JP2018009537A - Scroll compressor and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor and a refrigeration cycle device capable of suppressing inflow of liquid mass into a spiral structure in injecting a liquid refrigerant or a two-phase refrigerant to the spiral structure.SOLUTION: A scroll compressor includes a sealed container, a compression mechanism portion disposed in the sealed container, and having a fixed scroll and a swing scroll with which spiral bodies respectively disposed on base plates are combined, and a frame for fixing the fixed scroll to the sealed container. The fixed scroll or the frame has an injection port for introducing a liquid refrigerant or a two-phase refrigerant to the compression mechanism portion, and the liquid refrigerant or the two-phase refrigerant introduced from the injection port is injected toward a reverse direction of a swirling direction of the swing scroll at the outside of the spiral structure configured by combining the spiral bodies of the compression mechanism portion.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a scroll compressor having an injection port and a refrigeration cycle apparatus.

  Conventionally, in an air conditioner such as a multi air conditioning system for buildings, for example, an outdoor unit as an outdoor unit that is a heat source unit arranged outside a building is connected by piping to an indoor unit as an indoor unit arranged inside a building. This constitutes the refrigerant circuit. Then, the refrigerant is circulated through the refrigerant circuit, and the air is heated or cooled by heating and cooling the air using heat dissipation and heat absorption of the refrigerant.

  In such a scroll compressor used in an air conditioner, when high heating capacity is required under a condition where the outside air temperature is low such as in a cold district, the operation is difficult because the discharge temperature becomes high and exceeds the allowable temperature. May be. For this reason, it is necessary to take measures to reduce the discharge temperature so that the scroll compressor can be operated even under conditions of a low outside air temperature.

  Patent Document 1 and Patent Document 2 each have a fixed scroll and a swing scroll in which a spiral body is formed on each base plate, and a liquid refrigerant or two-phase structure in a spiral structure formed by combining the spiral bodies. A scroll compressor in which refrigerant is injected to reduce the discharge temperature is disclosed.

  Patent Document 1 discloses a structure in which an outlet of an injection tube is disposed in a compression chamber configured in a spiral structure.

  On the other hand, Patent Document 2 discloses a structure in which an outlet of an injection pipe is disposed so as to face an inlet of a suction chamber formed by a spiral structure.

Japanese Patent Laid-Open No. 04-321786 JP 2000-54972 A

  In the technique disclosed in Patent Document 1, since the outlet of the injection pipe is disposed in the compression chamber, when injecting liquid refrigerant or two-phase refrigerant, a liquid mass having a mass larger than that of gas is introduced into the compression chamber. Captured directly. If it does so, the refrigerator oil in a spiral structure will be diluted with a liquid refrigerant, and the viscosity of refrigerator oil will fall. The refrigerating machine oil is supplied to the tooth tips or tooth side surfaces of the fixed scroll and the swing scroll to seal the compression chamber. For this reason, when the viscosity of refrigerating machine oil falls, sealing performance will fall and it will cause inconveniences, such as a performance fall of a compressor.

  In the technique disclosed in Patent Document 2, since the outlet of the injection pipe is disposed opposite to the inlet of the suction chamber, a liquid mass having a large mass is directly formed when the liquid refrigerant or the two-phase refrigerant is injected. , Easy to be taken into the suction chamber. For this reason, there is a problem similar to Patent Document 1.

  The present invention has been made to solve the above-mentioned problems, and provides a scroll compressor and a refrigeration cycle apparatus that can suppress the inflow of a liquid mass into a spiral structure when liquid refrigerant or two-phase refrigerant is injected into the spiral structure. The purpose is to obtain.

  A scroll compressor according to the present invention includes a hermetic container, a compression mechanism unit provided in the hermetic container, and having a fixed scroll and an orbiting scroll in which spiral bodies provided on the respective base plates are combined with each other. The fixed scroll or frame has an injection port for introducing liquid refrigerant or two-phase refrigerant into the compression mechanism, and the liquid refrigerant or two-phase refrigerant introduced from the injection port In addition, the injection is performed in the direction opposite to the turning direction of the orbiting scroll outside the spiral structure formed by combining the spiral bodies of the compression mechanism section.

  A refrigeration cycle apparatus according to the present invention includes a scroll compressor, a condenser, a decompression device, an evaporator, a main circuit configured to circulate refrigerant, a condenser, and a decompression device. And an injection circuit connected to the injection port of the scroll compressor, and a flow rate adjusting valve for adjusting the flow rate of the injection circuit.

  According to the present invention, the liquid refrigerant or the two-phase refrigerant introduced from the injection port is directed in the direction opposite to the turning direction of the orbiting scroll outside the spiral structure formed by combining the spiral bodies of the compression mechanism section. Therefore, when the liquid refrigerant or the two-phase refrigerant is injected into the spiral structure, the inflow of the liquid mass into the spiral structure can be suppressed.

It is a schematic longitudinal cross-sectional view which shows the whole structure of the scroll compressor which concerns on Embodiment 1 of this invention. It is a schematic cross-sectional view of the vicinity of the compression mechanism portion of the scroll compressor according to Embodiment 1 of the present invention. It is a compression process figure which shows the operation | movement of (theta) = 0deg among 1 rotation of the rocking | swirling spiral body in the AA cross section in FIG. 1 in the scroll compressor which concerns on Embodiment 1 of this invention. It is a compression process figure which shows the operation | movement of (theta) = 90deg among 1 rotation of the rocking | swirling spiral body in the AA cross section in FIG. 1 in the scroll compressor which concerns on Embodiment 1 of this invention. It is a compression process figure which shows the operation | movement of (theta) = 180deg among 1 rotations of the rocking | swirling spiral body in the AA cross section in FIG. 1 in the scroll compressor which concerns on Embodiment 1 of this invention. It is a compression process figure which shows the operation | movement of (theta) = 270deg among 1 rotation of the rocking | swirling spiral body 1b in the AA cross section in FIG. 1 in the scroll compressor which concerns on Embodiment 1 of this invention. It is a figure which shows an example of the refrigerating-cycle apparatus containing the injection circuit provided with the scroll compressor which concerns on Embodiment 1 of this invention. It is a schematic cross section which shows the compression mechanism part vicinity of the scroll compressor which concerns on Embodiment 2 of this invention.

  Hereinafter, a scroll compressor and a refrigeration cycle apparatus according to an embodiment of the present invention will be described with reference to the drawings. Here, in FIG. 1 and the following drawings, the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below. And the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification.

Embodiment 1 FIG.
FIG. 1 is a schematic longitudinal sectional view showing the overall configuration of the scroll compressor according to Embodiment 1 of the present invention. FIG. 2 is a schematic cross-sectional view of the vicinity of the compression mechanism portion of the scroll compressor according to Embodiment 1 of the present invention.

  The scroll compressor 30 according to the first embodiment includes a compression mechanism unit 8, an electric mechanism unit 110 that drives the compression mechanism unit 8 via the rotating shaft 6, and other components. The scroll compressor 30 has a configuration in which these components are housed in an airtight container 100 constituting an outer shell. The rotating shaft 6 transmits the rotational force from the electric mechanism unit 110 to the orbiting scroll 1 inside the sealed container 100. The orbiting scroll 1 is eccentrically connected to the rotating shaft 6 and oscillates by the rotational force of the electric mechanism unit 110. The scroll compressor 30 is a so-called low pressure shell type in which the sucked low pressure refrigerant gas is once taken into the internal space of the sealed container 100 and then compressed. In the first embodiment, a low-pressure shell type is shown as an example, but the present invention is not limited to this.

  Inside the sealed container 100, a frame 7 and a sub-frame 9 are further arranged so as to face each other with the electric mechanism unit 110 sandwiched in the axial direction of the rotating shaft 6. The frame 7 is disposed on the upper side of the electric mechanism unit 110 and is positioned between the electric mechanism unit 110 and the compression mechanism unit 8. The sub frame 9 is positioned below the electric mechanism unit 110. The frame 7 is fixed to the inner peripheral surface of the sealed container 100 by shrink fitting, welding, or the like. Further, the subframe 9 is fixed to the inner peripheral surface of the sealed container 100 by shrink fitting through a subframe holder 9a, welding, or the like.

  A pump element 111 including a positive displacement pump is attached below the subframe 9 so as to support the rotary shaft 6 in the axial direction at the upper end surface. The pump element 111 supplies the refrigerating machine oil stored in the oil reservoir 100a at the bottom of the hermetic container 100 to sliding parts such as a main bearing 7a described later of the compression mechanism unit 8.

  The sealed container 100 is provided with a suction pipe 101 for sucking a refrigerant, a discharge pipe 102 for discharging the refrigerant, and an injection pipe 201. The refrigerant is taken into the space in the sealed container 100 through the suction pipe 101. The injection pipe 201 is for introducing a refrigerant into the compression mechanism 8 in the sealed container 100 separately from the suction pipe 101. The frame 7 has an injection port 202 for introducing a refrigerant through the injection pipe 201.

  Moreover, in Embodiment 1, the space in the airtight container 100 is defined as follows. A space that is a housing space in the sealed container 100 and is closer to the electric mechanism unit 110 than the frame 7 is defined as a first space 72. A space formed by the inner wall of the frame 7 and a later-described fixed base plate 2 a of the compression mechanism portion 8 is defined as a second space 73. A space closer to the discharge pipe 102 than a later-described fixed base plate 2 a of the compression mechanism unit 8 is a third space 74.

  The compression mechanism unit 8 has a function of compressing the refrigerant sucked from the suction pipe 101 and discharging the compressed refrigerant to the third space 74 that is a high-pressure part formed above the sealed container 100.

  The compression mechanism unit 8 includes a swing scroll 1 and a fixed scroll 2.

  The fixed scroll 2 is fixed to the sealed container 100 via the frame 7. The orbiting scroll 1 is disposed on the lower side of the fixed scroll 2 and is supported on an eccentric shaft portion 6a (described later) of the rotary shaft 6 so as to be freely swingable.

  The orbiting scroll 1 has an orbiting base plate 1a and an orbiting spiral body 1b that is a spiral projection provided on one surface of the orbiting base plate 1a. The fixed scroll 2 includes a fixed base plate 2a and a fixed spiral body 2b that is a spiral projection provided on one surface of the fixed base plate 2a. The oscillating spiral body 1b and the fixed spiral body 2b are configured according to an involute curve. The orbiting scroll 1 and the fixed scroll 2 are arranged in a sealed container 100 in a symmetrical spiral shape in which the orbiting spiral body 1b and the fixed spiral body 2b are combined in opposite phases with respect to the rotation center of the rotating shaft 6. Yes. Hereinafter, among the compression mechanism portion 8 constituted by the orbiting scroll 1 and the fixed scroll 2, in particular, a symmetrical spiral structure portion in which the orbiting spiral body 1 b and the fixed spiral body 2 b are combined is referred to as a spiral structure body 8 a. That's it.

  Here, as shown in FIG. 2, the center of the foundation circle of the involute curve drawn by the oscillating spiral body 1b is defined as a foundation circle center 204a. The center of the basic circle of the involute curve drawn by the fixed spiral body 2b is defined as a basic circle center 204b. As the base circle center 204a rotates around the base circle center 204b, the swinging spiral body 1b performs a swinging motion around the fixed spiral body 2b as shown in FIGS. 3A to 3D described later. The motion of the orbiting scroll 1 during the operation of the scroll compressor 30 will be described in detail later.

  In the oscillating spiral body 1b, the winding start is an end portion that is the innermost side from the basic circle center 204a, and the winding end is an end portion that is the outermost side from the basic circle center 204a. Similarly, in the fixed spiral body 2b, the winding start is the end that is the innermost from the basic circle center 204b, and the winding end is the end that is the outermost from the basic circle center 204b.

  At the inward surface 205a of the swinging scroll 1b of the swing scroll 1, the outermost surface 206b of the fixed spiral 2b of the fixed scroll 2 comes into contact with the inward surface 205a during the swinging motion of the swinging spiral 1b. The point on the side is defined as a winding end contact point 207a. In addition, on the inward surface 205b of the fixed scroll 2b of the fixed scroll 2, the outward surface 206a of the swing scroll 1b of the swing scroll 1 is most in contact with the inward surface 205b during the swinging motion of the swing scroll 1b. A point on the winding end side is defined as a winding end contact point 207b. The end-of-winding contact point 207a of the swinging spiral body 1b and the end-of-winding contact point 207b of the fixed spiral body 2b are disposed on opposite sides of the basic circle center 204a and the basic circle center 204b.

  When viewed along the spiral from the center of the basic circle to the end of winding, a plurality of contact points are formed between the inward surface 205a of the swinging spiral body 1b and the outward surface 206b of the fixed spiral body 2b. In other words, the gap between the inward surface 205a of the swinging spiral body 1b and the outward surface 206b of the fixed spiral body 2b is divided into a plurality of chambers by a plurality of contact points. Further, when viewed along the spiral from the center of the basic circle to the end of winding, a plurality of contact points are formed between the inward surface 205b of the fixed spiral body 2b and the outward surface 206a of the swing spiral body 1b. That is, the gap between the inward surface 205b of the fixed spiral body 2b and the outward surface 206a of the swinging spiral body 1b is divided into a plurality of chambers by a plurality of contact points.

  A spiral structure 8a in which the swing spiral body 1b and the fixed spiral body 2b are combined has a symmetrical spiral shape. For this reason, as shown in FIG. 2, in the spiral structure 8a, a plurality of pairs of chambers are formed from the outside of the spiral by the plurality of chambers.

  Further, on the outer periphery of the spiral structure 8 a, a refrigerant introduction port that leads the suction refrigerant sucked from the suction pipe 101 to the compression mechanism portion 8, and the suction refrigerant led from the refrigerant introduction port is placed in the suction chamber of the compression mechanism portion 8. A pair of intake ports and injection ports are arranged symmetrically about the rotation shaft 6 as a pair. Hereinafter, arrangement positions and the like will be described in the order of the suction ports 208a and 208b, the refrigerant introduction ports 7d and 7c, and the injection ports 202a and 202b.

  The suction port 208a passes through a winding end contact point 207a and a certain point on the outwardly facing surface 206b of the fixed spiral body 2b, and is a plane that is parallel to the vertical direction that is the axial direction of the rotating shaft 6 and has a minimum area. The suction port 208b passes through a winding end contact point 207b and a point on the outward face 206a of the swinging spiral body 1b, and is a plane that is parallel to the vertical direction that is the axial direction of the rotating shaft 6 and has a minimum area. .

  The suction chamber 70a is defined as a space surrounded by the suction port 208a, the inward surface 205a of the swing spiral body 1b, the outward surface 206b of the fixed spiral body 2b, the swing base plate 1a, and the fixed base plate 2a. The suction chamber 70b is defined as a space surrounded by the suction port 208b, the outward surface 206a of the swinging spiral body 1b, the inward surface 205b of the fixed spiral body 2b, the swinging base plate 1a, and the fixed base plate 2a.

  When the spiral body is viewed along the spiral from the suction end 208a or the suction port 208b on the winding end side to the winding start side, there is a place where the fixed spiral body 2b and the swinging spiral body 1b first contact each other. The suction chamber 70a is a space that is sandwiched between the first contact point and the suction port 208a. Further, the suction chamber 70b is a space sandwiched between the first contact point and the suction port 208b. In other words, the suction chamber 70a is a space in which the winding end contact point 207a is separated from the outward surface 206b of the fixed spiral body 2b and the suction port 208a is formed.

  The suction chamber 70b is a space in which the winding end contact point 207b is separated from the outward surface 206a of the swinging spiral body 1b and the suction port 208b is formed. As will be described later, when the swinging spiral body 1b turns, the position where the fixed spiral body 2b contacts the swinging spiral body 1b moves, and the width of the suction port 208a or the suction port 208b also changes. The volume of the suction chamber 70b varies.

  The suction ports 208a and 208b are openings, and the suction chambers 70a and 70b are unclosed chambers. For this reason, the suction chambers 70a and 70b are chambers having almost no pressure fluctuation.

  The refrigerant sucked into the sealed container 100 from the suction pipe 101 is sucked into the suction chamber 70a through the refrigerant introduction port 7c, and is sucked into the suction chamber 70b through the refrigerant introduction port 7d.

  The compression chamber 71a is defined as a space surrounded by the inward surface 205a of the swinging spiral body 1b, the outward surface 206b of the fixed spiral body 2b, the swinging base plate 1a, and the fixed base plate 2a. The compression chamber 71b is defined as a space surrounded by the outward face 206a of the swing spiral body 1b, the inward face 205b of the fixed spiral body 2b, the swing base plate 1a, and the fixed base plate 2a. Thus, the compression mechanism portion 8 is formed with a plurality of pairs of opposing compression chambers 71a and 71b.

  As described above, when the spiral body is viewed along the spiral from the suction end 208a or the suction port 208b on the winding end side to the winding start side, the place where the fixed spiral body 2b and the swinging spiral body 1b are in contact with each other is There are several. The compression chambers 71a and 71b are spaces sandwiched between two consecutive locations where a plurality of locations meet. As will be described later, when the swinging spiral body 1b rotates, the position where the fixed spiral body 2b and the swinging spiral body 1b are in contact with each other moves, and the volume of the compression chambers 71a and 71b varies due to the rotation.

  In addition, the compression chambers 71a and 71b are closed spaces, and the volume fluctuates. For this reason, the compression chambers 71 a and 71 b are chambers in which pressure fluctuations occur as the rotary shaft 6 rotates.

  That is, in the state shown in FIG. 2, the outermost chambers are the suction chambers 70a and 70b, and the other chambers are the compression chambers 71a and 71b. The innermost chambers near the foundation circle centers 204a and 204b at the beginning of winding are the inward surface 205a of the swinging spiral body 1b, the inward surface 205b of the fixed spiral body 2b, the swinging base plate 1a, and the fixed base plate 2a. It is an enclosed space. And the discharge port 2c which discharges the compressed refrigerant | coolant is provided in the part which forms the innermost chamber in the fixed base plate 2a.

  Thus, the swing scroll 1 and the fixed scroll 2 each have the swing spiral body 1b or the fixed spiral body 2b provided on the swing base plate 1a or the fixed base plate 2a. The body 1b and the fixed spiral body 2b are combined to form a plurality of chambers including the compression chambers 71a and 71b.

  The suction chambers 70a and 70b and the compression chambers 71a and 71b are sealed with the following configuration. That is, the tooth tip 1ba which is the axial end portion of the swinging spiral body 1b is in contact with the opposing fixed base plate 2a so as to slide, and the tooth tip which is the axial end portion of the fixed spiral body 2b. 2ba (see FIG. 1) is in contact with the opposed swing base plate 1a so as to slide. And the thickness of the rocking spiral body 1b and the fixed spiral body 2b is formed so as to have a certain thickness from the viewpoint of strength, and the tooth tip portion to be sealed becomes a flat surface having a width corresponding to the thickness. Yes.

  A hollow cylindrical boss 1d is formed at a substantially central portion of the surface of the rocking scroll 1 opposite to the surface on which the rocking spiral body 1b is formed in the rocking base plate 1a. An eccentric shaft portion 6a, which will be described later, formed on the upper end portion of the rotating shaft 6 is connected to the inside of the boss portion 1d via a slider 5, which will be described later.

  A baffle 4 is fixed to the surface of the fixed base plate 2 a of the fixed scroll 2 opposite to the swing scroll 1. The baffle 4 is formed with a through hole communicating with the discharge port 2 c of the fixed scroll 2, and a discharge valve 11 is provided in the through hole. A discharge muffler 12 is attached so as to cover the discharge port 2c.

  The frame 7 has a fixed scroll 2 and a thrust surface that supports the thrust force acting on the orbiting scroll 1 in the axial direction. In addition, refrigerant introduction ports 7 c and 7 d that penetrate the first space 72 and the second space 73 and lead the suctioned refrigerant sucked from the suction pipe 101 to the compression mechanism portion 8 are formed through the frame 7. .

  The electric mechanism unit 110 that supplies a rotational driving force to the rotary shaft 6 includes an electric motor stator 110a and an electric motor rotor 110b. The motor stator 110a is connected to a glass terminal (not shown) existing between the frame 7 and the motor stator 110a with a lead wire (not shown) in order to obtain electric power from the outside. The electric motor rotor 110b is fixed to the rotating shaft 6 by shrink fitting or the like. Further, in order to balance the entire rotation system of the scroll compressor 30, a first balance weight 60 is fixed to the rotary shaft 6, and a second balance weight 61 is fixed to the motor rotor 110b. Yes.

  The rotating shaft 6 includes an eccentric shaft portion 6 a on the upper side of the rotating shaft 6, a main shaft portion 6 b, and a sub shaft portion 6 c on the lower side of the rotating shaft 6. A boss 1d of the orbiting scroll 1 is fitted to the eccentric shaft 6a via the slider 5 and the orbiting bearing 1c, and slides with the orbiting bearing 1c via an oil film made of refrigeration oil. The oscillating bearing 1c is fixed in the boss 1d by press-fitting a bearing material used for a sliding bearing such as a copper-lead alloy, and the oscillating scroll 1 oscillates as the rotating shaft 6 rotates. It is like that. The main shaft portion 6b is fitted to a main bearing 7a disposed on the inner periphery of a boss portion 7b provided on the frame 7 via a sleeve 13, and slides with the main bearing 7a via an oil film of refrigeration oil. The main bearing 7a is fixed in the boss portion 7b by press-fitting a bearing material used for a sliding bearing such as a copper lead alloy.

  A sub-bearing 10 made of a ball bearing is provided at the center of the sub-frame 9, and the rotary shaft 6 is supported in the radial direction below the electric mechanism 110. The auxiliary bearing 10 may be pivotally supported by another bearing configuration other than the ball bearing. The auxiliary shaft portion 6 c is fitted with the auxiliary bearing 10 and slides with the auxiliary bearing 10. The axis of the main shaft portion 6 b and the sub shaft portion 6 c coincides with the axis of the rotary shaft 6.

  Next, operation | movement of the compression mechanism part 8 is demonstrated using FIG. 3A, FIG. 3B, FIG. 3C, and FIG. 3D.

  FIG. 3A is a compression process diagram showing an operation of θ = 0 deg during one rotation of the oscillating spiral body 1b in the AA cross section in FIG. 1 in the scroll compressor 30 according to the first embodiment of the present invention. is there. FIG. 3B is a compression process diagram showing an operation of θ = 90 deg during one rotation of the oscillating spiral body 1b in the AA cross section in FIG. 1 in the scroll compressor 30 according to Embodiment 1 of the present invention. is there. FIG. 3C is a compression process diagram illustrating an operation of θ = 180 deg during one rotation of the oscillating spiral body 1b in the AA cross section in FIG. 1 in the scroll compressor 30 according to Embodiment 1 of the present invention. is there. FIG. 3D is a compression process diagram illustrating an operation of θ = 270 deg during one rotation of the oscillating spiral body 1b in the AA cross section in FIG. 1 in the scroll compressor 30 according to the first embodiment of the present invention. is there.

  The rotational phase θ is a certain timing with a straight line connecting the basic circle center 204a-1 and the basic circle center 204b of the fixed spiral body 2b when the basic circle center of the swinging spiral body 1b at the start of compression is 204a-1. Is defined as an angle formed by a straight line connecting the basic circle center 204a of the swinging spiral body 1b and the basic circle center 204b of the fixed spiral body 2b. That is, the rotational phase θ is 0 deg at the start of compression, and varies from 0 deg to 360 deg. FIG. 3A to FIG. 3D show a situation in which the oscillating spiral body 1b oscillates with the rotational phase θ = 0 deg-> 90 deg-> 180 deg-> 270 deg.

  When a glass terminal (not shown) provided in the sealed container 100 is energized, the rotating shaft 6 is rotated by the electric motor rotor 110b. Then, the rotational force is transmitted to the rocking bearing 1c through the eccentric shaft portion 6a, and is transmitted from the rocking bearing 1c to the rocking scroll 1, and the rocking scroll 1 performs rocking motion. The refrigerant gas sucked into the sealed container 100 from the suction pipe 101 is taken into the suction chambers 70a and 70b.

  The state of FIG. 3A shows a state in which the outermost chamber is closed and the suction of the refrigerant is completed, and all the chambers including the outermost chamber are the compression chambers 71a and 71b. In this case, focusing on the outermost compression chambers 71a and 71b, the compression chambers 71a and 71b reduce the volume while moving from the outer peripheral portion toward the center in accordance with the swinging motion of the swing scroll 1. . The refrigerant gas in the compression chambers 71a and 71b is compressed as the volume of the compression chambers 71a and 71b decreases. Thus, in the spiral structure 8a, compression is performed while the orbiting scroll 1 revolves from the end of winding of the orbiting spiral body 1b toward the beginning of the winding, as indicated by the arrow in the turning direction of FIG.

  In general, in the scroll compressor 30, two spiral bodies are in contact with each other at a plurality of contact points from the outer peripheral end of the swinging spiral body 1 b and the fixed spiral body 2 b toward the spiral center along the involute curve. As shown in FIG. 3A, when the winding end contact point 207a is in contact with the outward surface 206b, and when the winding end contact point 207b is in contact with the outward surface 206a, it is the time when the inhalation is completed, At this time, the suction ports 208a and 208b are closed, and the outermost chamber is not the suction chambers 70a and 70b.

  As shown in FIG. 3A, when the suction is completed, the second point from the winding end contact point 207a that is the first contact point between the inward surface 205a of the swinging spiral body 1b and the outward surface 206b of the fixed spiral body 2b. The contact point 209a is a closed space. When the suction is completed, from the winding end contact point 207b, which is the first contact point between the outward surface 206a of the swinging spiral body 1b and the inward surface 205b of the fixed spiral body 2b, to the second contact point 209b. Becomes a closed space. However, when the suction ports 208a and 208b are slightly opened immediately before or after the completion of the suction, the second contact point 209a and 209b from the outside at the time when the suction is completed becomes the outermost contact point, and the suction ports 208a and 208a, Communicates with 208b.

  The suction chambers 70a and 70b are spaces whose volumes are changed by the rotation of the swinging spiral body 1b. That is, as the rotational phase θ increases, the suction chambers 70a and 70b move along the substantially tangential direction of the swinging spiral body 1b and the fixed spiral body 2b as shown in FIGS. 3B-> 3C-> 3D. Increase the volume. As the volume increases, the suction chambers 70 a and 70 b suck the refrigerant gas in the sealed container 100. At the time of FIG. 3A, the suction ports 208a and 208b are eliminated and the volume is maximized, and at the same time, the suction chambers 70a and 70b move to the compression chambers 71a and 71b.

  The compression chambers 71a and 71b have a volume that decreases toward the center due to the shape of the spiral. As described above, the volume changes due to the rotation of the rotary shaft 6 and compresses the refrigerant sucked into the compression chambers 71a and 71b. The compression chambers 71a and 71b at the center are in communication with the discharge port 2c shown in FIG. At the discharge port 2 c, the compressed refrigerant is discharged into the discharge muffler 12 through the discharge valve 11 and then discharged into the third space 74.

  Next, the injection port 202 which is a characteristic part of the first embodiment will be described with reference to FIGS. 1 and 2.

  In the frame 7, a pair of injection ports 202a and 202b are formed by drilling as outlets for introducing the injection refrigerant toward the second space 73 from the connection portions with the injection tubes 201a and 201b. Liquid refrigerant or two-phase refrigerant flows into the injection ports 202a and 202b from the outside of the scroll compressor 30 via the injection pipes 201a and 201b. The injection ports 202a and 202b are disposed at the outer end of the swirl along the swirl of the swinging scroll 1b of the swing scroll 1 when the coolant is ejected from the inside of the hole into the space outside the spiral structure 8a. Open in the direction of heading. Here, the outer end portion is an end portion near the outer periphery of the swing base plate 1a among the two end portions of the swing spiral body 1b, which is a so-called winding end portion.

  More specifically, the injection ports 202a and 202b are inclined such that the position of the refrigerant outlet is located on the inner circumferential surface of the frame 7 on the opposite side to the swirl direction from the hole penetrating in the radial direction in the frame 7. It is a hole. That is, the injection ports 202a and 202b are opened in the direction opposite to the turning direction. Thus, by setting the position of the refrigerant outlet on the inner circumferential surface of the frame 7 in the direction opposite to the turning direction, the injection ports 202a and 202b are directed in the direction toward the outer end along the swinging spiral body 1b. It becomes an opening hole. By configuring the injection ports 202a and 202b as described above, the liquid refrigerant or the two-phase refrigerant is injected toward the spiral structure 8a in the second space 73 in the direction opposite to the turning direction. .

  As shown in the drawing, the turning direction of the orbiting scroll 1 is the turning direction around the scroll center from the outer peripheral end of the scroll spiral to the center along the spiral. With this configuration, the refrigerant is blown out from the injection ports 202a and 202b toward the outer peripheral surface of the spiral structure 8a so as to generate a flow in the rotation direction opposite to the turning direction. That is, the injection ports 202a and 202b are provided in the annular space outside the spiral structure 8a so as to inject in the direction opposite to the moving direction (swirl direction) of the compression chamber inside the spiral structure 8a. Here, the annular space outside the spiral structure 8a is a space sandwiched between the swing base plate 1a and the fixed base plate 2a at the height in the axial direction of the rotating shaft 6, and the swing spiral body 1b and This is an annular space between the outermost surface of the fixed spiral body 2 b and the inner surface of the frame 7.

  Here, in FIG. 2, the injection ports 202 a and 202 b are provided on the wall portion 7 e joined to the sealed container 100 in the frame 7, and communicate with the second space 73. However, the member for providing the injection ports 202a and 202b is not limited to the frame 7, and may be provided on the fixed base plate 2a. In short, the injection ports 202a and 202b are located outside the spiral structure 8a and are formed so as to be opened in the direction toward the outer end along the swinging spiral body 1b of the swing scroll 1. It does not matter which member is formed.

  Further, if the injection is performed in the space outside the spiral structure 8a in the direction opposite to the moving direction (swirl direction) of the compression chamber inside the spiral structure 8a, the injection ports 202a and 202b can be variously changed. That is, here, the entire hole from the opening (inlet) on the outer peripheral surface side of the frame 7 to the opening (exit) on the inner peripheral surface side is the injection port 202a, 202b, but a part on the inner peripheral surface side is the injection port. It is good also as 202a, 202b. That is, “a part on the inner peripheral surface side of the whole hole extending from the outer peripheral surface side opening of the frame 7 to the inner peripheral surface side opening” along the swing spiral body 1 b of the swing scroll 1. What is necessary is just to set it as the structure opened in the direction which goes to, and it can be set as arbitrary structures about "the hole part of the other outer peripheral surface side".

  Note that “a part on the inner peripheral surface side of the entire hole extending from the opening on the outer peripheral surface side of the frame 7 to the opening on the inner peripheral surface side” means a refrigerant that is injected from that portion into the space outside the spiral structure 8a. It is only necessary to have a length that can determine the flow direction. Moreover, although the shape of the injection ports 202a and 202b has been described as a hole so far, it may be a groove. Specifically, a groove extending in the direction opposite to the turning direction may be formed on the inner peripheral surface of the frame 7. Moreover, it is good also as a structure which provides a cover in the side used as the back of the turning direction of a hole. As these structures, you may make it produce the swirl flow opposite to the inside of the spiral structure 8a.

  In the techniques disclosed in Patent Document 1 and Patent Document 2 described above, when performing injection for the purpose of lowering the discharge temperature, the injection refrigerant that has exited the injection port immediately enters the compression chamber or the suction chamber of the compression mechanism. For example, it was supposed to flow into the spiral structure. For this reason, the injected liquid mass having a large mass flows directly into the spiral structure, and the refrigerating machine oil in the spiral structure may be diluted.

  On the other hand, in the first embodiment, as described above, the injection ports 202a and 202b are arranged at positions outside the spiral structure 8a and toward the outer end along the swing spiral body 1b of the swing scroll 1. An opening is provided. For this reason, the injection refrigerant is blown out from the outside of the spiral structure 8a toward the outer periphery of the spiral structure 8a in the direction opposite to the direction in which the refrigerant is sucked. Thereby, the injection refrigerant is less likely to be taken into the suction chambers 70a and 70b, and the liquid mass of the injection refrigerant having a large mass is easily atomized before being taken into the suction chambers 70a and 70b. For this reason, in Embodiment 1, the dilution of the refrigerating machine oil in the spiral structure 8a can be suppressed, the decrease in performance accompanying the decrease in the viscosity of the refrigerating machine oil in the spiral structure 8a can be suppressed, and the discharge temperature can be reduced. Is possible.

  Further, the injection port 202a is arranged in the order of the refrigerant introduction port 7c, the suction port 208a of the suction chambers 70a and 70b, and the injection port 202a along the turning direction of the orbiting scroll 1. The injection port 202a was installed outside the angular range from the refrigerant introduction port 7c to the suction port 208a in the turning direction. If the injection port 202a is disposed within the angle range, the injection refrigerant is blown out toward the refrigerant inlet 7c. For this reason, the injection refrigerant flows down to the bottom of the sealed container 100 via the refrigerant introduction port 7c, resulting in a disadvantage that the refrigerating machine oil in the oil sump 100a is diluted. For this reason, this inconvenience can be suppressed by arranging the injection port 202a outside the angle range.

  The same applies to the injection port 202b side, and the refrigerant introduction port 7d, the suction port 208b, and the injection port 202b are arranged in this order along the turning direction of the orbiting scroll 1. The injection port 202a was installed outside the angular range from the refrigerant introduction port 7d to the suction port 208b in the turning direction. Thereby, the injection refrigerant can flow down to the bottom of the sealed container 100 via the refrigerant introduction port 7d, and the disadvantage that the refrigerating machine oil in the oil reservoir 100a is diluted can be suppressed.

  In order for the liquid mass of the injection refrigerant injected from the injection port 202a to be further atomized before being taken into the suction chamber 70a, the distance from the suction port 208a to the injection port 202a may be long. desirable. In other words, the smaller the angle α1 from the injection port 202a to the refrigerant inlet 7d in the turning direction, the better. The same applies to the suction chamber 70b side, and the smaller the angle α2 from the injection port 202b to the refrigerant introduction port 7c in the turning direction, the better.

  FIG. 4 is a diagram illustrating an example of a refrigeration cycle apparatus including an injection circuit including the scroll compressor according to Embodiment 1 of the present invention.

  A refrigeration cycle apparatus 300 shown in FIG. 4 includes a scroll compressor 30, a condenser 31, an expansion valve 32 as a decompression device, and an evaporator 33, which are sequentially connected by piping to circulate refrigerant. A circuit configured to do so.

  The refrigeration cycle apparatus 300 includes an injection circuit 34 that branches from between the condenser 31 and the expansion valve 32 and is connected to the scroll compressor 30.

  The injection circuit 34 is provided with an expansion valve 34a as a flow rate adjustment valve, and can adjust the flow rate to be injected into the suction chambers 70a, 70b of the scroll compressor 30.

  The opening degree of the expansion valve 32, the opening degree of the expansion valve 34a, and the rotation speed of the scroll compressor 30 are controlled by a control device (not shown).

  Note that a four-way valve (not shown) may be further provided in the refrigeration cycle apparatus 300 so that the refrigerant flow direction is switched in the reverse direction. In this case, if the condenser 31 installed on the downstream side of the scroll compressor 30 is the indoor unit side and the evaporator 33 is the outdoor unit side, the heating operation is performed, and the condenser 31 is the outdoor unit side and the evaporator 33 is the indoor unit side. Then, it becomes a cooling operation. The injection operation is normally performed during the heating operation, but the injection operation may be performed during the cooling operation.

  Below, the circuit which has the scroll compressor 30, the condenser 31, the expansion valve 32, and the evaporator 33 is described as a main circuit, and the refrigerant | coolant which circulates through this main circuit is described as a main refrigerant. Further, the refrigerant flowing through the injection circuit 34 is referred to as an injection refrigerant.

  Next, the flow of the refrigerant will be described.

(Main refrigerant flow)
In the main circuit, the main refrigerant discharged from the scroll compressor 30 returns to the scroll compressor 30 via the condenser 31, the expansion valve 32, and the evaporator 33. The refrigerant returning to the scroll compressor 30 flows into the sealed container 100 from the suction pipe 101.

  The low-pressure refrigerant that has flowed from the suction pipe 101 into the first space 72 in the sealed container 100 flows into the second space 73 through the two refrigerant inlets 7 d and 7 c installed in the frame 7. The low-pressure refrigerant that has flowed into the second space 73 is sucked into the suction chambers 70a and 70b with the relative swinging motion of the swinging spiral body 1b and the fixed spiral body 2b of the compression mechanism unit 8. The main refrigerant sucked into the suction chambers 70a and 70b is boosted from a low pressure to a high pressure by the geometric volume change of the compression chambers 71a and 71b accompanying the relative operation of the swinging spiral body 1b and the fixed spiral body 2b. The Then, the high-pressure main refrigerant is pushed out of the discharge valve 11 and discharged into the discharge muffler 12, and then discharged into the third space 74, from the discharge pipe 102 to the outside of the scroll compressor 30 as high-pressure refrigerant. Discharged.

(Injection refrigerant flow)
The injection refrigerant that is part of the main refrigerant discharged from the scroll compressor 30 and passed through the condenser 31 flows into the injection circuit 34, and flows into the injection pipes 201a and 201b of the scroll compressor 30 through the expansion valve 34a. . The liquid or two-phase injection refrigerant that has flowed into the injection tubes 201a and 201b flows into the injection ports 202a and 202b, respectively. As described above, the refrigerant flowing into the injection ports 202a and 202b passes through the second space 73 and flows into the suction chamber 70a or the suction chamber 70b in the compression mechanism unit 8.

  Here, in the first embodiment, as described above, the injection ports 202a and 202b are opened from the outside of the spiral structure 8a in the direction toward the outer end along the swinging spiral body 1b of the swing scroll 1. doing. Therefore, the flow direction of the injected refrigerant is opposite to the direction in which the refrigerant is sucked into the suction ports 208a and 208b. Thereby, the injection refrigerant is less likely to be taken into the suction chambers 70a and 70b, and the liquid mass of the injection refrigerant having a large mass is taken into the suction chambers 70a and 70b in a state of being atomized. For this reason, in Embodiment 1, the dilution of the refrigerating machine oil in the spiral structure 8a can be suppressed, the decrease in performance accompanying the decrease in the viscosity of the refrigerating machine oil in the spiral structure 8a can be suppressed, and the discharge temperature can be reduced. Is possible.

Embodiment 2. FIG.
The second embodiment is different from the first embodiment in the combination of the swing spiral body 1b of the swing scroll 1 and the fixed spiral body 2b of the fixed scroll 2. In the second embodiment, only the characteristic part will be described, and description of other parts will be omitted.

FIG. 5 is a schematic cross-sectional view showing the vicinity of the compression mechanism portion of the scroll compressor according to Embodiment 2 of the present invention.
In the first embodiment, the swinging spiral body 1b of the swinging scroll 1 and the fixed spiral body 2b of the fixed scroll 2 are combined in opposite phases. On the other hand, in the second embodiment, the swinging spiral body 1b of the swinging scroll 1 and the fixed spiral body 2b of the fixed scroll 2 are combined in the same phase with respect to the rotation center of the rotating shaft 6. Then, the winding end contact points 207a and 207b are not in antiphase with the basic circle center 204b but in phase, so that the spiral structure 8a of the compression mechanism unit 8 has an asymmetric spiral shape.

  When the spiral structure 8a has a symmetrical spiral shape as in the first embodiment, the suction chambers 70a and 70b are formed symmetrically around the rotation axis 6 in the spiral structure 8a. When the asymmetric spiral shape is used for 8a, the suction chambers 70a and 70b are formed adjacent to each other. Therefore, the injection port is one place of the injection port 202a. The injection port 202a has a range of an angle β up to 180 ° from the suction port 208 in the direction opposite to the turning direction of the orbiting scroll 1, that is, the direction toward the outer end along the orbiting scroll 1b of the orbiting scroll 1. Is provided.

  According to the second embodiment, the same effects as those of the first embodiment can be obtained, the spiral structure 8a has an asymmetric spiral shape, and the injection port 202a is connected from the suction port 208 to the swinging spiral body 1b of the swing scroll 1. Since the angle β is in the range of 180 ° along the direction toward the outer end, the following effects can be obtained. That is, the distance from the injection port 202a to the suction port 208 becomes longer than that in the first embodiment, and the time for separating a large mass of liquid in the injection refrigerant becomes longer. Therefore, the liquid mass can be further atomized to further suppress the performance deterioration associated with the viscosity reduction of the refrigerating machine oil of the spiral structure 8a. Note that the injection port 202a is located outside the spiral structure 8a and opened in the direction toward the outer end along the oscillating spiral 1b of the oscillating scroll 1 as in the first embodiment. It is.

  Further, as shown in FIG. 5, in the range of the angle β, the injection is performed outside the angle range from the suction port 208 to the refrigerant introduction port 7 d in the direction toward the outer end along the swinging spiral body 1 b of the swinging scroll 1. By providing the port 202a, it is possible to suppress the inconvenience that the injection refrigerant flows down to the bottom of the sealed container 100 via the refrigerant inlet 7d and the refrigerating machine oil in the oil reservoir 100a is diluted.

  1 oscillating scroll, 1a oscillating base plate, 1b oscillating spiral body, 1ba tooth tip, 1c oscillating bearing, 1d boss part, 2 fixed scroll, 2a stationary base plate, 2b stationary spiral body, 2ba tooth tip, 2c discharge Outlet, 4 Baffle, 5 Slider, 6 Rotating shaft, 6a Eccentric shaft part, 6b Main shaft part, 6c Subshaft part, 7 Frame, 7a Main bearing, 7b Boss part, 7c Refrigerant inlet, 7d Refrigerant inlet, 7e Wall part 8 compression mechanism section, 8a spiral structure, 8b spiral structure, 9 subframe, 9a subframe holder, 10 secondary bearing, 11 discharge valve, 12 discharge muffler, 13 sleeve, 30 scroll compressor, 31 condenser, 32 Expansion valve, 33 Evaporator, 34 Injection circuit, 34a Expansion valve, 60 First balance weight, 61 Second balance weight, 70a Entrance chamber, 70b Suction chamber, 71a Compression chamber, 71b Compression chamber, 72 First space, 73 Second space, 74 Third space, 100 Sealed container, 100a Oil reservoir, 101 Suction pipe, 102 Discharge pipe, 110 Electric mechanism section 110a motor stator, 110b motor rotor, 111 pump element, 201 injection pipe, 201a injection pipe, 201b injection pipe, 202 injection port, 202a injection port, 202b injection port, 204a basic circle center, 204a-1 basic circle center , 204b Center circle center, 205a inward surface, 205b inward surface, 206a outward surface, 206b outward surface, 207a contact point, 207b contact point, 208 suction port, 208a suction port, 208b suction port, 209a Sawaten, 209 b contact points, 300 refrigeration cycle apparatus, [alpha] 1 angle, [alpha] 2 the angle, beta angle, theta rotational phase.

Claims (7)

A sealed container;
A compression mechanism having a fixed scroll and an orbiting scroll, each of which is provided in the sealed container and in which spiral bodies provided on respective base plates are combined with each other;
A frame for fixing the fixed scroll to the sealed container;
The fixed scroll or the frame has an injection port for introducing a liquid refrigerant or a two-phase refrigerant into the compression mechanism section,
Injection of liquid refrigerant or two-phase refrigerant introduced from the injection port toward the direction opposite to the turning direction of the orbiting scroll outside the spiral structure formed by combining the spiral bodies of the compression mechanism section Scroll compressor.   The scroll compressor according to claim 1, wherein the injection port is provided at a position outside the spiral structure so as to open in a direction toward the outer end along the spiral body of the swing scroll. The frame has a refrigerant inlet that guides the sucked refrigerant to the compression mechanism part,
In the swirl direction of the orbiting scroll, the refrigerant introduction port, the suction port of the suction chamber of the compression mechanism unit, and the injection port are arranged in this order, and the injection port extends from the refrigerant introduction port to the The scroll compressor according to claim 1 or 2, wherein the scroll compressor is provided outside an angle range to the suction port in a turning direction. A rotation shaft for driving the compression mechanism,
The fixed scroll and the orbiting scroll are formed in a symmetrical spiral shape configured in combination with the same phase with respect to the rotation center of the rotating shaft,
4. The scroll compressor according to claim 3, wherein the injection port, the refrigerant introduction port, and the suction port are respectively arranged symmetrically about the rotation axis. A rotation shaft for driving the compression mechanism,
The said compression mechanism part is formed in the asymmetrical spiral shape comprised by combining the said fixed scroll and the said rocking scroll with the antiphase with respect to the rotation center of the said rotating shaft. Scroll compressor.   The scroll compressor according to claim 5, wherein the injection port is provided in an angle range of 180 ° in a direction from the suction port of the suction chamber of the compression mechanism portion toward the outer end along the spiral body of the swing scroll. . A main circuit comprising the scroll compressor according to any one of claims 1 to 6, a condenser, a decompression device, and an evaporator, and configured to circulate a refrigerant;
An injection circuit branched from between the condenser and the pressure reducing device and connected to the injection port of the scroll compressor;
A flow rate adjusting valve for adjusting a flow rate of the injection circuit, and a refrigeration cycle apparatus including the flow rate adjusting valve.

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