JP2006077579A - Hermetic compressor - Google Patents

Hermetic compressor Download PDF

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Publication number
JP2006077579A
JP2006077579A JP2004259243A JP2004259243A JP2006077579A JP 2006077579 A JP2006077579 A JP 2006077579A JP 2004259243 A JP2004259243 A JP 2004259243A JP 2004259243 A JP2004259243 A JP 2004259243A JP 2006077579 A JP2006077579 A JP 2006077579A
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Japan
Prior art keywords
discharge
lead
spring
closing
stopper
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JP2004259243A
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Japanese (ja)
Inventor
Masakazu Yamaoka
正和 山岡
Takeshi Matsumoto
松本　　剛
Terumasa Ide
照正 井出
Tomio Maruyama
富美夫 丸山
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Priority to JP2004259243A priority Critical patent/JP2006077579A/en
Priority to CNB2005800000602A priority patent/CN100419261C/en
Priority to EP20050721043 priority patent/EP1802869A1/en
Priority to PCT/JP2005/004856 priority patent/WO2006027864A1/en
Priority to US10/547,471 priority patent/US20080202613A1/en
Priority to KR1020057016187A priority patent/KR100723104B1/en
Publication of JP2006077579A publication Critical patent/JP2006077579A/en
Withdrawn legal-status Critical Current

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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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates
    • 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
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/18—Leaf springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S251/00—Valves and valve actuation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S251/00—Valves and valve actuation
    • Y10S251/902—Springs employed as valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7879—Resilient material valve
    • Y10T137/7888—With valve member flexing about securement
    • Y10T137/7891—Flap or reed

Abstract

<P>PROBLEM TO BE SOLVED: To prevent adsorption of a discharge lead and a spring lead, suppress a deterioration of refrigerating capacity and achieve high efficiency. <P>SOLUTION: A discharge valve device 114 is formed by fixing to a pad 125 of a valve plate 113 a discharge lead 126 equipped with an opening/closing part 131 and a discharge lead holding part 132, a spring lead 127 equipped with a movable part 133 and a spring holding part 130 and a stopper 128 equipped with a regulating part 137 and a stopper holding part 136 in this order. The spring lead 127 is formed in approximately crank-like side surface shape. A gap is created between the movable part 133 of the spring lead 127 and the opening/closing part 131 of the discharge lead 126 so as not to absorb each other. As a result, a delay in closing the discharge lead 126 can be prevented. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、冷凍冷蔵装置等に用いられる圧縮機に関するものである。   The present invention relates to a compressor used in a refrigeration apparatus or the like.

従来の密閉型圧縮機としては、運転時の低騒音化を図るとともに、吐出リードの開閉時における損失を低減させることでエネルギ効率を向上させる吐出弁装置を備えたものがある（例えば、特許文献１参照）。   As a conventional hermetic compressor, there is a compressor equipped with a discharge valve device that improves energy efficiency by reducing noise during opening and closing of the discharge lead while reducing noise during operation (for example, patent document) 1).

以下、図面を参照しながら上記従来の密閉型圧縮機を説明する。   Hereinafter, the conventional hermetic compressor will be described with reference to the drawings.

図７は従来の密閉型圧縮機の断面図、図８は従来の密閉型圧縮機の平面図、図９は従来の密閉型圧縮機の吐出弁装置の側面断面図、図１０は従来の密閉型圧縮機の吐出弁装置の分解図である。   7 is a cross-sectional view of a conventional hermetic compressor, FIG. 8 is a plan view of the conventional hermetic compressor, FIG. 9 is a side cross-sectional view of a discharge valve device of the conventional hermetic compressor, and FIG. It is an exploded view of the discharge valve apparatus of a type compressor.

図７、図８、図９、図１０、において、密閉容器１は冷却システム（図示しない）と連結される吐出管２と吸入管３を備えており、底部にオイル４を貯溜すると共に固定子５と回転子６とからなる電動要素７およびこれによって駆動される圧縮機構８を収容し、内部は冷媒９で満たされている。   7, 8, 9, and 10, the hermetic container 1 includes a discharge pipe 2 and a suction pipe 3 connected to a cooling system (not shown), and stores oil 4 at the bottom and a stator. The electric element 7 including the rotor 5 and the rotor 6 and the compression mechanism 8 driven by the electric element 7 are accommodated, and the inside is filled with the refrigerant 9.

次に圧縮機構８の主な構成について説明する。   Next, the main configuration of the compression mechanism 8 will be described.

シリンダ１０は略円筒形の圧縮室１１と、軸受け部１２を備えている。バルブプレート１３は反シリンダ１０側に吐出弁装置１４を備え、圧縮室１１を塞いでいる。ヘッド１５はバルブプレート１３を覆っている。吸入マフラー１６は一端を密閉容器１内に開口し、他端を圧縮室１１内に連通している。クランクシャフト１７は主軸部１８と偏心部１９を有し、シリンダの軸受け部１２に軸支されるとともに回転子６が圧入固定されている。ピストン２０は、圧縮室１１に往復摺動自在に挿入されるとともに、偏心部１９との間をコネクティングロッド２１によって連結されている。   The cylinder 10 includes a substantially cylindrical compression chamber 11 and a bearing portion 12. The valve plate 13 includes a discharge valve device 14 on the side opposite to the cylinder 10 and closes the compression chamber 11. The head 15 covers the valve plate 13. One end of the suction muffler 16 opens into the sealed container 1, and the other end communicates with the compression chamber 11. The crankshaft 17 has a main shaft portion 18 and an eccentric portion 19 and is supported by a bearing portion 12 of the cylinder and the rotor 6 is press-fitted and fixed. The piston 20 is inserted into the compression chamber 11 so as to be slidable back and forth, and is connected to the eccentric portion 19 by a connecting rod 21.

次に圧縮機構８に備わる吐出弁装置１４について説明する。   Next, the discharge valve device 14 provided in the compression mechanism 8 will be described.

バルブプレート１３は反シリンダ１０側に凹部２２を有し、凹部２２にはシリンダ１０と連通する吐出孔２３と吐出孔２３を囲うように形成した弁座部２４を設けるとともに、弁座部２４と略同一平面上に形成される台座部２５とを設けている。台座部２５には吐出リード２６と、スプリングリード２７と、ストッパ２８が順にリベット２９によって固定されている。   The valve plate 13 has a recess 22 on the side opposite to the cylinder 10, and the recess 22 is provided with a discharge hole 23 communicating with the cylinder 10 and a valve seat portion 24 formed so as to surround the discharge hole 23. A pedestal portion 25 formed on substantially the same plane is provided. A discharge lead 26, a spring lead 27, and a stopper 28 are sequentially fixed to the pedestal portion 25 by rivets 29.

吐出リード２６は舌状の板ばね材からなり、台座部２５に固定される吐出リード保持部３０と弁座部２４を開閉する開閉部３１とを備えている。   The discharge lead 26 is made of a tongue-shaped leaf spring material, and includes a discharge lead holding portion 30 fixed to the pedestal portion 25 and an opening / closing portion 31 for opening and closing the valve seat portion 24.

スプリングリード２７は舌状の板ばね材からなり、台座部２５に固定されるスプリングリード保持部３２と可動部３３とを備え、吐出リード２６の開閉部３１根元部近傍に折曲部３４を有している。   The spring lead 27 is made of a tongue-shaped leaf spring material, includes a spring lead holding portion 32 fixed to the pedestal portion 25 and a movable portion 33, and has a bent portion 34 near the base portion of the opening / closing portion 31 of the discharge lead 26. is doing.

ストッパ２８は、台座部２５に固定されるストッパ保持部３５と吐出リード２６の動きを規制する規制部３６とを備え、ストッパ２８の規制部３６は弁座部２４と台座部２５を含む平面に対して略平行な側面形状に整形されている。   The stopper 28 includes a stopper holding portion 35 fixed to the pedestal portion 25 and a restriction portion 36 that restricts the movement of the discharge lead 26, and the restriction portion 36 of the stopper 28 is a plane including the valve seat portion 24 and the pedestal portion 25. On the other hand, it is shaped into a substantially parallel side surface.

スプリングリード２７の可動部３３は吐出リード２６の開閉部３１およびストッパ２８の規制部３６とのいずれとの間にも所定の隙間を形成するように折曲部３４の折り曲げ角により調整されている。   The movable portion 33 of the spring lead 27 is adjusted by the bending angle of the bending portion 34 so as to form a predetermined gap between the opening / closing portion 31 of the discharge lead 26 and the restriction portion 36 of the stopper 28. .

以上のように構成された密閉型圧縮機について、以下その動作を説明する。   The operation of the hermetic compressor configured as described above will be described below.

電動要素７に電気が供給されると回転子６が回転し、クランクシャフト１７は回転駆動される。このとき、偏心部１９の偏心回転運動がコネクティングロッド２１を介してピストン２０に伝わることで、ピストン２０は圧縮室１１内を往復運動する。   When electricity is supplied to the electric element 7, the rotor 6 rotates and the crankshaft 17 is driven to rotate. At this time, the eccentric rotational movement of the eccentric portion 19 is transmitted to the piston 20 via the connecting rod 21, so that the piston 20 reciprocates in the compression chamber 11.

ピストン２０の往復運動に伴って密閉容器１内の冷媒９は吸入マフラー１６から圧縮室１１内へ吸入されるとともに、低圧の冷媒９が冷却システム（図示しない）から吸入管３を通って密閉容器１内に流入する。圧縮室１１内へ吸入された冷媒９は圧縮され、バルブプレート１３の吐出弁装置１４を経てヘッド１５内に吐出される。さらに、ヘッド１５内に吐出された高圧ガスは、吐出管２から冷却システム（図示しない）へと吐出される。
特開２００２−１９５１６０号公報 As the piston 20 reciprocates, the refrigerant 9 in the sealed container 1 is sucked into the compression chamber 11 from the suction muffler 16, and the low-pressure refrigerant 9 passes through the suction pipe 3 from the cooling system (not shown). 1 flows in. The refrigerant 9 sucked into the compression chamber 11 is compressed and discharged into the head 15 through the discharge valve device 14 of the valve plate 13. Further, the high-pressure gas discharged into the head 15 is discharged from the discharge pipe 2 to a cooling system (not shown).
JP 2002-195160 A

しかしながら、上記従来の構成では、密閉型圧縮機が起動した直後、本来の冷凍能力に比べ冷凍能力が低い状態が比較的長い時間維持されるという現象がたまに発生することを発明者らは見出した。そして今回、吐出リード２６やスプリングリード２７の挙動を解析することでそのメカニズムの解明に成功したので、以下にその説明をする。   However, the inventors have found that in the above-described conventional configuration, the phenomenon that the refrigeration capacity is lower than the original refrigeration capacity is maintained for a relatively long time immediately after the hermetic compressor is started. . And now, by analyzing the behavior of the discharge lead 26 and the spring lead 27, the mechanism has been clarified, and will be described below.

この低冷凍能力現象が発生し易い密閉型圧縮機の起動時は、冷凍サイクル（図示せず）から冷媒９とともにオイル４が戻ってくる。そして冷媒９とともにこのオイル４も圧縮、吐出するので、吐出リード２６やスプリングリード２７の間にはオイル４が多く介在している状態となっている。   When the hermetic compressor in which the low refrigeration capacity phenomenon is likely to occur, the oil 4 returns together with the refrigerant 9 from the refrigeration cycle (not shown). Since the oil 4 is also compressed and discharged together with the refrigerant 9, a large amount of the oil 4 is interposed between the discharge lead 26 and the spring lead 27.

また、一般に密閉型圧縮機の起動時は吸入圧力が高く、密閉容器１内が減圧されるまでの間、比較的密度の高い冷媒９を圧縮、吐出することとなり、吐出リード２６の開閉部３１には大きな過重がかかる。一方、吐出リード２６の開閉部３１はストッパ２８の規制部３６にて変位が規制されるので、吐出リード２６の開閉部３１は密度の高い冷媒９によってストッパ２８の規制部３６との間に配設しているスプリングリード２７の可動部３３に強く押し付けられることになる。   In general, when the hermetic compressor is started, the suction pressure is high, and the refrigerant 9 having a relatively high density is compressed and discharged until the inside of the hermetic container 1 is depressurized. Takes a heavy overload. On the other hand, since the displacement of the opening / closing part 31 of the discharge lead 26 is restricted by the restriction part 36 of the stopper 28, the opening / closing part 31 of the discharge lead 26 is arranged between the restriction part 36 of the stopper 28 by the high-density refrigerant 9. It is strongly pressed against the movable part 33 of the provided spring lead 27.

そして、上述したような大きな押し付け過重が働くことにより吐出リード２６の開閉部３１とスプリングリード２７の可動部３３とがオイル４で吸着してしまい、吐出リード２６とスプリングリード２７が一体化し、あたかも１枚の厚い吐出リードのようになって開閉動作をする。   Then, due to the large pressing weight as described above, the opening / closing portion 31 of the discharge lead 26 and the movable portion 33 of the spring lead 27 are adsorbed by the oil 4, and the discharge lead 26 and the spring lead 27 are integrated, as if It opens and closes like a thick discharge lead.

ここで、スプリングリード２７の可動部３３は折曲部３４にて吐出リード２６の開く方向に折曲げられているので、結果として、そのバネ力が吐出リード２６の閉じる方向と逆の方向に作用することとなり、吐出リード２６は開く方向に引っ張られ、閉じるタイミングが遅れる。   Here, since the movable portion 33 of the spring lead 27 is bent at the bent portion 34 in the direction in which the discharge lead 26 opens, as a result, the spring force acts in a direction opposite to the closing direction of the discharge lead 26. As a result, the discharge lead 26 is pulled in the opening direction, and the closing timing is delayed.

その結果、ピストン２０が圧縮室１１内で上死点を過ぎて吸入行程に入ってからの吐出リード２６は開いている時間が長くなり、その間圧縮室１１内には高圧の冷媒が逆流し、実質的なピストンの押しのけ容積が小さくなり、低冷凍能力現象が発生するのである。   As a result, the discharge lead 26 after the piston 20 passes the top dead center in the compression chamber 11 and enters the suction stroke becomes longer. During that time, the high-pressure refrigerant flows back into the compression chamber 11, The substantial displacement volume of the piston is reduced, and a low refrigeration capacity phenomenon occurs.

この低冷凍能力現象が発生している間は密閉型圧縮機の効率が悪く、消費電力量を増加させてしまうと同時に、この密閉型圧縮機を搭載している冷凍機器の冷えを鈍化させてしまうといった課題を生ずるものである。   While this low refrigeration capacity phenomenon occurs, the efficiency of the hermetic compressor is inferior and power consumption is increased, and at the same time, the cooling of the refrigeration equipment equipped with this hermetic compressor is slowed down. The problem that it ends up arises.

本発明は、上記従来の課題を解決するもので、吐出リードの閉じ遅れがほとんど無い、エネルギ効率の高い密閉型圧縮機を提供することを目的とする。   SUMMARY OF THE INVENTION The present invention solves the above-described conventional problems, and an object thereof is to provide a highly energy-efficient hermetic compressor that has almost no delay in closing a discharge lead.

上記従来の課題を解決するために、本発明の密閉型圧縮機は、スプリングリードは略クランク状の側面形状に整形され、吐出リード開閉部に対応する位置において吐出リード及びストッパに対し隙間を形成することで、オイル介在による吸着を断ち切り、吐出リードの閉じ遅れを防止するという作用を有する。   In order to solve the above conventional problems, in the hermetic compressor of the present invention, the spring lead is shaped into a substantially crank-shaped side surface, and a gap is formed between the discharge lead and the stopper at a position corresponding to the discharge lead opening / closing portion. By doing so, there is an effect that the adsorption due to oil inclusion is cut off and the discharge lead closing delay is prevented.

本発明の密閉型圧縮機は、吐出リードとスプリングリードの吸着を防止することができるので、エネルギ効率の高い密閉型圧縮機を提供することができる。   Since the hermetic compressor of the present invention can prevent the discharge lead and the spring lead from being adsorbed, a hermetic compressor with high energy efficiency can be provided.

請求項１に記載の発明は、密閉容器内に圧縮機構およびオイルを収容し、前記圧縮機構はピストンと、前記ピストンが往復動するシリンダと、前記シリンダの開口端を封止するとともに反シリンダ側に吐出弁装置を備えたバルブプレートを有し、前記吐出弁装置は、前記シリンダ内に連通する吐出孔と、前記吐出孔の外側に設けられた弁座部と、前記弁座部と略同一平面上に形成した台座部とを前記バルブプレートに形成し、板ばね材からなり前記吐出孔を開閉する開閉部と前記台座部に固定される吐出リード保持部とを備える吐出リードと、板ばね材からなり可動部と前記台座部に固定されるスプリングリード保持部とを備えるスプリングリードと、規制部と前記台座部に固定されるストッパ保持部とを備えるストッパとをこの順に前記保持部において固定してなるとともに、前記スプリングリードは略クランク状の側面形状に整形され、前記吐出リード開閉部に対応する位置において前記吐出リード及び前記ストッパに対し隙間を形成したもので、起動時等に吐出リードとスプリングリードの間にオイルが介在し、吐出リードに過大な過重がかった場合においても、スプリングリードの可動部と吐出リードの開閉部との間に空間が形成され、両者が吸着しないので、吐出リードの閉じ遅れを防ぎ、冷凍能力の低下を抑えエネルギ効率の高い密閉型圧縮機を提供することができる。   According to the first aspect of the present invention, a compression mechanism and oil are accommodated in a sealed container, and the compression mechanism seals a piston, a cylinder in which the piston reciprocates, an open end of the cylinder, and an anti-cylinder side. A valve plate having a discharge valve device, the discharge valve device having a discharge hole communicating with the cylinder, a valve seat portion provided outside the discharge hole, and substantially the same as the valve seat portion A discharge lead comprising a base portion formed on a flat surface on the valve plate, and comprising an opening / closing portion made of a leaf spring material for opening and closing the discharge hole and a discharge lead holding portion fixed to the base portion; and a leaf spring A spring lead comprising a movable part made of a material and a spring lead holding part fixed to the pedestal part, and a stopper comprising a regulating part and a stopper holding part fixed to the pedestal part in this order. The spring lead is shaped into a substantially crank-shaped side surface, and a gap is formed between the discharge lead and the stopper at a position corresponding to the discharge lead opening / closing portion. Even when oil is interposed between the discharge lead and the spring lead, and the discharge lead is excessively heavy, a space is formed between the movable part of the spring lead and the opening and closing part of the discharge lead, and the two do not adsorb. Therefore, it is possible to provide a hermetic compressor with high energy efficiency, which prevents a delay in closing the discharge lead and suppresses a decrease in refrigeration capacity.

請求項２に記載の発明は、請求項１に記載の発明に、吐出リードは吐出リード折曲部において開閉部側が弁座部側に折り曲げられたもので、吐出リードの開閉部を弁座部に押し付ける力が安定して得られるので、吐出リードの開閉部と弁座部のシール性が向上し、請求項１に記載の発明の効果に加えて、さらに効率を向上することができる。   The invention according to claim 2 is the invention according to claim 1, wherein the discharge lead is formed by bending the opening / closing portion side of the discharge lead bent portion to the valve seat portion side, and the opening / closing portion of the discharge lead is connected to the valve seat portion. Since the pressing force is stably obtained, the sealing performance of the opening / closing portion of the discharge lead and the valve seat portion is improved, and in addition to the effect of the invention of claim 1, the efficiency can be further improved.

請求項３に記載の発明は、請求項２に記載の発明の吐出リード折曲部を弁座部と台座部との間に形成された逃げ部に位置させたもので、吐出リードの開閉部の傾き量を安定させることができるので、吐出リードの開閉部を弁座部に押し付ける力をより安定して得ることができ、吐出リードの開閉部と弁座部のシール性が向上し、請求項２に記載の発明の効果に加えてさらに効率を向上することができる。   According to a third aspect of the present invention, the discharge lead bent portion according to the second aspect of the present invention is positioned at a relief portion formed between the valve seat portion and the pedestal portion. Since the amount of inclination of the discharge lead can be stabilized, the force for pressing the opening / closing portion of the discharge lead against the valve seat portion can be obtained more stably, and the sealing performance of the opening / closing portion of the discharge lead and the valve seat portion is improved. In addition to the effect of the invention described in Item 2, the efficiency can be further improved.

請求項４に記載の発明は、請求項１から３に記載の発明のストッパの規制部にスプリングリード側に折曲形成した当接部を形成されたもので、吐出リードの変位がストッパの規制部によって規制されるまでの間にスプリングリードの可動部の支持方式が片持ちから両持ちへ移行するので、途中過程において、スプリングリードの可動部のバネ力をより有効に得ることができ、段階的に必要なバネ特性を設定することが可能となる。その結果、低循環量領域においても、高循環量領域においても最適なバネ特性を得ることが可能となり、請求項１から３に記載の発明の効果に加えてさらに効率を向上することができる。   According to a fourth aspect of the present invention, a contact portion that is bent on the spring lead side is formed on the restriction portion of the stopper according to any one of the first to third aspects of the invention, and the displacement of the discharge lead causes the restriction of the stopper. Since the support method of the movable part of the spring lead shifts from cantilever to both-end until it is regulated by the part, the spring force of the movable part of the spring lead can be obtained more effectively in the middle of the process. It is possible to set necessary spring characteristics. As a result, optimum spring characteristics can be obtained both in the low circulation amount region and in the high circulation amount region, and the efficiency can be further improved in addition to the effects of the inventions of claims 1 to 3.

以下、本発明による圧縮機の実施の形態について、図面を参照しながら説明する。   Embodiments of a compressor according to the present invention will be described below with reference to the drawings.

（実施の形態１）
図１は本発明の実施の形態１における密閉型圧縮機の断面図、図２は同実施の形態における密閉型圧縮機の平面図、図３は同実施の形態における吐出弁装置の閉時の側面断面図、図４は同実施の形態における吐出弁装置の分解図、図５は同実施の形態における吐出弁装置の開時の側面断面図、図６は同実施の形態における吐出弁装置のバネ特性図である。 (Embodiment 1)
1 is a cross-sectional view of a hermetic compressor according to the first embodiment of the present invention, FIG. 2 is a plan view of the hermetic compressor according to the same embodiment, and FIG. 3 is a view when the discharge valve device according to the first embodiment is closed. 4 is an exploded view of the discharge valve device according to the embodiment, FIG. 5 is a side sectional view when the discharge valve device according to the embodiment is opened, and FIG. 6 is a view of the discharge valve device according to the embodiment. It is a spring characteristic figure.

図１、図２、図３、図４、図５、図６において、密閉容器１０１は冷却システム（図示しない）と連結される吐出管１０２と吸入管１０３を備えており、底部にオイル１０４を貯溜すると共に固定子１０５と回転子１０６とからなる電動要素１０７およびこれによって駆動される圧縮機構１０８を収容し、内部は冷媒１０９で満たされている。冷媒１０９は、好ましくは近年の環境問題に対応した特定フロン対象以外の冷媒１０９で例えばＲ１３４ａや自然冷媒であるＲ６００ａ等である。   1, 2, 3, 4, 5, and 6, the sealed container 101 includes a discharge pipe 102 and a suction pipe 103 connected to a cooling system (not shown), and oil 104 is provided at the bottom. The electric element 107 which stores and stores the electric element 107 which consists of the stator 105 and the rotor 106, and the compression mechanism 108 driven by this are accommodated, and the inside is filled with the refrigerant | coolant 109. FIG. The refrigerant 109 is preferably a refrigerant 109 other than the specific chlorofluorocarbon target corresponding to environmental problems in recent years, such as R134a or R600a which is a natural refrigerant.

次に圧縮機構１０８の主な構成について説明する。   Next, the main configuration of the compression mechanism 108 will be described.

シリンダ１１０は略円筒形の圧縮室１１１と、軸受け部１１２を備えている。バルブプレート１１３は反シリンダ１１０側に吐出弁装置１１４を備え、圧縮室１１１を塞いでいる。ヘッド１１５はバルブプレート１１３を覆っている。吸入マフラー１１６は一端を密閉容器１０１内に開口し、他端を圧縮室１１１内に連通している。クランクシャフト１１７は主軸部１１８と偏心部１１９を有し、シリンダ１１０の軸受け部１１２に軸支されるとともに固定子１０５に圧入固定されている。ピストン１２０は、圧縮室１１１に往復摺動自在に挿入されるとともに、偏心部１１９との間をコネクティングロッド１２１によって連結されている。   The cylinder 110 includes a substantially cylindrical compression chamber 111 and a bearing portion 112. The valve plate 113 includes a discharge valve device 114 on the side opposite to the cylinder 110 and closes the compression chamber 111. The head 115 covers the valve plate 113. One end of the suction muffler 116 opens into the sealed container 101 and the other end communicates with the compression chamber 111. The crankshaft 117 has a main shaft portion 118 and an eccentric portion 119, is supported by the bearing portion 112 of the cylinder 110 and is press-fitted and fixed to the stator 105. The piston 120 is inserted into the compression chamber 111 so as to be slidable back and forth, and is connected to the eccentric portion 119 by a connecting rod 121.

次に圧縮機構１０８に備わる吐出弁装置１１４について説明する。   Next, the discharge valve device 114 provided in the compression mechanism 108 will be described.

バルブプレート１１３は反シリンダ１１０側に凹部１２２を有し、凹部１２２にはシリンダ１１０と連通する吐出孔１２３と吐出孔１２３を囲うように形成した弁座部１２４を設けるとともに、弁座部１２４と略同一平面上に形成される台座部１２５とを設けている。   The valve plate 113 has a recess 122 on the side opposite to the cylinder 110. The recess 122 is provided with a discharge hole 123 communicating with the cylinder 110 and a valve seat portion 124 formed so as to surround the discharge hole 123. A pedestal portion 125 formed on substantially the same plane is provided.

台座部１２５には吐出リード１２６と、スプリングリード１２７と、ストッパ１２８が順にリベット１２９によって固定されている。吐出リード１２６は舌状の板ばね材からなり、台座部１２５に固定される吐出リード保持部１３０と弁座部１２４を開閉する開閉部１３１とを備えている。   A discharge lead 126, a spring lead 127, and a stopper 128 are fixed to the pedestal portion 125 in order by rivets 129. The discharge lead 126 is made of a tongue-shaped leaf spring material, and includes a discharge lead holding portion 130 fixed to the pedestal portion 125 and an opening / closing portion 131 that opens and closes the valve seat portion 124.

スプリングリード１２７は舌状の板ばね材からなり、台座部１２５に固定されるスプリングリード保持部１３２と可動部１３３とを備え、可動部１３３に設けた第一の折曲部１３４と第二の折曲部１３５によって略クランク状に整形されている。また、第一の折曲部１３４はスプリングリード１２７の可動部１３３の根元近傍に位置し、第二の折曲部１３５はスプリングリード１２７の可動部１３３に位置している。   The spring lead 127 is made of a tongue-shaped leaf spring material, and includes a spring lead holding part 132 and a movable part 133 fixed to the pedestal part 125, and a first bent part 134 and a second bent part provided on the movable part 133. The bent portion 135 is shaped into a substantially crank shape. The first bent portion 134 is located in the vicinity of the root of the movable portion 133 of the spring lead 127, and the second bent portion 135 is located in the movable portion 133 of the spring lead 127.

ストッパ１２８は、台座部１２５に固定されるストッパ保持部１３６と吐出リード１２６の動きを規制する規制部１３７とを備え、ストッパ１２８の規制部１３７は弁座部１２４と台座部１２５を含む平面に対して略平行な側面形状に整形されている。   The stopper 128 includes a stopper holding portion 136 fixed to the pedestal portion 125 and a restriction portion 137 that restricts the movement of the discharge lead 126, and the restriction portion 137 of the stopper 128 is a plane including the valve seat portion 124 and the pedestal portion 125. On the other hand, it is shaped into a substantially parallel side surface.

スプリングリード１２７の可動部１３３は吐出リード１２６の開閉部１３１およびストッパ１２８の規制部１３７とのいずれとの間にも隙間を有するように各々の折曲部の曲げ角を設定している。   The bending angle of each bent portion is set so that the movable portion 133 of the spring lead 127 has a gap between the opening / closing portion 131 of the discharge lead 126 and the restricting portion 137 of the stopper 128.

吐出リード１２６は、吐出リード折曲部１３８において開閉部１３１側が弁座部１２４側に折曲形成されている。   The discharge lead 126 is formed by bending the opening / closing portion 131 side of the discharge lead bent portion 138 to the valve seat portion 124 side.

弁座部１２４と台座部１２５との間には、台座部１２５より更に深い逃げ部１３９を形成しており、逃げ部１３９は逃げ部１３９に位置している。   A relief portion 139 deeper than the pedestal portion 125 is formed between the valve seat portion 124 and the pedestal portion 125, and the relief portion 139 is located at the relief portion 139.

ストッパ１２８はストッパ１２８の規制部１３７にスプリングリード１２７側に折曲形成した当接部１４０を形成しており、ストッパ１２８の当接部１４０は弁座部１２４と台座部１２５を含む平面に対して略平行な側面形状に形成してある。   The stopper 128 is formed with a contact portion 140 bent on the spring lead 127 side at the restriction portion 137 of the stopper 128, and the contact portion 140 of the stopper 128 is against a plane including the valve seat portion 124 and the pedestal portion 125. Are formed in substantially parallel side surfaces.

以上のように構成された密閉型圧縮機について、以下その動作、作用を説明する。   The operation and action of the hermetic compressor configured as described above will be described below.

電動要素１０７に電気が供給されると回転子１０６が回転し、クランクシャフト１１７は回転駆動される。このとき、偏心部１１９の偏心回転運動がコネクティングロッド１２１を介してピストン１２０に伝わることで、ピストン１２０は圧縮室１１１内を往復運動する。   When electricity is supplied to the electric element 107, the rotor 106 rotates and the crankshaft 117 is driven to rotate. At this time, the eccentric rotational motion of the eccentric portion 119 is transmitted to the piston 120 via the connecting rod 121, so that the piston 120 reciprocates in the compression chamber 111.

ピストン１２０の往復運動に伴って密閉容器１０１内の冷媒１０９は吸入マフラー１１６から圧縮室１１１内へ吸入されるとともに、低圧の冷媒１０９が冷却システム（図示しない）から吸入管１０３を通って密閉容器１０１内に流入する。圧縮室１１１内へ吸入された冷媒１０９は圧縮され、バルブプレート１１３の吐出弁装置１１４を経てヘッド１１５内に吐出される。さらに、ヘッド１１５内に吐出された高圧ガスは、吐出管１０２から冷却システム（図示しない）へと吐出される。   As the piston 120 reciprocates, the refrigerant 109 in the sealed container 101 is sucked into the compression chamber 111 from the suction muffler 116, and the low-pressure refrigerant 109 passes through the suction pipe 103 from the cooling system (not shown). 101 flows in. The refrigerant 109 sucked into the compression chamber 111 is compressed and discharged into the head 115 through the discharge valve device 114 of the valve plate 113. Further, the high-pressure gas discharged into the head 115 is discharged from the discharge pipe 102 to a cooling system (not shown).

ここで、密閉型圧縮機の起動時には、冷凍サイクル（図示せず）から冷媒１０９とともにオイル１０４が戻ってくる。そして冷媒１０９とともにこのオイル１０４も圧縮、吐出するので、吐出リード１２６やスプリングリード１２７の間にはオイル１０４が多く介在している状態となっている。   Here, when the hermetic compressor is started, the oil 104 returns together with the refrigerant 109 from the refrigeration cycle (not shown). Since the oil 104 is also compressed and discharged together with the refrigerant 109, a large amount of the oil 104 is interposed between the discharge lead 126 and the spring lead 127.

また、一般に密閉型圧縮機の起動時は吸入圧力が高く、密閉容器１内が減圧されるまでの間、比較的密度の高い冷媒１０９を圧縮、吐出することとなり、吐出リード１２６の開閉部１３１には大きな過重がかかる。   In general, when the hermetic compressor is started, the suction pressure is high, and the refrigerant 109 having a relatively high density is compressed and discharged until the inside of the hermetic container 1 is depressurized. Takes a heavy overload.

一方、吐出リード１２６の開閉部３１はストッパ１２８の規制部１３７にて変位が規制されるので、吐出リード１２６の開閉部１３１は密度の高い冷媒１０９によってストッパ１２８の規制部１３７との間に配設しているスプリングリード１２７の可動部１３３に強く押し付けられることになる。
その結果、吐出リード１２６の開閉部１３１とスプリングリード１２７の可動部１３３とがオイル１０４で吸着しようとする。 On the other hand, since the displacement of the opening / closing part 31 of the discharge lead 126 is restricted by the restriction part 137 of the stopper 128, the opening / closing part 131 of the discharge lead 126 is arranged between the restriction part 137 of the stopper 128 by the high-density refrigerant 109. It is strongly pressed against the movable part 133 of the provided spring lead 127.
As a result, the opening / closing part 131 of the discharge lead 126 and the movable part 133 of the spring lead 127 tend to be attracted by the oil 104.

しかしながら、スプリングリード１２７の可動部１３３に第一と第二の折曲げを形成しているので、吐出リード１２６の開閉部１３１とスプリングリード１２７の可動部１３３の間には、図５に示すように空間１４１が形成される。そのため、スプリングリード１２７の可動部１３３と吐出リード１２６の開閉部１３１はすぐに引き剥がされる。すなわち、吸着が持続せず、スプリングリード１２７と吐出リード１２６が一体化して動作することがないので、閉じ遅れを防ぐことができる。   However, since the first and second bent portions are formed in the movable portion 133 of the spring lead 127, the gap between the opening / closing portion 131 of the discharge lead 126 and the movable portion 133 of the spring lead 127 is as shown in FIG. A space 141 is formed. Therefore, the movable part 133 of the spring lead 127 and the opening / closing part 131 of the discharge lead 126 are immediately peeled off. That is, the adsorption does not continue, and the spring lead 127 and the discharge lead 126 do not operate integrally, so that a closing delay can be prevented.

その結果、圧縮室１１１内に高圧の冷媒が逆流することで起こる低冷凍能力現象を防ぐことができ、エネルギ効率の高い密閉型圧縮機を提供することができる。   As a result, it is possible to prevent a low refrigeration capacity phenomenon that occurs when a high-pressure refrigerant flows back into the compression chamber 111, and it is possible to provide a hermetic compressor with high energy efficiency.

また、吐出リード１２６は、吐出リード折曲部１３８において開閉部１３１側が弁座部１２４側に折曲形成しているので、吐出リード１２６の開閉部１３１には弁座部１２４に押し付ける力が働く。   Further, since the opening / closing portion 131 side of the discharge lead 126 is bent toward the valve seat portion 124 in the discharge lead bent portion 138, a force pressing the valve seat portion 124 acts on the opening / closing portion 131 of the discharge lead 126. .

従って吐出リード１２６の開閉部１３１が弁座部１２４から浮くことを防止することができ、さらに良好なシール性を保つことができるため、よりエネルギ効率の高い密閉型圧縮機を提供することができる。   Accordingly, the open / close portion 131 of the discharge lead 126 can be prevented from floating from the valve seat portion 124, and a better sealing performance can be maintained, so that a more energy efficient hermetic compressor can be provided. .

さらに、弁座部１２４と台座部１２５との間には台座部１２５より更に深い逃げ部１３９が形成され、吐出リード折曲部１３８は逃げ部１３９の間に位置しているので、逃げ部１３９が台座部１２５とスプリングリード１２７のバネ力によって押圧されることを防止できる。その結果、吐出リード１２６の開閉部１３１の傾き量を安定させることができ、安定した冷凍性能を備えた密閉型圧縮機を提供することができる。   Further, an escape portion 139 deeper than the seat portion 125 is formed between the valve seat portion 124 and the base portion 125, and the discharge lead bent portion 138 is located between the escape portions 139. Can be prevented from being pressed by the spring force of the base 125 and the spring lead 127. As a result, the amount of inclination of the opening / closing part 131 of the discharge lead 126 can be stabilized, and a hermetic compressor having stable refrigeration performance can be provided.

また、本実施の形態によれば、ストッパ１２８の規制部１３７にはスプリングリード１２７側に折曲形成した当接部１４０を形成しているので、スプリングリード１２７が当接部１４０に当接した上でさらに吐出リード１２６は変位をすることができるため、吐出リード１２６のバネ特性は、図６に示すように偏曲点を２つもち３段階の特性を得ることができる。   In addition, according to the present embodiment, since the contact portion 140 that is bent toward the spring lead 127 is formed in the restricting portion 137 of the stopper 128, the spring lead 127 contacts the contact portion 140. Further, since the discharge lead 126 can be displaced further, the spring characteristic of the discharge lead 126 has two bending points as shown in FIG.

すなわち第一の偏曲点は吐出リード１２６の開閉部１３１がスプリングリード１２７の可動部１３３に当接する点であり、以降、第二の編曲点までは吐出リード１２６の開閉部１３１とスプリングリード１２７の可動部１３３のバネの合成力が得られる。   That is, the first bending point is a point where the opening / closing part 131 of the discharge lead 126 abuts on the movable part 133 of the spring lead 127, and thereafter, the opening / closing part 131 of the discharge lead 126 and the spring lead 127 until the second bending point. The combined force of the spring of the movable portion 133 is obtained.

第二の編曲点はスプリングリード１２７の可動部１３３がストッパ１２８の当接部１４０に当接する点で、以降は、スプリングリードの支持方式が片持ちから両持ちへ移行することで、バネ力がさらに増加する。   The second arrangement point is that the movable part 133 of the spring lead 127 comes into contact with the contact part 140 of the stopper 128. Thereafter, the spring force is changed from cantilever to both-end so that the spring force is increased. Further increase.

以上のように偏曲点を２つもち３段階の特性を得ることで、吐出リード１２６の開きが大きいほど強いバネ力が働き、閉じる際のスピードが速くなることから、吐出リード１２６が大きく開く高循環量領域においても閉じ遅れが少なく、エネルギ効率の高い密閉型圧縮機を提供することができる。   As described above, having two inflection points and obtaining three-stage characteristics, the larger the opening of the discharge lead 126, the stronger the spring force works, and the faster the closing speed increases, so the discharge lead 126 opens widely. It is possible to provide a hermetic compressor that has little closing delay even in a high circulation amount region and has high energy efficiency.

以上のように、本発明にかかる密閉型圧縮機は、比較的循環量の多い場合でも、吐出リードの閉じ遅れがほとんど無い、エネルギ効率の高い密閉型圧縮機を提供することができるので、ＣＯ２冷媒を用いた冷凍空調機器の用途にも適用できる。   As described above, the hermetic compressor according to the present invention can provide a highly energy-efficient hermetic compressor with little delay in closing the discharge lead even when the circulation amount is relatively large. It can also be applied to refrigeration and air-conditioning equipment that uses refrigerant.

本発明の実施の形態１における密閉型圧縮機の断面図Sectional drawing of the hermetic compressor in Embodiment 1 of this invention 同実施の形態における密閉型圧縮機の平面図Plan view of hermetic compressor in the same embodiment 同実施の形態における吐出弁装置の閉時の側面断面図Side surface sectional view at the time of closing of the discharge valve device in the same embodiment 同実施の形態における吐出弁装置の分解図Exploded view of the discharge valve device in the same embodiment 同実施の形態における吐出弁装置の開時の側面断面図Side surface sectional view at the time of opening of the discharge valve device in the same embodiment 同実施の形態における吐出弁装置のバネ特性図Spring characteristic diagram of discharge valve device in same embodiment 従来の密閉型圧縮機の断面図Cross section of a conventional hermetic compressor 従来の密閉型圧縮機の平面図Plan view of a conventional hermetic compressor 従来の密閉型圧縮機の吐出弁装置の側面断面図Side sectional view of a discharge valve device of a conventional hermetic compressor 従来の密閉型圧縮機の吐出弁装置の分解図Exploded view of discharge valve device of conventional hermetic compressor

符号の説明Explanation of symbols

１０１ 密閉容器
１０４ オイル
１０８ 圧縮機構
１１０ シリンダ
１１３ バルブプレート
１１４ 吐出弁装置
１２０ ピストン
１２３ 吐出孔
１２４ 弁座部
１２５ 台座部
１２６ 吐出リード
１２７ スプリングリード
１２８ ストッパ
１３０ 吐出リード保持部
１３１ 開閉部
１３２ スプリングリード保持部
１３３ 可動部
１３６ ストッパ保持部
１３７ 規制部
１３８ 吐出リード折曲部
１３９ 逃げ部
１４０ 当接部 DESCRIPTION OF SYMBOLS 101 Airtight container 104 Oil 108 Compression mechanism 110 Cylinder 113 Valve plate 114 Discharge valve apparatus 120 Piston 123 Discharge hole 124 Valve seat part 125 Base part 126 Discharge lead 127 Spring lead 128 Stopper 130 Discharge lead holding part 131 Opening / closing part 132 Spring lead holding part 133 Movable part 136 Stopper holding part 137 Restriction part 138 Discharge lead bent part 139 Escape part 140 Contact part

Claims (4)

密閉容器内に圧縮機構およびオイルを収容し、前記圧縮機構はピストンと、前記ピストンが往復動するシリンダと、前記シリンダの開口端を封止するとともに反シリンダ側に吐出弁装置を備えたバルブプレートを有し、前記吐出弁装置は、前記シリンダ内に連通する吐出孔と、前記吐出孔の外側に設けられた弁座部と、前記弁座部と略同一平面上に形成した台座部とを前記バルブプレートに形成し、板ばね材からなり前記吐出孔を開閉する開閉部と前記台座部に固定される吐出リード保持部とを備える吐出リードと、板ばね材からなり可動部と前記台座部に固定されるスプリングリード保持部とを備えるスプリングリードと、規制部と前記台座部に固定されるストッパ保持部とを備えるストッパとをこの順に前記保持部において固定してなるとともに、前記スプリングリードは略クランク状の側面形状に整形され、前記吐出リード開閉部に対応する位置において前記吐出リード及び前記ストッパに対し隙間を形成した密閉型圧縮機。 A compression mechanism and oil are housed in a sealed container, and the compression mechanism seals a piston, a cylinder in which the piston reciprocates, a valve plate that seals the open end of the cylinder and has a discharge valve device on the non-cylinder side. The discharge valve device comprises: a discharge hole communicating with the cylinder; a valve seat provided outside the discharge hole; and a pedestal formed on substantially the same plane as the valve seat. A discharge lead formed on the valve plate and made of a leaf spring material and having an opening and closing portion for opening and closing the discharge hole and a discharge lead holding portion fixed to the pedestal portion; a movable portion made of a leaf spring material and the pedestal portion A spring lead having a spring lead holding portion fixed to the stopper and a stopper having a regulating portion and a stopper holding portion fixed to the pedestal portion are fixed in this order in the holding portion. Both the spring reed is shaped in a substantially crank-shaped side shape, a hermetic compressor forming a gap relative to the discharge reed and the stopper at a position corresponding to the discharge reed opening and closing unit. 吐出リードは吐出リード折曲部において開閉部側が弁座部側に折り曲げられた請求項１に記載の密閉型圧縮機。 The hermetic compressor according to claim 1, wherein the discharge lead is bent at the opening / closing portion side toward the valve seat portion at the discharge lead bent portion. 吐出リード折曲部を弁座部と台座部との間に形成された逃げ部に位置させた請求項２に記載の密閉型圧縮機。 The hermetic compressor according to claim 2, wherein the discharge lead bent portion is positioned in a relief portion formed between the valve seat portion and the pedestal portion. ストッパの規制部にスプリングリード側に折曲形成した当接部を形成した請求項１から３に記載の密閉型圧縮機。 The hermetic compressor according to any one of claims 1 to 3, wherein a contact portion that is bent toward the spring lead side is formed in the restriction portion of the stopper.
JP2004259243A 2004-09-07 2004-09-07 Hermetic compressor Withdrawn JP2006077579A (en)

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JP2004259243A JP2006077579A (en) 2004-09-07 2004-09-07 Hermetic compressor
CNB2005800000602A CN100419261C (en) 2004-09-07 2005-03-11 Hermetic compressor
EP20050721043 EP1802869A1 (en) 2004-09-07 2005-03-11 Hermetic compressor
PCT/JP2005/004856 WO2006027864A1 (en) 2004-09-07 2005-03-11 Hermetic compressor
US10/547,471 US20080202613A1 (en) 2004-09-07 2005-03-11 Hermetic Compressor
KR1020057016187A KR100723104B1 (en) 2004-09-07 2005-03-11 Hermetic compressor

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EP (1) EP1802869A1 (en)
JP (1) JP2006077579A (en)
KR (1) KR100723104B1 (en)
CN (1) CN100419261C (en)
WO (1) WO2006027864A1 (en)

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WO2006027864A1 (en) 2006-03-16
EP1802869A1 (en) 2007-07-04
KR100723104B1 (en) 2007-05-30
US20080202613A1 (en) 2008-08-28
KR20060038911A (en) 2006-05-04
CN100419261C (en) 2008-09-17

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