CN114787515A - Scroll compressor and refrigeration cycle device - Google Patents
Scroll compressor and refrigeration cycle device Download PDFInfo
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- CN114787515A CN114787515A CN201980102765.7A CN201980102765A CN114787515A CN 114787515 A CN114787515 A CN 114787515A CN 201980102765 A CN201980102765 A CN 201980102765A CN 114787515 A CN114787515 A CN 114787515A
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- scroll compressor
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- 238000005057 refrigeration Methods 0.000 title claims description 10
- 238000007906 compression Methods 0.000 claims abstract description 91
- 230000006835 compression Effects 0.000 claims abstract description 88
- 239000003507 refrigerant Substances 0.000 claims description 54
- 230000007246 mechanism Effects 0.000 description 28
- 238000010586 diagram Methods 0.000 description 20
- 238000006073 displacement reaction Methods 0.000 description 7
- 238000002347 injection Methods 0.000 description 5
- 239000007924 injection Substances 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 239000000470 constituent Substances 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 239000010721 machine oil Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 239000000758 substrate Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 229910000978 Pb alloy Inorganic materials 0.000 description 1
- WIKSRXFQIZQFEH-UHFFFAOYSA-N [Cu].[Pb] Chemical compound [Cu].[Pb] WIKSRXFQIZQFEH-UHFFFAOYSA-N 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
Abstract
A scroll compressor includes, in a sealed container, a fixed scroll portion having a fixed base plate and a fixed scroll provided on the fixed base plate, and an oscillating scroll portion having an oscillating base plate and an oscillating scroll provided on the oscillating base plate, the oscillating scroll portion being arranged so that a wrap of a scroll at the oscillating scroll meshes with a wrap of a scroll at the fixed scroll to form a compression chamber, the oscillating scroll having a thick portion provided at a position corresponding to an opening portion of a port provided on the fixed base plate and communicating with the compression chamber, the thick portion being formed so that an outward facing surface of the wrap smoothly protrudes outward in a radial direction of the scroll, the thick portion being thicker than other portions, the fixed scroll portion and the oscillating scroll portion having deformation portions at positions facing the thick portion, and both inward and outward facing surfaces of the wrap of the scroll portion being displaced in the same direction in the radial direction of the scroll and deformed forward and backward in the radial direction to form the deformation portion A shape portion.
Description
Technical Field
The present invention relates to a scroll compressor and a refrigeration cycle apparatus used in an air conditioner, a refrigerator, and the like.
Background
Conventionally, in an air conditioning apparatus such as a multi-air conditioner for a building, a refrigerant circuit is configured by connecting an outdoor unit, which is an outdoor unit that is a heat source unit disposed outside the building, and an indoor unit, which is an indoor unit disposed inside the building, by pipes. Then, the refrigerant in the refrigerant circuit is circulated, and the air is heated or cooled by heat radiation and heat absorption of the refrigerant, thereby heating or cooling the air-conditioning target space.
A crescent-shaped compression chamber of a scroll compressor used in such an air conditioner, which is formed by a pair of wraps of a scroll provided in a fixed scroll portion and an oscillating scroll portion, compresses a refrigerant by moving toward the center and reducing the volume thereof due to the oscillating motion of the oscillating scroll portion. Here, in order to suppress the overcompression in which the pressure of the compression chamber becomes equal to or higher than the discharge pressure, an "overflow port" for allowing the overcompressed refrigerant to escape to the discharge space is generally provided in the middle of the compression chamber. In view of the above, a scroll compressor is disclosed in which the tooth thickness of the orbiting scroll part is locally increased, and an injection hole serving as a relief port is provided in the fixed scroll part at a position facing the orbiting scroll part (see, for example, patent document 1).
Documents of the prior art
Patent literature
Patent document 1: japanese patent No. 5978823
Disclosure of Invention
Problems to be solved by the invention
The technique disclosed in patent document 1 is a technique of increasing the flow rate of the refrigerant introduced from the injection hole to the compression chamber while preventing communication between the adjacent compression chambers via the injection hole by increasing the injection hole of the fixed scroll portion as much as possible. Here, in the technique disclosed in patent document 1, the inward surface of the fixed scroll portion facing the thick portion obtained by locally increasing the tooth thickness of the orbiting scroll portion is concave, and the tooth thickness is thin. Therefore, the displacement is increased in the thin portion having a concave shape on the inward surface of the fixed scroll portion, and the leakage of the gas refrigerant from the compression chamber is increased, which may deteriorate the performance. Further, the compression operation becomes unstable, and the reliability may be lowered.
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a scroll compressor and a refrigeration cycle apparatus having high efficiency and high reliability.
Means for solving the problems
A scroll compressor includes, in a sealed container, a fixed scroll portion having a fixed base plate and a fixed scroll provided on the fixed base plate, and an oscillating scroll portion having an oscillating base plate and an oscillating scroll provided on the oscillating base plate, the oscillating scroll portion being arranged so that a wrap of an oscillating scroll meshes with a wrap of the fixed scroll to form a compression chamber, the oscillating scroll having a thick portion provided at a position corresponding to an opening of a port provided on the fixed base plate and communicating with the compression chamber, an outward facing surface of a wrap being smoothly protruded outward in a radial direction of the scroll so that the thick portion is thicker than other portions, the fixed scroll and the oscillating scroll having deformation portions at positions facing the thick portion, and both inward and outward facing surfaces of the wrap of the scroll being displaced in the same direction in the radial direction of the scroll and deformed back and forth in a direction in comparison with the radial direction to form the thick portion A deformation portion.
Effects of the invention
In the present invention, the deformed portion of the fixed scroll opposed to the thick portion of the oscillating scroll and the deformed portion of the oscillating scroll opposed to the deformed portion of the fixed scroll are formed in shapes in which the inward surface is concave and the outward surface is convex. Therefore, the reduction in tooth thickness at the deformed portions of the fixed scroll and the oscillating scroll can be suppressed. Therefore, leakage of the gas refrigerant from the compression chamber can be suppressed, and performance can be improved efficiently. In addition, the compression operation can be stabilized and the reliability can be improved.
Drawings
Fig. 1 is a schematic diagram showing the overall configuration of a scroll compressor according to embodiment 1.
Fig. 2 is a diagram showing the scroll shape and the like of the scroll compressor according to embodiment 1.
Fig. 3 is a diagram illustrating the geometry of the thick portion of the scroll compressor according to embodiment 1.
Fig. 4 is an enlarged view of a portion centered on a thick portion of the scroll compressor in embodiment 1.
Fig. 5 is a diagram illustrating the restriction conditions of the thick portion 80 and the spill port 4b in the scroll compressor according to embodiment 1.
Fig. 6 is a diagram illustrating a compression operation of a scroll of the scroll compressor according to embodiment 1.
Fig. 7 is a diagram illustrating a compression operation of a scroll in a case where the scroll of the fixed scroll of the scroll compressor in embodiment 1 has a shape satisfying a predetermined condition.
Fig. 8 is a diagram illustrating a contact point of a compression mechanism of a scroll compressor according to embodiment 1.
Fig. 9 is a diagram showing the scroll shape and the like of the scroll compressor in embodiment 2.
Fig. 10 is a diagram showing the scroll shape and the like of the scroll compressor according to embodiment 3.
Fig. 11 is a diagram showing a configuration example of a refrigeration cycle apparatus according to embodiment 5.
Detailed Description
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 and the like. In the following drawings, members denoted by the same reference numerals are the same or corresponding portions, which are common throughout the embodiments described below. The form of the constituent elements shown throughout the specification is merely an example, and is not limited to the form described in the specification. In particular, the combination of the constituent elements is not limited to the combination in each embodiment, and the constituent elements described in other embodiments can be applied to another embodiment. In the following description, the upper side and the lower side in the drawings are referred to as "upper side" and "lower side", respectively. The pressure and temperature are not particularly determined by the relationship with absolute values, but are relatively determined in the state, operation, and the like of the device and the like. In addition, in a case where a plurality of devices of the same kind are distinguished by a subscript, the subscript and the like may be omitted from description unless they are particularly distinguished or specified.
Embodiment 1.
Fig. 1 is a schematic diagram showing the overall configuration of a scroll compressor according to embodiment 1. In fig. 1, a schematic cross-sectional view is shown to show an internal structure of the scroll compressor. The scroll compressor according to embodiment 1 includes a compression mechanism 8 for compressing a fluid such as a refrigerant to be compressed, an electric mechanism 110 for driving the compression mechanism 8 via a rotary shaft 6, and other components. The compression mechanism 8, the electric mechanism 110, and the like are housed in the closed casing 100 constituting the outline. In the scroll compressor according to embodiment 1, the compression mechanism 8 is disposed above and the electric mechanism 110 is disposed below the compression mechanism 8 in the sealed container 100.
Further, the frame 7 and the sub-frame 9 are housed in the closed casing 100 so as to face each other with the electric mechanism section 110 interposed therebetween. The frame 7 is disposed above the electric mechanism 110 and between the electric mechanism 110 and the compression mechanism 8. The sub-frame 9 is disposed below the electric mechanism 110. The frame 7 is fixed to the inner peripheral surface of the hermetic container 100 by shrink fitting, welding, or the like. The sub-frame 9 is fixed to the inner peripheral surface of the hermetic container 100 by shrink fitting, welding, or the like via a sub-frame holder 9 a.
A pump element 111 including a displacement pump is mounted below the subframe 9. The pump element 111 is a device for supplying the refrigerating machine oil stored in the oil storage 100a at the bottom of the closed casing 100 to a sliding portion such as a main bearing 7a of the compression mechanism 8 described later. The pump element 111 supports the rotary shaft 6 in the axial direction at the upper end face.
The sealed container 100 is provided with a suction pipe 101 for sucking the refrigerant and a discharge pipe 102 for discharging the refrigerant.
The compression mechanism 8 is a device having a function of compressing the refrigerant sucked from the suction pipe 101 and discharging the compressed refrigerant to a high-pressure portion formed above in the closed casing 100. The compression mechanism 8 includes a fixed scroll 1 and an oscillating scroll 2. The fixed scroll portion 1 is fixed to the closed casing 100 via the frame 7. On the other hand, the orbiting scroll part 2 is disposed below the fixed scroll part 1, and is swingably supported by an eccentric shaft part 6a of a rotary shaft 6 described later.
The fixed scroll portion 1 includes a fixed base plate 1a and a fixed scroll 1b, and the fixed scroll 1b has a spiral-shaped projection as a wrap standing on one surface of the fixed base plate 1 a. The oscillating scroll portion 2 includes an oscillating base plate 2a and an oscillating scroll 2b, and the oscillating scroll 2b has a spiral projection as a wrap standing on one surface of the oscillating base plate 2 a. The fixed scroll portion 1 and the oscillating scroll portion 2 are disposed in the sealed container 100 in a symmetrical scroll shape in which the fixed scroll 1b and the oscillating scroll 2b are engaged with each other in opposite phases. A space between the fixed scroll 1b and the orbiting scroll 2b is a compression chamber 71, and the volume of the compression chamber 71 decreases from the radially outer side to the radially inner side as the rotating shaft 6 rotates.
The fixed scroll 1 has a discharge port 4a and a spill port 4b communicating with the discharge space 72. The discharge port 4a and the overflow port 4b are holes that penetrate the fixed substrate 1a from the discharge space 72 to the compression chamber 71, and communicate the discharge space 72 and the compression chamber 71. Therefore, the discharge port 4a and the relief port 4b have opening portions on the compression chamber 71 side. The discharge port 4a is provided with a discharge valve 10 a. The spill port 4b is provided with an overpressure relief valve 10 b. The scroll compressor of embodiment 1 has the relief ports 4b at two locations, but may have the relief ports 4b at 1 location or more than two locations.
The frame 7 has a thrust surface on which the fixed scroll portion 1 is fixedly disposed and which axially supports a thrust force acting on the orbiting scroll portion 2. The frame 7 has an introduction flow path 7c formed therethrough, and the introduction flow path 7c guides the refrigerant sucked from the suction pipe 101 into the compression mechanism 8. Further, an Oldham's ring (12) for preventing rotation in the orbiting motion of the orbiting scroll part (2) is disposed on the frame (7).
The electric mechanism 110 is a driving device that supplies a rotational driving force to the rotary shaft 6. The electric mechanism 110 includes a motor stator 110a and a motor rotor 110 b. Motor stator 110a is connected to a glass terminal (not shown) present between frame 7 and motor stator 110a by a lead wire (not shown) in order to obtain electric power from the outside. Further, the motor rotor 110b is fixed to the rotary shaft 6 by shrink fit or the like. In order to balance the entire rotation system of the scroll compressor, the 1 st balance weight 60 is fixed to the rotation shaft 6, and the 2 nd balance weight 61 is fixed to the motor rotor 110 b.
The rotary shaft 6 includes an upper eccentric shaft portion 6a, a middle main shaft portion 6b, and a lower sub shaft portion 6 c. The eccentric shaft portion 6a is eccentric with respect to the axis of the rotating shaft 6. The eccentric shaft portion 6a is fitted to the orbiting scroll portion 2 via the slider 5 with a balance weight and the orbiting bearing 2c, and the orbiting scroll portion 2 is made to perform an orbiting motion by the rotation of the rotary shaft 6. The main shaft portion 6b is fitted to a main bearing 7a disposed on the inner periphery of a cylindrical boss portion 7b provided on the frame 7 via a sleeve (not shown), and slides with respect to the main bearing 7a via an oil film formed of a refrigerating machine oil. The main bearing 7a is fixed to the boss 7b by press-fitting a bearing material used for a sliding bearing such as a copper-lead alloy.
The sub-frame 9 is provided at its upper portion with a sub-bearing 3 formed of a ball bearing. The sub-bearing 3 supports the rotary shaft 6 in the radial direction below the electric mechanism 110. Here, the sub-bearing 3 may be supported by a bearing structure other than a ball bearing. The sub shaft portion 6c is fitted to the sub bearing 3 and slides with respect to the sub bearing 3 via an oil film formed of refrigerating machine oil. The axial centers of the main shaft portion 6b and the sub shaft portion 6c coincide with the axial center of the rotating shaft 6.
Here, the space in the closed casing 100 is defined as follows. The 1 st space 73 is a space on the motor rotor 110b side of the frame 7 in the internal space of the sealed container 100. A space surrounded by the inner wall of the frame 7 and the fixed board 1a is defined as a 2 nd space 74.
Fig. 2 is a diagram showing the scroll shape and the like of the scroll compressor according to embodiment 1. Next, the structure and the like in the compression mechanism 8 inside the closed casing 100 will be further described. A plurality of spaces formed between the fixed scroll 1b and the oscillating scroll 2b by meshing of wraps at the fixed scroll 1b and the oscillating scroll 2b are the above-described compression chambers 71. The oscillating scroll 2b includes a thick portion 80 at a position facing the opening of the overflow port 4b in the middle of the outward surface of the scroll facing the opposite side from the center side at the wall surface of the scroll, and the thick portion 80 is formed with a wall surface smoothly connected to the outward surface of the oscillating scroll 2b in a convex curve. In the scroll compressor according to embodiment 1, the thick portion 80 is formed in a convex shape by combining 3 circular arcs, but the thick portion 80 may be formed in a shape of 4 circular arcs or more, a curve in which curvature changes continuously, or the like. The fixed scroll 1b has a deformed portion 81a, which is formed by locally deforming the scroll shape, at a position corresponding to the spill port 4b and the thick portion 80. The oscillating scroll 2b has a deformed portion 81b in which the scroll shape is partially deformed at a position corresponding to the deformed portion 81 a. The deformation portion 81a and the deformation portion 81b will be described further later. Here, in fig. 2, the crescent-shaped compression chambers 71 located at symmetrical positions are provided with a total of two overflow ports 4b at 1, respectively, but the present invention is not limited thereto. One spill port 4b of the two spill ports 4b is communicated with a compression chamber 71 having an inward surface of the fixed scroll 1b as a wall, and the other spill port 4b is communicated with the compression chamber 71 having an outward surface of the fixed scroll 1b as a wall, whereby the compression chambers 71 are symmetrical. However, the present invention is not limited thereto.
Fig. 3 is a diagram illustrating the geometry of the thick portion of the scroll compressor in embodiment 1. The thick portion 80 is formed in a convex shape smoothly continuing to the outward surface of the orbiting scroll 2 b. Here, "smoothly connected" means that geometrically, as shown in fig. 3, 3 points, which are a connection point of two adjacent circular arcs and each point of the center coordinates of curvature obtained from the two adjacent circular arcs, are arranged on a straight line. Here, although the thick portion 80 is connected to the outward surface of the orbiting scroll 2b, the thick portion 80 is integrated with the orbiting scroll 2b, and the wall surface of the thick portion 80 is also a part of the outward surface of the orbiting scroll 2 b. As shown in fig. 2 and 3, both the thick portions 80 have a shape in which only a specific portion bulges outward with respect to the orbiting scroll 2b having a scroll shape based on an involute curve or the like. As shown in fig. 2, one of the two overflow ports 4b, which is sandwiched between the fixed scroll 1b on the outer side and the oscillating scroll 2b on the inner side, is located on the inner side of the fixed scroll 1b in a concave shape corresponding to the boss of the oscillating scroll 2 b. On the other hand, the other overflow port 4b, which is sandwiched between the oscillating scrolls 2b on the outer side and the fixed scroll 1b on the inner side, is located on the opposite side to the projection of the oscillating scroll 2b and beside the fixed scroll 1b that is not uneven.
Fig. 4 is an enlarged view of a portion of the scroll compressor according to embodiment 1, the portion being centered on a thick portion. As described above, the thick portion 80 is a portion of the orbiting scroll 2b in which the outward surface of the orbiting scroll 2b has a convex surface at a position outside an imaginary line (an involute curve or the like indicated by a broken line in fig. 3 or the like, the same applies hereinafter) connecting the orbiting direction to the front and the rear as viewed in the axial direction, and the wrap of the scroll is thick. The opening of the overflow port 4b can be opened and closed by the convex portion. In the case of a thick portion 80 having a convex shape such as a curve having 3 or more circular arcs or continuously changing curvature, a line sequentially intersects a curve of a scroll such as an involute curve and a circular arc having a curvature center on the outer side of the thick portion 80 with respect to the spiral direction of the scroll (for example, r in fig. 4out_1) And an arc having a center of curvature inside thick portion 80 (e.g., r in fig. 4)out_2) And an arc having a center of curvature on the outer side of thick portion 80 (e.g., r in fig. 4)out_3) The curve of the spiral such as an involute curve is connected to form a convex shape of the thick portion 80.
The orbiting scroll part 2 is driven by the scroll compressor to perform an orbiting motion. A portion of the fixed scroll 1b that contacts the thick-walled portion 80 of the oscillating scroll 2b during the oscillating movement is a deformed portion 81a, and the deformed portion 81a is formed by deforming an outward surface and an inward surface thereof so as to displace in the same direction in the radial direction both before and after the rotation direction. Therefore, the inward surface of the deformed portion 81a of the fixed scroll 1b has a shape recessed from an imaginary line (an involute curve shown by a broken line in fig. 4 and the like, hereinafter the same applies) connecting the front and rear of the deformed portion 81 a. The outward surface of the deformation portion 81a is a surface having a shape convex with respect to an imaginary line connecting the front and rear. The shape of the deformed portion 81a of the fixed scroll 1b is also formed by the same number of arcs as the thick portion 80 of the oscillating scroll 2 b. Similarly, in the oscillating scroll 2b, a portion which comes into contact with the deformed portion 81a of the fixed scroll 1b during the oscillating motion is a deformed portion 81b, and the deformed portion 81b is formed by deforming an inward surface and an outward surface of the oscillating scroll 2b so as to be displaced in the same direction in the radial direction from the front and the rear of the rotation direction.
Here, the spiral directions of the fixed scroll 1b and the oscillating scroll 2b are indicated by involute angles. The involute angle is sometimes referred to as the swirl angle. The involute angle is an angle formed between the base circle and the line when the line is unwound around the center of the base circle. In the fixed scroll 1b and the oscillating scroll 2b according to embodiment 1, the involute of a circle, which is a trajectory traced by the ends of a line wound around a base circle when the line is unwound while being stretched, has a spiral shape. When the radius of the base circle is denoted by "a", the coordinates of points on the involute can be expressed by "a" (cos (θ) + θ · sin (θ)) and "a" (sin (θ) - θ · cos (θ)) in a rectangular coordinate system expressed by "x, y". At this time, θ becomes an involute angle. Therefore, the positions of the fixed scroll 1b and the oscillating scroll 2b at the scroll positions correspond to the involute angles. Thus, the position on the vortex can be represented by the involute angle.
Here, as the shape of the scroll, in addition to a shape formed based on a simple involute of a circle, for example, a case of using a scroll deformed into an ellipse or the like is also conceivable. In this case, the center of the spiral line of the spiral can be determined, and the angle around the center can be set to the involute angle θ.
The fixed scroll 1b and the oscillating scroll 2b are wraps, and have a thickness in the radial direction. When the thickness of the teeth is taken into consideration, when the center line is an involute of a circle, the coordinates (x, y) of a point on a line formed by an inward surface which is a surface facing the center side may be represented as x ═ a { cos (θ) + (θ - α) · sin (θ) } and y ═ a { sin (θ) - (θ - α) · cos (θ) }. The coordinates (x, y) of a point on a line formed by an outward surface that is an outward surface facing the side opposite to the center side, that is, the outer surface, may be represented by x ═ a { cos (θ) + (θ + α) · sin (θ) } and y ═ a { sin (θ) - (θ + α) · cos (θ) }.
Note that the shape of the spiral at the oscillating scroll 2b and the fixed scroll 1b in embodiment 1 is a shape shown by an involute curve of a base circle. However, the present invention is not limited thereto. For example, the compression chamber 71 may have another shape such as a shape formed by an algebraic spiral.
For example, the involute angle at the position of the thick portion 80 of the oscillating scroll 2b is set to the involute angle θ [ rad ]]At this time, the involute angle at the position of the deformation portion 81a of the fixed scroll 1b becomes θ + (2n-1) π [ rad ]]. The involute angle at the position of the deformation portion 81b of the oscillating scroll 2b is θ +2n pi [ rad ]]. Wherein n is a natural number of 1 or more. As shown in fig. 4, r represents a concave curvature radius at the inward surface of the circular arcs of the thick portion 80 and the deformed portion 81inThe convex curvature radius of the outward surface is defined as rout. The swing radius is denoted by e. At this time, the curvature radius of the corresponding arc on the concave-convex surface facing the thick portion 80 and the deformed portion 81 is set to all the arc portions rin＝routThe relation of + e holds. Therefore, the radius of curvature of the arc on the inward surface side is larger than the radius of curvature of the arc on the outward surface side by the swing radius. In FIG. 4, with respect to rinAnd routThe arcs of like corner labels numbered one to another are corresponding arcs.
Here, the thick portion 80 is located outside of an imaginary line such as an involute curve in a certain range. Thus, although with an involute angle θ rad]The position of the thick portion 80 is shown, but the thick portion 80 is not positioned only at the involute angle θ rad]The meaning of the position is that the thick portion 80 is located at the involute angle θ rad]The meaning of a certain range before and after.Exemplary thick-walled portion 80 is shown as r in FIG. 4out_2As shown, the center coordinate of the curvature is located on the center point side, and the most outwardly convex position is located at the portion of the outwardly convex arc. The involute angle at this position is the involute angle θ [ rad ] of the thick-walled portion 80]。
Further, the deformation portion 81a located outside the thick portion 80 is formed in a wider range than the range of the thick portion 80. When a plurality of deformation portions 81a are provided in the radial direction, the range of the shape to be deformed is wider as the deformation portion 81a located on the outer side is located.
The amount of deviation from the virtual line in the radial direction is defined as a displacement distance in the thick portion 80 and the deformation portion 81 b. The displacement distance of the inward surface and the outward surface of the deformation portion 81b at θ + (2n-1) π [ rad ] is the same as the displacement distance of the thick portion 80 at the involute angle θ [ rad ]. Therefore, the thickness of the radial direction tooth of the portion of the thick portion 80 outside the deformed portion 81b is the same as the thickness of the radial direction tooth of the scroll formed based on the imaginary line in front and rear of the deformed portion 81 b. Therefore, in the scroll compressor according to embodiment 1, the reduction in tooth thickness at the deformation portion 81 can be suppressed without forming a portion where the tooth thickness of the scroll becomes thin, and therefore, the deformation of the teeth is not likely to occur. The deformation portion 81b is displaced by the same distance in the radial direction as the thick portion 80, and the deformation portion 81b is deformed in a curved shape in a wider range. Therefore, the convex shape of the outer side of the deformation portion 81b is formed by a gently curved surface having a larger curvature radius than the thick portion 80. Therefore, the deformation of the deformation portion 81b is further less likely to occur.
Next, conditions regarding the position of the thick portion 80 for causing the relief port 4b to function under any operating conditions of the scroll compressor such as a low compression ratio operation will be described. One of the thick portions 80 for opening and closing the spill port 4b communicating with the compression chamber 71 is preferably located at a position satisfying an involute angle θ of "θ > swing scroll end angle-3 π - (fixed scroll end angle-swing scroll end angle) [ rad ]", and the compression chamber 71 is formed by an inward surface of the fixed scroll 1b and an outward surface of the swing scroll 2 b. Further, it is preferable that one of the thick portions 80 opening and closing the spill port 4b communicating with the compression chamber 71 is located at a position satisfying an involute angle θ of "θ > swing scroll end angle-2 π [ rad ]", and the compression chamber 71 is formed by an outward surface of the fixed scroll 1b and an inward surface of the swing scroll 2 b. Thereby, all the overflow ports 4b are opened and closed by the thick portion 80.
The convex shape of the thick portion 80 is most protruded from the portion of the involute scroll in the radial direction at the involute angle θ as viewed in the axial direction, and becomes a rounded apex portion as it goes outward, and the amount of protrusion from the involute scroll in the radial direction decreases as the angle deviates forward and backward from the apex portion, and for example, the protrusion disappears at a position deviated from the involute angle θ by 0.05 to 0.2[ rad ], and the thick portion 80 is continuous with the portion of the scroll formed by the involute curve. Therefore, the relationship "the tooth thickness of the oscillating scroll 2b at the involute angle θ is equal to the thickness in the radial direction of the involute scroll + the amount of projection in the radial direction, that is, the thickness of the scroll of the oscillating scroll 2b at the involute angle θ > the length in the radial direction of the spill port 4b > the thickness in the radial direction of the involute scroll". Here, when the overflow port 4b at point 1 is formed by a plurality of holes, the distance between the inner position of the innermost hole and the outer position of the outermost hole is defined as the length in the radial direction of the port.
Fig. 5 is a diagram illustrating the restriction conditions of the thick portion 80 and the spill port 4b in the scroll compressor according to embodiment 1. Herein, r ispThe radius of the overflow port 4b is set. In addition, rtThe radius of the arc having the center at the inner side of the outward facing surface in the thick portion 80 is set. Furthermore, LtThe maximum thickness of the thick portion 80 is set. At this time, when the spill port 4b extends across the compression chamber 71, the gas refrigerant leaks from the high-pressure compression chamber 71 to the low-pressure compression chamber 71. Therefore, L is preferablet>2rpIs true for all rt，rt>rpThe relationship of (c) is true.
Fig. 6 is a diagram illustrating a compression operation of a scroll in the scroll compressor according to embodiment 1. Next, the operation of the scroll compressor will be described. Fig. 6 (a) shows a state where the rotational phase is 0 ° or 360 °. Fig. 6 (b) shows a state where the rotational phase is 90 °. Fig. 6 (c) shows a state where the rotational phase is 180 °. Fig. 6 (d) shows a positional relationship of the scroll arrangement when the rotational phase is 270 °. As shown in fig. 6, when the scroll compressor performs compression, the fixed scroll 1b and the oscillating scroll 2b operate while the outward surfaces and the inward surfaces thereof are in contact with the inward surfaces and the outward surfaces facing each other.
Fig. 7 is a diagram illustrating a compression operation of a scroll in a case where the scroll of the fixed scroll of the scroll compressor in embodiment 1 has a shape satisfying a predetermined condition. When the scroll of the fixed scroll 1b has a shape satisfying "fixed scroll end angle ═ swing scroll end angle + pi [ rad ]", as shown in fig. 7, two spill ports, that is, the spill port 4b communicating with the compression chamber 71 formed on the inward surface of the fixed scroll 1b and the spill port 4b communicating with the compression chamber 71 formed on the outward surface of the fixed scroll 1b can be opened and closed by one thick portion 80.
When the motor stator 110a of the electric mechanism 110 is energized, the motor rotor 110b rotates upon receiving torque. The rotary shaft 6 fixed to the motor rotor 110b is driven to rotate. The rotational motion of the rotary shaft 6 is transmitted to the orbiting scroll 2 via the eccentric shaft portion 6 a. The oscillating scroll 2b of the oscillating scroll portion 2 performs an oscillating motion with an oscillation radius while being restricted in rotation by the oldham ring 12. Here, the swing radius refers to the amount of eccentricity of the eccentric shaft portion 6a with respect to the main shaft portion 6 b.
Next, the flow of the refrigerant in the scroll compressor will be described. Arrows shown in fig. 1 indicate the flow of refrigerant in the scroll compressor. As the electric mechanism 110 is driven, the refrigerant circulating in the refrigerant circuit flows into the 1 st space 73 in the sealed container 100 through the suction pipe 101. The low-pressure refrigerant flowing into the 1 st space 73 flows into the 2 nd space 74 through the introduction flow path 7c provided in the frame 7. The low-pressure refrigerant flowing into the 2 nd space 74 is sucked into the compression chamber 71 in accordance with the relative oscillating operation of the oscillating scroll 2b and the fixed scroll 1b of the compression mechanism portion 8. As shown in fig. 4, the refrigerant sucked into the compression chamber 71 is increased in pressure from a low pressure to a high pressure by a change in the geometric volume of the compression chamber 71 accompanying the relative movement of the orbiting scroll 2b and the fixed scroll 1 b. Then, the refrigerant having a high pressure passes through the discharge port 4a of the fixed scroll 1, pushes open the discharge valve 10a, and is discharged into the discharge space 72. When the pressure in the compression chamber 71 reaches the discharge pressure before reaching the discharge port 4a, the gas refrigerant in the compression chamber 71 passes through the spill port 4b provided during compression, pushes open the compression spill valve 10b, and is discharged into the discharge space 72. The refrigerant discharged from the discharge port 4a and the over-compression relief valve 10b into the discharge space 72 is discharged as a high-pressure refrigerant from the discharge pipe 102 to the outside of the compressor.
Fig. 8 is a diagram illustrating a contact point of a compression mechanism of a scroll compressor according to embodiment 1. Fig. 8 shows the compression process every 10 deg. from a certain rotational phase phi to phi +50 deg.. Here, the overflow port 4b is omitted in fig. 8. As described above, the thick portion 80 of the oscillating scroll 2b, and the deformed portion 81 of the fixed scroll 1b have shapes in which 3 or more arcs are smoothly connected to an involute curve. Then, in a part of the rotational phase, the orbiting scroll 2b and the fixed scroll 1b are in contact with each other at a contact point 82, and a compression chamber 71 is formed in a closed space. At this time, in the scroll compressor according to embodiment 1, when performing compression of +20 ° and +30 °, as shown in fig. 8, the respective scrolls of the oscillating scroll 2b and the fixed scroll 1b contact each other at two portions on the thick portion 80 and the involute curve, and the contact point 82 is 3 points. Therefore, the contact points 82 increase compared to a scroll formed only of an involute curve without the thick portion 80 and the deformed portion 81 in the oscillating scroll 2b and the fixed scroll 1 b. By increasing the number of contact points 82, leakage of the gas refrigerant from the compression chamber 71 can be suppressed. In addition, by increasing the number of contact points 82, the pressure applied to each contact point 82 at 1 is reduced, and therefore the refrigerant leakage suppression effect is further improved.
As described above, in the scroll compressor according to embodiment 1, the thick portion 80 is provided in the orbiting scroll 2b, whereby the diameter of the relief port 4b can be increased. By increasing the diameter of the spill port 4b, pressure loss can be suppressed, and excessive compression loss can be suppressed. However, in the conventional technique, only the inner surface of the fixed scroll 1b facing the thick portion 80 of the oscillating scroll 2b is deformed into a concave shape. Therefore, the tooth thickness at the deformed portion becomes thinner than other portions of the tooth of the scroll. On the other hand, in the scroll compressor according to embodiment 1, the fixed scroll 1b facing the thick portion 80 of the orbiting scroll 2b has the deformed portion 81 in which the inward surface is concave and the outward surface is convex, and thus a local reduction in tooth thickness is suppressed. Therefore, an increase in displacement at the deformed portions 81a and 81b of the fixed scroll 1b can be suppressed, and leakage of the gas refrigerant from the compression chamber 71 can be suppressed, so that the performance can be improved. In addition, the compression operation can be stabilized.
In addition, since the scroll compressor according to embodiment 1 has an increased number of contact points 82 forming the compression chamber 71, the leakage of the gas refrigerant from the compression chamber 71 and the pressure at each contact point 82 can be reduced. In addition, stress concentration of thick portion 80 can be relaxed. The fixed scroll 1b facing the thick portion 80 of the oscillating scroll 2b has a deformed portion 81b whose inner and outer surfaces are both convex in the radial direction, and can suppress scroll displacement and root stress.
The scroll compressor according to embodiment 1 has two spill ports 4 b. Further, the one spill port 4b communicates with the compression chamber 71 having the inward surface of the fixed scroll 1b as a wall, and the other spill port 4b communicates with the compression chamber 71 having the outward surface of the fixed scroll 1b as a wall, so that the spill ports 4b correspond to the symmetrical compression chambers 71, whereby the compressed fluid can be stably discharged. In this case, the opening of each overflow port 4b can be opened and closed by the thick portion 80, and the compression efficiency can be improved.
In the scroll compressor according to embodiment 1, the thick portion 80 and the deformed portion 81 are smoothly and continuously connected by a combination of a plurality of arcs in a spiral shape such as an involute curve. Therefore, the thick portion 80 and the deforming portion 81 can be stably brought into contact with each other, and compression leakage and the like of the compression chamber 71 can be prevented. In addition, the radius r of the overflow port 4b is setpRadius r of a circular arc having a center at a position inward of the outward surface of thick portion 80tAnd the maximum thickness L of the thick portion 80tSatisfy Lt>2rpAnd for all rtSatisfy rt>rpIn relation to (3), the overflow port 4b is made smaller than the thickness of the tooth at the thick-walled portion 80. Therefore, the spill port 4b crosses the plurality of compression chambers 71, and the fluid does not leak.
Fig. 9 is a diagram showing the scroll shape and the like of the scroll compressor in embodiment 2. Hereinafter, embodiment 2 will be described mainly focusing on a structure different from embodiment 1. The configuration not described in embodiment 2 is the same as the configuration described in embodiment 1. The shape of the spill port 4b of the scroll compressor of embodiment 2 is different from that of embodiment 1. As shown in fig. 9, the opening of the overflow port 4b of embodiment 2 is flat. By making the overflow port 4b flat, the area of the opening of the overflow port 4b can be made larger than the area of the circular opening. Therefore, the scroll compressor according to embodiment 2 can reduce the excessive compression loss as compared with the scroll compressor according to embodiment 1.
Embodiment 3.
Fig. 10 is a diagram showing the scroll shape and the like of the scroll compressor in embodiment 3. Hereinafter, embodiment 3 will be described mainly focusing on a structure different from embodiment 1. The configuration not described in embodiment 3 is the same as the configuration described in embodiment 1. The scroll compressor of embodiment 3 has a plurality of spill ports 4b communicating with one compression chamber 71. By providing a plurality of spill ports 4b to one compression chamber 71, the area of the opening of the spill port 4b can be increased. Therefore, the scroll compressor according to embodiment 3 can reduce the excessive compression loss as compared with the scroll compressor according to embodiment 1.
Embodiment 4.
In embodiment 1 described above, a scroll compressor has been described as an example of a low-pressure shell-type compressor in which the interior of the closed casing 100 is filled with a low-pressure refrigerant, but the present invention is not limited to this. The same effect can be obtained even in a high-pressure shell type scroll compressor in which the inside of the closed casing 100 is filled with a high-pressure refrigerant.
In embodiments 1 to 3, the overflow port 4b is described as an example, but the present invention is not limited to this. For example, the present invention may be applied to another port provided in the fixed base plate 1a, such as an injection port for forcibly injecting a liquid refrigerant or a two-phase refrigerant into the compression chamber 71, instead of the overflow port 4 b.
Fig. 11 is a diagram showing a configuration example of a refrigeration cycle apparatus according to embodiment 5. Here, fig. 11 shows an air conditioner as a refrigeration cycle apparatus. In the air conditioning apparatus of fig. 6, the outdoor unit 300 and the indoor units 200 are connected by refrigerant pipes 400 to form a refrigerant circuit through which a refrigerant circulates. The outdoor unit 300 includes the scroll compressor 301 described in embodiments 1 to 4. The outdoor unit 300 includes a four-way valve 302, an outdoor heat exchanger 303, an expansion valve 304, and an outdoor blower 305. The indoor unit 200 includes an indoor heat exchanger 201.
As described above, the scroll compressor 301 compresses and discharges the sucked refrigerant. Here, although not particularly limited, the operating frequency of the scroll compressor 301 may be arbitrarily changed by an inverter circuit or the like, for example. The four-way valve 302 is a valve for switching the flow of the refrigerant between the cooling operation and the heating operation.
The outdoor heat exchanger 303 exchanges heat between the refrigerant and air (outdoor air). For example, in the heating operation, the evaporator functions to evaporate and vaporize the refrigerant. In the cooling operation, the refrigerant functions as a condenser and condenses and liquefies the refrigerant. Further, the outdoor fan 305 sends outdoor air to the outdoor heat exchanger 303 to promote heat exchange between the outdoor air and the refrigerant.
The expansion valve 304, such as an expansion device serving as a pressure reducing device, reduces the pressure of the refrigerant and expands the refrigerant. In the case of an electronic expansion valve or the like, for example, the opening degree is adjusted based on an instruction from a control device (not shown) or the like. The indoor heat exchanger 201 performs heat exchange between air to be air-conditioned and refrigerant, for example. During a heating operation, the refrigerant condenses and liquefies by functioning as a condenser. In the cooling operation, the refrigerant evaporates and vaporizes by functioning as an evaporator. The indoor blower 202 sends air to be air-conditioned to the indoor heat exchanger 201, and promotes heat exchange between the air and the refrigerant.
As described above, the refrigeration cycle apparatus according to embodiment 5 is provided with the scroll compressor 301 described in embodiment 1 and embodiment 2 as a device, and thereby the outdoor unit 300 and the like can be downsized.
Description of the reference numerals
1. A fixed scroll portion; 1a, fixing a substrate; 1b, a fixed scroll; 2. an oscillating scroll portion; 2a, a swing substrate; 2b, an oscillating scroll; 2c, a swing bearing; 3. a secondary bearing; 4a, a discharge port; 4b, an overflow port; 5. a slider with a balancing weight; 6. a rotating shaft; 6a, an eccentric shaft portion; 6b, a main shaft part; 6c, a counter shaft part; 7. a frame; 7a, a main bearing; 7b, a hub; 7c, an introduction flow path; 8. a compression mechanism section; 9. a sub-frame; 9a, a subframe holder; 10a, a discharge valve; 10b, an over-compression overflow valve; 12. the Oldham ring; 60. 1, balancing weight; 61. a 2 nd balance weight; 71. a compression chamber; 72. a discharge space; 73. 1 st space; 74. a 2 nd space; 80. a thick-walled portion; 81. 81a, 81b, deformation portion; 82. a contact point; 100. a closed container; 100a, an oil reservoir; 101. a suction pipe; 102. a discharge pipe; 110. an electric mechanism section; 110a, a motor stator; 110b, a motor rotor; 111. a pump element; 200. an indoor unit; 201. an indoor heat exchanger; 202. an indoor blower; 300. an outdoor unit; 301. a scroll compressor; 302. a four-way valve; 303. an outdoor heat exchanger; 304. an expansion valve; 305. an outdoor blower; 400. refrigerant piping.
Claims (11)
1. A scroll compressor in which, in a scroll compressor,
the scroll compressor comprises a fixed scroll part and an oscillating scroll part in a closed container,
the fixed scroll portion has a fixed base plate and a fixed scroll provided on the fixed base plate,
the oscillating scroll portion has an oscillating base plate and an oscillating scroll provided on the oscillating base plate, and is configured to mesh a wrap of a scroll at the oscillating scroll with a wrap of a scroll at the fixed scroll to become a compression chamber,
the swing scroll includes a thick portion provided at a position corresponding to an opening of a port provided in the fixed base plate and communicating with the compression chamber, and an outward surface of the wrap is smoothly projected outward in a radial direction of the scroll so that the thick portion is thicker than other portions,
the fixed scroll and the oscillating scroll have deformation portions at positions facing the thick portion, and both inward and outward surface sides of the wrap of the scroll are displaced in the same direction in the radial direction of the scroll and deformed forward and backward in the spiral direction to form the deformation portions.
2. The scroll compressor of claim 1,
when the position of the thick portion is located at a position corresponding to an involute angle θ [ rad ] when the swirl direction of the scroll in the fixed scroll and the oscillating scroll is expressed by an involute angle based on a base circle of the scroll, the deformation portion of the fixed scroll is located at a position corresponding to θ + (2n-1) π [ rad ] and the deformation portion of the oscillating scroll is located at a position corresponding to θ +2n π [ rad ] in the case of a natural number n.
3. The scroll compressor according to claim 1 or 2,
the thick portion and the deformable portion have curved wall surfaces formed by connecting a plurality of arcs, and the arc on the inward surface side of the two corresponding arcs has a radius of curvature larger than the arc on the outward surface side of the two corresponding arcs, on the wall surface of the thick portion facing the deformable portion and on the wall surface of the deformable portion facing the deformable portion.
4. The scroll compressor according to any one of claims 1 to 3,
the fixed base plate has two or more ports, at least one of the ports communicates with the compression chamber having an inward surface of the wrap of the fixed scroll as a wall surface, and at least one of the ports communicates with the compression chamber having an outward surface of the fixed scroll as a wall surface.
5. The scroll compressor according to claim 4,
all the ports are opened and closed by the thick-walled portion of the oscillating scroll.
6. The scroll compressor according to any one of claims 3 to 5,
the shape of the thick portion and the wall surface at the deformation portion is a curve in which one or more circular arcs having a curvature center on the opposite side of the center of the scroll to the outer side of the thick portion in the rotational direction of the scroll, one or more circular arcs having a curvature center on the center side of the scroll to the inner side of the thick portion, and one or more circular arcs having a curvature center on the opposite side of the center of the scroll are connected in this order, and the curvature centers of two adjacent circular arcs of the circular arcs and the connection point of the two circular arcs are arranged on a straight line.
7. The scroll compressor according to any one of claims 1 to 6,
the port communicates the compression chamber with a discharge space in the closed container.
8. The scroll compressor according to any one of claims 3 to 7,
the radius of the port is set as rpR represents a radius having a center at a position inside the outward surface in the arc constituting the shape of the wall surface of the thick portiontThe maximum thickness of the thick portion is set to LtWhen has Lt>2rpAnd rt>rpThe relationship (c) in (c).
9. The scroll compressor according to any one of claims 1 to 8,
the opening of the port is flat.
10. The scroll compressor according to any one of claims 1 to 9,
a plurality of the ports communicate with one of the compression chambers.
11. A refrigerating cycle apparatus, wherein,
the refrigeration cycle apparatus includes a refrigerant circuit in which a condenser, a pressure reducing device, an evaporator, and the scroll compressor according to any one of claims 1 to 10 are connected by pipes to circulate a refrigerant.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/048596 WO2021117173A1 (en) | 2019-12-12 | 2019-12-12 | Scroll compressor and refrigeration cycle device |
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| Publication Number | Publication Date |
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| CN114787515A true CN114787515A (en) | 2022-07-22 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201980102765.7A Pending CN114787515A (en) | 2019-12-12 | 2019-12-12 | Scroll compressor and refrigeration cycle device |
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| JP (1) | JP6742567B1 (en) |
| CN (1) | CN114787515A (en) |
| WO (1) | WO2021117173A1 (en) |
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| DE102021207740A1 (en) | 2021-07-20 | 2023-01-26 | Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg | Scroll machine and vehicle air conditioner |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09158852A (en) * | 1995-12-13 | 1997-06-17 | Hitachi Ltd | Scroll type fluid machinery |
| JP2014020253A (en) * | 2012-07-17 | 2014-02-03 | Toyota Industries Corp | Scroll type compressor |
| CN105190042A (en) * | 2013-05-21 | 2015-12-23 | Lg电子株式会社 | Scroll compressor |
| WO2017138131A1 (en) * | 2016-02-10 | 2017-08-17 | 三菱電機株式会社 | Scroll compressor |
| CN107208633A (en) * | 2015-04-22 | 2017-09-26 | 三菱电机株式会社 | Screw compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103814218B (en) * | 2011-09-21 | 2016-03-09 | 大金工业株式会社 | Scroll compressor |
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2019
- 2019-12-12 CN CN201980102765.7A patent/CN114787515A/en active Pending
- 2019-12-12 JP JP2020528350A patent/JP6742567B1/en active Active
- 2019-12-12 WO PCT/JP2019/048596 patent/WO2021117173A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09158852A (en) * | 1995-12-13 | 1997-06-17 | Hitachi Ltd | Scroll type fluid machinery |
| JP2014020253A (en) * | 2012-07-17 | 2014-02-03 | Toyota Industries Corp | Scroll type compressor |
| CN105190042A (en) * | 2013-05-21 | 2015-12-23 | Lg电子株式会社 | Scroll compressor |
| CN107208633A (en) * | 2015-04-22 | 2017-09-26 | 三菱电机株式会社 | Screw compressor |
| WO2017138131A1 (en) * | 2016-02-10 | 2017-08-17 | 三菱電機株式会社 | Scroll compressor |
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| Publication number | Publication date |
|---|---|
| JP6742567B1 (en) | 2020-08-19 |
| WO2021117173A1 (en) | 2021-06-17 |
| JPWO2021117173A1 (en) | 2021-12-09 |
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