DE102019201477A1 - Motor-driven compressor - Google Patents

Abstract

An electric compressor includes a first scroll, a second scroll that engages the first scroll to produce orbital motion to form a compression chamber with the first scroll, a frame that moves in a radial direction on the opposite side of the first scroll the second scroll is interposed therebetween, forming a back pressure space with the second scroll so that the second scroll is held in a direction toward the first scroll by the pressure of the back pressure space, a back pressure passage connecting the compression chamber and the back pressure space. and a valve member provided on the back pressure passage and blocking the movement of a fluid from the back pressure space to the compression chamber.

Description

Background of the invention

Field of the invention

The present disclosure relates to a compressor, and more particularly to a motor-driven compressor driven by a motor.

Background of the invention

In general, compressors for compressing a refrigerant have been developed in vehicle air conditioning systems in a variety of forms. Recently, motor-driven compressors (or electric compressors) powered by electricity using motors have been actively developed because of the trend that vehicle parts become electronic / electric components.

Of the variety of electric compression systems, a spiral compression system suitable for high compression ratio operation is widely used. In the electric scroll type compressor, a motor part configured as a rotary motor is installed in a closed case, and a compression part including a fixed scroll and a revolving scroll is installed on one side of the motor part and the motor part and the compression part are installed by one Rotary shaft are connected, and wherein a rotational force is transmitted from the engine part to the compression part. The rotational force transmitted to the compression member causes the orbiting scroll to pivot relative to the fixed scroll to form a pair of two compression chambers, each of which includes a suction chamber, an intermediate pressure chamber, and a discharge chamber such that a refrigerant flows into the compression chamber both compression chambers is sucked and delivered simultaneously.

The related art electric compressor as described above is known to operate based on a system in which oil is separated from the refrigerant discharged from the compression chamber to a discharge part, whereby a part of the separated oil becomes a discharge part Counterpressure space is provided, which is provided on a rear surface of the orbiting scroll, and the orbiting scroll is held by the oil pressure in the direction of the fixed spiral. This is disclosed in Related Art 1 (Disclosure Japanese Patent Publication No. 2010-14108 , Published 21.1.2010) and the related art (published Korean Patent Publication No. 10-2016-0071899 , Publication date 9.12.2017).

Likewise, Related Art 3 (Korean Patent Application Laid-open No. 10-2013-0041740, published on Apr. 25, 2013) discloses a method of forming a counter-pressure hole on a revolving scroll to bypass a portion of a refrigerant compressed in the compression chamber to a back pressure space to hold the rear surface of the orbiting scroll.

Such a method is well known in the art and may be referred to as an intermediate pressure backpressure system.

However, in the case of the related intermediate pressure backpressure system, when the pressure of an intermediate pressure chamber is lower than the pressure of a back pressure space, refrigerant (or / and oil) of the back pressure space may flow back to the intermediate chamber due to a pressure difference through a back pressure hole, and the refrigerant flowing back to the intermediate pressure chamber forms a relatively high pressure in the intermediate pressure chamber, causing excessive compression.

When the pressure in the intermediate pressure chamber is lower than the pressure in the back pressure space, the refrigerant (or oil) in the back pressure space flows back to the intermediate pressure chamber due to the pressure difference through the back pressure hole. There is a problem in that the refrigerant flowing back to the intermediate pressure chamber forms a relatively high pressure relative to the pressure of the refrigerant compressed in the intermediate pressure chamber, causing an excessive compression loss.

In addition, in the intermediate pressure backpressure system of the related art, the back pressure space cooperates with the intermediate pressure chamber and thus is not maintained uniformly, failing to keep the orbiting scroll stable. As a result, a behavior of the orbiting scroll becomes unstable to cause the refrigerant in the compression chamber to leak.

Summary of the invention

Therefore, one aspect of the detailed description is to provide an electric compressor in which a pressure of a compression chamber and a pressure of a back pressure space are maintained uniformly in a system in which a part of a refrigerant that is compressed in an intermediate pressure chamber of a compression chamber, in a Counterpressure chamber is initiated, to keep a rotating spiral by the pressure of the back pressure chamber.

Another aspect of the detailed description is to provide an electric compressor in which refrigerant and oil are prevented from flowing back from a back pressure chamber to an intermediate pressure chamber due to a pressure difference between the intermediate pressure chamber and the back pressure space.

Another aspect of the detailed description is to provide an electric compressor in which refrigerant and oil are prevented from flowing back from a back pressure space to an intermediate pressure chamber by selectively opening and closing a flow path between the intermediate pressure chamber and the back pressure space.

Another aspect of the detailed description is to provide an electric compressor in which a valve for selectively opening and closing a flow path between the intermediate pressure chamber and the back pressure space is provided and the occurrence of abnormal noise during a process for opening and closing a compression chamber and the back pressure space is suppressed.

Another aspect of the detailed description is to provide an electric compressor in which a valve is smoothly moved during a process of opening and closing a compression chamber and a back pressure space.

Another aspect of the detailed description is to provide an electric compressor in which a valve for selectively opening and closing a flow path between the intermediate pressure chamber and the back pressure space is provided, and here, the valve can be easily mounted.

Another aspect of the detailed description is to provide an electric compressor in which a compression chamber and a back pressure space can be connected at a shortest distance to facilitate the manufacture of the electric compressor.

To achieve these and other advantages in accordance with the purpose of this specification, as embodied and broadly described herein, an electric compressor is provided in which a back pressure space is provided on a rear surface of a revolving scroll to provide back pressure in one direction forming a fixed scroll wherein a passage connecting a compression chamber between the fixed scroll and the orbiting scroll and the back pressure space is formed and a valve is provided to open and close the passage.

The orbiting scroll may be held by a frame coupled to the fixed scroll, and the passage may penetrate the fixed scroll and the frame.

The passage can penetrate the orbiting spiral.

The valve may be configured as a spool valve, and a connection recess may be formed so as to be connected to an outer peripheral surface of the valve and a side surface to open the passage.

To achieve these and other advantages in accordance with the purpose of this specification, as embodied and broadly described herein, an electric compressor includes: a first scroll, a second scroll engaged with the first scroll to produce orbital motion forming a compression chamber with the first spiral; a frame attached in a radial direction on the opposite side of the first spiral with the second spiral interposed therebetween, wherein a back pressure space is formed with the second spiral such that the second spiral is compressed by the pressure of the back pressure space in a direction toward the first spiral to be held; a counter pressure passage connecting the compression chamber and the back pressure space; and a valve member provided on the back pressure passage and blocking the movement of a fluid from the back pressure space to the compression chamber.

The back pressure passage may include a back pressure hole in which one end communicates with the compression chamber and the other end communicates with the back pressure space, and a valve receiving recess communicating with the back pressure hole and accommodating the valve element, and the valve element is a A check valve is configured to slidably move in accordance with a pressure difference between the compression chamber and the back pressure space in the valve receiving recess.

The valve member may include a valve portion that opens the back pressure passage at a first position and closes the back pressure passage at a second position.

The valve portion may include a first side surface, a second side surface, and a second side surface Have a circumferential surface connecting the first side surface and the second side surface, and a diameter of the first side surface and a diameter of the second side surface may be larger than an inner diameter of the counter-pressure hole and smaller than an inner diameter of the valve receiving recess.

The electric compressor may further include: an opening and closing surface formed on the first side surface of the valve portion so that at least a portion thereof is flat and larger than the inner diameter of the counter-pressure hole is formed to block the counter-pressure hole in the second position ; a holding surface formed on the second side surface of the valve portion and configured to be in contact with a side surface of the valve receiving recess; and a communicating recess deeply printed by a predetermined depth on the holding surface, opened to the peripheral surface of the valve portion, and at least partially overlapping a counter-pressure hole facing the second side surface.

The valve element may further include: at least one guide portion guiding the valve portion from the first position to the second position, and the at least one guide portion may extend in a radial direction toward an inner circumferential surface of the valve receiving recess on the peripheral surface of the valve portion.

The at least one guide portion may project from a portion without the at least a portion of the peripheral surface of the valve portion in a radial direction, and the connection recess may be opened to the peripheral surface of the valve portion positioned between the at least one guide portion.

The connection recess may have at least two end portions opened to the peripheral surface of the valve portion.

The guide portion may be provided plural times, and the plurality of guide portions may be formed along a circumferential direction at equal intervals.

The at least one guide portion may be a single guide portion, and an opposite angle of the guide portion may be greater than or equal to 180 °.

The at least one guide portion may have a thickness that is less than or equal to that of the valve portion.

A guide groove may be formed on an inner circumferential surface of the valve receiving recess so that the at least one guide portion is inserted into the guide groove to be restricted in a circumferential direction.

Further, an elastic member may be provided on one or both sides of the valve member in a moving direction.

The counter pressure passage may include: a first counter pressure hole provided on the first scroll and communicating with the compression chamber; and a second counter-pressure hole provided on the frame and communicating with the counter-pressure hole, the first counter-pressure hole and the second counter-pressure hole communicating with each other, and a valve-receiving recess receiving the valve element may be formed on a surface where the first counter-pressure hole is formed, or a surface where the second counter-pressure hole is formed, be formed.

The counterpressure passage may be formed to penetrate the second scroll facing the counterpressure space, a valve receiving recess may be formed in the center of the counterpressure passage, a stopper member limiting the movement of the valve element may be inserted into and coupled to the valve receiving recess be, and the stopper member may have a counter-pressure hole, which forms the counter-pressure passage.

To achieve these and other advantages according to the purpose of this specification, as embodied and broadly described herein, an electric compressor includes: a compression chamber formed between a first scroll and a second scroll and moving from an outside to an inside, so that their volume is reduced to compress a fluid; and a back pressure space formed between the second scroll and a frame holding the second scroll and holding the second scroll toward the first scroll; a back pressure flow path connecting the compression chamber and the back pressure space; a valve receiving recess provided in the middle of the backpressure flow path; and a check valve provided on the valve receiving recess and blocking the back pressure return flow path when a pressure of the back pressure space is higher than a pressure of the compression chamber.

The check valve may include a valve portion that is larger than an inner diameter of the backpressure flow path and smaller than an inner diameter of the valve receiving recess, wherein at least a portion of a side surface of the valve portion may be formed to be flat so as to be in close contact with one side of the valve portion To be a valve receiving recess to block the back pressure flow path, and the other side surface of the valve portion may have a connection recess to open the back pressure flow path in a state in which the other side surface of the valve portion is in close contact with the other side of the valve receiving recess.

The check valve may further include: a guide portion slidably brought into contact with an inner circumferential surface of the valve receiving recess to guide the valve portion, and at least one guide portion may project along a circumferential direction from a peripheral surface of the valve portion.

In the electric compressor according to the present disclosure, a counter pressure passage is formed between the compression chamber and the back pressure space, and a check valve is provided in the middle of the back pressure passage, whereby the refrigerant and oil can be prevented from flowing back to the compression chamber when a pressure of the compression chamber For example, when the compression is started, it is temporarily low.

Further, since the connection recess is formed on a side surface of the check valve, a large flow path area can be secured. As a result, the refrigerant and oil can move quickly from the intermediate pressure chamber to the back pressure space, effectively ensuring a back pressure.

Further, according to the present disclosure, since a flow path between the compression chamber and the back pressure space is selectively opened and closed, the pressure in the compression chamber and the pressure in the back pressure space are prevented from becoming destabilized, thus stabilizing the behavior of the orbiting scroll to compress the refrigerant evenly.

Further, in the present disclosure, an elastic member is added to a side of the check valve that opens and closes a flow path between the compression chamber and the back pressure space to suppress or minimize the occurrence of abnormal noise during the operation of opening and closing the check valve ,

Further, according to the present disclosure, the check valve opening and closing a flow path between the compression chamber and the back pressure space is guided by the guide projection and the guide recess to make the valve uniform, whereby the position of the passage can be constant Reliability of the check valve increased.

Further, according to the present disclosure, since a receiving recess for opening and closing a flow path is formed between the compression chamber and the back pressure space, the check valve can be easily mounted.

Further, in the present disclosure, since a passage connecting the compression chamber and the back pressure space is formed on the orbiting scroll forming the back pressure space, a distance between the compression chamber and the back pressure space can be minimized, which simplifies the manufacture of the electric compressor.

The broad scope of the applicability of the present application will become more apparent from the detailed description given hereinafter. It should be understood, however, that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, as will become apparent to those skilled in the art from the detailed description that various changes and modifications are possible within the scope of the invention.

list of figures

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments and, together with the description, serve to explain the principles of the invention.

• 1 ist eine Querschnittansicht, die das Innere eines elektrischen Kompressors gemäß der vorliegenden Offenbarung darstellt;
• 2 ist eine Draufsicht, die einen Zustand darstellt, in dem eine Hülle der festen Seite und eine Hülle der umlaufenden Seite in einem Kompressionsmechanismusteil gemäß 1 in Eingriff sind;
• 3 ist eine Querschnittansicht, die ein Beispiel darstellt, in dem ein Gegendruckloch derart ausgebildet ist, dass es eine feste Spirale und einen Rahmen gemäß der vorliegenden Offenbarung durchdringt;
• 4A und 4B sind jeweils vordere und hintere Perspektivansichten eines Rückschlagventils gemäß der vorliegenden Offenbarung;
• 5A und 5B sind jeweils vordere und hintere Querschnittansichten, die Zustände darstellen, in denen ein Rückschlagventil in eine Ventilaufnahmeaussparung gemäß der vorliegenden Offenbarung eingesetzt ist;
• 6A bis 8D stellen andere Ausführungsformen eines Rückschlagventils gemäß der vorliegenden Offenbarung dar, wobei 6A und 6B einen Fall darstellen, in dem ein einziger Führungsabschnitt bereitgestellt ist, 7A und 7B einen Fall darstellen, in dem zwei Führungsabschnitte bereitgestellt sind, und 8A bis 8D eine Verbindungsaussparung darstellen;
• 9A und 9B stellen einen Betrieb eines Rückschlagventils gemäß der vorliegenden Offenbarung dar, wobei 9A einen Zustand darstellt, in dem ein elektrischer Kompressor normal arbeitet, und 9B stellt einen Betrieb dar, wenn der elektrische Kompressor anläuft;
• 10 ist eine Perspektivansicht, die eine andere Ausführungsform eines Rückschlagventils gemäß der vorliegenden Offenbarung darstellt;
• 11A und 11B sind Querschnittansichten, die ein Beispiel darstellen, in dem ein Rückschlagventil ein elastisches Element gemäß der vorliegenden Offenbarung hat;
• 12 und 13 sind Querschnittansichten, die andere Ausführungsformen eines Rückschlagventils und einer Ventilaufnahmeaussparung gemäß der vorliegenden Offenbarung darstellen; und
• 14 ist eine Querschnittansicht, die ein Beispiel darstellt, in dem ein Gegendruckloch derart ausgebildet ist, dass es eine umlaufende Spirale durchdringt.

In the drawings:

• 1 FIG. 12 is a cross-sectional view illustrating the interior of an electric compressor according to the present disclosure; FIG.
• 2 FIG. 11 is a plan view illustrating a state in which a fixed-side shell and a circumferential-side shell are in one. FIG Compression mechanism part according to 1 are engaged;
• 3 FIG. 12 is a cross-sectional view illustrating an example in which a counter-pressure hole is formed so as to penetrate a fixed scroll and a frame according to the present disclosure; FIG.
• 4A and 4B FIG. 15 are front and rear perspective views, respectively, of a check valve according to the present disclosure; FIG.
• 5A and 5B 13 are front and rear cross-sectional views, respectively, illustrating states in which a check valve is inserted into a valve receiving recess according to the present disclosure;
• 6A to 8D illustrate other embodiments of a check valve according to the present disclosure, wherein 6A and 6B illustrate a case in which a single guide portion is provided 7A and 7B illustrate a case where two guide portions are provided, and 8A to 8D represent a connection recess;
• 9A and 9B illustrate operation of a check valve according to the present disclosure, wherein 9A represents a state in which an electric compressor operates normally, and 9B represents an operation when the electric compressor starts up;
• 10 FIG. 4 is a perspective view illustrating another embodiment of a check valve according to the present disclosure; FIG.
• 11A and 11B FIG. 15 is cross-sectional views illustrating an example in which a check valve has an elastic member according to the present disclosure; FIG.
• 12 and 13 FIG. 12 is cross-sectional views illustrating other embodiments of a check valve and a valve receiving recess according to the present disclosure; FIG. and
• 14 Fig. 12 is a cross-sectional view illustrating an example in which a counter-pressure hole is formed so as to penetrate a revolving scroll.

Detailed description of the invention

Now, a description of the exemplary embodiments will be given in detail with reference to the accompanying drawings. In the brief description with reference to the drawings, the same or equivalent components are given the same reference numerals and their description is not repeated.

Hereinafter, an electric compressor according to an embodiment of the present disclosure will be described in detail with reference to the accompanying drawings.

1 FIG. 12 is a cross-sectional view illustrating the interior of an electric compressor according to the present disclosure; and FIG 2 FIG. 10 is a plan view illustrating a state in which a fixed-side shell and a circumferential-side shell are provided in a compression mechanism part according to FIG 1 are engaged.

As in 1 and 2 10, a low-pressure electric scroll compressor (hereinafter referred to as an "electric compressor") according to the present embodiment includes a drive motor 103 which is a motor part, and a compression mechanism part 105 , the refrigerant using a rotational force of the drive motor 103 drives.

The compressor housing 101 includes an inlet opening 111 to which a suction pipe is connected, and an exhaust port 121 to which a delivery tube is connected. A suction room S1 is each at the inlet opening 111 trained and a delivery room S2 is at the outlet opening 121 educated. The drive motor 103 is in the intake chamber S1 installed, and the compressor of the present embodiment is a low-pressure compressor.

The compressor housing 101 includes a main body 110 in which the drive motor 103 is installed, and a rear housing 120 that with an open rear end of the main body 110 is coupled. An interior of the main housing 110 forms together with one side of the compression mechanism part 105 the suction space S1 , and an interior of the rear housing 120 forms together with the other side of the compression mechanism part 105 the delivery room S2 ,

The main body 110 has a cylindrical section 111 with a cylindrical shape, a closed section 112 extends integrally from a front end of the cylindrical portion 111 and is closed, and an opening 113 is at a rear end of the cylindrical portion 111 educated.

Meanwhile, the drive motor 103 , which forms a motor part, inside the main housing 110 press-fitted and coupled with it. The drive motor 103 includes a stator 131 inside the main body 110 is attached, and a rotor 132 inside the stator 131 is positioned and through an interaction with the stator 131 is turned.

The stator 131 is at an inner peripheral surface of the main body 110 shrink fit and attached. A rotary shaft 133 is to an inner peripheral surface of the rotor 132 press-fitted and coupled with it.

The rotary shaft 133 is with the middle of the rotor 132 coupled, and a rear end thereof, the compression mechanism part 105 is facing, as described later, to the frame 140 and the solid spiral 150 cantilevered.

Meanwhile, in the scroll compressor according to the present embodiment, the orbiting scroll coupled to the rotating shaft is held by the frame and is rotatively moved relative to the fixed scroll, thereby forming the compression mechanism part.

As in 1 and 2 illustrated, includes the compression mechanism part 105 a frame 140 a fixed spiral (hereinafter referred to as a "first spiral") 150 that from the frame 140 and a orbiting scroll (hereinafter referred to as a "second scroll") 160 between the frame 140 and the first spiral 150 is provided and makes a circular motion.

The frame 140 is with a front opening 113 of the main housing 110 coupled. The first spiral 150 gets stuck on a back surface of the frame 140 held, and the second spiral 160 will be rotatable on the back surface of the frame 140 held so that they make a circular motion between the first spiral 150 and the frame 140 makes. The second spiral 160 is in a non-centered manner with the rotary shaft 133 coupled with the rotor 132 of the drive motor 103 coupled, and makes a rotational movement relative to the first spiral 150 where a pair of compression chambers V is formed, comprising a suction chamber, an intermediate pressure chamber and a discharge chamber.

The frame 140 includes a disc plate section 141 with a disk shape and a frame side wall portion 142 from a rear side surface of the frame disk section 141 in the direction of the first spiral 150 protrudes and allows a side wall section 152 the first spiral 150 (which will be described below) is coupled.

A frame axial pressure surface 143 is on an inner side of the frame side wall portion 142 educated. The second spiral 160 is in an axial direction on the frame axial pressure surface 143 mounted and held on it. A backpressure room 144 is in the middle of the frame axial pressure surface 143 formed and with a portion of the refrigerant that is in the compression chamber V is compressed, and oil filled to the rear surface of the second spiral 160 to keep. Consequently, a pressure of the back pressure chamber corresponds 144 an intermediate pressure between a pressure of the suction space S1 and an end pressure (ie, discharge space) of the compression chamber V , This will be described later together with opening and closing of a check valve of the compression chamber and the back pressure chamber.

A frame shaft hole 145 through which the rotary shaft 133 is in the middle of the backpressure room 144 and a first bearing (not shown) is formed on an inner peripheral surface of the frame shaft hole 145 provided. The first bearing may be formed of a plain bearing, but in some cases it may be a ball bearing. Here, the sliding bearing is less expensive than the ball bearing, and hence the sliding bearing is advantageous in terms of cost, and the sliding bearing is also easily mounted and its weight and noise are reduced.

The back pressure chamber 144 can by a first sealing element 191 placed on a thrust surface between the frame 140 and the second spiral 160 is provided, and a second sealing element 192 that is between the inner peripheral surface of the frame 140 and an outer peripheral surface of the rotary shaft 133 is arranged to be sealed. The second sealing element 192 however, may be omitted in some cases.

Meanwhile, the first spiral 150 stuck with the frame 140 be coupled or can to the housing 110 Press-fitted and attached to it.

In the first spiral 150 is a solid spiral disc plate portion (hereinafter referred to as a "fixed side disc plate portion") 151 is formed to have a substantially disk shape, and a fixed spiral sidewall portion (hereinafter referred to as a "first sidewall portion") 152 that with the sidewall section 142 of the frame 140 is coupled to the edge of the disc plate portion 151 the solid side formed. A case 153 the solid side, with a shell 162 the circumferential side (to be described later) is engaged around the compression chamber V is on a front side of the disc plate section 151 the solid side formed. The case 153 the fixed side will later along with the shell 162 described the circulating page.

A suction flow path (not shown) is on a side of the first side wall portion 152 designed so that the suction chamber S1 and a suction chamber (not shown) communicate with each other, and a discharge port 155 is in a central portion of the disc plate portion 151 formed on the fixed side and communicates with a discharge chamber, so that the compressed refrigerant to the discharge space S2 is delivered. Only one discharge opening 155 may be formed such that it both with a first compression chamber V1 as well as a second compression chamber V2 (to be described later), or a first discharge port 155a and a second discharge opening 155b may be formed such that they each with the first compression chamber V1 and the second compression chamber V2 stay in contact.

The second spiral 160 can between the frame 140 and the first spiral 150 be provided and may be in a decentered manner with the rotary shaft 133 be coupled so that it is rotatable.

In the second spiral 160 is a orbiting scroll disk portion (hereinafter referred to as a "disk side disk portion") 161 formed so that it has a substantially disc shape, and a shell 162 the surrounding side, with the shell 153 the fixed side engages to form a compression chamber is on a rear side of the disc plate portion 161 formed the circumferential side. The case 162 The wrap around side can be along with the wrapper 153 the fixed side may be formed in an involute shape or may be formed in a variety of other shapes.

The case 162 The circumferential side may have a shape in which a plurality of circular arcs having different diameters and starting points are connected to each other, and the outermost curve may have a substantially oval shape with a longer axis and a shorter axis. This can also be the case 153 be the same on the firm side.

A rotary shaft coupling section 163 can in a penetrating manner in a central portion of the disc plate portion 161 be formed of the circumferential side. The rotary shaft coupling section 163 may be an inner end portion of the shell 162 form the circumferential side, and an eccentric section 133a the rotary shaft 133 (to be described later) may be rotatable in the Drehwellenkopplungsabschnitt 163 be used and coupled with it. An outer peripheral portion of the rotary shaft coupling portion 163 can with the shell 162 coupled to the circumferential side, during a compression process together with the shell 153 the fixed side to form the compression chamber V.

The rotary shaft coupling section 163 is formed so that it has a height which is on the same plane as the shell 162 the circumferential side overlaps, leaving the eccentric section 133a the rotary shaft 133 can be arranged at a height that is on the same level as the hull 162 the surrounding side overlaps. Consequently, a repulsive force and a compressive force of the refrigerant with respect to the disk-plate portion of the circumferential side are applied to the same plane so as to cancel each other, and thus the inclination of the second scroll 160 due to the effect of the compression force and the repulsive force can be prevented.

The rotary shaft coupling section 163 has a concave section 163a who with a head start 153a the shell 153 the fixed side (to be described later) on an outer peripheral portion which is an inner end of the sheath 153 the solid side faces, engages, and an enlarged portion 163b is on one side of the concave section 163 is formed and is on an upstream side along a direction of formation of the compression chamber V formed, and a thickness of the enlarged portion 163b is from an inner peripheral portion to an outer peripheral portion of the rotary shaft coupling portion 163 increased.

An enlarged section 163b is on one side of the section 163a along the formation direction of the compression chamber V formed to be the thickness from the inner peripheral portion to the outer peripheral portion of the rotary shaft coupling portion 163 on the upstream side to enlarge. In this way, a compression path of the first compression chamber V1 extended immediately before delivery, and as a result, a compression ratio of the first compression chamber V1 be increased so that it is close to a compression ratio of the second compression chamber V2 is.

A circular arc compression surface 163c with a circular arch shape is on the other side of the concave section 163a educated. A diameter of the circular arc compression surface 163c is through a thickness of an inner end portion of the sheath 153 the fixed side (ie, a thickness of a discharge end) and a circumferential radius of the sheath 162 the circumferential side determined. If here the thickness of the inner end portion of the shell 153 the solid side is increased, the diameter of the circular arc compression surface 163c increased. Consequently, a thickness of the wrapper of the circumferential side also becomes around the circular arc compression surface 163c Increased to ensure durability, and as a compression path is extended, also a compression ratio of the second compression chamber V2 be enlarged.

A lead 153a toward an outer peripheral portion of the rotary shaft coupling portion 163 protrudes, is in the vicinity of an inner end portion (suction end or start end) of the shell 153 the fixed side, the rotary shaft coupling section 163 corresponds, formed, and a contact portion 153b can from the projection 153a protrude, leaving it with the concave section 163a is engaged. That is, the inner end portion of the sheath 153 the fixed side may have a greater thickness than that of other sections. As a result, the sheath strength of the inner end portion, the largest compression force in the sheath 153 the solid side is exposed, can be improved to improve the durability.

The compression chamber V is between the disc plate section 151 the solid side and the shell 153 the fixed side and between the shell 162 the circumferential side and the disc plate section 161 formed on the circumferential side, and the suction chamber, the intermediate pressure chamber and the discharge chamber can be formed continuously according to a direction of movement of the sheaths.

The compression chamber V can be the first compression chamber VI between an inside surface of the shell 153 the solid side and an outside surface of the shell 162 the circumferential side is formed, and a second compression chamber V2 between an outside surface of the shell 153 the solid side and an inside surface of the shell 162 the circumferential side is formed comprise. That is, the first compression chamber V1 is between two contact points P11 and P12 formed, which are formed when the inner side surface of the shell 153 the solid side and the outside surface of the shell 162 the circumferential side in contact, and the second compression chamber V2 is between two contact points P21 and P22 formed, which are formed when the outer side surface of the shell 153 the solid side and the inside surface of the shell 162 the rotating side in contact.

If here in the first compression chamber V1 Immediately before giving off an angle with a greater value from angles passing through two lines connecting the center O the eccentric section, ie the middle O of the rotary shaft coupling section, and the two contact points P11 and P12 α, α may be smaller than 360 ° (α <360 °) at least immediately before the start of discharge, and a distance ℓ between normal vectors at the two contact points P11 and P12 has a value greater than 0.

As a result, the compression chamber has a smaller volume as compared with a case where the first compression chamber immediately before discharge comprises a fixed-side shell and a circumferential-side shell forming an involute curve, and thus both a compression ratio the first compression chamber V1 and a compression ratio of the second compression chamber V2 be improved.

In the figure, the reference numeral designates 137 a balance weight.

The scroll compressor according to the embodiment described above operates as follows.

That is, when power to the drive motor 103 is applied, the rotary shaft rotates 133 together with the rotor 132 to apply a torque to the second spiral 160 to transfer, and the second spiral 160 makes by a rotation protection mechanism a circulating movement, and consequently, the compression chamber V continuously moving toward the middle side while decreasing its volume.

The refrigerant then flows through the suction port 111 in the suction room S1 and that in the suction room S1 introduced refrigerant passes through a flow path formed on an outer peripheral surface of the stator 131 and an inner peripheral surface of the main body 110 or an air gap between the stator 131 and the rotor 132 is formed by the Ansaugströmungsweg 154 in the compression chamber V to be sucked.

Here comes some of the refrigerant that passes through the intake 111 in the suction room S1 is sucked in contact with the closed section 112 , which has a front side surface of the main body 110 is before it's the drive motor 103 passes. Consequently, the closed section exchanges 112 with the cold suction refrigerant heat and is cooled by this, to a (not shown) inverter module, which is on the outer side surface of the main housing 110 is attached to cool.

The refrigerant flowing through the suction chamber S1 in the compression chamber V is sucked in, by the first spiral 150 and the second spiral 160 Compresses and gets through the delivery port 155 to the delivery room S2 issued. In the delivery room S2 the refrigerant and oil are separated, and the refrigerant passes through the outlet port 121 delivered to a refrigeration cycle while the oil is in a lower portion of the discharge space S2 collects.

As described above, in the method of compressing the refrigerant in the compression chamber between the first scroll and the second scroll, the second scroll as the orbiting scroll due to the pressure of the compression chamber can be pushed toward the frame. In this case, a gap between the first scroll and the second scroll may be formed to cause leakage between the compression chambers. This phenomenon can be suppressed by pressure of the back pressure space formed on the back side of the second scroll, that is, between the second scroll and the frame.

As described above, in the back pressure space, a part of the refrigerant compressed in the middle of the compression chamber, that is, the intermediate pressure chamber is supplied to the back pressure space through the back pressure hole, and thus the pressure in the back pressure space forms the intermediate pressure. Therefore, the second scroll is urged toward the first scroll by the force of the pressure in the back pressure space, so that the second scroll can be prevented from moving away from the first scroll. Here, the counter-pressure hole may be formed so as to penetrate the first scroll and the frame, or may be formed to penetrate the second scroll. 3 FIG. 12 is a cross-sectional view illustrating an example in which the counter-pressure hole is formed so as to penetrate the first scroll and the frame.

As in 3 shown, the back pressure hole 170 a first counter-pressure hole 171 that at the first spiral 150 is formed, and a second counter-pressure hole 172 on the frame 140 is formed include.

A first end 171a the first counter-pressure hole 171 is open to the intermediate pressure chamber of the compression chamber V to communicate, and a second end 171b the first counter-pressure hole 171 is to a back surface (ie, a solid surface in contact with the frame) of the disc plate portion 151 the fixed side (that is, a mounting surface in contact with the frame) open.

A first end 172a the second counter-pressure hole 172 is to the front surface (ie, a solid surface in contact with the first spiral) of the frame-side wall portion 142 open to the second end 171b the first counter-pressure hole 171 to communicate, and the second end 172b the second counter-pressure hole 172 is open to with a sidewall surface of the back pressure chamber 144 to communicate. Consequently, there are the first counter-pressure hole 171 and the second counter-pressure hole 172 in communication with each other about the compression chamber V and the back pressure space 144 connect to.

When the compression chamber V and the backpressure room 144 through the counter-pressure hole 170 which, as described above, the first counter-pressure hole 171 and the second counter-pressure hole 172 are connected, moves the refrigerant with the intermediate pressure, which is compressed in the compression chamber A, through the counter-pressure hole 170 to the backpressure room 144 , and a back pressure, which is formed by the intermediate-pressure refrigerant, which is to the back pressure chamber 144 moves, holding the second spiral 160 in one direction on the first spiral 150 to.

However, the pressure in the compression chamber is changed while the compressor is operating, stopping and restarting, and while the pressure in the compression chamber is being changed, the pressure in the back pressure space becomes 144 also changed. For example, the pressure in the compression chamber V is not sufficiently reduced in an initial phase of the operation of the compressor or during a saving operation, so that the pressure in the intermediate pressure chamber is lower than the pressure in the back pressure space 144 is, but when the compressor reaches a normal operation, or during a power operation, the pressure in the compression chamber (intermediate pressure chamber) V higher than the pressure in the back pressure space 144 and this process is repeated. Here, when the pressure in the compression chamber V is higher than the pressure in the back pressure space 144 is, moves the refrigerant (or / and oil) in the compression chamber (intermediate pressure chamber) through the counter-pressure hole 170 to the backpressure room 144 , where a normal back pressure is generated, but when the pressure in the compression chamber V lower than the pressure in the back pressure space 144 is, the refrigerant (and / or oil) in the back pressure chamber 144 through the counter-pressure hole 170 flow back to the intermediate pressure chamber. In this case, the pressure in the intermediate pressure chamber can be increased, so that the compression efficiency is deteriorated due to excessive compression.

In view of this, in this embodiment, a valve receiving recess 175 in the Center of the counter-pressure hole 170 trained, and a check valve 180 Can be installed to the back pressure hole 170 optionally open and close while moving according to a pressure difference between the compression chamber (intermediate pressure chamber) and the back pressure space 144 between a first position P1 and a second position P2 emotional. Here is the first position P1 a position in which the counterpressure passage 170 open, and the second position P2 is a position in which the back pressure passage 170 closed (blocked).

The valve receiving recess 175 can be in the middle of the first counter-pressure hole 171 or the second counter-pressure hole 172 ie between the first ends 171a and 172a and the second ends 171b and 172b the first counter-pressure hole 171 or the second counter-pressure hole 172 be educated. Alternatively, the valve receiving recess 175 considering the processing or assembly at the second end 171b the first counter-pressure hole 171 or the first end 172a the second counter-pressure hole 172 be formed, or a half of the valve receiving recess 175 may be at the second end 171b the first counter-pressure hole 171 be formed and another half of the valve receiving recess 175 may be at the first end 172a the second counter-pressure hole 172 be educated. Hereinafter, an example will be described in which the valve receiving recess 175 at the second end 171b the first counter-pressure hole 171 is trained.

The valve receiving recess 175 is as a cylindrical recess with an inner diameter D2 that is larger than an inside diameter D1 the first counter-pressure hole 171 is, trained. Thus, a first valve seat surface 175 at an end portion of the valve receiving recess 175 adjacent to the first spiral 180 be formed, so that an opening and closing surface 181a having a first side surface in a valve section 181 the check valve 180 (which will be described later) is releasably secured. The first valve seat surface 175a may be flat or may be stepped such that a sealing surface for increasing a sealing force with respect to the check valve 180 the first counter-pressure hole 171 encloses.

Likewise, the other end of the valve receiving recess 175 open and an inside diameter D1 ' the second counter-pressure hole 172 is formed so that it is the same size as the inner diameter D1 the first counter-pressure hole 171 is, and in this way, a section without the second counter-pressure hole 172 through the front surface of the frame 140 blocked. Consequently, a second valve seat surface 175b in the vicinity of the end of the second counter-pressure hole 172 be formed, so that a holding surface 181 having a second side surface of the valve portion 181 the check valve 180 forms, is releasably secured. Like the first valve seat surface, the second valve seat surface may also be flat or have a sealing surface.

Meanwhile, the check valve 180 as described above, be configured as a spool valve that varies according to a pressure difference between the compression chamber V and the backpressure room 144 as a whole between the first position P1 and the second position P2 emotional.

The check valve 180 can the valve section 181 , which is essentially the counter-pressure hole 170 opens and closes, and a guide section 182 for guiding the valve section 181 so that it moves stably back and forth.

The valve section 181 can have a first side surface (opening and closing surface) 181a , a second side surface (holding surface) 181b and a peripheral surface which is the first side surface 181a and the second side surface 181b connects, and may have a short circular bar shape or a disc plate or a disc shape with a predetermined thickness.

A diameter D3 the first page surface 181a and a diameter D3 ' the second side surface 181b can be larger than the inside diameter D1 or D1 ' the counter-pressure hole 170 and smaller than the inner diameter D2 the valve receiving recess 175 his. Consequently, the valve section brings 181 the counter-pressure hole 170 in the first position P1 in connection and can the counter-pressure hole 170 in the second position P2 To block.

On the first side surface of the valve section 181 can have an opening and closing surface 181a for opening and closing the first counter-pressure hole 171 be educated. The opening surface 181a can be larger than the inside diameter D1 the first counter-pressure hole 171a be formed to the first counter-pressure hole 171 in the second position P2 to block. The opening surface 181a may be formed to be flat on the entire first side surface or may be flat only in a central portion of the first side surface and may not be formed at its periphery.

The second side surface of the valve section 181 can the holding surface 181b have that around the second backpressure hole 172 releasably attached to the second valve seat surface 175b should be attached. The holding surface 181b can be designed flat to be in the first position P1 in contact with a side surface of the valve 175 ie the second valve seat surface 175b , to be.

At least one leadership section 182 can be trained. Of course, several guide sections 182 with regard to the stability of the check valve 180 be beneficial. However, if the number of guide sections 182 big, can the speed of the check valve 180 be deteriorated due to frictional resistance. Therefore, it is necessary to know the number and a sectional area of the guide section 182 suitable for frictional resistance.

As in 4A to 5B For example, three guide sections may be illustrated 182 be educated. In this case, the guide sections 182 be formed at a distance of 120 degrees along the circumferential direction.

As further in 6A and 6B shown, only one guide section 182 be educated. However, if a guide section 182 provided, an enclosed angle ( α ) on both sides, which is the guide section 182 form, be 180 ° or greater. If the included angle ( α ) is smaller than 180 °, is an opening side angle between both sides of the guide portion 182 180 ° or larger, and as a result, an outer circumferential surface of the guide portion becomes 182 from the inner peripheral surface of the valve receiving recess 175 disconnected and she can not serve as a valve. Although the opening side angle in this case between the two side surfaces of the guide portion 182 180 ° or greater, the opening and closing surface can be 181a of course the first counter-pressure hole 171 open and close when a depth of the opening side is flat. The check valve 180 can then serve as a valve. Nevertheless, the valve section is 181 the check valve 180 in its movement in the valve receiving recess 175 in his behavior in the valve receiving recess 175 not uniform, but fluctuates, causing valve noise or failure in the uniform opening and closing of the counter-pressure hole, resulting in a deterioration of the reliability.

Likewise, the guide section 182 , as in 7A and 7B shown to be formed on both sides. In this case, the guide sections 182 be formed at an equal distance of 180 ° so that they are in equilibrium when the check valve 180 is moved.

Meanwhile, a connection recess 183 be formed so that they in a central portion of the holding surface 181b is deeply printed by a predetermined thickness, so that the second counter-pressure hole 172 even then is open when the holding surface 181b in contact with the second valve seat surface 175b is. As a result, it can be ensured that the area of the flow path of the refrigerant and the oil extending from the intermediate pressure chamber to the back pressure space 144 move, is large, and the back pressure against the orbiting scroll can be quickly ensured.

The connection recess 183 may be to a peripheral surface of the valve portion 181 be open and at least a portion of it can be the second counter-pressure hole 172 , that of the holding surface 181 facing, overlap. The connection recess 183 can have different shapes. For example, the connection recess 183 , as in 4B shown to have a T-shape. In this case, three opening ends 183a each between the guide sections 182 be open to form a type of connection flow path.

Likewise, the connection recess 183 be designed so that they, as in 8A shown on a peripheral surface of one side of the valve portion 181 is open and extends to a middle section, or may, as in 8B shown on a peripheral surface of one side of the valve portion 181 be open, extend to a central portion and be enlarged by the central portion, so that they are larger than the second counter-pressure hole 172 is. Alternatively, the connection recess 183 , as in 8C represented over both outer peripheral surfaces of the valve portion 181 be formed, or the entire second side surface 181b of the valve section 181 can, as in 8D Shown to be stepped to as the connection recess 181 to be used. In addition, the connection recess 183 as described above, have any shape as long as they are on the peripheral surface of the valve portion 181 is open and with the second counter-pressure hole 172 communicates.

Meanwhile, the check valve 180 be formed of a material that is light and slippery considering that it is a spool valve that is moved by a pressure difference.

Operational effects of the check valve 180 that is provided in the counter-pressure hole in the electric compressor according to the present embodiment as described above are as follows.

That is, when the compressor, as in 9A shown, operates normally or the pressure in the intermediate pressure chamber higher than the pressure in the back pressure chamber 144 is a part of moving in the intermediate pressure chamber V compressed refrigerant through the first counter-pressure hole 171 in the direction of the valve receiving recess 175 , Then the check valve 180 by the refrigerant flowing from the intermediate pressure chamber through the first counter-pressure hole 171 in the direction of the backpressure chamber 144 flows, pressed and in this way becomes the first counter-pressure hole 171 open. The refrigerant extending from the first backpressure chamber 144 to the valve receiving recess 175 moves, moves through the connection recess 183 between the on the second side surface of the check valve 180 trained holding surfaces 181b to the second counter-pressure hole 172 , and the refrigerant is in the back pressure chamber 144 introduced to form a back pressure.

If the compressor, however, as in 9B is shown, stopped or the pressure in the intermediate pressure chamber lower than the pressure in the back pressure chamber 144 is, the refrigerant flows in the back pressure chamber 144 through the second counter-pressure hole 172 into the valve receiving recess 175 , Then the check valve 180 by the refrigerant coming from the back pressure chamber 144 through the second counter-pressure hole 172 flows to the intermediate pressure chamber, pressed and is in the direction of the first counter-pressure hole 171 emotional. Then the opening surface becomes 181a the check valve 180 in close contact with the first valve seat surface 175a the valve receiving recess 175 brought to the first counter-pressure hole 171 to block. Then it prevents the refrigerant in the back pressure chamber 144 flows back to the intermediate pressure chamber. When the pressure of the compression chamber (intermediate pressure chamber) V is then increased to a predetermined pressure, the check valve 180 again in the direction of the second counter-pressure hole 172 too closed to open the back pressure hole. This sequential procedure is repeated.

In this way, the pressure when the compressor is operating or the pressure of the intermediate pressure chamber, even when the compressor is stopped or the pressure in the intermediate pressure chamber is reduced, can be maintained to be higher than the pressure of the back pressure chamber, whereby the second Spiral even at the initial drive of the compressor can be prevented from being excessively separated from the first spiral. Consequently, the pressure of the compression chamber is rapidly increased to the discharge pressure, which increases the compressor efficiency.

In addition, even when the pressure of the intermediate pressure chamber is low, when the compressor starts to operate, or in an initial phase of operation, the refrigerant flows at a relatively high pressure from the back pressure space back to the intermediate pressure chamber. Thus, pulsation of the pressure at the intermediate pressure chamber can be suppressed to make the compression process uniform, and loss due to excessive compression generated when the pressure at the intermediate pressure chamber is excessively increased can be prevented in advance.

In the embodiment described above, the thicknesses of the valve portion and the guide portion are equal. However, in some cases, the thickness of the guide portion may be thinner than the thickness of the valve portion. As in 10 is shown, for example, the thickness of the valve section 181 formed such that it is thicker than the thickness of the guide portion 182 is, and at a section where the valve section 181 and the guide section 182 may be in contact with each other, may have a stepped surface 182a be educated. In this case, the thickness of the guide section is 182 reduced so far, the area of the guide section 182 in contact with the inner peripheral surface of the valve receiving recess 175 is reduced to reduce the frictional resistance. Therefore, the check valve 180 be moved faster, leaving the check valve 180 even if the pressure in the intermediate pressure chamber is a little low at the time of restarting the compressor, it can be quickly opened to the pressure in the backpressure chamber 144 increase quickly.

Meanwhile, in the embodiments described above, the check valve is moved only by a pressure difference, but in some cases, an elastic member may be provided on at least one of both sides of the check valve in a moving direction.

If, for example, an elastic element 186 , as in 11A shown on the first side surface of the check valve 180 is provided, the counter-pressure hole 170 open faster, and if the elastic element 186 , as in 11B shown on the second side surface of the check valve 180 is installed, the counter-pressure hole can 170 be closed faster. If the elastic 186 on each of the first page surface 181a and the second side surface 181b the check valve 180 can be installed, noise, such as impact noise, during the process of opening and closing the check valve 180 occur, be absorbed, around the overall noise due to the check valve 180 to reduce.

Likewise, the inner peripheral surface of the valve receiving recess 175 in the above-described embodiments, a circular shape, and the guide portion 182 the check valve 180 has a circular arc shape, leaving the check valve 180 rotatable in the valve receiving recess 175 is provided. However, the valve receiving recess can 175 and the check valve 180 be engaged in the circumferential direction, so that the check valve 180 in a predetermined path along the valve receiving recess 175 can be moved.

For example, as in 12 shown, a guide recess 175c on an inner peripheral surface of the valve receiving recess 175 be formed, so that the guide section 182 the check valve 180 can be used in it. The guide recess 175c can along a length direction of the valve receiving recess 175 be educated. Because the guide section 182 in the guide recess 175c the valve receiving recess 175 is used, the check valve 180 thus prevented from rotating in a circumferential direction and reciprocates along the same path.

Alternatively, as in 13 shown, a guide recess 182b on an outer peripheral surface of the guide portion 182 be formed, and a leadership advantage 175d can on an inner peripheral surface of the valve receiving recess 175 be educated. A leadership advantage 175d the valve receiving recess 175 can in the guide recess 182b of the guide section 182 be used to stop the rotation of the check valve 180 in the circumferential direction. Of course, the guide projection and the guide recess may be formed on the guide portion and the valve receiving recess, respectively.

If the guide recess 175c or the leadership lead 175d as described above, on the valve receiving recess 175 is formed in an axial direction, the check valve rotates 180 not in the circumferential direction, and thus can the behavior of the check valve 180 be further stabilized.

In addition, the opening end 183a the connection recess 183 attached to the check valve 180 is provided in a predetermined position, for example, at the lowest position, be formed. If the electric compressor is installed in a lateral direction and if the oil in the compression chamber V through the first counter-pressure hole 171 together with the refrigerant into the valve receiving recess 175 The oil, albeit a part of the oil on the underside of the valve receiving recess, may be introduced 175 is present, through the connection recess 183 slightly in the direction of the second counter-pressure hole 172 be moved, and thus the pressure in the back pressure chamber 144 be increased faster to a suitable value.

Meanwhile, another embodiment of the electric compressor according to the present disclosure is as follows.

That is, in the above embodiments, the backpressure hole is formed so as to penetrate the first scroll and the frame, but the backpressure hole may be formed to penetrate the disk plate portion of the circumferential side of the second scroll. 14 FIG. 12 is a cross-sectional view illustrating an example in which the counter-pressure hole is formed so as to penetrate the orbiting scroll according to the present disclosure.

As shown in the figure, there is a first counter-pressure hole 271 in the intermediate pressure chamber V in the direction of the backpressure chamber 144 formed, and a valve receiving recess 275 may be formed to be at one end (the second end in the direction of the back pressure space in the drawing) from both ends of the first counter-pressure hole 271 is enlarged.

A stop element 276 with a second counter-pressure hole 272 can into an opening end of the valve receiving recess 275 be used and coupled with it. As a result, the check valve moves 180 inside the valve receiving recess 275 back and forth. The stop element 276 can attach to the valve receiving recess 275 can be press-fitted, can be engaged in a helical form or can be joined using an adhesive or welding.

The second backpressure hole 272 that together with the first counter-pressure hole 271 forms a counter pressure passage may be formed at a position and have a size which, as in the embodiment described above always with the connection recess 183 the check valve 180 communicates, and the opening and closing surface 181 the check valve 180 is larger than an inner diameter of the first counter-pressure hole 271 trained to the first counter-pressure hole 271 to open and close. The other basic configuration and the corresponding operational effects of the check valve 180 and of Counter-pressure holes are similar to those of the embodiments described above. However, the present embodiment can be easily machined as compared with the above-described embodiments. That is, in the embodiments described above, the back pressure hole is 170 designed so that it is the first spiral 150 and the frame 140 penetrates, and in this way becomes a path of the counter-pressure hole 170 extended. Thus, it is difficult, the counter-pressure hole 170 form, and there the first counter-pressure hole 171 and the second counter-pressure hole 172 must be precisely aligned, in the manufacture of the electric compressor, a high precision may be required. However, in the case of the formation of the counter-pressure hole 270 at the disc plate portion 161 the second spiral 160 as in the present embodiment, the length of the counter-pressure hole 270 in short, and there the counter-pressure hole 270 on which one element is formed, it is advantageous in the manufacture of the electric compressor. Because the length of the counter-pressure hole 170 is short, a pressure drop of the refrigerant can be limited so far, the back pressure of the back pressure chamber 144 is increased quickly.

The foregoing embodiments and advantages are merely exemplary in nature and are not to be considered as limiting the present disclosure. The present teachings are readily applicable to other types of devices. This description is intended to be illustrative and not intended to limit the scope of the claims. Many alternatives, modifications and variations will become apparent to those skilled in the art. The features, structures, methods, and other characteristics of the example embodiments described herein may be combined in a variety of ways to obtain additional and / or alternative exemplary embodiments.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• JP 201014108 [0004]
• KR 1020160071899 [0004]

Claims (15)

Electric compressor comprising: a first spiral (150); a second volute (160) engaging with the first volute (150) to provide orbital motion to form a compression chamber (V) with the first volute (150); a frame (140) fixed in a radial direction on the opposite side of the first scroll (150) with the second scroll (160) interposed therebetween, wherein a back pressure space (144) is formed with the second scroll (160) such that the second scroll (160) is held in a direction toward the first scroll (150) by the pressure of the back pressure space (144); a counter pressure passage connecting the compression chamber (V) and the back pressure space (144); and a valve member (180) provided on the back pressure passage and blocking movement of a fluid from the back pressure space (144) to the compression chamber (V). Electric compressor after Claim 1 wherein the counter pressure passage includes a counter pressure hole (170) having one end communicating with the compression chamber (V) and the other end communicating with the back pressure space (144), and a valve receiving recess (175) connected to the back pressure hole (175). 170) communicates with and receives the valve element (180), and the valve element (180) is configured as a check valve which slidably moves in accordance with a pressure difference between the compression chamber (V) and the back pressure space (144) in the valve receiving recess (175) , Electric compressor after Claim 2 wherein the valve member (180) includes a valve portion (181) which opens the back pressure passage at a first position (P1) and closes the back pressure passage at a second position (P2). Electric compressor after Claim 1 . 2 or 3 wherein the valve portion (181) has a first side surface (181a), a second side surface (181b) and a peripheral surface connecting the first side surface (181a) and the second side surface (181b), and a diameter (D3) of the first side surface (181a) and a diameter (D3 ') of the second side surface (181b) is larger than an inner diameter (D1, D1') of the counter-pressure hole (170) and smaller than an inner diameter (D2) of the valve receiving recess (175). Electric compressor after Claim 4 further comprising: an opening and closing surface (181a) formed on the first side surface (181a) of the valve portion (181) so that at least a portion thereof is flat and larger than the inner diameter (D1, D1 ') of the Counter-pressure hole (170) is formed to block the counter-pressure hole (170) in the second position (P2); a holding surface (181b) formed on the second side surface (181b) of the valve portion (181) and configured to be in contact with a side surface of the valve receiving recess (175); and a communication recess (183) deeply printed by a predetermined depth on the support surface (181b), opened to the peripheral surface of the valve portion (180), and a counter-pressure hole (172) facing the second side surface (181b) at least partially overlaps. Electric compressor according to one of the Claims 3 to 5 wherein the valve member (180) further comprises at least one guide portion (182) leading the valve portion (180) from the first position (P1) to the second position (P2), and the at least one guide portion (182) is in one Radially extending toward an inner peripheral surface of the valve receiving recess (175) on the peripheral surface of the valve portion (180). Electric compressor after Claim 6 wherein the at least one guide portion (182) protrudes from a portion without the at least a portion of the peripheral surface of the valve portion (181) in a radial direction, and the connection recess (183) to the peripheral surface of the valve portion (181) between the at least one guide portion (182) is positioned open. Electric compressor after Claim 7 wherein the connection recess (183) has at least two end portions opened to the peripheral surface of the valve portion (181). Electric compressor according to one of the Claims 6 to 8th comprising a plurality of guide portions (182), wherein the plurality of guide portions (182) are formed at equal intervals along a circumferential direction. Electric compressor according to one of the Claims 6 to 8th wherein the guide portion (182) is a single guide portion and an opposite angle of the guide portion (182) is greater than or equal to 180 °. Electric compressor according to one of the Claims 6 to 8th , wherein the at least one Guide portion (180) has a thickness which is less than or equal to that of the valve portion (181). Electric compressor according to one of the Claims 6 to 11 wherein a guide groove (175c) is formed on an inner circumferential surface of the valve receiving recess (175) so that the at least one guide portion (182) is inserted into the guide groove (175c) to be restricted in a circumferential direction. Electric compressor according to one of the Claims 1 to 12 further comprising: an elastic member (186) provided on one or both sides of the valve member in a moving direction. Electric compressor according to one of the Claims 1 to 13 wherein the counter pressure passage includes: a first counter pressure hole (171) provided on the first scroll (150) and communicating with the compression chamber (V); and a second counter-pressure hole (172) provided on the frame (140) and communicating with the counter-pressure hole, the first counter-pressure hole (171) and the second counter-pressure hole (172) communicating with each other, and a valve receiving recess (175). receiving the valve member (180) on a surface where the first counter-pressure hole (171) is formed or a surface where the second counter-pressure hole (172) is formed. Electric compressor according to one of the Claims 1 to 13 wherein the counterpressure passage is formed to penetrate the second scroll (160) facing the backpressure space (144), a valve receiving recess (275) is formed in the center of the backpressure passage, a stopper member (276) controlling the movement the valve member (180) is limited, in the valve receiving recess (275) inserted and coupled thereto, and the stopper member (276) has a counter-pressure hole (276), which forms the counter-pressure passage.

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