WO2024047989A1 - Compressor - Google Patents

Compressor Download PDF

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Publication number
WO2024047989A1
WO2024047989A1 PCT/JP2023/020890 JP2023020890W WO2024047989A1 WO 2024047989 A1 WO2024047989 A1 WO 2024047989A1 JP 2023020890 W JP2023020890 W JP 2023020890W WO 2024047989 A1 WO2024047989 A1 WO 2024047989A1
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WO
WIPO (PCT)
Prior art keywords
compressor
piston
hole
resin
connecting rod
Prior art date
Application number
PCT/JP2023/020890
Other languages
French (fr)
Japanese (ja)
Inventor
伸之 成澤
浩介 須藤
Original Assignee
株式会社日立産機システム
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Application filed by 株式会社日立産機システム filed Critical 株式会社日立産機システム
Publication of WO2024047989A1 publication Critical patent/WO2024047989A1/en

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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
    • 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

Definitions

  • the present invention relates to a compressor.
  • the compressor has a reciprocating compression system that converts the rotary motion of the prime mover into reciprocating motion via the crankshaft and connecting rod (hereinafter referred to as the connecting rod), causing the piston to reciprocate and compress the fluid sucked into the cylinder.
  • the connecting rod connecting rod
  • reciprocating compressors There are two types of reciprocating compressors: a normal piston type in which a piston is swingably attached to a connecting rod via a bearing, and a swinging piston type in which a piston is directly attached to a connecting rod.
  • the latter type of oscillating piston type has a simpler structure than the normal piston type because it does not have a bearing or piston pin, and there are no design restrictions regarding bearing temperature to ensure lubrication.
  • the mass of moving parts can be reduced.
  • Patent Document 1 discloses a compressor in which a piston whose compression chamber side is made of resin is fixed to a connecting rod from the crankcase side with a screw. Inserting the screw from the crankcase side in this manner prevents the screw from being heated by the high temperature compressed gas in the compression chamber. This makes it possible to suppress creep deformation of the resin of the piston around the screw, thereby suppressing the occurrence of loosening of the screw.
  • the piston of Patent Document 1 has an insert structure in which a metal insert part is embedded inside a resin, and the insert part is connected to a connecting rod with a screw.
  • the insert part is provided with a shape in which the edge located on the connecting rod side bites into the resin, and when a vertical load is applied to the piston, the insert member and the resin are separated by the edge. It's suppressed.
  • the load acting on the piston is not limited to the vertical direction.
  • the technique of Patent Document 1 has room for improvement regarding the structure of the insert component on the compression chamber side.
  • An object of the present invention is to provide a compressor that can further suppress a decrease in the strength of a piston caused by a difference in thermal expansion between the resin and the insert component.
  • the present invention provides a compressor in which a piston supported by a connecting rod reciprocates within a cylinder while rocking, the piston having at least a surface that contacts an inner circumferential wall of the cylinder.
  • the compressor includes a resin forming a surface on the compression chamber side, an insert part embedded inside the resin, and a through hole provided in the insert part and filled with the resin.
  • FIG. 1 is a schematic side view of a compressor according to a first embodiment of the present invention. 1 is a partially sectional view showing the configuration of a compressor main body according to a first embodiment of the present invention.
  • FIG. 2 is a schematic side view of a connecting rod and a piston fixed to the small end of the connecting rod of the compressor according to the first embodiment of the present invention.
  • 4 is a sectional view taken along line IV-IV in FIG. 3.
  • FIG. FIG. 1 is a perspective view of an insert component according to a first embodiment of the present invention. 5 is a sectional view taken along line VI-VI in FIG. 4.
  • FIG. FIG. 3 is a schematic side view of a piston according to a second embodiment of the present invention.
  • FIG. 7 is a schematic side view of a connecting rod of a compressor and a piston fixed to a small end of the connecting rod according to a third embodiment of the present invention.
  • FIG. 7 is an exploded perspective view of a connecting rod and a piston according to a third embodiment of the present invention.
  • FIG. 9 is a sectional view taken along line XX in FIG. 8; 11 is a sectional view taken along line XI-XI in FIG. 10.
  • FIG. 9 is a schematic cross-sectional view taken along line XX in FIG. 8.
  • FIG. It is a back perspective view of the insert component based on 4th Embodiment of this invention.
  • compressors according to the first to fourth embodiments of the present invention will be explained using the drawings.
  • the compressor of the present invention can be applied to various compressors that employ a swinging piston type among compressors that compress various fluids such as air and refrigerant, and the type, model, and application thereof are not particularly limited.
  • FIG. 1 is a schematic side view of a compressor 10 according to a first embodiment of the present invention.
  • the compressor 10 includes a compressor body 1, an electric motor 2 that drives the compressor body 1, a tank 3 that stores fluid discharged by the compressor body 1, a compressor pulley 4, and an electric motor. It includes a pulley 5 and a transmission belt 6.
  • FIG. 2 is a partial cross-sectional view showing the configuration of the compressor main body 1 according to the first embodiment of the present invention.
  • the compressor main body 1 is a device that compresses fluid, and as shown in FIG. have.
  • FIGS. 1 and 2 show a case where the compressor 10 is a one-cylinder, one-stage compressor that includes a pair of pistons and cylinders.
  • the present invention is not limited thereto, and the compressor 10 may include a plurality of pairs of pistons and cylinders.
  • the compressor main body 1 is arranged and fixed on the tank 3 so that the crankshaft 24 and the rotation axis of the electric motor 2 are arranged in parallel.
  • a compressor pulley 4 is attached to the crankshaft 24, and an electric motor pulley 5 is attached to the rotating shaft of the electric motor 2.
  • a transmission belt 6 for transmitting the power of the electric motor 2 to the compressor body 1 is wound around the compressor pulley 4 and the electric motor pulley 5.
  • the compressor main body 1 is connected to the electric motor 2 via the electric motor pulley 5, the transmission belt 6, and the compressor pulley 4.
  • the invention is not limited to this, and the crankshaft 24 of the compressor main body 1 and the rotating shaft of the electric motor 2 may be directly connected, for example, using a shaft joint.
  • the compressor pulley 4 may be provided with blades. The blades rotate with the rotation of the compressor pulley 4 and generate cooling air toward the compressor body 1, thereby cooling the compressor body 1.
  • FIG. 3 is a schematic side view of the connecting rod 32 of the compressor 10 according to the present embodiment and the piston 33 fixed to the small end 32b of the connecting rod 32. As shown in FIG. 3, the piston 33 is fixed to the tip of the small end 32b of the connecting rod 32 with a screw 35 (a hexagon socket head bolt in this embodiment).
  • the piston 33 has at least an outer circumferential surface 33a that contacts the inner circumferential wall 22a (see FIG. 2) of the cylinder 22, and an upper surface 33c exposed within the compression chamber 22b (see FIG. 2) of the cylinder 22, which are made of resin 36. There is.
  • a piston ring 34 is attached to the piston 33. Further, it is preferable that the outer circumferential surface 33a of the piston 33 is a spherical surface having a diameter slightly smaller than the diameter of the inner circumferential side of the cylinder 22.
  • FIG. 4 is a cross-sectional view taken along IV-IV in FIG. 3.
  • the piston 33 includes a resin 36 and an insert component 41 embedded inside the resin 36.
  • the resin 36 and the insert component 41 are integrally molded by insert molding.
  • the resin 36 it is preferable to use, for example, polytetrafluoroethylene (PTFE), which has excellent abrasion resistance, or polyphenylene sulfide (PPS), which has excellent thermal expansion coefficient.
  • PTFE polytetrafluoroethylene
  • PPS polyphenylene sulfide
  • a ring groove 33b for mounting the piston ring 34 is provided in the resin 36. Note that the piston ring 34 may not be used. In this case, the ring groove 33b is not provided in the resin 36.
  • the piston 33 is provided with an annular portion 33d that annularly covers a portion of the insert part 41 on the connecting rod 32 side with the resin 36.
  • the annular portion 33d is connected to the resin forming the outer peripheral surface 33a of the piston 33.
  • annular portion 33d fits into an annular groove 32e provided in the small end 32b of the connecting rod 32. Thereby, the piston 33 can be positioned with respect to the small end 32b of the connecting rod 32.
  • FIG. 5 is a perspective view of the insert component 41 according to this embodiment.
  • the insert component 41 is a border hat-shaped member made of metal (for example, aluminum alloy), and has a cylindrical portion 41a, a lid portion 41b, a flange portion 41c, and a through hole 41d.
  • the upper opening of the cylindrical portion 41a is closed by the lid portion 41b, and the cylindrical portion 41a and the lid portion 41b form a cavity 41e (see FIG. 4) that opens on the lower side.
  • the flange portion 41c is an annular portion extending radially outward from the lower outer peripheral wall of the cylindrical portion 41a.
  • the outer peripheral wall of the cylindrical portion 41a, the upper surface of the lid portion 41b, the upper surface and side surfaces of the flange portion 41c, and the radially outer side of the lower surface of the flange portion 41c are covered with the resin 36.
  • the inner circumferential wall of the cylindrical portion 41a, the lower surface of the lid portion 41b, and the radially inner side of the lower surface of the collar portion 41c are not covered with the resin 36 and are exposed.
  • the through hole 41d is provided in the insert part 41, and the through hole 41d is filled with resin. As shown in FIG. 5, the four through holes 41d of this embodiment are linearly arranged in the groove 41f of the lid part 41b.
  • the groove 41f is formed along a groove 33f (see FIG. 3) provided on the upper surface 33c of the piston 33 to prevent the piston 33 from coming into contact with the suction valve plate 26a (see FIG. 2) provided on the valve plate 26.
  • This is a recessed portion of the lid portion 41b. Therefore, the lid portion 41b is thin with the groove 41f, and the through hole 41d can be easily provided therein.
  • the arrangement of the through holes 41d is not limited to the above, and many other arrangements can be considered.
  • the through holes 41d may be arranged along a direction intersecting the groove 41f so that the frictional resistance between the piston 33 and the cylinder 22 can accommodate the load that causes the resin 36 to be peeled off from the piston 33. Further, it is sufficient to have at least one through hole 41d.
  • the through hole 41d is separated from the center 41o of the insert component 41 by a predetermined distance D or more (see FIG. 5).
  • the predetermined distance D is the radius of the gate of the mold used when insert-molding the piston 33.
  • the through hole 41d includes a tapered portion 41g (see FIG. 4) whose diameter increases on the inside of the piston 33 (on the side of the cavity 41e).
  • the tapered portion 41g of this embodiment has a shape (chamfered shape) in which the opening of the through hole 41d provided on the lower surface of the lid portion 41b is widened.
  • the through hole 41d may include a tapered portion 41g whose diameter increases on the inside of the piston 33, and may also include a reverse tapered portion whose diameter increases on the opposite side, as shown in FIG. 5, for example.
  • the slope angle ⁇ (see FIG. 4) of the tapered portion 41g with respect to the inner wall of the through hole 41d is greater than 0 degrees and less than 60 degrees. This makes it possible to suppress the occurrence of cracks even when a resin with high edge sensitivity is used.
  • FIG. 6 is a sectional view taken along line VI-VI in FIG. 4.
  • the lower part of the insert component 41 is provided with a screw hole 41h that opens downward.
  • the small end portion 32b of the connecting rod 32 is provided with a through hole 32c that overlaps with the screw hole 41h.
  • the screw 35 inserted into the through hole 32c toward the piston 33 is preferably screwed into the screw hole 41h to fix the piston 33 to the connecting rod 32.
  • the small end 32b of the connecting rod 32 is provided with a recess 32f that opens upward.
  • the recess 32f preferably communicates with a cavity 41e provided in the insert component 41 and opening on the lower side.
  • a hollow portion 37 is formed between the piston 33 and the small end portion 32b of the connecting rod 32.
  • the piston 33 of the compressor 10 according to the present embodiment is provided in an insert part 41 embedded in the resin 36 that constitutes at least a surface 33a that contacts the inner circumferential wall 22a of the cylinder 22 and a surface 33c on the compression chamber 22b side.
  • a through hole 41d filled with resin 36 is provided.
  • the resin 36 that covers the compression chamber 22b side of the insert component 41 is bonded to the insert component 41 by the resin 36 that fills the through hole 41d provided in the insert component 41.
  • the piston 33 of the compressor 10 according to the present embodiment can suppress its deformation. can.
  • the through hole 41d provided in the insert component 41 is provided with the tapered portion 41g whose diameter increases on the inside of the piston 33 (on the side of the cavity 41e).
  • the resin 36 filled in 41d cannot move to the outside of the piston 33. Therefore, the piston 33 of the compressor 10 according to the present embodiment can further suppress peeling of the resin 36 covering the insert component 41 from the insert component 41.
  • the slope angle ⁇ of the tapered portion 41g with respect to the inner wall of the through hole 41d is greater than 0 degrees and less than 60 degrees. Therefore, the inclination angle of the tapered portion 36a (see FIG. 4) of the resin 36 filled in the through hole 41d is greater than 0 degrees and less than 60 degrees with respect to the side wall of the resin 36 filled in the through hole 41d. Thereby, it is possible to suppress the occurrence of cracks in the tapered portion 36a of the resin 36.
  • the through hole 41d is separated from the center 41o of the insert component 41 by a predetermined distance D or more, as shown in FIG. Therefore, when insert molding the piston 33, the through hole 41d can be provided outside the radius of the gate provided at a position overlapping the approximate center of the insert component 41 fixed to the mold. Thereby, occurrence of molding defects such as sink marks in the resin 36 can be suppressed. Therefore, it is possible to suppress the generation of a gap between the resin 36 and the insert component 41, which causes tensile stress to be generated in the resin 36 due to the pressure of the compression chamber 22b, and it is possible to suppress a decrease in the strength of the resin 36.
  • the mass of the reciprocating portion including the piston 33 and the connecting rod 32 can be reduced. Therefore, vibration of the compressor main body 1 caused by reciprocating inertia force can be suppressed.
  • the screw 35 that fixes the piston 33 to the connecting rod 32 is inserted into the through hole 32c of the connecting rod 32 toward the piston 33, and the connecting rod 35 provided in the insert part 41 of the piston 33 is inserted into the through hole 32c of the connecting rod 32.
  • the piston 33 is fixed to the connecting rod 32 by screwing into the screw hole 41h that opens on the side. Thereby, the screw 35 is not exposed in the compression chamber 22b, so that the screw 35 can be prevented from loosening due to the compression heat in the compression chamber 22b.
  • FIG. 7 is a schematic side view of a piston 233 according to a second embodiment of the invention.
  • the piston 233 according to this embodiment differs from the piston 33 according to the first embodiment in the position of the through hole 241d provided in the insert component 241.
  • the through hole 41d is provided in the lid portion 41b.
  • the piston 233 is provided at the flange 241c of the insert component 241 sandwiched between the resin 236.
  • FIG. 8 is a schematic side view of a connecting rod 332 and a piston 33 fixed to a small end 332b of the connecting rod 332 of a compressor according to a third embodiment of the present invention.
  • FIG. 9 is an exploded perspective view of the connecting rod 332 and piston 33 according to this embodiment.
  • FIG. 10 is a sectional view taken along line XX in FIG.
  • FIG. 11 is a sectional view taken along line XI-XI in FIG.
  • the connecting rod 332 according to this embodiment differs from the connecting rod 32 according to the first embodiment in that it includes communication holes (first communication hole 332g, second communication hole 332h) that communicate the inside and outside of the hollow part 37. .
  • the first communication hole 332g is a communication hole that is sandwiched between the radially extending groove 332i provided at the upper part of the small end portion 332b and the lower end 33e of the piston 33, and communicates between the inside and outside of the hollow portion 37. It opens on the inner peripheral wall 22a (see FIG. 2) side.
  • the second communication hole 332h is provided at the lower part of the small end 332b of the connecting rod 332, passes through the bottom surface 332j of the recess 332d, communicates between the inside and outside of the hollow portion 37, and opens toward the crankcase 21 side. .
  • the compressor according to this embodiment includes communication holes (first communication hole 332g, second communication hole 332h) that communicate the inside and outside of the hollow part 37, so that the heat accumulated in the hollow part 37 is transferred to the outside of the hollow part 37. can be released.
  • the compressor according to the present embodiment is provided with two or more communication holes (first communication hole 332g, second communication hole 332h), and at least one of the communication holes (first communication hole 332g) is connected to the cylinder. 22, and at least one other (second communication hole 332h) opens toward the crankcase 21 side.
  • crankcase 21 since the crankcase 21 breathes outside air through the breathing filter, cooling air equivalent to the outside temperature can be supplied into the hollow portion 37, and cooling efficiency can be further improved.
  • FIG. 13 is a rear perspective view of an insert component 441 according to a fourth embodiment of the present invention.
  • the insert component 441 according to the present embodiment is different from the insert component 41 according to the first embodiment in that a radiation fin is provided on the surface of the insert component 441 on the connecting rod 32 side (the lower surface 441h of the lid portion 441b of the insert component 441). 441j.
  • the radiation fins 441j of this embodiment are protruded from the lower surface 441h of the lid portion 441b of the insert component 441 toward the connecting rod 32, and are bonded to the inner wall 441k of the cylindrical portion 441a of the insert component 441, thereby increasing the strength. . Moreover, it is preferable that the radiation fins 441j are provided avoiding the through holes 441d.
  • the insert component 441 according to this embodiment has a radiation fin 441j on the surface (lower surface 441h) on the connecting rod 32 side. Therefore, the insert component 441 can be efficiently cooled, the thermal expansion of the insert component 441 can be reduced, and a decrease in the strength of the resin 36 covering the compression chamber 22b side of the insert component 441 can be further suppressed.
  • the present invention is not limited to the embodiments described above, and includes various modifications.
  • the embodiments described above are described in detail to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to having all the configurations described.
  • SYMBOLS 1 Compressor main body, 10... Compressor, 21... Crank case, 22... Cylinder, 22a... Inner peripheral wall, 22b... Compression chamber, 32, 332... Connecting rod, 32c... Through hole, 33, 233... Piston, 35... Screw , 36,236... Resin, 36a... Tapered part, 37... Hollow part, 41,241,441... Insert part, 41a... Cylindrical part, 41b, 441b... Lid part, 41c, 241c...
  • Flange part 41d, 241d, 441d ...Through hole, 41e...Gap, 41g...Tapered part, 41h...Screw hole, 41o...Center, 332g...First communication hole, 332h...Second communication hole, 441j...Radiation fin

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

Provided is a compressor (10) in which a piston (33) supported by a connecting rod (32) reciprocates while swinging inside a cylinder (22), wherein the piston (33) comprises: a resin (36) constituting at least a surface (33a) contacting an inner peripheral wall (22a) of the cylinder (22) and a surface (33c) on a compression chamber (22b) side; an insert component (41) embedded in the resin (36); and a penetration hole (41d) provided in the insert component (41) and having the resin (36) filled therein.

Description

圧縮機compressor
　本発明は、圧縮機に関する。 The present invention relates to a compressor.
　圧縮機には、原動機の回転運動をクランクシャフト、コネクティングロッド（以下、コンロッド）を介して往復動運動に転換し、ピストンを往復運動させることにより、シリンダ内に吸入した流体を圧縮する往復動圧縮機がある。この往復動圧縮機には、ピストンが軸受を介して首振り可能にコンロッドに取り付けられた通常ピストン方式と、ピストンがコンロッドに直接取付けられた揺動ピストン方式とがある。 The compressor has a reciprocating compression system that converts the rotary motion of the prime mover into reciprocating motion via the crankshaft and connecting rod (hereinafter referred to as the connecting rod), causing the piston to reciprocate and compress the fluid sucked into the cylinder. There is a chance. There are two types of reciprocating compressors: a normal piston type in which a piston is swingably attached to a connecting rod via a bearing, and a swinging piston type in which a piston is directly attached to a connecting rod.
　後者の揺動ピストン方式は、通常ピストン方式と比較して軸受やピストンピンを持たない分だけ構造が簡素であり、軸受温度に関し潤滑を確保する上での設計的な制限がないことや、往復動する部分の質量を低減することができる。 The latter type of oscillating piston type has a simpler structure than the normal piston type because it does not have a bearing or piston pin, and there are no design restrictions regarding bearing temperature to ensure lubrication. The mass of moving parts can be reduced.
　この揺動ピストン方式の圧縮機として、特許文献１には、圧縮室側が樹脂で構成されたピストンをクランクケース側からネジによってコンロッドに固定した圧縮機が開示されている。このようにクランクケース側からネジを挿入すると、圧縮室内の高温の圧縮気体によるネジの加熱が防止される。これによりネジの周囲のピストンの樹脂のクリープ変形を抑制できるので、ネジの緩みの発生を抑制できる。 As this swing piston type compressor, Patent Document 1 discloses a compressor in which a piston whose compression chamber side is made of resin is fixed to a connecting rod from the crankcase side with a screw. Inserting the screw from the crankcase side in this manner prevents the screw from being heated by the high temperature compressed gas in the compression chamber. This makes it possible to suppress creep deformation of the resin of the piston around the screw, thereby suppressing the occurrence of loosening of the screw.
特開２０２１-１１０２７４号公報JP2021-110274A
　特許文献１のピストンは、樹脂の内部に金属製のインサート部品が埋め込まれたインサート構造を有しており、当該インサート部品がコンロッドとネジで結合されている。 The piston of Patent Document 1 has an insert structure in which a metal insert part is embedded inside a resin, and the insert part is connected to a connecting rod with a screw.
　通常、こうしたインサート構造では、樹脂とインサート部品（金属）の熱膨張率の差に起因する変形や、樹脂の成形欠陥（例えばひけ）に起因する密着不良により、樹脂とインサート部品との間に隙間が生じてピストンの強度が低下し得る点に留意する必要がある。これに関して特許文献１では、インサート部品においてコンロッド側に位置する縁部が樹脂に対して食い込んだ形状を設け、ピストンに上下方向の荷重が作用した場合のインサート部材と樹脂の分離を当該縁部によって抑制している。 Normally, in this type of insert structure, there is a gap between the resin and the insert part due to deformation due to the difference in thermal expansion coefficient between the resin and the insert part (metal), or poor adhesion due to molding defects of the resin (for example, sink marks). It should be noted that this may occur and the strength of the piston may decrease. Regarding this, in Patent Document 1, the insert part is provided with a shape in which the edge located on the connecting rod side bites into the resin, and when a vertical load is applied to the piston, the insert member and the resin are separated by the edge. It's suppressed.
　しかし、ピストンに作用する荷重は上下方向に限られない。つまり、樹脂の熱膨張によるピストンの変形をさらに抑制する観点からは、特許文献１の技術はインサート部品の圧縮室側の構造に関して改善の余地がある。 However, the load acting on the piston is not limited to the vertical direction. In other words, from the viewpoint of further suppressing deformation of the piston due to thermal expansion of the resin, the technique of Patent Document 1 has room for improvement regarding the structure of the insert component on the compression chamber side.
　本発明の目的は、樹脂とインサート部品の熱膨張差に起因したピストンの強度低下をさらに抑制できる圧縮機を提供することにある。 An object of the present invention is to provide a compressor that can further suppress a decrease in the strength of a piston caused by a difference in thermal expansion between the resin and the insert component.
　上記目的を達成するために、本発明は、コンロッドに支持されたピストンがシリンダ内を揺動しながら往復動する圧縮機であって、前記ピストンは、少なくとも前記シリンダの内周壁に接触する面と圧縮室側の面とを構成する樹脂と、前記樹脂の内部に埋め込まれたインサート部品と、前記インサート部品に設けられ前記樹脂が充填された貫通孔とを備える。 In order to achieve the above object, the present invention provides a compressor in which a piston supported by a connecting rod reciprocates within a cylinder while rocking, the piston having at least a surface that contacts an inner circumferential wall of the cylinder. The compressor includes a resin forming a surface on the compression chamber side, an insert part embedded inside the resin, and a through hole provided in the insert part and filled with the resin.
　本発明によれば、樹脂とインサート部品の熱膨張差に起因したピストンの強度低下をさらに抑制できる圧縮機を提供できる。上記した以外の課題、構成及び効果は、以下の実施形態の説明により明らかにされる。 According to the present invention, it is possible to provide a compressor that can further suppress a decrease in the strength of the piston due to the difference in thermal expansion between the resin and the insert component. Problems, configurations, and effects other than those described above will be made clear by the following description of the embodiments.
本発明の第１実施形態に係る圧縮機の概略側面図である。1 is a schematic side view of a compressor according to a first embodiment of the present invention. 本発明の第１実施形態に係る圧縮機本体の構成を示す一部断面図である。1 is a partially sectional view showing the configuration of a compressor main body according to a first embodiment of the present invention. 本発明の第１実施形態に係る圧縮機のコンロッドとコンロッドの小端部に固定されたピストンの概略側面図である。FIG. 2 is a schematic side view of a connecting rod and a piston fixed to the small end of the connecting rod of the compressor according to the first embodiment of the present invention. 図３のIV－IV断面図である。4 is a sectional view taken along line IV-IV in FIG. 3. FIG. 本発明の第１実施形態に係るインサート部品の斜視図である。FIG. 1 is a perspective view of an insert component according to a first embodiment of the present invention. 図４のVI－VI断面図である。5 is a sectional view taken along line VI-VI in FIG. 4. FIG. 本発明の第２実施形態に係るピストンの概略側面図である。FIG. 3 is a schematic side view of a piston according to a second embodiment of the present invention. 本発明の第３実施形態に係る圧縮機のコンロッドとコンロッドの小端部に固定されたピストンの概略側面図である。FIG. 7 is a schematic side view of a connecting rod of a compressor and a piston fixed to a small end of the connecting rod according to a third embodiment of the present invention. 本発明の第３実施形態に係るコンロッドとピストンの展開斜視図である。FIG. 7 is an exploded perspective view of a connecting rod and a piston according to a third embodiment of the present invention. 図８のＸ－Ｘ断面図である。FIG. 9 is a sectional view taken along line XX in FIG. 8; 図１０のXI－XI断面図である。11 is a sectional view taken along line XI-XI in FIG. 10. FIG. 図８のＸ－Ｘ断面模式図である。9 is a schematic cross-sectional view taken along line XX in FIG. 8. FIG. 本発明の第４実施形態に係るインサート部品の背面斜視図である。It is a back perspective view of the insert component based on 4th Embodiment of this invention.
　以下、図面を用いて、本発明の第１実施形態～第４実施形態に係る圧縮機の構成及び動作について説明する。本発明の圧縮機は空気や冷媒などの各種流体を圧縮する圧縮機のうち、揺動ピストン方式を採用する様々な圧縮機に適用可能であり、その種類や型式、用途は特に限定されない。 Hereinafter, the configuration and operation of compressors according to the first to fourth embodiments of the present invention will be explained using the drawings. The compressor of the present invention can be applied to various compressors that employ a swinging piston type among compressors that compress various fluids such as air and refrigerant, and the type, model, and application thereof are not particularly limited.
　　（第１実施形態）
　図１は、本発明の第１実施形態に係る圧縮機１０の概略側面図である。図１に示すように圧縮機１０は、圧縮機本体１と、圧縮機本体１を駆動する電動機２と、圧縮機本体１が吐出す流体を貯留するタンク３と、圧縮機プーリ４と、電動機プーリ５と、伝動ベルト６とを備えている。 (First embodiment)
FIG. 1 is a schematic side view of a compressor 10 according to a first embodiment of the present invention. As shown in FIG. 1, the compressor 10 includes a compressor body 1, an electric motor 2 that drives the compressor body 1, a tank 3 that stores fluid discharged by the compressor body 1, a compressor pulley 4, and an electric motor. It includes a pulley 5 and a transmission belt 6.
　図２は、本発明の第１実施形態に係る圧縮機本体１の構成を示す一部断面図である。圧縮機本体１は流体を圧縮する装置で、図２に示すように、クランクケース２１と、シリンダ２２と、シリンダヘッド２３と、クランクシャフト２４と、バルブプレート２６と、コンロッド３２と、ピストン３３とを有している。 FIG. 2 is a partial cross-sectional view showing the configuration of the compressor main body 1 according to the first embodiment of the present invention. The compressor main body 1 is a device that compresses fluid, and as shown in FIG. have.
　なお、図１，２に、圧縮機１０が１対のピストン・シリンダを備える１気筒１段圧縮機である場合を示した。しかし、これに限定されず、圧縮機１０は複数対のピストン・シリンダを備える圧縮機でもよい。 Note that FIGS. 1 and 2 show a case where the compressor 10 is a one-cylinder, one-stage compressor that includes a pair of pistons and cylinders. However, the present invention is not limited thereto, and the compressor 10 may include a plurality of pairs of pistons and cylinders.
　圧縮機本体１は、クランクシャフト２４と電動機２の回転軸とが平行に配置されるように、タンク３上に配置して固定されている。クランクシャフト２４には圧縮機プーリ４が取り付けられ、電動機２の回転軸には電動機プーリ５が取り付けられている。そして、圧縮機プーリ４と電動機プーリ５とには、電動機２の動力を圧縮機本体１に伝達するための伝動ベルト６が巻回されている。 The compressor main body 1 is arranged and fixed on the tank 3 so that the crankshaft 24 and the rotation axis of the electric motor 2 are arranged in parallel. A compressor pulley 4 is attached to the crankshaft 24, and an electric motor pulley 5 is attached to the rotating shaft of the electric motor 2. A transmission belt 6 for transmitting the power of the electric motor 2 to the compressor body 1 is wound around the compressor pulley 4 and the electric motor pulley 5.
　そのため、電動機２を起動させると、電動機プーリ５と伝動ベルト６と圧縮機プーリ４を介して、クランクシャフト２４が回転する。そして、クランクシャフト２４のクランクピンに取り付けられたコンロッド３２の大端部３２ａが円運動する。これにより、コンロッド３２の小端部３２ｂに取り付けられたピストン３３が、シリンダ２２内を揺動しながら往復動する。そのため、流体はシリンダヘッド２３の取入口からシリンダ２２の圧縮室２２ｂ内に流入し、ピストン３３により圧縮され、シリンダヘッド２３の吐出口からタンク３に吐出される。 Therefore, when the electric motor 2 is started, the crankshaft 24 rotates via the electric motor pulley 5, the transmission belt 6, and the compressor pulley 4. Then, the large end 32a of the connecting rod 32 attached to the crank pin of the crankshaft 24 moves circularly. As a result, the piston 33 attached to the small end 32b of the connecting rod 32 reciprocates within the cylinder 22 while rocking. Therefore, the fluid flows into the compression chamber 22b of the cylinder 22 from the intake port of the cylinder head 23, is compressed by the piston 33, and is discharged from the discharge port of the cylinder head 23 into the tank 3.
　なお、図１に示す圧縮機１０では、圧縮機本体１が電動機２に電動機プーリ５と伝動ベルト６と圧縮機プーリ４を介して接続されている。しかし、これに限定されず、圧縮機本体１のクランクシャフト２４と電動機２の回転軸とを、例えば、軸継手を用いて直接、接続してもよい。 In the compressor 10 shown in FIG. 1, the compressor main body 1 is connected to the electric motor 2 via the electric motor pulley 5, the transmission belt 6, and the compressor pulley 4. However, the invention is not limited to this, and the crankshaft 24 of the compressor main body 1 and the rotating shaft of the electric motor 2 may be directly connected, for example, using a shaft joint.
　また、圧縮機プーリ４に羽根を設けてもよい。この羽根は圧縮機プーリ４の回転に伴って回転し冷却風を圧縮機本体１に向けて発生させ、圧縮機本体１を冷却することができる。 Additionally, the compressor pulley 4 may be provided with blades. The blades rotate with the rotation of the compressor pulley 4 and generate cooling air toward the compressor body 1, thereby cooling the compressor body 1.
　図３は、本実施形態に係る圧縮機１０のコンロッド３２とコンロッド３２に小端部３２ｂに固定されたピストン３３の概略側面図である。図３に示すように、ピストン３３は、コンロッド３２の小端部３２ｂの先端にネジ３５（本実施形態では六角穴付きボルト）によって固定されている。 FIG. 3 is a schematic side view of the connecting rod 32 of the compressor 10 according to the present embodiment and the piston 33 fixed to the small end 32b of the connecting rod 32. As shown in FIG. 3, the piston 33 is fixed to the tip of the small end 32b of the connecting rod 32 with a screw 35 (a hexagon socket head bolt in this embodiment).
　ピストン３３は、少なくとも、シリンダ２２の内周壁２２ａ（図２参照）に接触する外周面３３ａと、シリンダ２２の圧縮室２２ｂ（図２参照）内に露出する上面３３ｃとが樹脂３６によって構成されている。 The piston 33 has at least an outer circumferential surface 33a that contacts the inner circumferential wall 22a (see FIG. 2) of the cylinder 22, and an upper surface 33c exposed within the compression chamber 22b (see FIG. 2) of the cylinder 22, which are made of resin 36. There is.
　ピストン３３には、ピストンリング３４が取り付けられている。また、ピストン３３の外周面３３ａは、シリンダ２２の内周側の直径よりわずかに小さい直径の球面となっていることが好ましい。 A piston ring 34 is attached to the piston 33. Further, it is preferable that the outer circumferential surface 33a of the piston 33 is a spherical surface having a diameter slightly smaller than the diameter of the inner circumferential side of the cylinder 22.
　図４は、図３のIV－IV断面図である。図４に示すように、ピストン３３は、樹脂３６と、樹脂３６の内部に埋め込まれたインサート部品４１を備えている。樹脂３６とインサート部品４１とはインサート成形により一体に成形されている。 FIG. 4 is a cross-sectional view taken along IV-IV in FIG. 3. As shown in FIG. 4, the piston 33 includes a resin 36 and an insert component 41 embedded inside the resin 36. The resin 36 and the insert component 41 are integrally molded by insert molding.
　樹脂３６は、例えば、耐摩耗性に優れるポリテトラフルオロエチレン（Ｐｏｌｙ　Ｔｅｔｒａ　Ｆｌｕｏｒｏ　Ｅｔｈｙｌｅｎｅ、ＰＴＦＥ）や、熱膨張率に優れるポリフェニレンサルファイド（Ｐｏｌｙ　Ｐｈｅｎｙｌｅｎｅ　Ｓｕｌｆｉｄｅ、ＰＰＳ）を用いることが好ましい。 As the resin 36, it is preferable to use, for example, polytetrafluoroethylene (PTFE), which has excellent abrasion resistance, or polyphenylene sulfide (PPS), which has excellent thermal expansion coefficient.
　樹脂３６には、ピストンリング３４を装着するためのリング溝３３ｂが設けられている。なお、ピストンリング３４を使用しないこともできる。この場合には、樹脂３６にリング溝３３ｂは設けられない。 A ring groove 33b for mounting the piston ring 34 is provided in the resin 36. Note that the piston ring 34 may not be used. In this case, the ring groove 33b is not provided in the resin 36.
　ピストン３３には、インサート部品４１のコンロッド３２側の一部を、樹脂３６が環状に覆う環状部３３ｄが設けられていることが好ましい。環状部３３ｄは、ピストン３３の外周面３３ａを形成する樹脂と繋がっている。これにより、ピストン３３が往復動慣性力や摩擦力によってクランクケース２１側に引き下げ荷重を受けた場合でも、インサート部品４１がピストン３３のコンロッド３２側に抜け出すことを抑制できる。 Preferably, the piston 33 is provided with an annular portion 33d that annularly covers a portion of the insert part 41 on the connecting rod 32 side with the resin 36. The annular portion 33d is connected to the resin forming the outer peripheral surface 33a of the piston 33. Thereby, even if the piston 33 receives a downward load toward the crankcase 21 due to reciprocating inertia force or frictional force, the insert component 41 can be prevented from slipping out of the piston 33 toward the connecting rod 32 side.
　さらに、環状部３３ｄは、コンロッド３２の小端部３２ｂに設けられた環状溝３２ｅと嵌合する。これにより、コンロッド３２の小端部３２ｂに対してピストン３３を位置決めすることができる。 Further, the annular portion 33d fits into an annular groove 32e provided in the small end 32b of the connecting rod 32. Thereby, the piston 33 can be positioned with respect to the small end 32b of the connecting rod 32.
　図５は、本実施形態に係るインサート部品４１の斜視図である。インサート部品４１は、金属（例えば、アルミニウム合金）により形成されたボーダーハット状の部材で、円筒部４１ａと、蓋部４１ｂと、鍔部４１ｃと、貫通孔４１ｄとを有している。 FIG. 5 is a perspective view of the insert component 41 according to this embodiment. The insert component 41 is a border hat-shaped member made of metal (for example, aluminum alloy), and has a cylindrical portion 41a, a lid portion 41b, a flange portion 41c, and a through hole 41d.
　円筒部４１ａは、蓋部４１ｂにより上方の開口を塞がれ、円筒部４１ａと蓋部４１ｂによって、下側に開口する空隙部４１ｅ（図４参照）が形成されている。 The upper opening of the cylindrical portion 41a is closed by the lid portion 41b, and the cylindrical portion 41a and the lid portion 41b form a cavity 41e (see FIG. 4) that opens on the lower side.
　鍔部４１ｃは、円筒部４１ａの下部外周壁から径方向外側に延伸する環状の部分である。 The flange portion 41c is an annular portion extending radially outward from the lower outer peripheral wall of the cylindrical portion 41a.
　図４に示すように、円筒部４１ａの外周壁と、蓋部４１ｂの上面と、鍔部４１ｃの上面と側面と、鍔部４１ｃの下面の径方向外側とが、樹脂３６によって覆われている。一方、円筒部４１ａの内周壁と、蓋部４１ｂの下面と、鍔部４１ｃの下面の径方向内側とは、樹脂３６によって覆われず、露出する。 As shown in FIG. 4, the outer peripheral wall of the cylindrical portion 41a, the upper surface of the lid portion 41b, the upper surface and side surfaces of the flange portion 41c, and the radially outer side of the lower surface of the flange portion 41c are covered with the resin 36. . On the other hand, the inner circumferential wall of the cylindrical portion 41a, the lower surface of the lid portion 41b, and the radially inner side of the lower surface of the collar portion 41c are not covered with the resin 36 and are exposed.
　貫通孔４１ｄは、インサート部品４１に設けられ、貫通孔４１ｄには樹脂が充填されている。本実施形態の貫通孔４１ｄは、図５に示すように、蓋部４１ｂの溝４１ｆに直線状に４つ配設されている。 The through hole 41d is provided in the insert part 41, and the through hole 41d is filled with resin. As shown in FIG. 5, the four through holes 41d of this embodiment are linearly arranged in the groove 41f of the lid part 41b.
　溝４１ｆは、バルブプレート２６に設けられた吸込み弁板２６ａ（図２参照）にピストン３３が当接することを避けるためにピストンに３３の上面３３ｃに設けられた溝３３ｆ（図３参照）に沿って蓋部４１ｂを凹ませた部分である。そのため、蓋部４１ｂは溝４１ｆで薄くなっており、容易に貫通孔４１ｄを設けることができる。 The groove 41f is formed along a groove 33f (see FIG. 3) provided on the upper surface 33c of the piston 33 to prevent the piston 33 from coming into contact with the suction valve plate 26a (see FIG. 2) provided on the valve plate 26. This is a recessed portion of the lid portion 41b. Therefore, the lid portion 41b is thin with the groove 41f, and the through hole 41d can be easily provided therein.
　ただし、貫通孔４１ｄの配置は、上記に限定されず、多数考えられ得る。例えば、ピストン３３とシリンダ２２との摩擦抵抗によって、ピストン３３から樹脂３６を引き剥がす荷重に対応できるように、溝４１ｆに対して交差する方向に沿って貫通孔４１ｄを配列しても良い。また、貫通孔４１ｄは、少なくとも１つ有ればよい。 However, the arrangement of the through holes 41d is not limited to the above, and many other arrangements can be considered. For example, the through holes 41d may be arranged along a direction intersecting the groove 41f so that the frictional resistance between the piston 33 and the cylinder 22 can accommodate the load that causes the resin 36 to be peeled off from the piston 33. Further, it is sufficient to have at least one through hole 41d.
　貫通孔４１ｄは、インサート部品４１の中心４１ｏから所定距離Ｄ（図５参照）以上に離れていることが好ましい。また、所定距離Ｄは、ピストン３３をインサート成形する時に用いる金型のゲートの半径であることが好ましい。このように略円筒形状のピストン３３を射出成型によって構成する場合、金型のゲートはインサート部品４１の中央の上方に設けることが多く、その直下に貫通孔４１ｄを設けることは、成形欠陥防止の観点から避けた方が良いためである。 It is preferable that the through hole 41d is separated from the center 41o of the insert component 41 by a predetermined distance D or more (see FIG. 5). Moreover, it is preferable that the predetermined distance D is the radius of the gate of the mold used when insert-molding the piston 33. When the substantially cylindrical piston 33 is formed by injection molding in this way, the gate of the mold is often provided above the center of the insert part 41, and providing the through hole 41d directly below it is a good way to prevent molding defects. This is because it is better to avoid it from this point of view.
　また、貫通孔４１ｄはピストン３３の内側（空隙部４１ｅ側）に径が拡大するテーパ部４１ｇ（図４参照）を備えることが好ましい。本実施形態のテーパ部４１ｇは、蓋部４１ｂの下面に設けられた貫通孔４１ｄの開口部が広がった形状（面取り形状）をしている。なお、貫通孔４１ｄは、ピストン３３の内側に径が拡大するテーパ部４１ｇを備えればよく、例えば、図５に示すように、逆側に径が拡大する逆テーパ部を備えても良い。 Furthermore, it is preferable that the through hole 41d includes a tapered portion 41g (see FIG. 4) whose diameter increases on the inside of the piston 33 (on the side of the cavity 41e). The tapered portion 41g of this embodiment has a shape (chamfered shape) in which the opening of the through hole 41d provided on the lower surface of the lid portion 41b is widened. The through hole 41d may include a tapered portion 41g whose diameter increases on the inside of the piston 33, and may also include a reverse tapered portion whose diameter increases on the opposite side, as shown in FIG. 5, for example.
　また、貫通孔４１ｄの内壁に対するテーパ部４１ｇの勾配角θ（図４参照）が、０度より大きくかつ６０度以下であることが好ましい。これにより、エッジ感度が高い樹脂を使用した場合においても、クラックの発生を抑制することができる。 Furthermore, it is preferable that the slope angle θ (see FIG. 4) of the tapered portion 41g with respect to the inner wall of the through hole 41d is greater than 0 degrees and less than 60 degrees. This makes it possible to suppress the occurrence of cracks even when a resin with high edge sensitivity is used.
　図６は、図４のVI－VI断面図である。図６に示すようにインサート部品４１の下部には、下方に開口するネジ穴４１ｈが設けられていることが好ましい。また、コンロッド３２の小端部３２ｂには、ネジ穴４１ｈと重畳する貫通孔３２ｃが設けられていることが好ましい。そして、貫通孔３２ｃにピストン３３に向かって挿入されたネジ３５は、ネジ穴４１ｈに螺合され、ピストン３３をコンロッド３２に固定することが好ましい。 FIG. 6 is a sectional view taken along line VI-VI in FIG. 4. As shown in FIG. 6, it is preferable that the lower part of the insert component 41 is provided with a screw hole 41h that opens downward. Further, it is preferable that the small end portion 32b of the connecting rod 32 is provided with a through hole 32c that overlaps with the screw hole 41h. The screw 35 inserted into the through hole 32c toward the piston 33 is preferably screwed into the screw hole 41h to fix the piston 33 to the connecting rod 32.
　このとき、インサート部品４１の下面４１ｉとコンロッド３２の小端部３２ｂの上面３２ｄとが当接する。インサート部品４１とコンロッド３２は金属により形成されているため、熱膨張率に大きな差がなく、インサート部品４１のネジ穴４１ｈに螺合するネジ３５が圧縮室２２ｂから伝わる圧縮熱によって緩むことを抑制できる。 At this time, the lower surface 41i of the insert part 41 and the upper surface 32d of the small end 32b of the connecting rod 32 come into contact. Since the insert part 41 and the connecting rod 32 are made of metal, there is no large difference in coefficient of thermal expansion, and the screw 35 screwed into the screw hole 41h of the insert part 41 is prevented from loosening due to compression heat transmitted from the compression chamber 22b. can.
　また、コンロッド３２の小端部３２ｂには、上側に開口する凹部３２ｆが設けられていることが好ましい。また、ピストン３３をコンロッド３２に固定することにより凹部３２ｆは、インサート部品４１に設けられた下側に開口する空隙部４１ｅと連通することが好ましい。これにより、ピストン３３とコンロッド３２の小端部３２ｂの間には、中空部３７が形成されていることが好ましい。 Furthermore, it is preferable that the small end 32b of the connecting rod 32 is provided with a recess 32f that opens upward. Further, by fixing the piston 33 to the connecting rod 32, the recess 32f preferably communicates with a cavity 41e provided in the insert component 41 and opening on the lower side. As a result, it is preferable that a hollow portion 37 is formed between the piston 33 and the small end portion 32b of the connecting rod 32.
　［効果］
　本実施形態に係る圧縮機１０のピストン３３は、少なくともシリンダ２２の内周壁２２ａに接触する面３３ａと圧縮室２２ｂ側の面３３ｃとを構成する樹脂３６の内部に埋め込まれたインサート部品４１に設けられ、樹脂３６が充填された貫通孔４１ｄを備える。 [effect]
The piston 33 of the compressor 10 according to the present embodiment is provided in an insert part 41 embedded in the resin 36 that constitutes at least a surface 33a that contacts the inner circumferential wall 22a of the cylinder 22 and a surface 33c on the compression chamber 22b side. A through hole 41d filled with resin 36 is provided.
　そのため、インサート部品４１の圧縮室２２ｂ側を覆う樹脂３６は、インサート部品４１に設けられた貫通孔４１ｄに充填された樹脂３６によってインサート部品４１に結合される。 Therefore, the resin 36 that covers the compression chamber 22b side of the insert component 41 is bonded to the insert component 41 by the resin 36 that fills the through hole 41d provided in the insert component 41.
　これにより、本実施形態に係る圧縮機１０のピストン３３は、インサート部品４１の圧縮室２２ｂ側を覆う樹脂３６が圧縮室２２ｂから伝わる圧縮熱によって熱膨張した場合でも、その変形を抑制することができる。 Thereby, even if the resin 36 covering the compression chamber 22b side of the insert part 41 thermally expands due to the compression heat transmitted from the compression chamber 22b, the piston 33 of the compressor 10 according to the present embodiment can suppress its deformation. can.
　したがって、インサート部品４１と樹脂３６との熱膨張率の差によってインサート部品４１の圧縮室２２ｂ側を覆う樹脂３６がインサート部品４１から剥がれ、樹脂３６の強度が低下し樹脂３６に亀裂が生じることを抑制できる。 Therefore, it is possible to prevent the resin 36 covering the compression chamber 22b side of the insert part 41 from peeling off from the insert part 41 due to the difference in coefficient of thermal expansion between the insert part 41 and the resin 36, reducing the strength of the resin 36 and causing cracks in the resin 36. It can be suppressed.
　また、本実施形態に係る圧縮機１０のピストン３３では、インサート部品４１に設けられた貫通孔４１ｄがピストン３３の内側（空隙部４１ｅ側）に径が拡大するテーパ部４１ｇを備えるので、貫通孔４１ｄに充填された樹脂３６はピストン３３の外側に移動できない。そのため、本実施形態に係る圧縮機１０のピストン３３は、インサート部品４１を覆う樹脂３６がインサート部品４１から剥がれることをさらに抑制できる。 In addition, in the piston 33 of the compressor 10 according to the present embodiment, the through hole 41d provided in the insert component 41 is provided with the tapered portion 41g whose diameter increases on the inside of the piston 33 (on the side of the cavity 41e). The resin 36 filled in 41d cannot move to the outside of the piston 33. Therefore, the piston 33 of the compressor 10 according to the present embodiment can further suppress peeling of the resin 36 covering the insert component 41 from the insert component 41.
　本実施形態に係る圧縮機１０のピストン３３では、貫通孔４１ｄの内壁に対するテーパ部４１ｇの勾配角θが、０度より大きくかつ６０度以下である。そのため、貫通孔４１ｄに充填された樹脂３６のテーパ部３６ａ（図４参照）の勾配角は、貫通孔４１ｄに充填された樹脂３６の側壁に対して０度より大きくかつ６０度以下となる。これにより、樹脂３６のテーパ部３６ａにクラックが発生することを抑制できる。 In the piston 33 of the compressor 10 according to the present embodiment, the slope angle θ of the tapered portion 41g with respect to the inner wall of the through hole 41d is greater than 0 degrees and less than 60 degrees. Therefore, the inclination angle of the tapered portion 36a (see FIG. 4) of the resin 36 filled in the through hole 41d is greater than 0 degrees and less than 60 degrees with respect to the side wall of the resin 36 filled in the through hole 41d. Thereby, it is possible to suppress the occurrence of cracks in the tapered portion 36a of the resin 36.
　また、本実施形態に係る圧縮機１０のピストン３３では、図５に示すように、貫通孔４１ｄがインサート部品４１の中心４１ｏから所定距離Ｄ以上離れている。そのため、ピストン３３をインサート成形する時に、金型に固定されたインサート部品４１の略中央と重畳する位置に設けられるゲートの半径の外側に貫通孔４１ｄを設けることができる。これにより、樹脂３６にひけ等の成形不良が発生することを抑制できる。そのため、圧縮室２２ｂの圧力によって引張応力を樹脂３６に発生させる原因となる樹脂３６とインサート部品４１との間の隙間の発生を抑制でき、樹脂３６の強度低下を抑制できる。 Furthermore, in the piston 33 of the compressor 10 according to the present embodiment, the through hole 41d is separated from the center 41o of the insert component 41 by a predetermined distance D or more, as shown in FIG. Therefore, when insert molding the piston 33, the through hole 41d can be provided outside the radius of the gate provided at a position overlapping the approximate center of the insert component 41 fixed to the mold. Thereby, occurrence of molding defects such as sink marks in the resin 36 can be suppressed. Therefore, it is possible to suppress the generation of a gap between the resin 36 and the insert component 41, which causes tensile stress to be generated in the resin 36 due to the pressure of the compression chamber 22b, and it is possible to suppress a decrease in the strength of the resin 36.
　さらに、本実施形態に係る圧縮機１０では、ピストン３３とコンロッド３２の間に中空部３７が形成されているので、ピストン３３及びコンロッド３２を含む往復動部分の質量を低減できる。そのため、往復動慣性力に起因する圧縮機本体１の振動を抑制できる。 Furthermore, in the compressor 10 according to the present embodiment, since the hollow portion 37 is formed between the piston 33 and the connecting rod 32, the mass of the reciprocating portion including the piston 33 and the connecting rod 32 can be reduced. Therefore, vibration of the compressor main body 1 caused by reciprocating inertia force can be suppressed.
　また、本実施形態に係る圧縮機１０では、ピストン３３をコンロッド３２に固定するネジ３５が、コンロッド３２の貫通孔３２ｃにピストン３３に向かって挿入され、ピストン３３のインサート部品４１に設けたコンロッド３２側に開口するネジ穴４１ｈに螺合し、ピストン３３をコンロッド３２に固定する。これにより、ネジ３５は圧縮室２２ｂ内に露出しないので、ネジ３５が圧縮室２２ｂ内の圧縮熱によって緩むことを抑制できる。 Further, in the compressor 10 according to the present embodiment, the screw 35 that fixes the piston 33 to the connecting rod 32 is inserted into the through hole 32c of the connecting rod 32 toward the piston 33, and the connecting rod 35 provided in the insert part 41 of the piston 33 is inserted into the through hole 32c of the connecting rod 32. The piston 33 is fixed to the connecting rod 32 by screwing into the screw hole 41h that opens on the side. Thereby, the screw 35 is not exposed in the compression chamber 22b, so that the screw 35 can be prevented from loosening due to the compression heat in the compression chamber 22b.
　　（第２実施形態）
　図７は、本発明の第２実施形態に係るピストン２３３の概略側面図である。本実施形態に係るピストン２３３が、第１実施形態に係るピストン３３と異なる点は、インサート部品２４１に設けられた貫通孔２４１ｄの位置である。 (Second embodiment)
FIG. 7 is a schematic side view of a piston 233 according to a second embodiment of the invention. The piston 233 according to this embodiment differs from the piston 33 according to the first embodiment in the position of the through hole 241d provided in the insert component 241.
　即ち、第１実施形態に係るピストン３３では、貫通孔４１ｄが蓋部４１ｂに設けられている。それに対し、本実施形態に係るピストン２３３では、樹脂２３６によって挟み込まれたインサート部品２４１の鍔部２４１ｃに設けられている。 That is, in the piston 33 according to the first embodiment, the through hole 41d is provided in the lid portion 41b. On the other hand, in the piston 233 according to the present embodiment, the piston 233 is provided at the flange 241c of the insert component 241 sandwiched between the resin 236.
　［効果］
　本実施形態に係る圧縮機のピストン２３３では、樹脂２３６によって挟み込まれたインサート部品２４１の鍔部２４１ｃに設けられているので、樹脂２３６によって挟み込まれた鍔部２４１ｃが、樹脂２３６から外れてしまうことを抑制できる。 [effect]
In the piston 233 of the compressor according to the present embodiment, since the piston 233 is provided at the flange 241c of the insert component 241 sandwiched by the resin 236, the flange 241c sandwiched by the resin 236 does not come off from the resin 236. can be suppressed.
　　（第３実施形態）
　図８は、本発明の第３実施形態に係るに係る圧縮機のコンロッド３３２とコンロッド３３２の小端部３３２ｂに固定されたピストン３３の概略側面図である。図９は、本実施形態に係るコンロッド３３２とピストン３３の展開斜視図である。図１０は、図８のＸ－Ｘ断面図である。図１１は、図１０のXI－XI断面図である。 (Third embodiment)
FIG. 8 is a schematic side view of a connecting rod 332 and a piston 33 fixed to a small end 332b of the connecting rod 332 of a compressor according to a third embodiment of the present invention. FIG. 9 is an exploded perspective view of the connecting rod 332 and piston 33 according to this embodiment. FIG. 10 is a sectional view taken along line XX in FIG. FIG. 11 is a sectional view taken along line XI-XI in FIG.
　本実施形態に係るコンロッド３３２が、第１実施形態に係るコンロッド３２と異なる点は、中空部３７の内外を連通する連通孔（第１連通孔３３２ｇ，第２連通孔３３２ｈ）を備える点である。 The connecting rod 332 according to this embodiment differs from the connecting rod 32 according to the first embodiment in that it includes communication holes (first communication hole 332g, second communication hole 332h) that communicate the inside and outside of the hollow part 37. .
　第１連通孔３３２ｇは、小端部３３２ｂの上部に設けられた径方向に延伸する溝３３２ｉとピストン３３の下端３３ｅとによって挟まれ、中空部３７の内外を連通する連通孔で、シリンダ２２の内周壁２２ａ（図２参照）側に開口している。 The first communication hole 332g is a communication hole that is sandwiched between the radially extending groove 332i provided at the upper part of the small end portion 332b and the lower end 33e of the piston 33, and communicates between the inside and outside of the hollow portion 37. It opens on the inner peripheral wall 22a (see FIG. 2) side.
　また、第２連通孔３３２ｈは、コンロッド３３２の小端部３３２ｂの下部に設けられ、凹部３３２ｄの底面３３２ｊを貫通して中空部３７の内外を連通する連通孔で、クランクケース２１側に開口する。 The second communication hole 332h is provided at the lower part of the small end 332b of the connecting rod 332, passes through the bottom surface 332j of the recess 332d, communicates between the inside and outside of the hollow portion 37, and opens toward the crankcase 21 side. .
　［効果］
　本実施形態に係る圧縮機では、中空部３７の内外を連通する連通孔（第１連通孔３３２ｇ，第２連通孔３３２ｈ）を備えるので、中空部３７内に溜まった熱を中空部３７外に放出することができる。 [effect]
The compressor according to this embodiment includes communication holes (first communication hole 332g, second communication hole 332h) that communicate the inside and outside of the hollow part 37, so that the heat accumulated in the hollow part 37 is transferred to the outside of the hollow part 37. can be released.
　また、本実施形態に係る圧縮機は、連通孔（第１連通孔３３２ｇ，第２連通孔３３２ｈ）が２つ以上設けられ、連通孔のうちの少なくとも１つ（第１連通孔３３２ｇ）がシリンダ２２の内周壁２２ａ側に開口し、他の少なくとも１つ（第２連通孔３３２ｈ）がクランクケース２１側に開口している。 Further, the compressor according to the present embodiment is provided with two or more communication holes (first communication hole 332g, second communication hole 332h), and at least one of the communication holes (first communication hole 332g) is connected to the cylinder. 22, and at least one other (second communication hole 332h) opens toward the crankcase 21 side.
　これにより、ピストン３３がクランクケース２１側に移動したときに、図１２に示すように、流体がクランクケース２１側に開口する第２連通孔３３２ｈから中空部３７内に流入し、シリンダ２２の内周壁２２ａ側に開口する第１連通孔３３２ｇから中空部３７外に放出されるので、冷却効果を高めることができる。 As a result, when the piston 33 moves toward the crankcase 21 side, as shown in FIG. Since the air is discharged to the outside of the hollow portion 37 from the first communication hole 332g that opens toward the peripheral wall 22a, the cooling effect can be enhanced.
　なお、クランクケース２１は呼吸フィルタを介して外気を呼吸しているため、中空部３７内には外気温相当の冷却風を供給でき、冷却効率をさらに向上させることができる。 Incidentally, since the crankcase 21 breathes outside air through the breathing filter, cooling air equivalent to the outside temperature can be supplied into the hollow portion 37, and cooling efficiency can be further improved.
　また、この連通孔の個数や方向は、取り得る開口面積や強度の関係から、他にもいくつものパターンが考えられる。しかし、中空部３７の内部に対して積極的に空気を流すことを考慮した場合、この連通孔は、２つ以上を、互いに異なる方向に向けて設けることが望ましい。 In addition, many other patterns can be considered for the number and direction of the communicating holes, depending on the possible opening area and strength. However, in consideration of actively flowing air into the interior of the hollow portion 37, it is desirable to provide two or more communication holes facing in different directions.
　　（第４実施形態）
　図１３は、本発明の第４実施形態に係るインサート部品４４１の背面斜視図である。本実施形態に係るインサート部品４４１が、第１実施形態に係るインサート部品４１と異なる点は、インサート部品４４１のコンロッド３２の側の面（インサート部品４４１の蓋部４４１ｂの下面４４１ｈ）に、放熱フィン４４１ｊを有する点である。 (Fourth embodiment)
FIG. 13 is a rear perspective view of an insert component 441 according to a fourth embodiment of the present invention. The insert component 441 according to the present embodiment is different from the insert component 41 according to the first embodiment in that a radiation fin is provided on the surface of the insert component 441 on the connecting rod 32 side (the lower surface 441h of the lid portion 441b of the insert component 441). 441j.
　本実施形態の放熱フィン４４１ｊは、インサート部品４４１の蓋部４４１ｂの下面４４１ｈからコンロッド３２の側に突出され、インサート部品４４１の円筒部４４１ａの内壁４４１ｋに結合させることで、強度が高くなっている。また、放熱フィン４４１ｊは、貫通孔４４１ｄを避けて設けることが好ましい。 The radiation fins 441j of this embodiment are protruded from the lower surface 441h of the lid portion 441b of the insert component 441 toward the connecting rod 32, and are bonded to the inner wall 441k of the cylindrical portion 441a of the insert component 441, thereby increasing the strength. . Moreover, it is preferable that the radiation fins 441j are provided avoiding the through holes 441d.
　［効果］
　本実施形態に係るインサート部品４４１は、コンロッド３２の側の面（下面４４１ｈ）に、放熱フィン４４１ｊを有する。そのため、インサート部品４４１を効率よく冷却することができ、インサート部品４４１の熱膨張を軽減し、インサート部品４４１の圧縮室２２ｂ側を覆う樹脂３６の強度低下をさらに抑制できる。 [effect]
The insert component 441 according to this embodiment has a radiation fin 441j on the surface (lower surface 441h) on the connecting rod 32 side. Therefore, the insert component 441 can be efficiently cooled, the thermal expansion of the insert component 441 can be reduced, and a decrease in the strength of the resin 36 covering the compression chamber 22b side of the insert component 441 can be further suppressed.
　なお、本発明は上記した実施形態に限定されるものではなく、様々な変形例が含まれる。例えば、上述した実施形態は本発明を分かりやすく説明するために詳細に説明したものであり、必ずしも説明した全ての構成を備えるものに限定されるものではない。また、ある実施形態の構成の一部を他の実施形態の構成に置き換えることが可能であり、また、ある実施形態の構成に他の実施形態の構成を加えることも可能である。また、各実施形態の構成の一部について、他の構成の追加・削除・置換をすることが可能である。 Note that the present invention is not limited to the embodiments described above, and includes various modifications. For example, the embodiments described above are described in detail to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to having all the configurations described. Furthermore, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. Furthermore, it is possible to add, delete, or replace some of the configurations of each embodiment with other configurations.
　１…圧縮機本体、１０…圧縮機、２１…クランクケース、２２…シリンダ、２２ａ…内周壁、２２ｂ…圧縮室、３２，３３２…コンロッド、３２ｃ…貫通孔、３３，２３３…ピストン、３５…ネジ、３６，２３６…樹脂、３６ａ…テーパ部、３７…中空部、４１，２４１，４４１…インサート部品、４１ａ…円筒部、４１ｂ，４４１ｂ…蓋部、４１ｃ，２４１ｃ…鍔部、４１ｄ，２４１ｄ，４４１ｄ…貫通孔、４１ｅ…空隙部、４１ｇ…テーパ部、４１ｈ…ネジ穴、４１ｏ…中心、３３２ｇ…第１連通孔、３３２ｈ…第２連通孔、４４１ｊ…放熱フィン DESCRIPTION OF SYMBOLS 1... Compressor main body, 10... Compressor, 21... Crank case, 22... Cylinder, 22a... Inner peripheral wall, 22b... Compression chamber, 32, 332... Connecting rod, 32c... Through hole, 33, 233... Piston, 35... Screw , 36,236... Resin, 36a... Tapered part, 37... Hollow part, 41,241,441... Insert part, 41a... Cylindrical part, 41b, 441b... Lid part, 41c, 241c... Flange part, 41d, 241d, 441d ...Through hole, 41e...Gap, 41g...Tapered part, 41h...Screw hole, 41o...Center, 332g...First communication hole, 332h...Second communication hole, 441j...Radiation fin

Claims (10)

  1. 　コンロッドに支持されたピストンがシリンダ内を揺動しながら往復動する圧縮機であって、
    　前記ピストンは、
    　少なくとも前記シリンダの内周壁に接触する面と圧縮室側の面とを構成する樹脂と、
    　前記樹脂の内部に埋め込まれたインサート部品と、
    　前記インサート部品に設けられ、前記樹脂が充填された貫通孔とを備えることを特徴とする圧縮機。     A compressor in which a piston supported by a connecting rod reciprocates while swinging within a cylinder,
    The piston is
    a resin forming at least a surface that contacts the inner circumferential wall of the cylinder and a surface on the compression chamber side;
    an insert part embedded inside the resin;
    A compressor comprising: a through hole provided in the insert part and filled with the resin.
  2. 　請求項１に記載の圧縮機であって、
    　前記貫通孔は、前記ピストンの内側に径が拡大するテーパ部を備えることを特徴とする圧縮機。     The compressor according to claim 1,
    The compressor, wherein the through hole includes a tapered portion whose diameter increases toward the inside of the piston.
  3. 　請求項２に記載の圧縮機であって、
    　前記貫通孔の内壁に対する前記テーパ部の勾配角が、０度より大きくかつ６０度以下であることを特徴とする圧縮機。     The compressor according to claim 2,
    A compressor characterized in that a slope angle of the tapered portion with respect to an inner wall of the through hole is greater than 0 degrees and less than 60 degrees.
  4. 　請求項１に記載の圧縮機であって、
    　前記貫通孔が前記インサート部品の中心から所定距離以上離れていることを特徴とする圧縮機。     The compressor according to claim 1,
    A compressor characterized in that the through hole is separated from the center of the insert part by a predetermined distance or more.
  5. 　請求項１に記載の圧縮機において、
    　前記ピストンと前記コンロッドとの間に中空部が形成されていることを特徴とする圧縮機。     The compressor according to claim 1,
    A compressor characterized in that a hollow portion is formed between the piston and the connecting rod.
  6. 　請求項５に記載の圧縮機において、
    　前記中空部の内外を連通する連通孔を備えることを特徴とする圧縮機。     The compressor according to claim 5,
    A compressor comprising a communication hole that communicates between the inside and outside of the hollow part.
  7. 　請求項６に記載の圧縮機において、
    　前記連通孔は、２つ以上設けられ、
    　前記連通孔のうちの少なくとも１つがクランクケース側に開口し、他の少なくとも１つが前記シリンダの側壁側に開口していることを特徴とする圧縮機。     The compressor according to claim 6,
    Two or more communicating holes are provided,
    A compressor characterized in that at least one of the communication holes opens toward the crankcase, and at least one of the other communication holes opens toward the side wall of the cylinder.
  8. 　請求項６に記載の圧縮機において、
    　前記インサート部品の前記コンロッドの側の面に、放熱フィンを有することを特徴とする圧縮機。     The compressor according to claim 6,
    A compressor characterized in that a radiation fin is provided on a surface of the insert part on a side of the connecting rod.
  9. 　請求項１に記載の圧縮機であって、
    　前記貫通孔は、前記樹脂によって挟み込まれた前記インサート部品の鍔部に設けられていることを特徴とする圧縮機。     The compressor according to claim 1,
    A compressor characterized in that the through hole is provided in a flange of the insert component sandwiched between the resin.
  10. 　請求項１に記載の圧縮機において、
    　前記インサート部品にはネジ穴が設けられ、
    　前記コンロッドには前記ネジ穴と重畳する貫通孔が設けられ、
    　前記貫通孔に前記ピストンに向かって挿入されたネジが、前記ネジ穴と螺合され、前記ピストンを前記コンロッドに固定することを特徴とする圧縮機。     The compressor according to claim 1,
    The insert part is provided with a screw hole,
    The connecting rod is provided with a through hole that overlaps with the screw hole,
    A compressor characterized in that a screw inserted into the through hole toward the piston is screwed into the screw hole to fix the piston to the connecting rod.
PCT/JP2023/020890 2022-09-02 2023-06-05 Compressor WO2024047989A1 (en)

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JP2022-139934 2022-09-02
JP2022139934A JP2024035464A (en) 2022-09-02 2022-09-02 compressor

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5239071A (en) * 1975-09-23 1977-03-26 Akebono Brake Ind Co Ltd Improved piston in a liquid pressure
JPS60118825U (en) * 1984-01-19 1985-08-10 オムロン株式会社 push button switch
JPS60184768A (en) * 1984-02-07 1985-09-20 フエスト　カ−ゲ− Piston
JPH0710615U (en) * 1993-07-28 1995-02-14 エヌティエヌ株式会社 Synthetic resin piston for compressor
JP2005133696A (en) * 2003-10-31 2005-05-26 Anest Iwata Corp Oilless reciprocating fluid machine
WO2022158111A1 (en) * 2021-01-20 2022-07-28 株式会社日立産機システム Compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5239071A (en) * 1975-09-23 1977-03-26 Akebono Brake Ind Co Ltd Improved piston in a liquid pressure
JPS60118825U (en) * 1984-01-19 1985-08-10 オムロン株式会社 push button switch
JPS60184768A (en) * 1984-02-07 1985-09-20 フエスト　カ−ゲ− Piston
JPH0710615U (en) * 1993-07-28 1995-02-14 エヌティエヌ株式会社 Synthetic resin piston for compressor
JP2005133696A (en) * 2003-10-31 2005-05-26 Anest Iwata Corp Oilless reciprocating fluid machine
WO2022158111A1 (en) * 2021-01-20 2022-07-28 株式会社日立産機システム Compressor

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