JP2007132257A

JP2007132257A - Scroll compressor

Info

Publication number: JP2007132257A
Application number: JP2005325690A
Authority: JP
Inventors: Daisuke Funakoshi; 大輔船越; Noboru Iida; 飯田　　登; Hiroyuki Kono; 博之河野; Kiyoshi Sawai; 澤井　　清
Original assignee: Matsushita Electric Industrial Co Ltd
Current assignee: Panasonic Holdings Corp
Priority date: 2005-11-10
Filing date: 2005-11-10
Publication date: 2007-05-31

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll compressor capable of coping with a wide range of operation mode by reducing mechanical loss due to reduction of operation frequency by increasing volume in a high speed operation range, and reducing leak loss and motor loss due to operation frequency increase by reducing volume in a low speed operation range without changing size of a compressor main body. <P>SOLUTION: Apparent suction shut in volume can be reduced by returning fluid in a process of compression to a suction chamber 13 from a middle hole 24a of a bypass 25, and the compressor can be efficiently operated over the wide range from low capacity to high capacity. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、空調機、冷凍機、ブロワ、給湯機等に使用されるスクロール圧縮機に関するものである。 The present invention relates to a scroll compressor used for an air conditioner, a refrigerator, a blower, a water heater, and the like.

運転モードの多様化にともない、大容量での大能力運転から小容量での小能力運転まで幅広い運転が求められてきた。一般的に高速運転することにより、機械的な損失は増加する。また、逆に低速運転することにより、流体の漏れが増大し体積効率が悪化し、さらにモーターの効率が悪化する傾向にある。吸入容積を大きくした場合、同等能力を得るために運転周波数を下げることから、機械損失が減少し高速運転域の性能は良化するが、逆に低速運転域の性能は流体の漏れ損失とモーター損失増加により悪化する。また、吸入容積を小さくした場合、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により低速運転域の性能は良化するが、逆に高速運転域の性能は機械的損失増加により悪化する。よって、高速運転域では吸入容積を大きくし、さらに低速運転域では吸入容積を小さくすることが求められてきた。 With the diversification of operation modes, a wide range of operation has been demanded, from large capacity operation with large capacity to small capacity operation with small capacity. In general, mechanical loss increases with high speed operation. On the other hand, by operating at low speed, fluid leakage increases, volumetric efficiency deteriorates, and motor efficiency tends to deteriorate. When the suction volume is increased, the operating frequency is lowered to obtain the same capacity, so the mechanical loss is reduced and the performance in the high-speed operating area is improved, but conversely the performance in the low-speed operating area is the fluid leakage loss and the motor. Deteriorated by increased loss. In addition, when the suction volume is reduced, the operating frequency is increased to obtain the same capacity, so the performance in the low-speed operating area is improved by reducing fluid leakage loss and motor loss, but conversely the performance in the high-speed operating area. Is exacerbated by increased mechanical losses. Therefore, it has been demanded to increase the suction volume in the high speed operation region and further reduce the suction volume in the low speed operation region.

図１１は、特許文献１に記載された従来のスクロール圧縮機を示すものである。図８に示すように、旋回スクロール羽根もしくは固定スクロール羽根の少なくとも一方にその巻き終わり位置からその渦巻き形状に沿ってさらに延ばした延長羽根を設け、この延長羽根の内壁およびこれと対向する他の羽根の外壁の少なくとも一方を羽根の厚みが薄くなる方向に変位させた変位面とし、その変位面と対向する他の羽根の壁面との間は最も接近した時でも一定の隙間ができるように構成し、その隙間は低速運転時には延長羽根部分に存在する吸入冷媒を巻き終わり側に逃がすことが出来、且つ高速運転時には延長羽根部分に存在する吸入流体の大部分を巻き終わり側に逃がすことなく圧縮室側に閉じ込むことができ、擬似的に吸入流体の閉じ込み容積を変化させることから、幅広い運転モードに対応することが可能となった。
特開平１１−８２３３１号公報 FIG. 11 shows a conventional scroll compressor described in Patent Document 1. In FIG. As shown in FIG. 8, at least one of the orbiting scroll blade and the fixed scroll blade is provided with an extension blade further extending along the spiral shape from the end position of the winding, and the inner wall of this extension blade and the other blades facing this At least one of the outer walls of the blade is a displacement surface that is displaced in the direction in which the thickness of the blade becomes thinner, and a constant gap is formed between the displacement surface and the wall surface of the other blade facing the blade even when it is closest. The clearance allows the suction refrigerant present in the extension blade part to escape to the end of winding during low speed operation, and the compression chamber without releasing most of the suction fluid present in the extension blade part to the end of winding during high speed operation. It is possible to accommodate a wide range of operation modes since the volume of the suction fluid is changed in a pseudo manner.
JP-A-11-82331

しかしながら、前記従来の構成では、低速から高速の各運転条件において、羽根の厚みが薄くなる方向に変位させた変位面と対向する他の羽根壁面の間のわずかな隙間に、オイル潤滑されるが、同じ運転条件でもオイル量、粘度などに違いが生じた場合、各運転条件ごとに一定のシール性が得られず、閉じこめた吸入流体を巻き終わりに逃がす量がそれぞれの運転条件で一定に決めることができず、希望通りの容積が得られない可能性があるため、さらなる運転モードの多様化に対応することが必要である。 However, in the conventional configuration, oil lubrication is performed in a slight gap between the displacement surface that is displaced in a direction in which the thickness of the blade becomes thinner and the other blade wall surface facing the blade surface in each operating condition from low speed to high speed. If there is a difference in the oil amount, viscosity, etc. even under the same operating conditions, a certain level of sealing performance cannot be obtained for each operating condition, and the amount of the trapped suction fluid that escapes at the end of winding is determined according to the operating conditions. Therefore, it is necessary to cope with further diversification of operation modes because the desired volume may not be obtained.

本発明は、前記従来の課題を解決するもので、容積の可変により小能力から大能力の広い範囲に渡って効率よく運転することが出来るスクロール圧縮機を提供することを目的とする。 The present invention solves the above-described conventional problems, and an object thereof is to provide a scroll compressor that can be operated efficiently over a wide range from a small capacity to a large capacity by changing the volume.

前記従来の課題を解決するために、圧縮空間と吸入室を連通させるバイパスで圧縮途中の流体を吸入室に逃がし、バイパスの端部に中間孔と吸入孔を持ち、中間孔は、固定スクロールの鏡板上または旋回スクロールの支持円板上の少なくともどちらか一方にあり、且つ一対の圧縮空間のどちらか一方にだけに臨み、固定スクロールの鏡板上の中間孔は旋回スクロールラップ厚みで一定区間完全にふさぐことの出来る位置と大きさであり、また旋
回スクロールの支持円板上の中間孔は固定スクロールラップ厚みで一定区間完全にふさぐことの出来る位置と大きさであることで、閉じ込めた流体を吸入室に運転条件ごとにある一定量逃がすことが可能となり、小能力から大能力の広い範囲に渡って効率良く運転することが可能となり、さらなる運転モードの多様化に対応できる。 In order to solve the above-described conventional problems, fluid that is being compressed is released to the suction chamber by a bypass that connects the compression space and the suction chamber, and has an intermediate hole and a suction hole at the end of the bypass. It is located on at least one of the end plate or on the support disk of the orbiting scroll and faces only one of the pair of compression spaces. The intermediate hole on the support disk of the orbiting scroll can be closed and the position and size can be completely closed by a fixed scroll wrap thickness. It is possible to escape a certain amount to the room for each operating condition, and it is possible to operate efficiently over a wide range from small capacity to large capacity. It can respond to the diversification of the mode.

本発明のスクロール圧縮機は、容積の可変により小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 The scroll compressor of the present invention can be efficiently operated over a wide range from a small capacity to a large capacity by changing the volume.

第１の発明は、固定スクロールの一部をなす鏡板の一面に直立して形成された渦巻き状のインボリュートの固定スクロールラップ対して、旋回スクロールの一部をなすインボリュートのラップが支持円板上に直立するとともに、前記固定スクロールラップに類似した形状の旋回スクロールラップを互いに噛み合わせて、両スクロール間に渦巻き形の対称形の一対の圧縮空間を形成し、前記固定スクロールラップの中心部に吐出室に通じる吐出口を設け、前記固定スクロールラップの外側には吸入室を設け、自転阻止部材を介して前記旋回スクロールが前記固定スクロールに対し旋回運動を行うことによって、前記各圧縮空間が吸入側より吐出側に向けて連続移行する複数個の圧縮室に区画されて流体を圧縮すべく容積変化し、前記圧縮空間と前記吸入室を連通させるバイパスで圧縮途中の流体を前記吸入室に逃がし、前記バイパスの端部に中間孔と吸入孔を持ち、前記中間孔は、前記固定スクロールの前記鏡板上または前記旋回スクロールの前記支持円板上の少なくともどちらか一方に２個以上あり、且つ前記一対の圧縮空間のどちらか一方にだけに臨み、前記固定スクロールの前記鏡板上の前記中間孔は前記旋回スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、また前記旋回スクロールの前記支持円板上の前記中間孔は前記固定スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであることから、圧縮途中の流体を前記吸入室に効率よく逃がすことにより、見かけ上の吸入閉じ込み容積を小さくでき、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により、高い性能を得ることができる。さらに、前記中間孔の数を増やすことにより、バイパス通過時の圧力損失を低減することができ、多くの圧縮流体を逃がすことができる。 In the first aspect of the present invention, the involute wrap forming a part of the orbiting scroll is arranged on the support disk in contrast to the spiral involute fixed scroll wrap formed upright on one surface of the end plate forming a part of the fixed scroll. The orbiting scroll wrap having a shape similar to the fixed scroll wrap is engaged with each other to form a pair of spiral symmetric compression spaces between the scrolls, and a discharge chamber at the center of the fixed scroll wrap. And a suction chamber provided outside the fixed scroll wrap, and the orbiting scroll performs a orbiting motion with respect to the fixed scroll via a rotation prevention member. A plurality of compression chambers that continuously move toward the discharge side, the volume of which is changed to compress the fluid, and the compression space; The fluid in the middle of compression escapes to the suction chamber by a bypass communicating with the suction chamber, and has an intermediate hole and a suction hole at the end of the bypass, and the intermediate hole is formed on the end plate of the fixed scroll or on the orbiting scroll. There are two or more on at least one of the support disks and only one of the pair of compression spaces, and the intermediate hole on the end plate of the fixed scroll has a constant thickness of the orbiting scroll wrap. The section can be completely closed, and the upstream and downstream compression spaces are not desired at the same time and size, and the intermediate hole on the support disc of the orbiting scroll has the fixed scroll wrap thickness Since the position and size of the compression space on the upstream side and the downstream side are not desired at the same time, the fluid during compression can be completely closed. By efficiently escaping to the suction chamber, the apparent suction confinement volume can be reduced, and the operating frequency is increased to obtain the same capacity, so that high performance is obtained by reducing fluid leakage loss and motor loss. Can do. Furthermore, by increasing the number of the intermediate holes, it is possible to reduce the pressure loss when passing the bypass, and to release a lot of compressed fluid.

第２の発明は、固定スクロールの一部をなす鏡板の一面に直立して形成された渦巻き状のインボリュートの固定スクロールラップ対して、旋回スクロールの一部をなすインボリュートのラップが支持円板上に直立するとともに、前記固定スクロールラップに類似した形状の旋回スクロールラップを互いに噛み合わせて、両スクロール間に渦巻き形の対称形の一対の圧縮空間を形成し、前記固定スクロールラップの中心部に吐出室に通じる吐出口を設け、前記固定スクロールラップの外側には吸入室を設け、自転阻止部材を介して前記旋回スクロールが前記固定スクロールに対し旋回運動を行うことによって、前記各圧縮空間が吸入側より吐出側に向けて連続移行する複数個の圧縮室に区画されて流体を圧縮すべく容積変化し、前記圧縮空間と前記吸入室を連通させるバイパスで圧縮途中の流体を前記吸入室に逃がし、前記バイパスの端部に第１中間孔と第２中間孔と吸入孔を持ち、前記第１中間孔は、前記固定スクロールの前記鏡板上または前記旋回スクロールの前記支持円板上の少なくともどちらか一方に１個以上あり、且つ前記一対の圧縮空間のうち一方にだけ臨み、前記固定スクロールの前記鏡板上の前記第１中間孔は前記旋回スクロールラップ厚みで一定区間完全にふさぐことにふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、また前記旋回スクロールの前記支持円板上の前記第１中間孔は前記固定スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、前記第２中間孔は、前記固定スクロールの前記鏡板上または前記旋回スクロールの前記支持円板上の少な
くともどちらか一方に１個以上あり、且つ前記一対の圧縮空間のうち他方にだけ臨み、前記固定スクロールの前記鏡板上の前記第２中間孔は前記旋回スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、また前記旋回スクロールの前記支持円板上の前記第２中間孔は前記固定スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであることから、前記一対の圧縮空間の両方の第１中間孔と第２中間孔から圧縮途中の流体を前記吸入室に逃がすことにより、流体がバイパスの中間孔を通過する時の圧力損失を抑え、さらに見かけ上の吸入閉じ込み容積を小さくでき、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により、より高い性能を得ることができる。さらに、前記中間孔の数を増やすことにより、バイパス通過時の圧力損失を低減することができ、多くの圧縮流体を吸入室に逃がすことができる。 In the second invention, the involute wrap forming a part of the orbiting scroll is formed on the support disk, while the spiral scroll involute fixed scroll wrap formed upright on one surface of the end plate forming a part of the fixed scroll. The orbiting scroll wrap having a shape similar to the fixed scroll wrap is engaged with each other to form a pair of spiral symmetric compression spaces between the scrolls, and a discharge chamber at the center of the fixed scroll wrap. And a suction chamber provided outside the fixed scroll wrap, and the orbiting scroll performs a orbiting motion with respect to the fixed scroll via a rotation prevention member. A plurality of compression chambers that continuously move toward the discharge side, the volume of which is changed to compress the fluid, and the compression space; The fluid that is being compressed by the bypass communicating with the suction chamber is released to the suction chamber, and has a first intermediate hole, a second intermediate hole, and a suction hole at the end of the bypass, and the first intermediate hole is formed by the fixed scroll. One or more on at least one of the end plate or on the support disc of the orbiting scroll and facing only one of the pair of compression spaces, the first intermediate on the end plate of the fixed scroll The hole can be closed to completely cover a certain section with the thickness of the orbiting scroll wrap, and has an undesired position and size in the compression space on the upstream side and the downstream side, and the support circle of the orbiting scroll. The first intermediate hole on the plate can be completely closed by a fixed scroll wrap thickness, and a position and a large position that the upstream and downstream compression spaces are not desired simultaneously. The at least one second intermediate hole is provided on at least one of the end plate of the fixed scroll and the support disc of the orbiting scroll, and only in the other of the pair of compression spaces. The second intermediate hole on the end plate of the fixed scroll can be completely filled with the orbiting scroll wrap thickness for a certain interval, and the upstream and downstream compression spaces are not desired at the same time and size. In addition, the second intermediate hole on the support disk of the orbiting scroll can be completely closed by a fixed scroll wrap thickness, and the upstream and downstream compression spaces are not desired simultaneously. Because of the position and size, the fluid is bypassed by allowing the fluid in the middle of compression to escape from the first intermediate hole and the second intermediate hole in both of the pair of compression spaces to the suction chamber. The pressure loss when passing through the middle hole of the path is suppressed, the apparent suction confinement volume can be reduced, and the operating frequency is increased to obtain the equivalent capacity. Higher performance can be obtained. Furthermore, by increasing the number of the intermediate holes, it is possible to reduce the pressure loss when passing the bypass, and to release a large amount of compressed fluid to the suction chamber.

第３の発明は、固定スクロールの一部をなす鏡板の一面に直立して形成された渦巻き状のインボリュートの固定スクロールラップ対して、旋回スクロールの一部をなすインボリュートのラップが支持円板上に直立するとともに、前記固定スクロールラップに類似した形状の旋回スクロールラップを互いに噛み合わせて、両スクロール間に渦巻き形の対称形の一対の圧縮空間を形成し、前記圧縮空間の吸入閉じこみ容積の一方を他方よりも小さくし、前記固定スクロールラップの中心部に吐出室に通じる吐出口を設け、前記固定スクロールラップの外側には吸入室を設け、自転阻止部材を介して前記旋回スクロールが前記固定スクロールに対し旋回運動を行うことによって、前記各圧縮空間が吸入側より吐出側に向けて連続移行する複数個の圧縮室に区画されて流体を圧縮すべく容積変化し、前記圧縮空間と前記吸入室を連通させるバイパスで圧縮途中の流体を前記吸入室に逃がし、前記バイパスの端部に中間孔と吸入孔を持ち、前記中間孔は、前記固定スクロールの前記鏡板上または前記旋回スクロールの前記支持円板上の少なくともどちらか一方に２個以上あり、且つ前記吸入閉じこみ容積の大きな前記圧縮空間にだけに臨み、前記固定スクロールの前記鏡板上の前記中間孔は前記旋回スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、また前記旋回スクロールの前記支持円板上の前記中間孔は前記固定スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであることから、前記圧縮空間の吸入閉じこみ容積の大きい方の中間孔から圧縮途中の流体を前記吸入室に逃がすことにより、見かけ上の吸入閉じ込み容積を小さく出来、前記圧縮空間の吸入とじ込み容積の小さい方と大きい方の容積比の差が小さくなり、両方の圧縮空間がバランス良く容積変化するため、軸のトルク変動が小さくなることから、低騒音化と高効率化が実現できる。また、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により、より高い性能を得ることができる。さらに、前記中間孔の数を増やすことにより、バイパス通過時の圧力損失を低減することができ、多くの圧縮流体を吸入室に逃がすことができる。 According to a third aspect of the present invention, the involute wrap forming a part of the orbiting scroll is formed on the support disk, while the spiral scroll involute fixed scroll wrap formed upright on one surface of the end plate forming a part of the fixed scroll. A swivel scroll wrap having a shape similar to that of the fixed scroll wrap is engaged with each other to form a pair of spiral symmetric compression spaces between the scrolls, and one of the suction confinement volumes of the compression space Is made smaller than the other, a discharge port leading to a discharge chamber is provided at the center of the fixed scroll wrap, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll is fixed to the fixed scroll via a rotation prevention member. The plurality of pressures in which the compression spaces continuously shift from the suction side to the discharge side by performing a swiveling motion on the The volume is changed so as to compress the fluid divided into chambers, and the fluid in the middle of compression is released to the suction chamber by a bypass communicating the compression space and the suction chamber, and has an intermediate hole and a suction hole at the end of the bypass. The intermediate hole is provided at least two on the end plate of the fixed scroll or on the support disc of the orbiting scroll, and faces only the compression space having a large suction confinement volume, The intermediate hole on the end plate of the fixed scroll can be completely filled with a certain section with the thickness of the orbiting scroll wrap, and has an undesired position and size in the upstream and downstream compression spaces at the same time, and The intermediate hole on the support disc of the orbiting scroll can be completely closed by a fixed scroll wrap thickness, and the compressed air on the upstream side and the downstream side can be closed. Therefore, an apparent suction confinement volume can be obtained by allowing the fluid in the middle of compression to escape to the suction chamber from the intermediate hole having the larger suction confinement volume in the compression space. The difference in volume ratio between the smaller and larger volumes of the suction and suction space in the compression space becomes smaller, and both compression spaces change in volume in a well-balanced manner. And high efficiency can be realized. In addition, since the operating frequency is increased in order to obtain the same capability, higher performance can be obtained by reducing fluid leakage loss and motor loss. Furthermore, by increasing the number of the intermediate holes, it is possible to reduce the pressure loss when passing the bypass, and to release a large amount of compressed fluid to the suction chamber.

第４の発明は、固定スクロールの一部をなす鏡板の一面に直立して形成された渦巻き状のインボリュートの固定スクロールラップ対して、旋回スクロールの一部をなすインボリュートのラップが支持円板上に直立するとともに、前記固定スクロールラップに類似した形状の旋回スクロールラップを互いに噛み合わせて、両スクロール間に渦巻き形の対称形の一対の圧縮空間を形成し、前記圧縮空間の吸入閉じこみ容積の一方を他方よりも小さくし、前記固定スクロールラップの中心部に吐出室に通じる吐出口を設け、前記固定スクロールラップの外側には吸入室を設け、自転阻止部材を介して前記旋回スクロールが前記固定スクロールに対し旋回運動を行うことによって、前記各圧縮空間が吸入側より吐出側に向けて連続移行する複数個の圧縮室に区画されて流体を圧縮すべく容積変化し、前記圧縮空間と前記吸入室を連通させるバイパスで圧縮途中の流体を前記吸入室に逃がし、前記バイパスの端部に中間孔と吸入孔を持ち、前記中間孔は、前記固定スクロールの前記鏡板上
または前記旋回スクロールの前記支持円板上の少なくともどちらか一方に２個以上あり、且つ前記吸入閉じこみ容積の小さな前記圧縮空間にだけに臨み、前記固定スクロールの前記鏡板上の前記中間孔は前記旋回スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、また前記旋回スクロールの前記支持円板上の前記中間孔は前記固定スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであることから、前記圧縮空間の吸入閉じこみ容積の小さい方の中間孔から圧縮途中の流体を前記吸入室に逃がすことにより、見かけ上の吸入閉じ込み容積を小さくでき、前記圧縮空間の吸入とじ込み容積の小さい方をさらに小さくすることが出来、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により、より高い性能を得ることができる。さらに、前記中間孔の数を増やすことにより、バイパス通過時の圧力損失を低減することができ、多くの圧縮流体を吸入室に逃がすことができる。 According to a fourth aspect of the present invention, the involute wrap forming a part of the orbiting scroll is formed on the support disk, while the spiral scroll involute fixed scroll wrap formed upright on one surface of the end plate forming a part of the fixed scroll. A swivel scroll wrap having a shape similar to that of the fixed scroll wrap is engaged with each other to form a pair of spiral symmetric compression spaces between the scrolls, and one of the suction confinement volumes of the compression space Is made smaller than the other, a discharge port leading to a discharge chamber is provided at the center of the fixed scroll wrap, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll is fixed to the fixed scroll via a rotation prevention member. The plurality of pressures in which the compression spaces continuously shift from the suction side to the discharge side by performing a swiveling motion on the The volume is changed so as to compress the fluid divided into chambers, and the fluid in the middle of compression is released to the suction chamber by a bypass communicating the compression space and the suction chamber, and has an intermediate hole and a suction hole at the end of the bypass. The intermediate holes are provided at least two on the end plate of the fixed scroll or on the support disk of the orbiting scroll, and only face the compression space having a small suction confinement volume, The intermediate hole on the end plate of the fixed scroll can be completely filled with a certain section with the thickness of the orbiting scroll wrap, and has an undesired position and size in the upstream and downstream compression spaces at the same time, and The intermediate hole on the support disk of the orbiting scroll can be completely closed by a fixed scroll wrap thickness, and the compressed air on the upstream side and the downstream side can be closed. Therefore, the apparent suction confinement volume can be obtained by allowing the fluid in the middle of compression to escape to the suction chamber from the smaller intermediate hole of the suction confinement volume of the compression space. Can be made smaller, the smaller the suction volume of the compression space can be further reduced, and the operating frequency is increased in order to obtain the same capacity, so higher performance can be achieved by reducing fluid leakage loss and motor loss. Obtainable. Further, by increasing the number of the intermediate holes, it is possible to reduce the pressure loss when passing the bypass, and to release a lot of compressed fluid to the suction chamber.

第５の発明は、固定スクロールの一部をなす鏡板の一面に直立して形成された渦巻き状のインボリュートの固定スクロールラップ対して、旋回スクロールの一部をなすインボリュートのラップが支持円板上に直立するとともに、前記固定スクロールラップに類似した形状の旋回スクロールラップを互いに噛み合わせて、両スクロール間に渦巻き形の対称形の一対の圧縮空間を形成し、前記圧縮空間の吸入閉じこみ容積の一方を他方よりも小さくし、前記固定スクロールラップの中心部に吐出室に通じる吐出口を設け、前記固定スクロールラップの外側には吸入室を設け、自転阻止部材を介して前記旋回スクロールが前記固定スクロールに対し旋回運動を行うことによって、前記各圧縮空間が吸入側より吐出側に向けて連続移行する複数個の圧縮室に区画されて流体を圧縮すべく容積変化し、前記圧縮空間と前記吸入室を連通させるバイパスで圧縮途中の流体を前記吸入室に逃がし、前記バイパスの端部に第１中間孔と第２中間孔と吸入孔を持ち、前記第１中間孔は、前記固定スクロールの前記鏡板上または前記旋回スクロールの前記支持円板上の少なくともどちらか一方に１個以上あり、且つ前記吸入閉じこみ容積の大きな前記圧縮空間にだけに臨み、前記固定スクロールの前記鏡板上の前記第１中間孔は前記旋回スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、また前記旋回スクロールの前記支持円板上の前記第１中間孔は前記固定スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、前記第２中間孔は、前記固定スクロールの前記鏡板上または前記旋回スクロールの前記支持円板上の少なくともどちらか一方に１個以上あり、且つ前記吸入閉じこみ容積の小さな前記圧縮空間にだけに臨み、前記固定スクロールの前記鏡板上の前記第２中間孔は前記旋回スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであり、また前記旋回スクロールの前記支持円板上の前記第２中間孔は前記固定スクロールラップ厚みで一定区間完全にふさぐことが出来、上流側と下流側の前記圧縮空間に同時に望むことのない位置と大きさであることから、前記圧縮空間の吸入閉じこみ容積の大きい方の第１中間孔と前記圧縮空間の吸入閉じこみ容積の小さい方の第２中間孔から圧縮途中の流体を前記吸入室に逃がすことにより、見かけ上の吸入閉じ込み容積を小さくでき、前記圧縮空間の吸入とじ込み容積の小さい方と大きい方を両方とも小さくすることができ、容積比の設定に自由度が増す。また、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により、より高い性能を得ることができる。さらに、前記中間孔の数を増やすことにより、バイパス通過時の圧力損失を低減することができ、多くの圧縮流体を吸入室に逃がすことができる。 According to a fifth aspect of the present invention, the involute wrap forming a part of the orbiting scroll is arranged on the support disk, while the spiral scroll involute fixed scroll wrap is formed upright on one surface of the end plate forming a part of the fixed scroll. A swivel scroll wrap having a shape similar to that of the fixed scroll wrap is engaged with each other to form a pair of spiral symmetric compression spaces between the scrolls, and one of the suction confinement volumes of the compression space Is made smaller than the other, a discharge port leading to a discharge chamber is provided at the center of the fixed scroll wrap, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll is fixed to the fixed scroll via a rotation prevention member. The plurality of pressures in which the compression spaces continuously shift from the suction side to the discharge side by performing a swiveling motion on the The volume of the fluid is changed so as to compress the fluid divided into chambers, and the fluid in the middle of compression is released to the suction chamber by a bypass communicating the compression space and the suction chamber. There is an intermediate hole and a suction hole, and the first intermediate hole is at least one on the end plate of the fixed scroll or on the support disk of the orbiting scroll, and has the suction confinement volume. Facing only the large compression space, the first intermediate hole on the end plate of the fixed scroll can be completely closed by the orbiting scroll wrap thickness, and the compression space on the upstream side and the downstream side can be desired simultaneously. The first intermediate hole on the support disk of the orbiting scroll can be completely covered by a fixed scroll wrap thickness for a certain interval. The position and the size are not desired simultaneously in the upstream and downstream compression spaces, and the second intermediate hole is at least either on the end plate of the fixed scroll or on the support disc of the orbiting scroll. The second intermediate hole on the end plate of the fixed scroll can be completely blocked by a thickness of the orbiting scroll wrap so as to face only the compression space having one or more on one side and having a small volume of suction confinement. The position and size of the second and second holes on the support disk of the orbiting scroll are fixed to the fixed scroll wrap thickness. Since the position and the size of the compression space on the upstream side and the downstream side are not desired at the same time, the suction confinement volume of the compression space is large. By allowing the fluid in the middle of compression to escape to the suction chamber from the smaller first intermediate hole and the second intermediate hole having the smaller suction confinement volume of the compression space, the apparent suction confinement volume can be reduced, It is possible to reduce both the smaller and the larger of the suction and entrapment volume of the compression space, and increase the degree of freedom in setting the volume ratio. In addition, since the operating frequency is increased in order to obtain the same capability, higher performance can be obtained by reducing fluid leakage loss and motor loss. Furthermore, by increasing the number of the intermediate holes, it is possible to reduce the pressure loss when passing the bypass, and to release a large amount of compressed fluid to the suction chamber.

第６の発明は、吸入孔の径を中間孔の径より大きくすることで、圧縮途中の流体をバイパスの吸入孔を通過して吸入室に戻す時の圧力損失を低減することが可能となり、効率よく運転することができる。 In the sixth aspect of the invention, by making the diameter of the suction hole larger than the diameter of the intermediate hole, it becomes possible to reduce the pressure loss when returning the fluid being compressed through the bypass suction hole to the suction chamber, It is possible to drive efficiently.

第７の発明は、低速運転域でバイパスを連通させることにより、見かけ上の吸入閉じ込み容積を小さくし、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により、高い性能を得ることができるようになり、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 In the seventh aspect of the invention, the bypass is communicated in the low speed operation range, thereby reducing the apparent suction confinement volume and increasing the operation frequency in order to obtain the same capacity, thereby reducing the fluid leakage loss and the motor loss. As a result, high performance can be obtained, and operation can be efficiently performed over a wide range from small capacity to large capacity.

第８の発明は、高速運転域でバイパスを非連通させることにより、圧縮途中の流体を逃がさずに前記吸入閉じ込み容積を一定にし、もともとの前記吸入閉じ込み容積を大きくすることで、高い性能を得ることができるようになり、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 According to an eighth aspect of the present invention, high performance can be achieved by disabling the bypass in the high-speed operation range, thereby making the suction confining volume constant without escaping fluid in the middle of compression, and increasing the original suction confining volume. Can be obtained, and can be operated efficiently over a wide range from small capacity to large capacity.

（実施の形態１）
図１は、本発明の実施の形態におけるスクロール圧縮機の縦断面図を示すものである。 (Embodiment 1)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present invention.

図１において、鉄製の密閉容器１の内部全体は吐出管２に連通する高圧雰囲気となり、その中央部にモータ３、上部に圧縮部が配置され、モータ３の回転子３ａに固定されたクランクシャフト４の一端を支承する圧縮部の本体フレーム５が密閉容器１に固定されており、その本体フレーム５に固定スクロール６が取り付けられている。 In FIG. 1, the entire inside of the iron sealed container 1 is a high-pressure atmosphere communicating with the discharge pipe 2, a motor 3 at the center, a compression part at the top, and a crankshaft fixed to the rotor 3 a of the motor 3. A main body frame 5 of a compression portion that supports one end of 4 is fixed to the sealed container 1, and a fixed scroll 6 is attached to the main body frame 5.

クランクシャフト４に設けられた主軸方向の油穴７は、その一端が給油ポンプ装置８に通じ、他端が最終的に旋回スクロール９の旋回軸受１０に通じている。固定スクロール６と噛み合って圧縮室１１を形成する旋回スクロール９は、渦巻き状の旋回スクロールラップ９ｂと旋回軸受１０とを直立させたラップ支持円板９ａとからなり、固定スクロール６と本体フレーム５との間に配置されている。 The oil hole 7 in the main shaft direction provided in the crankshaft 4 has one end communicating with the oil supply pump device 8 and the other end finally communicating with the orbiting bearing 10 of the orbiting scroll 9. The orbiting scroll 9 that meshes with the fixed scroll 6 to form the compression chamber 11 includes a spiral orbiting scroll wrap 9b and a wrap support disk 9a in which the orbiting bearing 10 is erected, and the fixed scroll 6 and the main body frame 5 It is arranged between.

固定スクロール６は、鏡板６ａと渦巻き状の固定スクロールラップ６ｂとからなり、固定スクロールラップ６ｂの中央部に吐出口１２、外周部に吸入室１３が配置されている。 The fixed scroll 6 includes an end plate 6a and a spiral fixed scroll wrap 6b. A discharge port 12 is disposed at the center of the fixed scroll wrap 6b, and a suction chamber 13 is disposed at the outer periphery.

クランクシャフト４の主軸部４ａから偏心してクランクシャフト４の上端部に配置された旋回軸部４ｂは、旋回スクロール９の旋回軸受１０と係合摺動し、クランクシャフト４の下端部に配置された副軸部４ｃは密閉容器１内に溶接や焼き嵌めして固定された副軸受１９により軸支され、主軸部４ａ、旋回軸部４ｂ、副軸部４ｃの三点で支持された構成をしている。旋回スクロール９のラップ支持円板９ａと本体フレーム５に設けられた第１のスラスト軸受１５ａとの間は、油膜形成可能な微小隙間が設けられている。ラップ支持円板９ａには旋回軸受１０とほぼ同心の環状シール部材１６が遊合状態で装着されており、その環状シール部材１６はその内側の背面室１７と外側の背圧室１８とを仕切っている。 The orbiting shaft portion 4b that is eccentric from the main shaft portion 4a of the crankshaft 4 and is disposed at the upper end portion of the crankshaft 4 engages and slides with the orbiting bearing 10 of the orbiting scroll 9 and is disposed at the lower end portion of the crankshaft 4. The auxiliary shaft portion 4c is pivotally supported by an auxiliary bearing 19 fixed by welding or shrink fitting in the sealed container 1, and is supported at three points of the main shaft portion 4a, the turning shaft portion 4b, and the auxiliary shaft portion 4c. ing. Between the lap support disk 9a of the orbiting scroll 9 and the first thrust bearing 15a provided on the main body frame 5, a minute gap capable of forming an oil film is provided. An annular seal member 16 that is substantially concentric with the slewing bearing 10 is mounted on the lap support disk 9a in a loose state, and the annular seal member 16 partitions the back chamber 17 inside and the back pressure chamber 18 outside. ing.

給油ポンプ装置８によって吸い上げられた潤滑油はクランクシャフト４の油穴７を通り旋回スクロール９の旋回軸受１０と旋回軸部１４との間に形成された軸方向の内部空間２０へ導かれ、一方は旋回スクロール９のラップ支持円板９ａの背面に設けられた絞り部２１を経由して固定スクロール６と本体フレーム５とによって囲まれて形成される背圧室１８へと通じ、旋回スクロール９を固定スクロールラップ６ｂ外周部の第２のスラスト軸受１５ｂに押さえつける機能を持った背圧調整弁２２、オイル供給通路２２ａを通って吸入室１３へと導かれる。もう一方は旋回軸受１０、背面室１７、主軸受１４を通り圧縮部外部へ排出される。 The lubricating oil sucked up by the oil supply pump device 8 passes through the oil hole 7 of the crankshaft 4 and is guided to the axial inner space 20 formed between the orbiting bearing 10 and the orbiting shaft portion 14 of the orbiting scroll 9. Is connected to the back pressure chamber 18 formed by being surrounded by the fixed scroll 6 and the main body frame 5 through the throttle portion 21 provided on the back surface of the lap support disk 9a of the orbiting scroll 9, The oil is guided to the suction chamber 13 through the back pressure adjusting valve 22 and the oil supply passage 22a having a function of pressing against the second thrust bearing 15b on the outer peripheral portion of the fixed scroll wrap 6b. The other passes through the slewing bearing 10, the back chamber 17, and the main bearing 14 and is discharged to the outside of the compression unit.

吐出口１２の出口側を開閉する逆止弁装置２３が固定スクロール６の鏡板６ａの平面上に取り付けられており、その逆止弁装置２３は薄鋼板製のリード弁２３ａと弁押さえ２３ｂとからなる。 A check valve device 23 that opens and closes the outlet side of the discharge port 12 is mounted on the plane of the end plate 6a of the fixed scroll 6, and the check valve device 23 includes a reed valve 23a made of a thin steel plate and a valve presser 23b. Become.

固定スクロール６の鏡板６ａ上にバイパス２５の両端部に中間孔２８と吸入孔２４があり、バイパス２５と中間孔２８の間とバイパス２５と吸入穴２４の間にそれぞれ高圧が加わることでバイパス２５を連通させず、低圧が加わることで連通させる中間側逆支弁装置２７ａと吸入側逆支弁装置２７ｂを持ち、電磁弁２６によりバイパス２５への圧力を高圧・低圧と切り替える構成をしている。 An intermediate hole 28 and a suction hole 24 are provided at both ends of the bypass 25 on the end plate 6 a of the fixed scroll 6. By applying high pressure between the bypass 25 and the intermediate hole 28 and between the bypass 25 and the suction hole 24, the bypass 25 is provided. The intermediate side reversely supported valve device 27a and the suction side reversely supported valve device 27b communicated by applying a low pressure without being communicated, and the solenoid valve 26 switches the pressure to the bypass 25 between high pressure and low pressure.

図２は図１における固定スクロール６と旋回スクロール９とバイパス２５と電磁弁２６などの圧縮機構部周辺の拡大断面図である。 FIG. 2 is an enlarged cross-sectional view of the periphery of the compression mechanism portion such as the fixed scroll 6, the orbiting scroll 9, the bypass 25, and the electromagnetic valve 26 in FIG. 1.

以上のように構成されたスクロール圧縮機について、以下その動作、作用を説明する。 About the scroll compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

まず、運転モードの多様化にともない、大容量での大能力運転から小容量での小能力運転まで幅広い運転が求められてきた。高速運転域では機械的な損失は増加し、低速運転域では流体の漏れ損失の増大による体積効率の悪化とモーター損失の増大による効率の悪化の傾向がある。吸入容積を大きくした場合、同等能力を得るために運転周波数を下げることから、機械損失の減少により高速運転域の性能は良化する。逆に低速運転域の性能は流体の漏れ損失とモーター損失の増加により悪化する。また、吸入容積を小さくした場合、同等能力を得るために運転周波数が上げることから，流体の漏れ損失とモーター損失の減少により低速運転域の性能は良化するが、逆に高速運転域の性能は機械的損失増加により悪化する。よって、高速運転域では吸入容積を大きくし、さらに低速運転域では吸入容積を小さくすることで小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 First, with the diversification of operation modes, a wide range of operation has been demanded from large capacity operation with large capacity to small capacity operation with small capacity. Mechanical loss increases in the high-speed operation region, and in the low-speed operation region, there is a tendency for deterioration in volume efficiency due to increase in fluid leakage loss and efficiency deterioration due to increase in motor loss. When the suction volume is increased, the operating frequency is lowered to obtain the same capacity, so the performance in the high-speed operating area is improved due to the reduction in mechanical loss. On the other hand, the performance in the low-speed operating range deteriorates due to an increase in fluid leakage loss and motor loss. In addition, when the suction volume is reduced, the operating frequency is increased in order to obtain the same capacity, so the performance in the low-speed operating area is improved by reducing fluid leakage loss and motor loss, but conversely the performance in the high-speed operating area. Is exacerbated by increased mechanical losses. Therefore, it is possible to operate efficiently over a wide range from a small capacity to a large capacity by increasing the suction volume in the high speed operation range and further decreasing the suction volume in the low speed operation range.

そこで、図３に示すように、中間孔２８が一方の圧縮空間１１の上流側と下流側が同時に望むことで中間孔２８内での圧縮流体の移動が起こり、圧力損失が生じてしまうために、図４に示すように、一方の圧縮空間１１の上流側と下流側が同時に望むことがないような構造とし、図５に示すように、中間孔２８が固定スクロール６の鏡板６ａ上に２個あり、一対の圧縮空間１１のどちらか一方にだけに望み、低速運転域ではバイパス２５を連通させ、圧縮途中の流体を吸入室１３に戻し、見かけ上の吸入閉じ込み容積を小さくし、同等能力を得るために運転周波数を上げることから、流体の漏れ損失とモーター損失の減少により、より高い性能を得ることができる。また高速運転域ではバイパス２５を非連通させ、圧縮途中の流体を吸入室１３に逃がさずに、前記吸入閉じ込み容積を一定にし、もともとの前記吸入閉じ込み容積を大きくすることで、より高い性能を得ることができるようになり、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 Therefore, as shown in FIG. 3, since the intermediate hole 28 desires the upstream side and the downstream side of one compression space 11 at the same time, movement of the compressed fluid in the intermediate hole 28 occurs and pressure loss occurs. As shown in FIG. 4, the structure is such that the upstream side and the downstream side of one compression space 11 are not desired at the same time, and there are two intermediate holes 28 on the end plate 6a of the fixed scroll 6 as shown in FIG. Desirable only in one of the pair of compression spaces 11, the bypass 25 is communicated in the low speed operation region, the fluid in the middle of compression is returned to the suction chamber 13, the apparent suction confinement volume is reduced, and the equivalent capacity is achieved. Since the operating frequency is increased in order to obtain higher performance by reducing fluid leakage loss and motor loss. Further, in the high-speed operation region, the bypass 25 is disconnected, the fluid in the middle of compression is not released into the suction chamber 13, the suction confining volume is made constant, and the original suction confining volume is increased, thereby achieving higher performance. Can be obtained, and can be operated efficiently over a wide range from small capacity to large capacity.

また、図６に示すように、第１中間孔２８ａは固定スクロール６の鏡板６ａ上で、一対の圧縮空間１１の一方にだけに臨み、同様に第２中間孔２８ｂは一対の圧縮空間１１の他方にだけに臨むように２個あり、他方の圧縮空間１１の上流側と下流側が同時に望むことがない構造とし、第１中間孔２８ａと第２中間孔２８ｂの両方から圧縮途中の流体を吸入室１３に逃がすことができ、流体がバイパス２５の第１中間孔２８ａと第２中間孔２８ｂを通過する時の圧力損失を抑え、さらに見かけ上の吸入閉じ込み容積を小さくできることから、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 Further, as shown in FIG. 6, the first intermediate hole 28 a faces only one of the pair of compression spaces 11 on the end plate 6 a of the fixed scroll 6, and similarly, the second intermediate hole 28 b is formed in the pair of compression spaces 11. There are two so that only the other side faces, and the upstream side and the downstream side of the other compression space 11 are not desired at the same time, and the fluid in the middle of compression is sucked from both the first intermediate hole 28a and the second intermediate hole 28b From the small capacity, it is possible to escape to the chamber 13 and suppress the pressure loss when the fluid passes through the first intermediate hole 28a and the second intermediate hole 28b of the bypass 25 and further reduce the apparent suction confinement volume. It is possible to operate efficiently over a wide range of large capacity.

また、図７に示すように、圧縮空間１１の吸入閉じこみ容積の一方を他方よりも小さくした場合、中間孔２８は固定スクロール６の鏡板６ａ上で、一対の圧縮空間１１の吸入容積の大きい方にだけに臨むように２個あり、圧縮空間１１の上流側と下流側が同時に望むことがない構造とすることにより、圧縮空間１１の吸入とじ込み容積の小さい方と大きい方の容積比を小さくすることができ、両方の圧縮空間１１がバランス良く容積変化するため、軸のトルク変動が小さくなり、低騒音化と高効率化が実現でき、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 Further, as shown in FIG. 7, when one of the suction confinement volumes of the compression space 11 is made smaller than the other, the intermediate hole 28 has a large suction volume of the pair of compression spaces 11 on the end plate 6 a of the fixed scroll 6. There are two so as to face only the direction, and the upstream side and the downstream side of the compression space 11 are not desired at the same time, thereby reducing the volume ratio of the compression space 11 with the smaller and larger suction volumes. Because the volume of both compression spaces 11 changes in a balanced manner, the torque fluctuation of the shaft is reduced, low noise and high efficiency can be realized, and operation efficiently over a wide range from small capacity to large capacity. I can do it.

また、図８に示すように、圧縮空間１１の吸入閉じこみ容積の一方を他方よりも小さくした場合、中間孔２８は固定スクロール６の鏡板６ａ上で、一対の圧縮空間１１の吸入容積の小さい方にだけに臨むように２個あり、圧縮空間１１の上流側と下流側が同時に望むことがない構造とすることにより、容積比をさらに大きく取ることが出来、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 As shown in FIG. 8, when one of the suction confining volumes of the compression space 11 is made smaller than the other, the intermediate hole 28 has a small suction volume of the pair of compression spaces 11 on the end plate 6 a of the fixed scroll 6. There are two so as to face only the direction, and by making the structure that the upstream side and the downstream side of the compression space 11 do not want at the same time, the volume ratio can be further increased, from a small capacity to a wide range of large capacity It is possible to drive efficiently across.

また、図９に示すように、圧縮空間１１の吸入閉じこみ容積の一方を他方よりも小さくした場合、第１中間孔２８ａは固定スクロール６の鏡板６ａ上で、一対の圧縮空間１１の吸入容積の大きい方にだけに臨むように２個あり、圧縮空間１１の上流側と下流側が同時に望むことがない構造であり、第２中間孔２８ｂは固定スクロール６の鏡板６ａ上で、一対の圧縮空間１１の吸入容積の小さい方にだけに臨むように２個あり、圧縮空間１１の上流側と下流側が同時に望むことがない構造とすることにより、一対の圧縮空間１１の第１中間孔２８ａと第２中間孔２８ｂの両方から圧縮途中の流体を吸入室１３に逃がすことができ、流体がバイパス２５の第１中間孔と第２中間孔を通過する時の圧力損失を抑え、さらに見かけ上の吸入閉じ込み容積を小さく出来、且つ容積比を大きく取ることが出来、容積設定の自由度が広がることから、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 Further, as shown in FIG. 9, when one of the suction confining volumes of the compression space 11 is made smaller than the other, the first intermediate hole 28 a is on the end plate 6 a of the fixed scroll 6 and the suction volume of the pair of compression spaces 11. The two intermediate holes 28b are arranged on the end plate 6a of the fixed scroll 6 so that the upstream side and the downstream side of the compression space 11 are not desired at the same time. The number of the first intermediate holes 28a of the pair of compression spaces 11 and the number of the first intermediate holes 28a of the pair of compression spaces 11 is such that the upstream side and the downstream side of the compression space 11 are not desired at the same time. The fluid in the middle of compression can be released from both of the two intermediate holes 28b to the suction chamber 13, and the pressure loss when the fluid passes through the first intermediate hole and the second intermediate hole of the bypass 25 is suppressed, and the apparent suction is further performed. Confinement The possible small and can be a large volume ratio, because the spreading freedom volume setting can be operated efficiently over a wide range of large capacity from a small capacity.

また、図１０に示すように、吸入孔２４の径を中間孔２８の径より大きくすることで、圧縮途中の流体をバイパス２５を通して吸入室１３に戻す時の圧力損失を低減することが可能となり、さらに効率よく運転することができる。 Also, as shown in FIG. 10, by making the diameter of the suction hole 24 larger than the diameter of the intermediate hole 28, it is possible to reduce the pressure loss when returning the fluid being compressed to the suction chamber 13 through the bypass 25. It is possible to drive more efficiently.

以上のように、特に低速運転域において圧縮途中の流体をバイパス２５の中間孔２８から吸入室１３に逃がすことにより、見かけ上の吸入閉じ込み容積を小さく出来、小能力から大能力の広い範囲に渡って効率よく運転することが出来る。 As described above, the apparent suction confining volume can be reduced by releasing the fluid in the middle of compression from the intermediate hole 28 of the bypass 25 to the suction chamber 13 especially in the low speed operation region, and the range from small capacity to large capacity can be reduced. It is possible to drive efficiently across.

以上のように、本発明にかかるスクロール圧縮機は、圧縮途中の流体をバイパスの中間孔から吸入室に戻すことにより、見かけ上の吸入閉じ込み容積を小さく出来、小能力から大能力の広い範囲に渡って効率よく運転することが可能となり、ＨＦＣ系冷媒やＨＣＦＣ系冷媒を用いたエアーコンディショナー用圧縮機のほかに、自然冷媒ＣＯ₂を用いたエアーコンディショナーやヒートポンプ式給湯機などの用途にも適用できる。 As described above, the scroll compressor according to the present invention can reduce the apparent suction confinement volume by returning the fluid in the middle of compression from the bypass intermediate hole to the suction chamber. In addition to air conditioner compressors using HFC refrigerants and HCFC refrigerants, it can also be used for applications such as air conditioners using natural refrigerant CO ₂ and heat pump water heaters. Applicable.

本発明の実施の形態における縦型スクロール圧縮機の縦断面図1 is a longitudinal sectional view of a vertical scroll compressor according to an embodiment of the present invention. 本発明の実施の形態における縦型スクロール圧縮機構部拡大断面図The vertical scroll compression mechanism part expanded sectional view in embodiment of this invention 本発明の実施の形態における中間孔内での圧縮流体の移動がある場合の旋回スクロールと固定スクロール構成図Orbiting scroll and fixed scroll configuration diagram when there is movement of compressed fluid in the intermediate hole in the embodiment of the present invention 本発明の実施の形態における中間孔内での圧縮流体の移動がない場合の旋回スクロールと固定スクロール構成図Orbiting scroll and fixed scroll configuration diagram when there is no movement of compressed fluid in the intermediate hole in the embodiment of the present invention 本発明の実施の形態における一対の圧縮空間の一方にのみ中間孔がある旋回スクロールと固定スクロール構成図Orbiting scroll and fixed scroll configuration diagram having an intermediate hole only in one of a pair of compression spaces in an embodiment of the present invention 本発明の実施の形態における一対の圧縮空間の一方と他方に中間孔がある旋回スクロールと固定スクロール構成図FIG. 3 is a configuration diagram of a turning scroll and a fixed scroll having an intermediate hole in one and the other of a pair of compression spaces in an embodiment of the present invention. 本発明の実施の形態における吸入閉じ込み容積が大きい方に第１中間孔がある旋回スクロールと固定スクロール構成図FIG. 3 is a configuration diagram of an orbiting scroll and a fixed scroll having a first intermediate hole in a larger suction confinement volume in the embodiment of the present invention. 本発明の実施の形態における吸入閉じ込み容積が小さい方に第２中間孔がある旋回スクロールと固定スクロール構成図Orbiting scroll and fixed scroll configuration diagram having a second intermediate hole in the smaller suction confinement volume in the embodiment of the present invention 本発明の実施の形態における吸入閉じ込み容積が大きい方と小さい方のそれぞれに第１中間孔と第２中間孔がある旋回スクロールと固定スクロール構成図FIG. 3 is a configuration diagram of an orbiting scroll and a fixed scroll having a first intermediate hole and a second intermediate hole in each of the larger and smaller suction confinement volumes in the embodiment of the present invention. 本発明の実施の形態における吸入孔の径を中間孔の径より大きくした旋回スクロールと固定スクロール構成図Orbiting scroll and fixed scroll configuration diagram in which the diameter of the suction hole is larger than the diameter of the intermediate hole in the embodiment of the present invention 従来の縦型スクロール圧縮機の９０度置きの旋回の動作状態図Operational state diagram of turning at 90 degree intervals of a conventional vertical scroll compressor

Explanation of symbols

１密閉容器
２吐出管
３モータ
３ａ回転子
３ｂ固定子
４クランクシャフト
４ａ主軸部
４ｂ旋回軸部
４ｃ副軸部
５本体フレーム
６固定スクロール
６ａ鏡板
６ｂ固定スクロールラップ
７油穴
８給油ポンプ装置
９旋回スクロール
９ａ支持円板
９ｂ旋回スクロールラップ
１０旋回軸受
１１圧縮空間
１２吐出口
１３吸入室
１４主軸受
１５ａ第１のスラスト軸受
１５ｂ第２のスラスト軸受
１６環状シール部材
１７背面室
１８背圧室
１９副軸受
２０内部空間
２１絞り部
２２背圧調整弁
２２ａオイル供給通路
２３逆止弁装置
２３ａリード弁
２３ｂ弁押さえ
２４吸入孔
２５バイパス
２６電磁弁
２７ａ中間側逆支弁装置
２７ｂ吸入側逆支弁装置
２８中間孔
２８ａ第１中間孔
２８ｂ第２中間孔
１２０固定スクロール
１２１羽根
１２１ａ基本羽根
１２１ｂ延長羽根
１２１ｂ１変位面
１２２鏡板
１３０旋回スクロール
１３０ａ旋回軸
１３１羽根
１３１ａ基本羽根
１３１ｂ延長羽根
１３１ｂ１変位面
１３２鏡板
１４０吸入ポート
１４１、１４１ａ、１４１ｂ、１４１ｂ１圧縮室
１４１ｃ閉じ込み部
１４２自転防止旋回駆動機構
１４３オルダムリング
１４５吐出ポート
１５１段差 DESCRIPTION OF SYMBOLS 1 Airtight container 2 Discharge pipe 3 Motor 3a Rotor 3b Stator 4 Crankshaft 4a Main shaft part 4b Turning shaft part 4c Subshaft part 5 Body frame 6 Fixed scroll 6a End plate 6b Fixed scroll wrap 7 Oil hole 8 Oil supply pump device 9 Turning scroll 9a support disk 9b orbiting scroll lap 10 orbiting bearing 11 compression space 12 discharge port 13 suction chamber 14 main bearing 15a first thrust bearing 15b second thrust bearing 16 annular seal member 17 back chamber 18 back pressure chamber 19 sub bearing 20 Internal space 21 Throttle part 22 Back pressure adjustment valve 22a Oil supply passage 23 Check valve device 23a Reed valve 23b Valve retainer 24 Suction hole 25 Bypass 26 Solenoid valve 27a Intermediate side reverse valve device 27b Suction side reverse valve device 28 Intermediate hole 28a First 1 intermediate hole 28b 2nd intermediate hole 120 solid Scroll 121 Blade 121a Basic blade 121b Extension blade 121b1 Displacement surface 122 End plate 130 Orbiting scroll 130a Orbiting shaft 131 Blade 131a Basic blade 131b Extension blade 131b1 Displacement surface 132 End plate 140 Suction port 141, 141a, 141b, 141b1 Compression chamber 141c Closed portion 141c Anti-spinning turning drive mechanism 143 Oldham ring 145 Discharge port 151 Step

Claims

The involute wrap, which forms part of the orbiting scroll, stands upright on the support disk while the fixed scroll wrap of the spiral involute formed upright on one side of the end plate, which forms part of the fixed scroll, is fixed on the support disk. A swirl scroll wrap having a shape similar to the scroll wrap is meshed with each other to form a pair of spiral symmetrical compression spaces between the scrolls, and a discharge port leading to the discharge chamber is provided at the center of the fixed scroll wrap. In addition, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll performs a orbiting motion with respect to the fixed scroll via a rotation prevention member, whereby each compression space is continuously directed from the suction side toward the discharge side. The volume is changed to compress the fluid by dividing into a plurality of compression chambers to be transferred, and the compression space and the suction chamber are connected. The fluid that is being compressed by the bypass is allowed to escape to the suction chamber, and has an intermediate hole and a suction hole at the end of the bypass. The intermediate hole is on the end plate of the fixed scroll or on the support disk of the orbiting scroll. 2 or more in at least one of them, facing only one of the pair of compression spaces, and the intermediate hole on the end plate of the fixed scroll is completely covered with a certain interval by the thickness of the orbiting scroll wrap. The intermediate hole on the support disk of the orbiting scroll is completely fixed by a fixed scroll wrap thickness at a position and size that are not desired simultaneously in the upstream and downstream compression spaces. A scroll compressor characterized by having a position and a size that can be blocked and is not desired simultaneously in the compression space on the upstream side and the downstream side.

The involute wrap, which forms part of the orbiting scroll, stands upright on the support disk while the fixed scroll wrap of the spiral involute formed upright on one side of the end plate, which forms part of the fixed scroll, is fixed on the support disk. A swirl scroll wrap having a shape similar to the scroll wrap is meshed with each other to form a pair of spiral symmetrical compression spaces between the scrolls, and a discharge port leading to the discharge chamber is provided at the center of the fixed scroll wrap. In addition, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll performs a orbiting motion with respect to the fixed scroll via a rotation prevention member, whereby each compression space is continuously directed from the suction side toward the discharge side. The volume is changed to compress the fluid by dividing into a plurality of compression chambers to be transferred, and the compression space and the suction chamber are connected. A fluid that is being compressed by the bypass is released to the suction chamber, and has a first intermediate hole, a second intermediate hole, and a suction hole at an end of the bypass, and the first intermediate hole is formed on the end plate of the fixed scroll or There is one or more on at least one of the support discs of the orbiting scroll and only one of the pair of compression spaces faces, and the first intermediate hole on the end plate of the fixed scroll is the orbiting scroll. The wrap thickness can be used to completely block a certain section, and the upstream and downstream compression spaces are undesired positions and sizes at the same time. One intermediate hole can be completely filled with a fixed section by the thickness of the fixed scroll wrap, and has an undesired position and size at the upstream and downstream compression spaces at the same time. One or more second intermediate holes are provided on at least one of the end plate of the fixed scroll and the support disc of the orbiting scroll, and face only the other of the pair of compression spaces, and the fixed scroll The second intermediate hole on the end plate can be completely closed by the orbiting scroll wrap thickness and has a position and size that are not desired simultaneously in the upstream and downstream compression spaces, and The second intermediate hole on the support disk of the orbiting scroll can be completely covered with a fixed scroll wrap thickness at a certain interval, and at an undesired position and size at the upstream and downstream compression spaces at the same time. A scroll compressor characterized by being.

The involute wrap, which forms part of the orbiting scroll, stands upright on the support disk while the fixed scroll wrap of the spiral involute formed upright on one side of the end plate, which forms part of the fixed scroll, is fixed on the support disk. The orbiting scroll wrap having a shape similar to the scroll wrap is engaged with each other to form a pair of spiral-shaped symmetrical compression spaces between the two scrolls, and one of the suction confinement volumes of the compression space is made smaller than the other. A discharge port leading to a discharge chamber is provided at the center of the fixed scroll wrap, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll performs an orbiting motion with respect to the fixed scroll via a rotation prevention member. Thus, each compression space is partitioned into a plurality of compression chambers that continuously transition from the suction side toward the discharge side. The volume is changed to compress the fluid, and the fluid in the middle of compression is released to the suction chamber by a bypass communicating the compression space and the suction chamber, and an intermediate hole and a suction hole are provided at the end of the bypass. Two or more on the end plate of the fixed scroll or on the support disk of the orbiting scroll, and only facing the compression space having a large suction confinement volume, The intermediate hole on the end plate can be completely covered with the orbiting scroll wrap thickness by a certain interval, has an undesired position and size in the compression space on the upstream side and the downstream side, and The intermediate hole on the support disk can be completely closed by a fixed scroll wrap thickness, and can be desired in the compression space on the upstream side and the downstream side at the same time. Scroll compressor, which is a preparative's no position and size.

The involute wrap, which forms part of the orbiting scroll, stands upright on the support disk while the fixed scroll wrap of the spiral involute formed upright on one side of the end plate, which forms part of the fixed scroll, is fixed on the support disk. The orbiting scroll wrap having a shape similar to the scroll wrap is engaged with each other to form a pair of spiral-shaped symmetrical compression spaces between the two scrolls, and one of the suction confinement volumes of the compression space is made smaller than the other. A discharge port leading to a discharge chamber is provided at the center of the fixed scroll wrap, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll performs an orbiting motion with respect to the fixed scroll via a rotation prevention member. Thus, each compression space is partitioned into a plurality of compression chambers that continuously transition from the suction side toward the discharge side. The volume is changed to compress the fluid, and the fluid in the middle of compression is released to the suction chamber by a bypass communicating the compression space and the suction chamber, and an intermediate hole and a suction hole are provided at the end of the bypass. Two or more on the end plate of the fixed scroll or on the support disk of the orbiting scroll, and only facing the compression space having a small suction confinement volume, The intermediate hole on the end plate can be completely covered with the orbiting scroll wrap thickness by a certain interval, has an undesired position and size in the compression space on the upstream side and the downstream side, and The intermediate hole on the support disk can be completely closed by a fixed scroll wrap thickness, and can be desired in the compression space on the upstream side and the downstream side at the same time. Scroll compressor, which is a preparative's no position and size.

The involute wrap, which forms part of the orbiting scroll, stands upright on the support disk while the fixed scroll wrap of the spiral involute formed upright on one side of the end plate, which forms part of the fixed scroll, is fixed on the support disk. The orbiting scroll wrap having a shape similar to the scroll wrap is engaged with each other to form a pair of spiral-shaped symmetrical compression spaces between the two scrolls, and one of the suction confinement volumes of the compression space is made smaller than the other. A discharge port leading to a discharge chamber is provided at the center of the fixed scroll wrap, a suction chamber is provided outside the fixed scroll wrap, and the orbiting scroll performs an orbiting motion with respect to the fixed scroll via a rotation prevention member. Thus, each compression space is partitioned into a plurality of compression chambers that continuously transition from the suction side toward the discharge side. The volume of the fluid is changed to compress the fluid, and the fluid in the middle of compression is released to the suction chamber by a bypass that connects the compression space and the suction chamber. The first intermediate hole, the second intermediate hole, and the suction hole are disposed at the end of the bypass. And at least one of the first intermediate holes on the end plate of the fixed scroll or the support disc of the orbiting scroll, and in the compression space having a large suction confinement volume. The first intermediate hole on the end plate of the fixed scroll can be completely closed by the orbiting scroll wrap thickness, and the upstream and downstream compression spaces are not desired simultaneously. The first intermediate hole on the support disk of the orbiting scroll can be completely closed by a fixed scroll wrap thickness, and can be closed upstream and downstream. At least one of the second intermediate holes on the end plate of the fixed scroll or on the support disc of the orbiting scroll. The second intermediate hole on the end plate of the fixed scroll can be completely closed by a thickness of the orbiting scroll wrap, facing only the compression space having a small suction confinement volume, The second intermediate hole on the support disk of the orbiting scroll can be completely covered by a fixed scroll wrap thickness with a position and size that are not desired simultaneously in the downstream compression space. A scroll compressor having a position and a size that are not desired simultaneously in the compression space on the upstream side and the downstream side.

The scroll compressor according to any one of claims 1 to 5, wherein a diameter of the suction hole is larger than a diameter of the intermediate hole.

The scroll compressor according to any one of claims 1 to 6, wherein a bypass is communicated in a low-speed operation range, fluid in the middle of compression is allowed to escape to the suction chamber, and an apparent suction confinement volume is reduced.

The scroll compressor according to any one of claims 1 to 7, wherein in the high-speed operation region, the bypass is not communicated, and the suction confining volume is made constant without escaping fluid during compression.