WO2015156144A1 - Compressor - Google Patents
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- WO2015156144A1 WO2015156144A1 PCT/JP2015/059534 JP2015059534W WO2015156144A1 WO 2015156144 A1 WO2015156144 A1 WO 2015156144A1 JP 2015059534 W JP2015059534 W JP 2015059534W WO 2015156144 A1 WO2015156144 A1 WO 2015156144A1
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- valve
- seat plate
- valve seat
- port
- compressor
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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
- F04B39/10—Adaptations or arrangements of distribution members
Definitions
- the present invention relates to a compressor.
- Patent Document 1 JP 2007-146761
- an annular valve seat surface surrounding the discharge hole is formed on the valve plate, an annular seal surface surrounding the annular valve seat surface is formed on the valve plate, and the annular valve seat surface is on the cylinder bore side relative to the annular seal surface.
- the shape of the annular valve seat surface surrounding the discharge hole of the reciprocating compressor of Patent Document 1 and the annular seal surface surrounding the annular valve seat surface is constant regardless of the circumferential position.
- the pressure difference applied to the valve increases, and the amount of deformation of the valve increases between the open end side and the fixed end side of the valve.
- the discharge hole of the reciprocating compressor of Patent Document 1 is not shaped to follow the deformation of the valve, the sealing performance was lowered.
- the reciprocating compressor of Patent Document 1 cannot improve the compression efficiency because the compressed air flows backward from the discharge chamber side of the cylinder to the compression chamber side particularly when trying to obtain high-pressure compressed air. It was.
- an object of the present invention is to provide a compressor that improves the sealing performance between a valve and a discharge (suction) port, suppresses the backflow of compressed air, and improves the compression efficiency.
- the present invention provides a reciprocating compressor in which a motor compresses fluid by driving a piston, and a valve seat plate provided with a port through which fluid passes as the piston reciprocates;
- the valve seat plate is provided with a valve that opens and closes the port, and an inclined surface that is lowered toward the center of the port is formed on a surface of the valve seat plate that contacts the valve.
- the present invention it is possible to provide a compressor that improves the sealing performance between the valve and the discharge (suction) port, suppresses the backflow of compressed air, and improves the compression efficiency.
- Sectional drawing (top dead center) of the compression part of the compressor concerning the Example of this invention Sectional drawing (bottom dead center) of the compression part of the compressor concerning the Example of this invention Detailed view of valve seat plate and valve of compressor according to embodiment of the present invention
- Sectional drawing of the compressor concerning the Example of this invention Detailed view of valve seat plate and valve of compressor according to modification of the present invention
- the piston 21 provided in the cylinder 11 so as to be able to reciprocate is constituted by a disk-like retainer 24 fastened to a connecting rod 22 by a bolt 23.
- the cylinder 11 is connected to the crankcase 1.
- the crankcase 1 accommodates a drive source such as a motor, and the piston 21 is connected to a rotating shaft 2 of the motor via an eccentric shaft 3 and a bearing 4.
- the motor is driven, the rotary shaft 2 rotates, and the rotary motion of the rotary shaft 2 is converted into the eccentric motion of the eccentric shaft 3 via the bearing 4.
- the piston 21 connected to the eccentric shaft 3 reciprocates while swinging in the cylinder 11.
- the piston 21 compresses a fluid such as air by reciprocating while swinging in the cylinder 11.
- the lip ring 25 provided on the outer peripheral side of the swing piston 21 is formed in a ring shape using a resin material. Further, the lip ring 25 is sandwiched between the connecting rod 22 and the retainer 24 and is fixed in a state of being fastened by the bolt 23. Further, the lip ring 25 is in sliding contact with the inner peripheral surface of the cylinder 11 with a tightening margin. The lip ring 25 expands and contracts following the swing of the swing piston 21 and seals between the piston 21 and the cylinder 11.
- valve seat plate 14 fixed between the cylinder 11 and the cylinder head 12 is provided with a discharge port 17. Further, a valve 18 that opens and closes the discharge port due to a pressure difference is fixed to the valve seat plate 14 by a bolt 19.
- valve 18 contacts the valve seat plate 14 and the discharge port 17 is closed.
- the pressure inside the cylinder 11 rises and the pressure difference between the upper and lower sides of the valve 18 increases, the valve 18 is pushed up and the valve seat plate 14 is raised.
- the discharge port 17 is opened. At this time, air is discharged from the compression chamber 7 to the discharge chamber 6, and the air is compressed.
- the valve 18 opens and closes the discharge port, and the air sucked in the suction process is discharged from the cylinder to the tank connected to the outside in the discharge process, thereby compressing the air.
- valve seat plate in the present embodiment will be described with reference to FIG.
- the pressure on the discharge chamber 6 side of the valve 18 (the upper side when the valve 18 is placed on the valve seat plate 14) is high, and the pressure on the compression chamber 7 side (the valve 18 on the valve seat plate 14).
- the pressure on the lower side is low, the pressure difference applied to the valve 18 becomes large, and the valve 18 is deformed by strongly contacting the valve seat plate 14.
- the valve seat plate 14 is not formed in a shape considering the deformation of the valve 18, a gap is formed between the valve 18 and the valve seat plate 14, and the sealing performance of the discharge port 17 is lowered.
- the valve 18 is a fixed end with one end fixed by a bolt 19 and the other end is an open end.
- the deformation of the valve 18 around the discharge port 17 varies depending on the circumferential direction of the discharge port 17.
- the deformation angle ⁇ on the open end side 18a of the valve 18 and the deformation angle ⁇ on the fixed end side 18b have a relationship of ⁇ > ⁇ . That is, the closer to the open end, the larger the deformation angle, and the closer to the fixed end, the smaller the deformation angle.
- the inclined portion 14a is provided on the surface of the valve seat plate 14 on the side in contact with the valve 18 to form an inclined surface.
- the valve 18 is arranged so as to be above the valve seat plate 14, the inclined surface is formed so as to become lower as it approaches the discharge port 17.
- the inclined surface is not formed as a chamfer at the time of forming the discharge port 17, but is formed to improve the sealing performance by contacting the valve 18 and the valve seat plate 14 with a width as described above. Although it depends on the dimensions of the valve 18 and the valve seat plate, the inclination angle of the inclined surface is 10 ° or less. Further, in order to further improve the sealing performance, the inclination angle of the inclined surface is made different depending on the position in the circumferential direction corresponding to the deformation of the valve 18. Specifically, the inclined portion 14a of the valve seat plate 14 has a shape in which the inclination angle on the open end side of the valve 18 is large ( ⁇ ) and the inclination angle on the fixed end side is small ( ⁇ ). That is, the closer to the open end, the greater the inclination angle, and the closer to the fixed end, the smaller the inclination angle.
- the ratio h / r is h / r. r differs depending on the position in the circumferential direction. At this time, h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
- the inclination angles ( ⁇ ) and ( ⁇ ) and the ratio h / r of the inclined portion are preferably determined by taking into consideration the deformation amount and sealing performance of the valve 18 by simulation and measurement.
- the inclination angle of the inclined portion and the ratio h / r may be a constant value regardless of the position in the circumferential direction, and the valve 18 and the valve seat plate 14 are in contact with each other with a width, so that the sealing performance can be improved. .
- valve seat plate 14 corresponds to the deformation of the valve 18, the valve 18 is not deformed such as minute undulations or wrinkles in the circumferential direction, and the valve 18 and the valve seat shown in FIG.
- the valve 18 and the valve seat plate 14 come into contact with each other with a certain width over the entire circumference as in the surface pressure distribution of the contact portion with the plate 14 (becomes surface contact), and the clearance between the valve seat plate 14 and the valve 18 is reduced. Can be small. Therefore, in the suction process, the backflow from the discharge chamber 6 to the compression chamber 6 can be effectively prevented, and the discharge performance can be improved.
- the deformation (swell) of the fixed end side portion 18c of the valve 18 is reduced, and the stress generated in this portion can be reduced. For this reason, the thickness of the valve 18 can be reduced, the sound of the valve 18 hitting the valve seat plate 14 can be suppressed, and the noise during operation of the compressor can be suppressed.
- the inclined portion 14a of the valve seat plate 14 is configured to be smoothly connected to the circumferential direction. Since the amount of deformation of the valve 18 continuously changes in the circumferential direction, the inclination angle of the inclined portion 14a of the valve seat plate 14 and the ratio h / r of h and r also change correspondingly. By doing so, the backflow from the discharge chamber 6 to the compression chamber 6 can be more effectively prevented, and the discharge performance can be improved.
- valve seat plate 14 on the discharge port 17 side has been described.
- the same configuration is applied to the shape of the valve seat plate on the suction port side, thereby improving the sealing performance between the valve and the suction port. Compression performance can be improved.
- the flat inclined portion 14a is formed on the valve seat plate 14.
- the inclined portion 14a may be curved instead of flat.
- the ratio h / r is h / r. r differs depending on the position in the circumferential direction. h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
- the inclined portion 14a is formed on the valve seat plate 14, but a stepped portion may be used instead of the inclined portion 14a.
- the valve seat plate 14 is provided with a plurality of step portions 14b, and the difference in height between the radially outer side and the radially inner side viewed from the center of the discharge port 17 (because there are a plurality of steps in FIG. 5).
- the difference in height between the highest and the lowest) is h
- the radial length of the step is r (in FIG. 5, there are multiple steps, so the difference between the closest and farthest to the port)
- H / r ratio h / r varies depending on the position in the circumferential direction.
- h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
- the stepped portion 14b is provided in a plurality of steps, the stepped corner 14c of the valve 18 and the valve seat plate 14 is in line contact with each other in a circumferential shape, and a plurality of line contacts are formed.
- a plurality of minute gaps can be formed in the leakage passage, backflow (leakage) from the discharge chamber 6 to the compression chamber 6 can be effectively prevented by the labyrinth effect and the discharge performance can be improved.
- a combination of an inclined portion and a step portion may be formed on the valve seat plate.
- the sealing performance is improved by reducing the gap between the valve 18 and the valve seat plate 14. It is possible to improve the discharge performance by effectively preventing the backflow of compressed air.
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- General Engineering & Computer Science (AREA)
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Abstract
The purpose of the present invention is to provide a compressor in which sealing of a valve and a discharge (intake) port is improved, compressed air backflow is minimized, and compression efficiency is improved. To achieve this purpose, the present invention provides a compressor for compressing a fluid in the driving of a motor, wherein the compressor is characterized in being provided with a valve seat plate provided with a port through which the fluid passes, and a valve provided to the valve seat plate, the valve opening and closing the port, an inclined surface that lowers toward the center of the port being formed in the surface of the valve seat plate that is in contact with the valve.
Description
本発明は、圧縮機に関するものである。
The present invention relates to a compressor.
本技術分野の背景技術として、特開２００７－１４６７６１号公報（特許文献１）がある。
There is JP 2007-146761 (Patent Document 1) as background art in this technical field.
特許文献１には、「吐出孔を取り囲む環状弁座面が弁板に形成され、環状弁座面を取り囲む環状シール面が弁板に形成され、環状弁座面は環状シール面よりもシリンダボア側へオフセットしており、吐出室内圧とシリンダボア内圧との差圧が零の時に吐出弁は環状シール面に当接し、前記差圧が正の所定値に達すると吐出弁は弾性変形して環状弁座面に当接する」往復動圧縮機が記載されている。
In Patent Document 1, an annular valve seat surface surrounding the discharge hole is formed on the valve plate, an annular seal surface surrounding the annular valve seat surface is formed on the valve plate, and the annular valve seat surface is on the cylinder bore side relative to the annular seal surface. When the differential pressure between the discharge chamber pressure and the cylinder bore pressure is zero, the discharge valve contacts the annular seal surface, and when the differential pressure reaches a positive predetermined value, the discharge valve is elastically deformed and the annular valve A reciprocating compressor that abuts the seat is described.
特許文献１の往復動圧縮機の吐出孔を取り囲む環状弁座面と環状弁座面を取り囲む環状シール面の形状は周方向の位置によらず一定である。ここで、高圧の圧縮空気を得ようとすると、弁にかかる圧力差が大きくなり、弁の開放端側と固定端側とで弁の変形量が大きくなる。このとき特許文献１の往復動圧縮機の吐出孔は弁の変形に追従した形状になっていないため、シール性が低下していた。このため、特許文献１の往復動圧縮機は、特に高圧の圧縮空気を得ようとしたときに圧縮空気がシリンダの吐出室側から圧縮室側に逆流して圧縮効率を向上させることができなかった。
The shape of the annular valve seat surface surrounding the discharge hole of the reciprocating compressor of Patent Document 1 and the annular seal surface surrounding the annular valve seat surface is constant regardless of the circumferential position. Here, when trying to obtain high-pressure compressed air, the pressure difference applied to the valve increases, and the amount of deformation of the valve increases between the open end side and the fixed end side of the valve. At this time, since the discharge hole of the reciprocating compressor of Patent Document 1 is not shaped to follow the deformation of the valve, the sealing performance was lowered. For this reason, the reciprocating compressor of Patent Document 1 cannot improve the compression efficiency because the compressed air flows backward from the discharge chamber side of the cylinder to the compression chamber side particularly when trying to obtain high-pressure compressed air. It was.
上記問題点に鑑み、本発明は、弁と吐出（吸入）ポートとのシール性を向上させ、圧縮空気の逆流を抑制し、圧縮効率を向上させた圧縮機を提供することを目的とする。
In view of the above problems, an object of the present invention is to provide a compressor that improves the sealing performance between a valve and a discharge (suction) port, suppresses the backflow of compressed air, and improves the compression efficiency.
上記課題を解決するため、本発明は、モータがピストンを駆動することにより流体を圧縮する往復動圧縮機において、前記ピストンの往復動に伴い流体が通過するポートが設けられた弁座板と、前記弁座板に設けられ、前記ポートを開閉する弁とを備え、前記弁座板の前記弁と接触する側の面に、前記ポートの中心部に向けて低くなるような傾斜面を形成したことを特徴とする圧縮機を提供する。
In order to solve the above problems, the present invention provides a reciprocating compressor in which a motor compresses fluid by driving a piston, and a valve seat plate provided with a port through which fluid passes as the piston reciprocates; The valve seat plate is provided with a valve that opens and closes the port, and an inclined surface that is lowered toward the center of the port is formed on a surface of the valve seat plate that contacts the valve. A compressor characterized by the above is provided.
本発明によれば、弁と吐出（吸入）ポートとのシール性を向上させ、圧縮空気の逆流を抑制し、圧縮効率を向上させた圧縮機を提供することができる。
According to the present invention, it is possible to provide a compressor that improves the sealing performance between the valve and the discharge (suction) port, suppresses the backflow of compressed air, and improves the compression efficiency.
以下、本発明に係る圧縮機の実施例を、図１－図５を用いて説明する。
Hereinafter, an embodiment of a compressor according to the present invention will be described with reference to FIGS.
図４を用いて本実施例にかかる往復動圧縮機の全体構造について説明する。
The overall structure of the reciprocating compressor according to this embodiment will be described with reference to FIG.
シリンダ１１内に往復動可能に設けられたピストン２１は、コネクティングロッド２２にボルト２３によって締結された円板状のリテーナ２４とによって構成されている。
The piston 21 provided in the cylinder 11 so as to be able to reciprocate is constituted by a disk-like retainer 24 fastened to a connecting rod 22 by a bolt 23.
シリンダ１１はクランクケース１に接続される。クランクケース１は、モータ等の駆動源を収容するもので、ピストン２１はモータの回転軸２に偏心軸３、軸受４を介して接続されている。モータが駆動すると、回転軸２が回転し、軸受４を介して回転軸２の回転運動が偏心軸３の偏心運動に変換される。偏心軸３の偏心運動に伴い、偏心軸３に接続されたピストン２１がシリンダ１１内を揺動しつつ往復動する。ピストン２１は、シリンダ１１内を揺動しつつ往復動することにより、空気などの流体を圧縮する。
The cylinder 11 is connected to the crankcase 1. The crankcase 1 accommodates a drive source such as a motor, and the piston 21 is connected to a rotating shaft 2 of the motor via an eccentric shaft 3 and a bearing 4. When the motor is driven, the rotary shaft 2 rotates, and the rotary motion of the rotary shaft 2 is converted into the eccentric motion of the eccentric shaft 3 via the bearing 4. Along with the eccentric motion of the eccentric shaft 3, the piston 21 connected to the eccentric shaft 3 reciprocates while swinging in the cylinder 11. The piston 21 compresses a fluid such as air by reciprocating while swinging in the cylinder 11.
揺動ピストン２１の外周側に設けられたリップリング２５は、樹脂材料を用いてリング状に形成されている。また、リップリング２５は、コネクティングロッド２２とリテーナ２４に挟まれて、ボルト２３によって締結された状態で固定されている。さらに、リップリング２５はシリンダ１１の内周面に締代をもって摺接している。リップリング２５は、揺動ピストン２１の揺動に追従して拡縮径し、ピストン２１とシリンダ１１との間をシールする。
The lip ring 25 provided on the outer peripheral side of the swing piston 21 is formed in a ring shape using a resin material. Further, the lip ring 25 is sandwiched between the connecting rod 22 and the retainer 24 and is fixed in a state of being fastened by the bolt 23. Further, the lip ring 25 is in sliding contact with the inner peripheral surface of the cylinder 11 with a tightening margin. The lip ring 25 expands and contracts following the swing of the swing piston 21 and seals between the piston 21 and the cylinder 11.
シリンダ１１とシリンダヘッド１２の間に固定された弁座板１４には吐出ポート１７が設けられている。また、弁座板１４には圧力差によって吐出ポートを開閉する弁１８がボルト１９によって固定されている。
The valve seat plate 14 fixed between the cylinder 11 and the cylinder head 12 is provided with a discharge port 17. Further, a valve 18 that opens and closes the discharge port due to a pressure difference is fixed to the valve seat plate 14 by a bolt 19.
図１、図２を用いて本実施例における往復度圧縮機の動作について説明する。
The operation of the reciprocating compressor according to this embodiment will be described with reference to FIGS.
通常、弁１８は弁座板１４に接触して吐出ポート１７が閉状態となっている。図１に示すように、圧縮工程においてピストン２１がシリンダ１１内を上昇し、シリンダ１１内部の圧力が上昇して弁１８の上下の圧力差が大きくなると、弁１８が押し上げられて弁座板１４から離れ、吐出ポート１７が開状態となる。このとき、圧縮室７から吐出室６へ空気が吐出され、空気が圧縮される。
Normally, the valve 18 contacts the valve seat plate 14 and the discharge port 17 is closed. As shown in FIG. 1, when the piston 21 rises in the cylinder 11 in the compression process, the pressure inside the cylinder 11 rises and the pressure difference between the upper and lower sides of the valve 18 increases, the valve 18 is pushed up and the valve seat plate 14 is raised. The discharge port 17 is opened. At this time, air is discharged from the compression chamber 7 to the discharge chamber 6, and the air is compressed.
また、図２に示すように、吸込工程においてピストン２１がシリンダ１１内を下降し、シリンダ１１内部の圧力が減少して弁１８の上下の圧力差が小さくなると、弁１８が弁座板１４に押し付けられて、吐出ポート１７が閉状態となる。このようにして、吐出室６から圧縮室７へ空気が逆流しないようにしている。
Further, as shown in FIG. 2, when the piston 21 descends in the cylinder 11 in the suction process and the pressure inside the cylinder 11 decreases and the pressure difference between the upper and lower sides of the valve 18 becomes smaller, the valve 18 moves to the valve seat plate 14. The discharge port 17 is closed by being pressed. In this way, air does not flow backward from the discharge chamber 6 to the compression chamber 7.
ピストン２１の往復動に伴い、弁１８によって吐出ポートが開閉し、吸込工程で吸い込まれた空気が吐出工程でシリンダから外部に接続されたタンクに吐出されることにより、空気が圧縮される。
As the piston 21 reciprocates, the valve 18 opens and closes the discharge port, and the air sucked in the suction process is discharged from the cylinder to the tank connected to the outside in the discharge process, thereby compressing the air.
図３を用いて本実施例おける弁座板の形状について説明する。
The shape of the valve seat plate in the present embodiment will be described with reference to FIG.
例えば、吸込工程時において、弁１８の吐出室６側（弁１８を弁座板１４の上に配置した時の上側）の圧力が高く、圧縮室７側（弁１８を弁座板１４の上に配置した時の下側）の圧力が低い場合において、弁１８にかかる圧力差が大きくなり、弁１８が弁座板１４に強く接触することにより、弁１８が変形する。 このとき、弁１８の変形を考慮した形状に弁座板１４を形成しないと、弁１８と弁座板１４との間に隙間が形成されてしまい、吐出ポート１７のシール性が低下する。
For example, during the suction process, the pressure on the discharge chamber 6 side of the valve 18 (the upper side when the valve 18 is placed on the valve seat plate 14) is high, and the pressure on the compression chamber 7 side (the valve 18 on the valve seat plate 14). When the pressure on the lower side is low, the pressure difference applied to the valve 18 becomes large, and the valve 18 is deformed by strongly contacting the valve seat plate 14. At this time, if the valve seat plate 14 is not formed in a shape considering the deformation of the valve 18, a gap is formed between the valve 18 and the valve seat plate 14, and the sealing performance of the discharge port 17 is lowered.
ここで、弁１８は一方の端をボルト１９で固定された固定端であり、他方の端は開放された開放端である。吐出ポート１７の周辺における弁１８の変形は吐出ポート１７の周方向によって異なる。具体的には、図３に示すように、弁１８の開放端側１８ａの変形角度αと固定端側１８ｂの変形角度βはα ＞ β の関係になる。即ち、開放端に近づけば近づくほど変形角度は大きくなり、固定端に近づけば近づくほど変形角度は小さくなる。
Here, the valve 18 is a fixed end with one end fixed by a bolt 19 and the other end is an open end. The deformation of the valve 18 around the discharge port 17 varies depending on the circumferential direction of the discharge port 17. Specifically, as shown in FIG. 3, the deformation angle α on the open end side 18a of the valve 18 and the deformation angle β on the fixed end side 18b have a relationship of α> β. That is, the closer to the open end, the larger the deformation angle, and the closer to the fixed end, the smaller the deformation angle.
そこで、本実施例では、弁座板１４の弁１８と接触する側の面には傾斜部１４ａが設けて傾斜面を形成した。弁１８が弁座板１４よりも上になるように配置したとき、傾斜面は吐出ポート１７に近づくにつれて低くなるように形成されている。
Therefore, in this embodiment, the inclined portion 14a is provided on the surface of the valve seat plate 14 on the side in contact with the valve 18 to form an inclined surface. When the valve 18 is arranged so as to be above the valve seat plate 14, the inclined surface is formed so as to become lower as it approaches the discharge port 17.
傾斜面は、吐出ポート１７形成時の面取りとして行うものではなく、上記のように、幅を持って弁１８と弁座板１４が接触しシール性を向上させるために形成するものであるため、弁１８と弁座板の寸法等により異なるが、傾斜面の傾斜角は１０°以下で形成される。
さらに、よりシール性を高めるために、弁１８の変形に対応して斜面の傾斜角を周方向の位置により異ならせるようにした。具体的には、弁座板１４の傾斜部１４ａは弁１８の開放端側の傾斜角が大きく（α）、固定端側の傾斜角が小さく（β）なる形状とした。即ち、開放端に近づけば近づくほど傾斜角を大きくなるようにし、固定端に近づけば近づくほど傾斜角を小さくなるようにした。 The inclined surface is not formed as a chamfer at the time of forming thedischarge port 17, but is formed to improve the sealing performance by contacting the valve 18 and the valve seat plate 14 with a width as described above. Although it depends on the dimensions of the valve 18 and the valve seat plate, the inclination angle of the inclined surface is 10 ° or less.
Further, in order to further improve the sealing performance, the inclination angle of the inclined surface is made different depending on the position in the circumferential direction corresponding to the deformation of thevalve 18. Specifically, the inclined portion 14a of the valve seat plate 14 has a shape in which the inclination angle on the open end side of the valve 18 is large (α) and the inclination angle on the fixed end side is small (β). That is, the closer to the open end, the greater the inclination angle, and the closer to the fixed end, the smaller the inclination angle.
さらに、よりシール性を高めるために、弁１８の変形に対応して斜面の傾斜角を周方向の位置により異ならせるようにした。具体的には、弁座板１４の傾斜部１４ａは弁１８の開放端側の傾斜角が大きく（α）、固定端側の傾斜角が小さく（β）なる形状とした。即ち、開放端に近づけば近づくほど傾斜角を大きくなるようにし、固定端に近づけば近づくほど傾斜角を小さくなるようにした。 The inclined surface is not formed as a chamfer at the time of forming the
Further, in order to further improve the sealing performance, the inclination angle of the inclined surface is made different depending on the position in the circumferential direction corresponding to the deformation of the
ここで、傾斜部１４ａの吐出ポート１７の中心から見た径方向外側と径方向内側の高さの差をｈ、傾斜部の径方向長さをｒとしたとき、ｈとｒの比ｈ/ｒは周方向の位置によって異なっている。このとき、ｈ/ｒを弁１８の開放端に近づくほど大きく、固定端に近づくほど小さくなっている。
Here, when the difference in height between the radially outer side and the radially inner side viewed from the center of the discharge port 17 of the inclined portion 14a is h, and the radial length of the inclined portion is r, the ratio h / r is h / r. r differs depending on the position in the circumferential direction. At this time, h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
傾斜部の傾斜角（α）及び（β）や比ｈ/ｒは、望ましくは、シミュレーションや計測により、弁１８の変形量やシール性を考慮してそれぞれ決定する。但し、傾斜部の傾斜角や比ｈ/ｒを周方向の位置に関わらず一定の値としてもよく、幅を持って弁１８と弁座板１４が接触するためシール性の向上が可能である。
The inclination angles (α) and (β) and the ratio h / r of the inclined portion are preferably determined by taking into consideration the deformation amount and sealing performance of the valve 18 by simulation and measurement. However, the inclination angle of the inclined portion and the ratio h / r may be a constant value regardless of the position in the circumferential direction, and the valve 18 and the valve seat plate 14 are in contact with each other with a width, so that the sealing performance can be improved. .
これにより、弁座板１４の形状が弁１８の変形に対応したものとなるため、弁１８に周方向において微小なうねりやしわなどの変形が発生せず、図３に示す弁１８と弁座板１４との接触部の面圧分布のように全周にわたってある幅で弁１８と弁座板１４とが接触するようになり（面接触となり）、弁座板１４と弁１８との隙間を小さくすることができる。そのため、吸込工程において、吐出室６から圧縮室６への逆流を効果的に防止でき、吐出性能を向上させることができる。
Thereby, since the shape of the valve seat plate 14 corresponds to the deformation of the valve 18, the valve 18 is not deformed such as minute undulations or wrinkles in the circumferential direction, and the valve 18 and the valve seat shown in FIG. The valve 18 and the valve seat plate 14 come into contact with each other with a certain width over the entire circumference as in the surface pressure distribution of the contact portion with the plate 14 (becomes surface contact), and the clearance between the valve seat plate 14 and the valve 18 is reduced. Can be small. Therefore, in the suction process, the backflow from the discharge chamber 6 to the compression chamber 6 can be effectively prevented, and the discharge performance can be improved.
また、弁１８の固定端側部分１８ｃの変形（盛り上がり）が小さくなり、この部分に発生する応力を小さくすることができる。このため、弁１８の厚さを薄くするでき、弁１８が弁座板１４を叩く音を小さく抑え、圧縮機運転時の騒音を小さく抑えることが可能となる。
Further, the deformation (swell) of the fixed end side portion 18c of the valve 18 is reduced, and the stress generated in this portion can be reduced. For this reason, the thickness of the valve 18 can be reduced, the sound of the valve 18 hitting the valve seat plate 14 can be suppressed, and the noise during operation of the compressor can be suppressed.
さらに、本実施例では、弁座板１４の傾斜部１４ａは円周方向に対して滑らかにつながるように構成した。弁の１８の変形量は円周方向に対して連続的に変化するため、それに対応して、弁座板１４の傾斜部１４ａの傾斜角とｈとｒの比ｈ/ｒも連続的に変化させることにより、吐出室６から圧縮室６への逆流をより効果的に防止でき、吐出性能を向上させることができる。
Furthermore, in this embodiment, the inclined portion 14a of the valve seat plate 14 is configured to be smoothly connected to the circumferential direction. Since the amount of deformation of the valve 18 continuously changes in the circumferential direction, the inclination angle of the inclined portion 14a of the valve seat plate 14 and the ratio h / r of h and r also change correspondingly. By doing so, the backflow from the discharge chamber 6 to the compression chamber 6 can be more effectively prevented, and the discharge performance can be improved.
本実施例では、吐出ポート１７側の弁座板１４の形状について説明してきたが、吸込ポート側の弁座板の形状についても同様の構成することにより、弁と吸込ポートとのシール性を向上させ、圧縮性能を向上させることできる。
In this embodiment, the shape of the valve seat plate 14 on the discharge port 17 side has been described. However, the same configuration is applied to the shape of the valve seat plate on the suction port side, thereby improving the sealing performance between the valve and the suction port. Compression performance can be improved.
なお、本実施例では、弁座板１４に平面状の傾斜部１４ａを形成したが、傾斜部１４ａは平面状ではなく曲面状であってもよい。このとき、傾斜部１４ａの吐出ポート１７の中心から見た径方向外側と径方向内側の高さの差をｈ、傾斜部の径方向長さをｒとしたとき、ｈとｒの比ｈ/ｒは周方向の位置によって異なっている。ｈ/ｒは弁１８の開放端に近づくほど大きくなり、固定端に近づくほど小さくなるようにする。
In the present embodiment, the flat inclined portion 14a is formed on the valve seat plate 14. However, the inclined portion 14a may be curved instead of flat. At this time, when the difference in height between the radially outer side and the radially inner side viewed from the center of the discharge port 17 of the inclined portion 14a is h, and the radial length of the inclined portion is r, the ratio h / r is h / r. r differs depending on the position in the circumferential direction. h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
また、本実施例では、弁座板１４に傾斜部１４ａを形成したが、傾斜部１４ａに代えて段差部にしてもよい。図５に示すように、弁座板１４に複数の段差部１４ｂを設け、吐出ポート１７の中心から見た径方向外側と径方向内側の高さの差（図５では段差が複数段あるため、最も高いところと低いところの高さの差）をｈ、段差部の径方向長さをｒ（図５では段差が複数段あるため、ポートに最も近いところと遠いところの差）としたとき、ｈとｒの比ｈ/ｒは周方向の位置によって異なっている。ｈ/ｒは弁１８の開放端に近づくほど大きくなり、固定端に近づくほど小さくなるようにする。
In the present embodiment, the inclined portion 14a is formed on the valve seat plate 14, but a stepped portion may be used instead of the inclined portion 14a. As shown in FIG. 5, the valve seat plate 14 is provided with a plurality of step portions 14b, and the difference in height between the radially outer side and the radially inner side viewed from the center of the discharge port 17 (because there are a plurality of steps in FIG. 5). , The difference in height between the highest and the lowest) is h, and the radial length of the step is r (in FIG. 5, there are multiple steps, so the difference between the closest and farthest to the port) , H / r ratio h / r varies depending on the position in the circumferential direction. h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
また、段差部１４ｂが複数段設けてあるため、弁１８と弁座板１４の段差の角部１４ｃが円周状に線接触し、複数の線接触が形成される。これにより、漏れ通路に複数の微小隙間を形成できるため、ラビリンス効果によって吸込工程において、吐出室６から圧縮室６への逆流（漏れ）を効果的に防止でき、吐出性能を向上させることができる。
Further, since the stepped portion 14b is provided in a plurality of steps, the stepped corner 14c of the valve 18 and the valve seat plate 14 is in line contact with each other in a circumferential shape, and a plurality of line contacts are formed. Thereby, since a plurality of minute gaps can be formed in the leakage passage, backflow (leakage) from the discharge chamber 6 to the compression chamber 6 can be effectively prevented by the labyrinth effect and the discharge performance can be improved. .
なお、ｈ/ｒは周方向の位置によらず一定としても複数の線接触が形成されシール性の向上が可能である。
In addition, even if h / r is constant regardless of the position in the circumferential direction, a plurality of line contacts are formed, and the sealing performance can be improved.
また、本実施例では、傾斜部と段差部を組み合わせたものを弁座板に形成してもよい。
In the present embodiment, a combination of an inclined portion and a step portion may be formed on the valve seat plate.
以上より本実施例によれば、弁１８と弁座板１４とが強く接触し、弁１８が変形した場合でも、弁１８と弁座板１４との間の隙間を小さくすることでシール性を向上させ、圧縮空気の逆流を効果的に防止して吐出性能を向上できる。
As described above, according to the present embodiment, even when the valve 18 and the valve seat plate 14 are in strong contact with each other and the valve 18 is deformed, the sealing performance is improved by reducing the gap between the valve 18 and the valve seat plate 14. It is possible to improve the discharge performance by effectively preventing the backflow of compressed air.
これまで説明してきた実施例は、何れも本発明を実施するにあたっての具体化の一例を示したものに過ぎず、これらによって本発明の技術的範囲が限定的に解釈されない。すなわち、本発明はその技術思想、又はその主要な特徴から逸脱することなく、様々な形で実施することができる。
The embodiments described so far are merely examples of implementation in carrying out the present invention, and the technical scope of the present invention is not limitedly interpreted by these embodiments. That is, the present invention can be implemented in various forms without departing from the technical idea or the main features thereof.
１ クランクケース
２ 軸
３ 偏心軸
４ 軸受
５ 錘
６ 吐出室
７ 圧縮室
１１ シリンダ
１２ シリンダヘッド
１４ 弁座板
１４ａ 傾斜部
１７ 吐出ポート
１８ 弁
１８ａ 弁開放端側
１８ｂ 弁固定端側
１９ ボルト
２１ ピストン
２２ コネクティングロッド
２３ ボルト
２４ リテーナ
２５ リップリング
α 弁開放端側変形角度（吐出ポート端傾斜角度）
β 弁固定端側変形角度（吐出ポート端傾斜角度） DESCRIPTION OFSYMBOLS 1 Crankcase 2 Shaft 3 Eccentric shaft 4 Bearing 5 Weight 6 Discharge chamber 7 Compression chamber 11 Cylinder 12 Cylinder head 14 Valve seat board 14a Inclination part 17 Discharge port 18 Valve 18a Valve open end side 18b Valve fixed end side 19 Bolt 21 Piston 22 Connecting rod 23 Bolt 24 Retainer 25 Lip ring α Valve open end side deformation angle (discharge port end tilt angle)
β Valve fixed end side deformation angle (discharge port end tilt angle)
２ 軸
３ 偏心軸
４ 軸受
５ 錘
６ 吐出室
７ 圧縮室
１１ シリンダ
１２ シリンダヘッド
１４ 弁座板
１４ａ 傾斜部
１７ 吐出ポート
１８ 弁
１８ａ 弁開放端側
１８ｂ 弁固定端側
１９ ボルト
２１ ピストン
２２ コネクティングロッド
２３ ボルト
２４ リテーナ
２５ リップリング
α 弁開放端側変形角度（吐出ポート端傾斜角度）
β 弁固定端側変形角度（吐出ポート端傾斜角度） DESCRIPTION OF
β Valve fixed end side deformation angle (discharge port end tilt angle)
Claims (9)
- モータが駆動することにより流体を圧縮する圧縮機において、
前記流体が通過するポートが設けられた弁座板と、
前記弁座板に設けられ、前記ポートを開閉する弁とを備え、
前記弁座板の前記弁と接触する側の面に、前記ポートの中心部に向けて低くなるような傾斜面を形成したことを特徴とする圧縮機。 In a compressor that compresses fluid by driving a motor,
A valve seat plate provided with a port through which the fluid passes;
A valve provided on the valve seat plate for opening and closing the port;
The compressor characterized by forming the inclined surface which becomes low toward the center part of the said port in the surface at the side which contacts the said valve seat plate. - 前記傾斜面の傾斜角を周方向の位置により異ならせることを特徴とする請求項１に記載の圧縮機。 The compressor according to claim 1, wherein an inclination angle of the inclined surface is varied depending on a position in a circumferential direction.
- 前記弁の開放端に近い部分における前記傾斜面の傾斜角を前記開放端から遠い部分における前記傾斜面の傾斜角よりも大きくすることを特徴とする請求項２に記載の圧縮機。 3. The compressor according to claim 2, wherein an inclination angle of the inclined surface in a portion near the open end of the valve is made larger than an inclination angle of the inclined surface in a portion far from the open end.
- 前記傾斜面の傾斜角は連続的に変化することを特徴とする請求項２に記載の圧縮機。 The compressor according to claim 2, wherein the inclination angle of the inclined surface changes continuously.
- モータがピストンを駆動することにより流体を圧縮する往復動圧縮機において、
前記ピストンの往復動に伴い流体が通過するポートが設けられた弁座板と、
前記弁座板に設けられ、前記ポートを開閉する弁とを備え、
前記弁座板の前記弁と接触する側の面に、前記ポートの中心部に向けて低くなるような傾斜部または複数の段差部を形成したことを特徴とする圧縮機。 In a reciprocating compressor in which a motor compresses fluid by driving a piston,
A valve seat plate provided with a port through which fluid passes as the piston reciprocates;
A valve provided on the valve seat plate for opening and closing the port;
The compressor according to claim 1, wherein an inclined portion or a plurality of step portions are formed on a surface of the valve seat plate that comes into contact with the valve so as to become lower toward a center portion of the port. - 前記傾斜部または複数の段差部の径方向の高さの差をｈ、径方向長さをｒとしたとき、ｈ/ｒを周方向位置により異ならせることを特徴とする請求項５に記載の圧縮機。 The difference in height in the radial direction of the inclined part or the plurality of stepped parts is h, and the radial length is r, h / r is made different depending on the circumferential position. Compressor.
- 前記弁の開放端に近い部分における前記傾斜部または前記段差部の径方向の高さの差ｈと径方向長さｒの比ｈ/ｒを前記開放端から遠い部分における前記傾斜部または前記段差部の径方向の高さの差ｈと径方向長さｒの比ｈ/ｒよりも大きくすることを特徴とする請求項６に記載の圧縮機。 The ratio h / r between the radial height difference h and the radial length r of the inclined portion or the stepped portion in the portion near the open end of the valve is the inclined portion or the stepped portion in the portion far from the open end. The compressor according to claim 6, wherein the ratio is larger than a ratio h / r between a radial height difference h and a radial length r.
- 前記傾斜部を平面または曲面により形成することを特徴とする請求項５に記載の圧縮機。 The compressor according to claim 5, wherein the inclined portion is formed by a flat surface or a curved surface.
- 前記傾斜部または前記段差部の径方向の高さの差ｈと径方向長さｒの比ｈ/ｒを連続的に変化することを特徴とする請求項６に記載の圧縮機。 The compressor according to claim 6, wherein a ratio h / r between a radial height difference h and a radial length r of the inclined portion or the stepped portion is continuously changed.
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| JP2007146761A (en) * | 2005-11-28 | 2007-06-14 | Sanden Corp | Reciprocating compressor |
| WO2012043017A1 (en) * | 2010-09-27 | 2012-04-05 | 大豊工業株式会社 | Vane pump |
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| SG30647G (en) * | 1991-01-28 | 1995-09-01 | Sanden Corp | Slant plate type compressor with variable displacement mechanism |
| CN1071002C (en) * | 1994-11-15 | 2001-09-12 | 三电有限公司 | Valved discharge mechanism of fluid displacement apparatus |
| CN1234970C (en) * | 1995-04-20 | 2006-01-04 | Lg电子株式会社 | Valve device of sealed compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2003120563A (en) * | 2001-10-09 | 2003-04-23 | Seiko Instruments Inc | Gas compressor |
| JP2007146761A (en) * | 2005-11-28 | 2007-06-14 | Sanden Corp | Reciprocating compressor |
| WO2012043017A1 (en) * | 2010-09-27 | 2012-04-05 | 大豊工業株式会社 | Vane pump |
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| WO2021065038A1 (en) * | 2019-10-01 | 2021-04-08 | 株式会社日立産機システム | Compressor |
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