保
修平 永田
Shuhei Nagata
修平 永田
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Hitachi Global Life Solutions Inc
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Hitachi Global Life Solutions Inc
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Priority to CN201811029438.7A priority patent/CN110318980B/en
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    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods

Abstract

To reduce sound occurring due to piston reciprocating motion.SOLUTION: A compressor has a piston, a connecting rod whose small end part is positioned in the piston, and a piston pin inserted into the piston and the small end part and attaching the connecting rod to the piston, where the small end part and the piston pin are relatively rotatable with a gap interposed therebetween, and the piston pin has a recess extending in an axial direction of the piston pin. In the compressor, one or more recesses are provided, and when the piston pin is viewed in the axial direction, another recess is positioned within a range excluding a recess prohibition region obtained by rotating the recess by 180° around the center of the piston pin.SELECTED DRAWING: Figure 3

Description

本発明は、圧縮機及びこれを有する機器に関する。     The present invention relates to a compressor and a device having the compressor.

特許文献１は、ピストンピン５９に油溝３を設けた構成を開示している（図４）。   Patent Document 1 discloses a configuration in which an oil groove 3 is provided in a piston pin 59 (FIG. 4).

特開平７−２２４７６１号公報JP-A-7-224761

ピストンピン式のピストンがシリンダ内を往復動するとき、往復動に伴って音が発生することがある。特に、ピストンピンに油溝のような凹部を設けた場合、その凹部の配置次第で音が大きくなるところ、特許文献１はこの点について何ら検討していない。   When a piston pin type piston reciprocates in a cylinder, a sound may be generated along with the reciprocation. In particular, when a concave portion such as an oil groove is provided in the piston pin, the sound becomes loud depending on the arrangement of the concave portion, but Patent Document 1 does not consider this point at all.

上記事情に鑑みてなされた本発明は、
ピストンと、
小端部が該ピストン内に位置するコンロッドと、
該ピストン及び前記小端部内に挿通されて、前記ピストンに前記コンロッドを取付けるピストンピンと、を有し、
前記小端部と前記ピストンピンとは、隙間を挟んで相対的に回転自在であり、
前記ピストンピンは、該ピストンピンの軸方向に延在する凹部を有する圧縮機であって、
前記凹部が１つである、又は、
前記凹部が２つ以上であり、かつ、前記ピストンピンの軸方向視において、前記ピストンピンの中心を中心にして前記凹部を１８０°回転させた凹部禁止領域を除いた範囲に、別の凹部が位置することを特徴とする。 The present invention made in view of the above circumstances,
A piston,
A connecting rod whose small end is located in the piston;
A piston pin that is inserted into the piston and the small end and attaches the connecting rod to the piston;
The small end portion and the piston pin are relatively rotatable with a gap therebetween,
The piston pin is a compressor having a recess extending in the axial direction of the piston pin,
The number of the recesses is one, or
There are two or more recesses, and in the axial view of the piston pin, there is another recess in a range excluding a recess prohibition region obtained by rotating the recess by 180 ° around the center of the piston pin. It is characterized by being located.

実施例１の圧縮機のピストン、ピストンピン、コンロッド、及び固定ピンのＹ方向断面図Y direction sectional drawing of the piston of the compressor of Example 1, a piston pin, a connecting rod, and a fixed pin 実施例１のピストンピンの側面図Side view of the piston pin of Example 1 上側は実施例１のシリンダ内を往復動するピストンのＺ方向視図、下側はピストンピンの拡大図The upper side is a Z direction view of the piston that reciprocates in the cylinder of Example 1, and the lower side is an enlarged view of the piston pin. 実施例１の圧縮工程時のコンロッドを含むＺ方向断面図Z direction sectional view including a connecting rod during the compression process of Example 1 実施例１の吸入工程時のコンロッド１３を含むＺ方向断面図Z direction sectional view including the connecting rod 13 during the inhalation process of the first embodiment

以下、本発明の実施例について添付の図面を参照しつつ説明する。同様の構成要素には同様の符号を付し、同様の説明は繰り返さない。     Embodiments of the present invention will be described below with reference to the accompanying drawings. Similar components are denoted by the same reference numerals, and the same description will not be repeated.

本発明の各種の構成要素は必ずしも個々に独立した存在である必要はなく、一の構成要素が複数の部材から成ること、複数の構成要素が一の部材から成ること、或る構成要素が別の構成要素の一部であること、或る構成要素の一部と他の構成要素の一部とが重複すること、などを許容する。   The various components of the present invention do not necessarily have to be independent of each other. One component is composed of a plurality of members, a plurality of components are composed of one member, and one component is separated from another. And a part of a certain component and a part of another component are allowed to overlap.

（ピストン１１まわりの構成の概要）
本実施例では、ピストン１１の往復動方向をＸ方向（圧縮時におけるピストン１１の移動方向（圧縮方向、上死点方向）が−Ｘ方向、吸入時におけるピストン１１の移動方向（吸入方向、下死点方向）が＋Ｘ方向）、ピストンピンの軸方向をＺ方向、Ｘ及びＺ方向に直交する方向をＹ方向とする。
図１は本実施例の圧縮機のピストン１１、ピストンピン１２、コンロッド１３、及び固定ピン１４のＹ方向断面図である。図２はピストンピン１２の側面図である。図３のうち上側は本実施例のシリンダ１９内を往復動するピストン１１のＺ方向視図である。図３のうち下側はピストンピン１２の拡大図である。 (Outline of the configuration around the piston 11)
In this embodiment, the reciprocating direction of the piston 11 is the X direction (the moving direction of the piston 11 at the time of compression (compression direction, top dead center direction) is the −X direction, and the moving direction of the piston 11 at the time of suction (inhalation direction, downward) The dead center direction) is + X direction), the axial direction of the piston pin is the Z direction, and the direction orthogonal to the X and Z directions is the Y direction.
FIG. 1 is a sectional view in the Y direction of a piston 11, a piston pin 12, a connecting rod 13, and a fixing pin 14 of the compressor of this embodiment. FIG. 2 is a side view of the piston pin 12. The upper side of FIG. 3 is a Z direction view of the piston 11 that reciprocates in the cylinder 19 of this embodiment. The lower side of FIG. 3 is an enlarged view of the piston pin 12.

圧縮機は、ピストン１１、ピストンピン１２、コンロッド１３、固定ピン１４、シリンダ１９を有する。ピストン１１は、シリンダ１９内を往復動するよう構成されている。   The compressor has a piston 11, a piston pin 12, a connecting rod 13, a fixed pin 14, and a cylinder 19. The piston 11 is configured to reciprocate within the cylinder 19.

ピストンピン１２は、ピストン１１のＺ方向に貫通して設けられた孔内に配されており、軸方向中央側がコンロッド１３の小端部１３１の円環内に位置し、軸方向両端側がピストン１１の孔の内面に接している。これにより、ピストンピン１２は、ピストン１１と小端部１３１とを回転自在に固定している。
ピストンピン１２は、Ｘ方向に延在する固定横孔１２１と、側面Ｚ方向に延在する軸方向凹部１２２と、側面周方向に延在する周方向凹部１２３を有している。 The piston pin 12 is disposed in a hole that penetrates in the Z direction of the piston 11, the axial center side is located in the ring of the small end portion 131 of the connecting rod 13, and both axial ends are on the piston 11. It is in contact with the inner surface of the hole. Thereby, the piston pin 12 is fixing the piston 11 and the small end part 131 rotatably.
The piston pin 12 has a fixed lateral hole 121 extending in the X direction, an axial recess 122 extending in the side Z direction, and a circumferential recess 123 extending in the side circumferential direction.

コンロッド１３は、両端それぞれを形成する中空円環の小端部１３１と大端部１３２と、これらを結ぶ棒状の部分を有する。大端部１３２には、例えば冷蔵庫向けの圧縮機構造として公知の、偏心回転（公転）運動するシャフト（不図示）が配されている。シャフトの公転中心にはスパイラル溝が配されたクランクシャフトが配されている。圧縮機底部に貯留された潤滑油は、クランクシャフトの回転に伴い汲み上げられ、公知の構成によってピストン１１やピストンピン１２に供給される。   The connecting rod 13 has a small end portion 131 and a large end portion 132 of a hollow ring forming both ends, and a rod-like portion connecting these. The large end portion 132 is provided with a shaft (not shown) that performs an eccentric rotation (revolution) motion, which is known as a compressor structure for a refrigerator, for example. A crankshaft with a spiral groove is arranged at the center of revolution of the shaft. The lubricating oil stored at the bottom of the compressor is pumped up along with the rotation of the crankshaft, and is supplied to the piston 11 and the piston pin 12 by a known configuration.

固定ピン１４は、固定横孔１２１及びピストン１１のうち固定横孔１２１の延長線上部分に設けられている孔に差し込まれている。固定ピン１４はＸ方向に略平行である。   The fixed pin 14 is inserted into a hole provided in a portion of the fixed horizontal hole 121 and the piston 11 on the extension line of the fixed horizontal hole 121. The fixing pin 14 is substantially parallel to the X direction.

（凹部１２２の配置）
本実施例のピストンピン１２は、軸方向凹部１２２として、第１軸方向凹部１２２１と第２軸方向凹部１２２２とを有している。第２軸方向凹部１２２２は，図３に示すようなピストンピン１２の軸方向視において、第１軸方向凹部１２２１をピストンピン中心Ｃを中心として１８０°回転させた位置を除く領域に形成されている。すなわち，第１軸方向凹部１２２１の吸入側端部１２２１ｓとピストンピン中心Ｃとを通る直線Ｌ１および，第１軸方向凹部１２２１の圧縮側端部１２２１ｄとピストンピン中心Ｃとを通る直線Ｌ２とで挟まれ，ピストンピン中心Ｃに対して第１軸方向凹部１２２１と反対側のピストンピン１２表面上の凹部禁止領域に，第２軸方向凹部１２２２はかからないものとする。 (Arrangement of recess 122)
The piston pin 12 of the present embodiment has a first axial recess 1221 and a second axial recess 1222 as the axial recess 122. The second axial recess 1222 is formed in a region excluding the position obtained by rotating the first axial recess 1221 about the piston pin center C by 180 ° in the axial direction view of the piston pin 12 as shown in FIG. Yes. That is, a straight line L1 passing through the suction side end 1221s of the first axial recess 1221 and the piston pin center C, and a straight line L2 passing through the compression side end 1221d of the first axial recess 1221 and the piston pin center C. It is assumed that the second axial recess 1222 is not applied to the recess forbidden area on the surface of the piston pin 12 opposite to the first axial recess 1221 with respect to the piston pin center C.

（コンロッド１３の揺動）
ピストン１１が往復動するに際しては、コンロッド１３は、大端部１３２内に配されてシャフトの回転運動と、ピストンピン１２により回転自在に固定された小端部１３１とに起因して、ピストンピン１２を中心とした揺動運動が行われる。 (Oscillation of connecting rod 13)
When the piston 11 reciprocates, the connecting rod 13 is disposed in the large end portion 132 and is caused by the rotational movement of the shaft and the small end portion 131 fixed rotatably by the piston pin 12. Oscillating motion about 12 is performed.

図４は本実施例の圧縮工程時のコンロッド１３を含むＺ方向断面図である。コンロッド１３は、本実施例では圧縮工程時、ピストンピン１２を中心にして反時計回りＤ１に揺動する。これにより、第１軸方向凹部１２２１内に存在する潤滑油は小端部１３１とピストンピン１２との相対運動に引きずられて，吸入側端部１２２１ｓ側に流れようとする。ピストンピン１２と小端部１３１内径面との間には，回転自在に双方を繋ぎとめる理由から，軸受隙間（ピストンピン１２外径と小端部１３１内径の径方向隙間）が設けられているが，この軸受隙間は、第１軸方向凹部１２２１底面と小端部１３１内径面との隙間よりも狭いために，第１軸方向凹部１２２１内で発生した潤滑油の周方向Ｄ１への流れは、吸入側端部１２２１ｓにおいてせき止められる。潤滑油流れがせき止められた際には，潤滑油流れの運動量の一部が圧力となる（動圧）。そのため，コンロッド１３の揺動運動に伴って，第１軸方向凹部１２２１内には潤滑油の動圧に基づく油膜反力が発生する。その反力方向はピストンピン中心Ｃに対して第１軸方向凹部１２２１とは反対方向である。本実施例のように、第１軸方向凹部１２２１が中心Ｃから−Ｙ方向に位置する場合、反力方向は、＋Ｙ方向である。   FIG. 4 is a cross-sectional view in the Z direction including the connecting rod 13 during the compression process of the present embodiment. In this embodiment, the connecting rod 13 swings counterclockwise D1 around the piston pin 12 during the compression process. As a result, the lubricating oil present in the first axial recess 1221 is pulled by the relative movement between the small end portion 131 and the piston pin 12 and tends to flow toward the suction side end portion 1221s. A bearing gap (a radial gap between the outer diameter of the piston pin 12 and the inner diameter of the small end portion 131) is provided between the piston pin 12 and the inner diameter surface of the small end portion 131 for the purpose of rotatably connecting them. However, since this bearing gap is narrower than the gap between the bottom surface of the first axial recess 1221 and the inner diameter surface of the small end 131, the flow of the lubricating oil generated in the first axial recess 1221 in the circumferential direction D1 is The suction side end portion 1221s is blocked. When the lubricating oil flow is stopped, a part of the momentum of the lubricating oil flow becomes pressure (dynamic pressure). Therefore, an oil film reaction force based on the dynamic pressure of the lubricating oil is generated in the first axial recess 1221 as the connecting rod 13 swings. The reaction force direction is opposite to the first axial recess 1221 with respect to the piston pin center C. When the first axial recess 1221 is located in the −Y direction from the center C as in the present embodiment, the reaction force direction is the + Y direction.

ここでピストンピン１２に加わる外力の力学的バランスを考える。図１に示したように，ピストンピン１２の軸方向両端部はピストン１１と接続しており，ピストン１１に加わる圧縮荷重はピストンピン１２の軸方向両端部に伝達される。また，ピストンピン１２の軸方向中央付近はコンロッド１３の小端部１３１が接続しており，ピストン１１から伝達された圧縮荷重は小端部１３１にて受けることとなる。すなわち圧縮工程時でピストンピン１２に加わる力は，ピストンピン１２の軸方向両端部に対する略＋Ｘ方向への圧縮荷重と，ピストンピン１２の軸方向中央付近に対する略−Ｘ方向への圧縮反力となる。なお、小端部１３１にて受ける圧縮反力は，大端部１３２に接続されて大端部１３２を公転させる（大端部１３２の外側に位置する点を軸として回転させる）クランクシャフト（図示せず）の回転トルクに起因する力である。この圧縮反力を受ける周方向範囲は、上述のようにピストンピン１２から略−Ｘ方向であるから、図４に例示するような領域Ｒ１の角度領域として表現できる。こうしたシリンダ１９内のガス圧縮に伴う外力（圧縮荷重）の他に，ピストンピン１２には前述したような軸方向凹部１２２での潤滑油の流れに起因する動圧効果による油膜反力を受ける。   Here, the mechanical balance of the external force applied to the piston pin 12 is considered. As shown in FIG. 1, both end portions in the axial direction of the piston pin 12 are connected to the piston 11, and the compressive load applied to the piston 11 is transmitted to both end portions in the axial direction of the piston pin 12. Further, the small end portion 131 of the connecting rod 13 is connected near the center in the axial direction of the piston pin 12, and the compressive load transmitted from the piston 11 is received by the small end portion 131. That is, the force applied to the piston pin 12 during the compression process includes a compressive load in the approximately + X direction on both axial ends of the piston pin 12 and a compressive reaction force in the approximately −X direction on the vicinity of the axial center of the piston pin 12. Become. Note that the compression reaction force received at the small end portion 131 is connected to the large end portion 132 and revolves the large end portion 132 (rotates about a point located outside the large end portion 132) (see FIG. (Not shown) due to rotational torque. Since the circumferential direction range that receives this compression reaction force is substantially −X direction from the piston pin 12 as described above, it can be expressed as an angle region of the region R1 as illustrated in FIG. In addition to the external force (compression load) associated with gas compression in the cylinder 19, the piston pin 12 receives an oil film reaction force due to the dynamic pressure effect caused by the flow of the lubricating oil in the axial recess 122 as described above.

なお，軸方向凹部１２２内では、潤滑油の運動に起因する動圧効果による油膜反力が発生するが，ピストンピン１２と小端部１３１との間に隙間があるため，固体接触による軸支ができない。そのため，例えば図４に例示する領域Ｒ１内に軸方向凹部１２１，１２２を設けた場合，軸方向凹部１２１，１２２では圧縮荷重を支えられないから、領域Ｒ１のうち、軸方向凹部１２１，１２２を除く領域に力が集中する（もし、領域Ｒ１の全部に軸方向凹部１２１，１２２が設けられると、例えば軸方向凹部の端部近傍に力が集中する）。このため、ピストンピン１２のごく一部の領域の面圧が高くなり，ピストンピン１２と小端部１３１との間の摺動状況が過酷となり信頼性上好ましくない。   In the axial recess 122, an oil film reaction force is generated due to the dynamic pressure effect caused by the movement of the lubricating oil. However, since there is a gap between the piston pin 12 and the small end 131, the shaft support due to solid contact is generated. I can't. Therefore, for example, when the axial recesses 121 and 122 are provided in the region R1 illustrated in FIG. 4, the axial recesses 121 and 122 cannot support the compressive load. The force concentrates on the excluded region (if the axial recesses 121 and 122 are provided in the entire region R1, for example, the force concentrates near the end of the axial recess). For this reason, the surface pressure in a very small area of the piston pin 12 becomes high, and the sliding state between the piston pin 12 and the small end portion 131 becomes severe, which is not preferable in terms of reliability.

また、ピストンピン１２の小端部１３１内における運動を考える。すでに説明したとおり，ピストンピン１２と小端部１３１の間には軸受隙間が設けられているため，ピストンピン１２が外力を受けると，ピストンピン１２は軸受隙間を挟んで小端部１３１に対して相対的に運動することとなる。ここでピストンピン１２に軸方向凹部１２２を設けた場合，軸方向凹部１２２と小端部１３１内径面との半径方向隙間が拡大する（半径方向で軸受隙間が拡大する）。ピストンピン１２と小端部１３１の半径隙間を過剰に拡大すると，ピストンピン１２の半径方向の運動を大きく許容することとなり，ピストンピン１２と小端部１３１の衝突に基づく騒音増大や，小端部１３１の半径隙間内におけるピストンピン１２の運動が，ピストン１１がシリンダ１９内周面に衝突振動を繰り返すピストンスラップ現象を引き起こし，騒音を増大させる虞が生じる。   Also, consider the movement in the small end 131 of the piston pin 12. As already described, since a bearing gap is provided between the piston pin 12 and the small end portion 131, when the piston pin 12 receives an external force, the piston pin 12 sandwiches the bearing gap with respect to the small end portion 131. Will exercise relatively. Here, when the axial recess 122 is provided in the piston pin 12, the radial clearance between the axial recess 122 and the inner diameter surface of the small end 131 increases (the bearing clearance increases in the radial direction). If the radial gap between the piston pin 12 and the small end portion 131 is excessively enlarged, the movement of the piston pin 12 in the radial direction is greatly allowed, and noise increases due to the collision between the piston pin 12 and the small end portion 131, The movement of the piston pin 12 in the radial gap of the portion 131 causes a piston slap phenomenon in which the piston 11 repeats collision vibration on the inner peripheral surface of the cylinder 19, which may increase noise.

本実施例においては，第２軸方向凹部１２２２は，第１軸方向凹部１２２１をピストンピン中心Ｃを中心として１８０°回転させた凹部禁止領域を除く領域に形成されている。そのため，第１軸方向凹部１２２１において発生した油膜反力は，第２軸方向凹部１２２２が存在しないピストンピン１２の外周面（すなわち第１軸方向凹部１２２１をピストンピン中心Ｃを中心として１８０°回転させた位置）で受けることができる。仮に本実施例と異なり，この油膜反力を受ける領域に第２軸方向凹部１２２２が存在する場合，第２軸方向凹部１２２２と小端部１３１との半径方向隙間は，第２軸方向凹部１２２２外側における半径方向隙間と比して大きくなるため，前述したメカニズムによりピストンピン１２が小端部１３１内で運動できる自由度が高くなり，騒音増大の要因となる。また，角度領域Ｒ１に軸方向凹部１２２を設けた場合と同様の理屈で，第２軸方向凹部１２２２周辺の面圧が増大する虞があるため，信頼性上好ましくない。   In the present embodiment, the second axial recess 1222 is formed in a region excluding the recess prohibition region obtained by rotating the first axial recess 1221 about the piston pin center C by 180 °. Therefore, the oil film reaction force generated in the first axial recess 1221 is rotated by 180 ° on the outer peripheral surface of the piston pin 12 where the second axial recess 1222 does not exist (that is, the first axial recess 1221 is centered on the piston pin center C). Position). If the second axial recess 1222 is present in the region that receives this oil film reaction force unlike the present embodiment, the radial clearance between the second axial recess 1222 and the small end 131 is the second axial recess 1222. Since it is larger than the radial gap on the outside, the mechanism described above increases the degree of freedom with which the piston pin 12 can move within the small end 131, causing increased noise. Further, the same reasoning as when the axial concave portion 122 is provided in the angular region R1 and the surface pressure around the second axial concave portion 1222 may increase, which is not preferable in terms of reliability.

このため、本実施例では上記のように、領域Ｒ１を避けて凹部１２２を配し、一方の凹部１２２１に対して中心Ｃを中心として１８０°回転させた凹部禁止領域を除く領域に他方の凹部１２２２を配することで、ピストンピン１２と小端部１３１との間に潤滑油を供給する凹部を配しつつも、音の低減が可能となる。領域Ｒ１としては、例えば、ピストンピン１２の軸方向視において、中心Ｃを起点として＋Ｘ軸方向に延びる仮想の半直線を基線として例えば±４５°内に収まる領域とするのが好ましい。   For this reason, in this embodiment, as described above, the concave portion 122 is arranged avoiding the region R1, and the other concave portion is formed in the region excluding the concave portion prohibiting region rotated by 180 ° about the center C with respect to one concave portion 1221 By arranging 1222, it is possible to reduce sound while arranging a recess for supplying lubricating oil between the piston pin 12 and the small end 131. For example, the region R1 is preferably a region that falls within, for example, ± 45 ° with a virtual half line extending in the + X-axis direction starting from the center C as a base line when the piston pin 12 is viewed in the axial direction.

図５は本実施例の吸入工程時のコンロッド１３を含むＺ方向断面図である。コンロッド１３は、本実施例では吸入工程時、ピストンピン１２を中心にして時計回りＤ２に揺動する。これにより、図４における説明と同様に、第１軸方向凹部１２２１に存在する潤滑油は圧縮側端部１２２１ｄに向けて動かされるため、潤滑油により圧縮側端部１２２１ｄからピストンピン１２中心に向けて圧力が生じる。   FIG. 5 is a cross-sectional view in the Z direction including the connecting rod 13 during the inhalation process of the present embodiment. In the present embodiment, the connecting rod 13 swings clockwise D2 around the piston pin 12 during the suction process. Accordingly, the lubricating oil present in the first axial recess 1221 is moved toward the compression side end portion 1221d as in the description in FIG. 4, and therefore, the lubricating oil moves from the compression side end portion 1221d toward the center of the piston pin 12. Pressure.

また、同様に圧縮方向側に凹部禁止領域Ｒ２が設定される。しかし、凹部禁止領域Ｒ２にかかる力は、ピストン１１の吸入工程時に付加されるものであるから、凹部禁止領域Ｒ１に付加される力より小さい。このため、凹部１２２１，１２２２は−Ｘ方向に偏らせることができる。すなわち、凹部１２２１，１２２２間の周方向離間長さは、本実施例のように、ピストンピン１２の中心Ｃから見て圧縮方向側（−Ｘ方向側）よりも吸引方向側（＋Ｘ方向側）の方が長いことが好ましい。このように、凹部禁止領域Ｒ２の範囲は、凹部禁止領域Ｒ１の範囲より狭い。   Similarly, a recessed portion forbidden region R2 is set on the compression direction side. However, since the force applied to the recessed portion prohibited area R2 is applied during the suction process of the piston 11, it is smaller than the force applied to the recessed portion prohibited area R1. For this reason, the concave parts 1221 and 1222 can be biased in the −X direction. That is, the circumferential separation length between the concave portions 1221 and 1222 is the suction direction side (+ X direction side) rather than the compression direction side (−X direction side) when viewed from the center C of the piston pin 12 as in this embodiment. Is preferably longer. Thus, the range of the recessed portion prohibited area R2 is narrower than the range of the recessed portion prohibited area R1.

（シリンダ１９からの力）
別実施例として、必ずしも原理は明らかではないが凹部１２２１，１２２２は、中心Ｃを起点として±Ｙ方向に延びる仮想の半直線それぞれを基線として、±５°の範囲に収まる領域を除く領域に設けると好ましい。ピストンピン１２は、ピストン１１の往復動に伴い小端部１３１からＹ方向への力を受けてピストン１１に押圧される。このため、Ｙ方向の力を受けるべき領域に凹部が存在すると潤滑油に力が伝達されて大きな音が発生すると思われる。 (Force from cylinder 19)
As another embodiment, although the principle is not necessarily clear, the concave portions 1221 and 1222 are provided in regions excluding a region that falls within a range of ± 5 ° with each virtual half line extending in the ± Y direction starting from the center C as a base line. And preferred. The piston pin 12 receives a force in the Y direction from the small end portion 131 as the piston 11 reciprocates, and is pressed against the piston 11. For this reason, if there is a recess in a region that should receive a force in the Y direction, it is considered that the force is transmitted to the lubricating oil and a loud noise is generated.

（その他）
また、本実施例では２つの凹部１２２１，１２２２を設けたが、潤滑に支障がなければ、簡易に、１つの凹部のみを配することで、中心Ｃを中心にして凹部１２２１を１８０°回転させた凹部禁止領域に別の凹部が位置しないようにしても良い。 (Other)
In this embodiment, the two concave portions 1221 and 1222 are provided. However, if there is no problem with lubrication, the concave portion 1221 can be rotated 180 ° around the center C by simply arranging one concave portion. Alternatively, another recess may not be located in the recessed portion prohibited area.

本実施例の圧縮機は、冷蔵庫など種々の機器に適用できる。   The compressor of the present embodiment can be applied to various devices such as a refrigerator.

１１ ピストン
１２ ピストンピン
１２１ 固定横孔
１２２ 軸方向凹部
１２２１ 第１軸方向凹部
１２２２ 第２軸方向凹部
１２３ 周方向凹部
１３ コンロッド
１３１ 小端部
１３２ 大端部
１４ 固定ピン
１９ シリンダ 11 piston 12 piston pin 121 fixed lateral hole 122 axial recess 1221 first axial recess 1222 second axial recess 123 circumferential recess 13 connecting rod 131 small end 132 large end 14 fixing pin 19 cylinder

Claims (6)

ピストンと、
小端部が該ピストン内に位置するコンロッドと、
該ピストン及び前記小端部内に挿通されて、前記ピストンに前記コンロッドを取付けるピストンピンと、を有し、
前記小端部と前記ピストンピンとは、隙間を挟んで相対的に回転自在であり、
前記ピストンピンは、該ピストンピンの軸方向に延在する凹部を有する圧縮機であって、
前記凹部が１つである、又は、
前記凹部が２つ以上であり、かつ、前記ピストンピンの軸方向視において、前記ピストンピンの中心を中心にして前記凹部を１８０°回転させた凹部禁止領域を除いた範囲に、別の凹部が位置することを特徴とする圧縮機。 A piston,
A connecting rod whose small end is located in the piston;
A piston pin that is inserted into the piston and the small end and attaches the connecting rod to the piston;
The small end portion and the piston pin are relatively rotatable with a gap therebetween,
The piston pin is a compressor having a recess extending in the axial direction of the piston pin,
The number of the recesses is one, or
There are two or more recesses, and in the axial view of the piston pin, there is another recess in a range excluding a recess prohibition region obtained by rotating the recess by 180 ° around the center of the piston pin. A compressor characterized by being located. 前記凹部が２つ以上であり、かつ、前記ピストンピンの軸方向視において、前記ピストンピンの中心を中心にして前記凹部を１８０°回転させた凹部禁止領域を除いた範囲に、別の凹部が位置することを特徴とする請求項１に記載の圧縮機。   There are two or more recesses, and in the axial view of the piston pin, there is another recess in a range excluding a recess prohibition region obtained by rotating the recess by 180 ° around the center of the piston pin. The compressor according to claim 1, wherein the compressor is located. 前記凹部は、前記ピストンピンの軸方向視において、前記ピストンピンの中心を起点として、前記ピストンの下死点方向に延びる仮想の半直線を基線として±３０°内に収まる領域を除く領域にその全部が位置することを特徴とする請求項１又は２に記載の圧縮機。   In the axial view of the piston pin, the concave portion is formed in a region excluding a region that falls within ± 30 ° with a virtual half line extending from the center of the piston pin in the direction of the bottom dead center of the piston as a base line. The compressor according to claim 1 or 2, wherein all are located. 前記凹部は、前記ピストンピンの軸方向視において、前記ピストンピンの中心を起点として、前記ピストンの往復動方向及び前記ピストンピンの軸方向に直交する２つの方向それぞれに延びる仮想の半直線それぞれを基線として、±５°内に収まる領域を除く領域にその全部が位置することを特徴とする請求項１乃至３何れか一項に記載の圧縮機。   Each of the concave portions, when viewed in the axial direction of the piston pin, has an imaginary half-line extending from the center of the piston pin in each of two directions orthogonal to the reciprocating direction of the piston and the axial direction of the piston pin. 4. The compressor according to claim 1, wherein the compressor is entirely located in a region excluding a region that falls within ± 5 ° as a base line. 5. 前記２つの凹部の周方向の離間長さは、前記ピストンピンの中心から見て上死点方向側よりも下死点方向側の方が長いことを特徴とする請求項２乃至４何れか一項に記載の圧縮機。   5. The circumferential distance between the two recesses is longer on the bottom dead center side than on the top dead center side when viewed from the center of the piston pin. The compressor according to item. 請求項１乃至５何れか一項に記載の圧縮機を有する機器。   The apparatus which has a compressor as described in any one of Claims 1 thru | or 5.
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