WO2020165967A1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
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- WO2020165967A1 WO2020165967A1 PCT/JP2019/005046 JP2019005046W WO2020165967A1 WO 2020165967 A1 WO2020165967 A1 WO 2020165967A1 JP 2019005046 W JP2019005046 W JP 2019005046W WO 2020165967 A1 WO2020165967 A1 WO 2020165967A1
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- spiral body
- scroll
- fixed
- curve
- scroll compressor
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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
Definitions
- the present invention relates to a scroll compressor used for an air conditioner, a refrigerator, and the like.
- a scroll compressor used for an air conditioner, a refrigerator, and the like includes a compression mechanism section that compresses a refrigerant in a compression chamber formed by combining a fixed scroll and an orbiting scroll, and a container that houses the compression mechanism section. It has a different configuration.
- Each of the fixed scroll and the orbiting scroll has a structure in which a spiral body is erected on a base plate, and the spiral bodies mesh with each other to form a compression chamber. By swinging the swing scroll, the compression chamber moves while reducing the volume, and the refrigerant is sucked and compressed in the compression chamber.
- the technology aims to increase the suction capacity of the compression chamber as much as possible to increase the compression function while keeping the container diameter the same. Development is important. In order to increase the suction volume of the compression chamber while keeping the container diameter the same, it is necessary to devise the spiral shape of the spiral body.
- An Oldham ring which has the function of preventing the orbiting scroll from rotating, is located near the compression mechanism of the scroll compressor. Considering that the key part of the Oldham ring is released, it is desirable that the outer shape of the base plate of the orbiting scroll is flat rather than circular in order to improve the packing density of the compressor parts.
- the spiral shape of the spiral body also has a flat shape so that the limited space on the base plate can be effectively utilized to secure a large suction volume of the compression chamber. It is possible. Therefore, as in Patent Document 1, making the spiral shape of the spiral body a flat shape is effective in increasing the suction volume of the compression chamber.
- Patent Document 1 describes that the contour of the spiral body and the spiral shape are made flat, but the specific definition of the spiral shape is not described.
- the spiral shape of the spiral body there is a technology defined by an involute curve with a perfect circle having a predetermined radius as a basic circle as described above.However, even when the spiral shape is a flat shape, it is not necessary to manufacture the spiral body. It is necessary to specifically define the spiral shape.
- the present invention has been made in view of the above points, and an object thereof is to provide a scroll compressor capable of defining a spiral shape of a spiral body having a flat contour by an expression.
- a scroll compressor includes a fixed scroll in which a fixed scroll is erected on a fixed base plate and a swing scroll in which a swing scroll is set up on a swing base plate.
- a scroll compressor that compresses refrigerant in a compression chamber formed by meshing with an oscillating scroll, one of the outer curve and the inner curve of each of the fixed scroll and the oscillating scroll is used to extend the base circle.
- the length w( ⁇ ) of the extended arm is a function that increases while changing in a sine wave or cosine wave with ⁇ [rad] as one cycle with respect to the angle of extension ⁇ .
- the spiral shape of the spiral body is defined by the formulas (1) and (2) using the expansion angle ⁇ and the basic circle radius a in the x and y coordinate systems, and also the formulas (1) and
- the extension arm length w( ⁇ ) in Expression (2) is a function that increases while changing in a sine wave shape or a cosine wave shape with ⁇ [rad] as one cycle with respect to the extension angle ⁇ .
- y a ⁇ sin ⁇ -w( ⁇ ) ⁇ cos ⁇ (2)
- FIG. 3 is a plan view showing a fixed scroll and a swing scroll of the compression mechanism portion of the scroll compressor according to Embodiment 1 of the present invention.
- FIG. 5 is a compression process diagram showing an operation during one rotation of the orbiting scroll in the scroll compressor according to Embodiment 1 of the present invention. It is explanatory drawing of the spiral drafting method which comprises the compression mechanism part of the scroll compressor which concerns on Embodiment 1 of this invention.
- FIG. 1 is a schematic vertical cross-sectional view of the overall configuration of a scroll compressor according to Embodiment 1 of the present invention.
- the scroll compressor 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 rotary shaft 6, and other components, which form an outer shell. It has a configuration of being housed inside the closed container 100.
- a frame 7 and a sub-frame 9 are housed so as to face each other with the electric mechanism section 110 interposed therebetween.
- the frame 7 is arranged on the upper side of the electric mechanism unit 110 and is located between the electric mechanism unit 110 and the compression mechanism unit 8.
- the sub-frame 9 is located below the electric mechanism unit 110.
- the frame 7 is fixed to the inner peripheral surface of the closed container 100 by shrink fitting or welding.
- the sub-frame 9 is fixed to the inner peripheral surface of the closed container 100 by shrink fitting, welding or the like via the sub-frame holder 9a.
- a pump element 112 including a positive displacement pump is attached below the subframe 9.
- the pump element 112 supplies the refrigerating machine oil stored in the oil sump 100a at the bottom of the closed container 100 to sliding parts such as a main bearing 7a of the compression mechanism 8 described later.
- the pump element 112 axially supports the rotary shaft 6 at its upper end surface.
- the closed 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 section 8 has a function of compressing the refrigerant sucked from the suction pipe 101 and discharging the compressed refrigerant to a high pressure section formed in the upper portion of the closed container 100.
- the compression mechanism section 8 includes a fixed scroll 1 and an orbiting scroll 2.
- the fixed scroll 1 is fixed to the closed container 100 via the frame 7.
- the oscillating scroll 2 is disposed below the fixed scroll 1 and is oscillatably supported by an eccentric shaft portion 6a of the rotary shaft 6 described later.
- the fixed scroll 1 includes a fixed base plate 1a and a fixed spiral body 1b, which is a spiral protrusion standing on one surface of the fixed base plate 1a.
- the oscillating scroll 2 includes an oscillating base plate 2a and an oscillating scroll body 2b which is a spiral protrusion provided upright on one surface of the oscillating base plate 2a.
- the fixed scroll 1 and the orbiting scroll 2 are arranged in the hermetic container 100 in a symmetrical spiral shape in which the fixed scroll 1b and the orbiting scroll 2b are meshed with each other in opposite phases.
- a compression chamber 71 is formed between the fixed spiral body 1b and the oscillating spiral body 2b, the volume of which decreases as the rotary shaft 6 rotates from the outer side toward the inner side in the radial direction.
- a baffle 4 is fixed to the surface of the fixed base plate 1a of the fixed scroll 1 opposite to the orbiting scroll 2.
- the baffle 4 is formed with a through hole 4a communicating with the discharge port 1c of the fixed scroll 1, and the discharge valve 11 is provided in the through hole 4a.
- a discharge muffler 12 is attached to the baffle 4 so as to cover the through hole 4a.
- the frame 7 has a fixed scroll 1 and a thrust surface that axially supports the thrust force acting on the orbiting scroll 2. Further, the frame 7 has an opening 7 c penetratingly formed therein for guiding the refrigerant sucked from the suction pipe 101 into the compression mechanism portion 8.
- an Oldham ring 14 is arranged on the frame 7 to prevent rotation of the orbiting scroll 2 during the orbiting motion.
- the key portion 14 a of the Oldham ring 14 is arranged on the outer peripheral side of the swing base plate 2 a of the swing scroll 2.
- the electric mechanism unit 110 supplies a rotational driving force to the rotating shaft 6, and includes an electric motor stator 110a and an electric motor rotor 110b.
- the electric motor stator 110a is connected to a glass terminal (not shown) existing between the frame 7 and the electric motor stator 110a with a lead wire (not shown) in order to obtain electric power from the outside.
- the electric motor stator 110a is fixed to the rotary shaft 6 by shrink fitting or the like.
- a first balance weight 60 is fixed to the rotating shaft 6 and a second balance weight 61 is fixed to the electric motor stator 110a in order to balance the entire rotation system of the scroll compressor.
- the rotary shaft 6 is composed of an eccentric shaft portion 6a above the rotary shaft 6, a main shaft portion 6b, and a sub shaft portion 6c below the rotary shaft 6.
- the eccentric shaft portion 6a is fitted to the orbiting scroll 2 via the slider 5 with the balance weight and the orbiting bearing 2c, and the orbiting scroll 2 is caused to orbit by the rotation of the rotating shaft 6.
- the main shaft portion 6b is fitted via a sleeve 13 to a main bearing 7a arranged on the inner circumference of a cylindrical boss portion 7b provided on the frame 7, and slides on the main bearing 7a via an oil film of refrigerating machine oil. To do.
- the main bearing 7a is fixed in the boss 7b by press-fitting a bearing material such as a copper-lead alloy used for a slide bearing.
- a sub-bearing 10 made up of a ball bearing is provided on the upper portion of the sub-frame 9, and the rotary shaft 6 is supported in the radial direction at the lower portion of the electric mechanism unit 110.
- the sub bearing 10 may be supported by a bearing structure other than the ball bearing.
- the sub shaft portion 6c is fitted with the sub bearing 10 and slides on the sub bearing 10 through an oil film of refrigerating machine oil.
- the axes of the main shaft portion 6b and the auxiliary shaft portion 6c coincide with the axis of the rotary shaft 6.
- the space inside the closed container 100 is defined as follows. Of the internal space of the closed container 100, the space on the electric motor rotor 110b side of the frame 7 is referred to as a first space 72. Further, the space formed by the inner wall of the frame 7 and the fixed base plate 1a is referred to as a second space 73. Further, the space on the discharge pipe 102 side of the fixed base plate 1a is referred to as a third space 74.
- FIG. 2 is a cross-sectional view of the compression mechanism portion of the scroll compressor according to the first embodiment of the present invention.
- FIG. 3 is a plan view showing a fixed spiral body and an oscillating spiral body of the compression mechanism portion of the scroll compressor according to Embodiment 1 of the present invention. 2 and 3, in order to facilitate the distinction between the fixed scroll 1b of the fixed scroll 1 and the swing scroll 2b of the swing scroll 2, the swing scroll 2b of the swing scroll 2 is hatched. It has been given. The same applies to the figures described below.
- the airtight container 100 has a perfect circular shape in plan view, and is fixed inside the airtight container 100 with the outer peripheral surface of the frame 7 being in contact with the inner surface of the airtight container 100. Therefore, the outer peripheral surface of the frame 7 also has a perfect circular shape.
- the fixed scroll 1b of the fixed scroll 1 and the orbiting scroll 2 are arranged in the second space 73 inside the frame 7, the fixed scroll 1b of the fixed scroll 1 and the orbiting scroll 2 are arranged.
- the key portion 14 a of the Oldham ring 14 is arranged in the second space 73.
- the outer shape of the swing base plate 2a is a flat shape. Note that the flat shape includes an elliptical shape and an elliptical shape, and in short, refers to any shape that is flatter than a circle.
- the rocking spiral body 2b standing on the rocking base plate 2a is also made flat so that the rocking base plate 2a is
- the space can be effectively used and the space efficiency can be improved.
- the fixed base plate 1a and the fixed base plate 1a and the fixed spiral body 1b have a flat shape.
- the volume of the compression chamber 71 can be increased while the size of the closed container 100 remains the same, and the compression function can be improved.
- the closed container 100 can be downsized.
- the fixed spiral body 1b and the swinging spiral body 2b are not distinguished from each other, and both are collectively referred to as a "spiral body".
- FIG. 4 is a compression process diagram showing an operation during one rotation of the orbiting scroll in the scroll compressor according to Embodiment 1 of the present invention.
- FIG. 4A shows the position of the spiral body when the rotation phase is 0 [rad] (2 ⁇ [rad]).
- FIG. 4B shows the position of the spiral body when the rotation phase is ⁇ /2 [rad].
- FIG. 4C shows the position of the spiral body when the rotation phase is ⁇ [rad].
- FIG. 4D shows the position of the spiral body when the rotation phase is 3 ⁇ /2 [rad].
- the electric motor stator 110a of the electric mechanism unit 110 When the electric motor stator 110a of the electric mechanism unit 110 is energized, the electric motor rotor 110b receives a rotational force and rotates. Accordingly, the rotary shaft 6 fixed to the electric motor rotor 110b is rotationally driven. The rotary motion of the rotary shaft 6 is transmitted to the orbiting scroll 2 via the eccentric shaft portion 6a.
- the oscillating scroll 2b of the oscillating scroll 2 oscillates with an oscillating radius while its rotation is restricted by the Oldham ring 14.
- the swing radius means the amount of eccentricity of the eccentric shaft portion 6a with respect to the main shaft portion 6b.
- the refrigerant flows from the external refrigeration cycle into the first space 72 in the closed container 100 via the suction pipe 101.
- the low-pressure refrigerant that has flowed into the first space 72 flows into the second space 73 through the two openings 7c provided in the frame 7.
- the low-pressure refrigerant that has flowed into the second space 73 is sucked into the compression chamber 71 as the rocking spiral body 2b and the fixed scroll body 1b of the compression mechanism portion 8 relatively rock.
- the refrigerant sucked into the compression chamber 71 is increased in pressure from low pressure to high pressure due to the geometrical volume change of the compression chamber 71 due to the relative movement of the oscillating spiral body 2b and the fixed spiral body 1b as shown in FIG.
- the high-pressure refrigerant passes through the discharge port 1c of the fixed scroll 1 and the through hole 4a of the baffle 4, pushes the discharge valve 11 open, and is discharged into the discharge muffler 12.
- the refrigerant discharged into the discharge muffler 12 is discharged into the third space 74 and discharged from the discharge pipe 102 as a high-pressure refrigerant to the outside of the compressor.
- the contours of the oscillating spiral body 2b and the fixed spiral body 1b are flat, and the spiral shape is also flat.
- the spiral shape of the spiral body is a flat shape, even when the swing spiral body 2b is operated with a constant swing radius as shown in FIG.
- the outward surface and the inward surface of the device operate while contacting the inward surface and the outward surface of the fixed spiral body 1b facing each other.
- the first embodiment is characterized in that the spiral shape of the spiral body having a flat contour is defined by an equation.
- the spiral shape is determined by an outer curve that specifies the outward surface of the spiral body and an inner curve that specifies the inward surface of the spiral body.
- one of the outer curve and the inner curve of the spiral body is a curve that is an extension line of the basic circle, and in the x, y coordinate system.
- a curve defined by the formula (1) and the formula (2) is obtained by using the expansion angle ⁇ .
- a in the formulas (1) and (2) is the radius of the basic circle.
- the extension arm length w( ⁇ ) in the equations (1) and (2) is the point on the curve at the extension angle ⁇ of the extension line from the point on the circumference at the extension angle ⁇ of the base circle. It is the length of a straight line connecting the lines, and is given by a function that changes in a sine wave shape or a cosine wave shape with ⁇ [rad] as one cycle. Thereby, the spiral shape of the spiral body having a flat contour can be defined by an equation.
- the extension arm length w( ⁇ ) changes in a sine wave shape or a cosine wave shape as described above, but in the first embodiment, as an example, it changes in a sine wave shape as in Expression (3). Let it be done. Note that ⁇ and ⁇ in the equation (3) are coefficients. N is a natural number of 1 or more.
- ⁇ holds even if it is a positive value or a negative value.
- ⁇ is a positive value. Note that the flatness of the contour changes by changing ⁇ . Further, by changing ⁇ , the reduction ratio of the wall thickness of the spiral body changes. Specific changes in the spiral body when ⁇ and ⁇ are changed will be described in the second and third embodiments.
- the spiral shape is determined by the outer curve that specifies the outward surface of the spiral body and the inner curve that specifies the inward surface of the spiral body as described above.
- a method for drawing a spiral shape when the outer curve is defined by the equations (1) and (2) will be described with reference to FIG.
- FIG. 5 is an explanatory diagram of a spiral-shaped drawing method that constitutes the compression mechanism portion of the scroll compressor according to the first embodiment of the present invention.
- the steps (a), (b), (c), and (d) are drawn.
- an extension line 30 of the basic circle is drawn.
- the extension arm length w( ⁇ ) increases in a sine wave shape with ⁇ [rad] as one cycle, depending on the extension angle ⁇ as described above.
- the incision line 30 drawn here is the outer curve.
- the curve 30 drawn in the step (a) becomes the outer curve of the oscillating spiral body 2b
- the curve 33 drawn in the step (d) becomes the inner curve of the oscillating spiral body 2b
- the hatched area in the step (d). Is the cross section of the oscillating spiral body 2b.
- the extension arm length w( ⁇ ) is a swinging spiral when the value of ⁇ is 0.5, the value of ⁇ is 0.015, and the value of N is 1 in the formula (3).
- the shape of the body 2b is described.
- the same procedure as that of the above-mentioned swing spiral body 2b is performed, and in the specification having the same thickness as the swing spiral body 2b, the shape of the swing spiral body 2b is rotated by ⁇ [rad]. It becomes a shape.
- the spiral-shaped drawing method in which the outer curve is defined by the equations (1) and (2) has been described, but the inner curve is defined by the equations (1) and (2).
- the method of drawing a spiral shape in the case of the curved line is basically the same.
- the outer curve may be drawn as follows. First, the procedure of FIG. 5(a) is performed, and then the curve portion of the curve 30 located outside the curve 31 in FIG. 5(b) is not used in the subsequent drawing procedure. Then, a plurality of circles 32 each having a center on the curve 31 and a radius equal to the swing radius of the swing scroll 2 are drawn. The inner envelope of this circle group is the outer curve.
- FIG. 6 is a diagram showing an example of characteristics of the extension arm length w( ⁇ ) used for drawing the spiral shape of the spiral body in the scroll compressor according to the first embodiment of the present invention.
- the vertical axis in FIG. 6 represents the ratio of w( ⁇ ) to the product of the basic circle radius a and the expansion angle ⁇ .
- the horizontal axis of FIG. 6 indicates the extension angle ⁇ [rad].
- the waveform of the extended arm length w( ⁇ ) shown in FIG. 6 it is shown that the larger the value of w( ⁇ )/a ⁇ , the thicker the spiral body becomes. Therefore, at ⁇ /2, 3 ⁇ /2, 5 ⁇ /2, and 7 ⁇ /2, the wall thickness of the spiral body increases.
- the spiral body is extended in the direction of the extension angle having a peak of more than 1.0. Therefore, in the example of FIG. 6, when the expansion angle is ⁇ /2, 3 ⁇ /2, 5 ⁇ /2, and 7 ⁇ /2, the peak that exceeds 1.0 is present, and as shown in FIG. It becomes a stretched shape.
- the peak period of the extended arm length w( ⁇ ) is ⁇ [rad].
- ⁇ is 0.015, which is 0 or more, so the cycle of the peak of the extended arm length w( ⁇ ) is slightly shorter than ⁇ [rad].
- the peak period of the extended arm length w( ⁇ ) becomes slightly longer than ⁇ [rad].
- the period of the extension arm length w( ⁇ ) may deviate from ⁇ [rad] depending on the value of ⁇ , but the deviation is slight. Therefore, the expression “the length of the extended arm w( ⁇ ) changes in a sine wave with ⁇ [rad] as one cycle with respect to the extended angle ⁇ ” indicates that the cycle matches ⁇ [rad]. It is not limited to this, but includes cases where there is some deviation.
- the spiral shape of the spiral body is defined by the above equations (1) and (2) using the expansion angle ⁇ .
- the extension arm length w( ⁇ ) in the equations (1) and (2) is a function that changes into a sine wave or a cosine wave with ⁇ [rad] as one cycle with respect to the extension angle ⁇ . .. Accordingly, the spiral shape of the spiral body having a flat contour can be defined by an equation.
- the spiral body according to the first embodiment has a flat shape along with the base plate, the mounting density of the spiral body on the base plate can be improved.
- the packing density of the spiral body can be improved, and the total length of the spiral of the spiral body is set to be long. It becomes possible to do. Since the total length of the spiral of the spiral body can be increased, the area of the entire axial end surface of the spiral body can be set large.
- Some scroll compressors have a compliant mechanism that allows the fixed scroll 1 and the orbiting scroll 2 to come into contact with each other in the axial direction. Even in this type of scroll compressor, the surface pressure generated at the tip end surface of the scroll is reduced. It can be reduced. Therefore, abrasion and seizure due to sliding can be suppressed, and reliability can be improved.
- the rotational phases of 0 and ⁇ slide on the side surface of the spiral body as compared with the rotational phases of ⁇ /2 and 3 ⁇ /2 in FIG.
- the speed can be set small. Therefore, by setting the sliding speed to be low in the rotation phase where the gas load in the horizontal direction is large, and setting the sliding speed to be large in the rotation phase where the gas load in the horizontal direction is small, the PV value on the side surface of the spiral body is set. Can be reduced.
- the PV value is the product of the load and the sliding speed. Since the PV value can be reduced in this way, abrasion and seizure due to sliding can be suppressed, and reliability can be improved.
- Embodiment 2 a change in flatness of the contour of the spiral body according to the value of ⁇ in the above formula (3) will be described.
- the second embodiment will be described focusing on the configuration different from that of the first embodiment, and the configuration not described in the second embodiment is the same as that of the first embodiment.
- FIG. 7 is a diagram showing changes in the flatness of the outer curve of the scroll in the scroll compressor according to the second embodiment of the present invention.
- the value of ⁇ is fixed to 0.005 and the value of N is fixed to 1.
- the oblateness is the ratio D1/D2 of the major axis D1 and the minor axis D2 as shown in FIG. 7(a). Therefore, as shown in FIG. 7, the oblateness increases as the value of ⁇ increases.
- the same effect as that of the first embodiment is obtained, and by changing the value of ⁇ , it becomes possible to arbitrarily set the flatness of the contour of the spiral body. Therefore, by changing ⁇ according to the shape of the base plate and setting the flatness of the contour of the spiral body, the contour of the spiral body is optimized and the packing density of the spiral body on the base plate is improved. be able to.
- Embodiment 3 the change in the reduction ratio of the wall thickness of the spiral body according to the value of ⁇ in the above formula (3) will be described.
- the third embodiment will be described focusing on the configuration different from the first embodiment, and the configuration not described in the third embodiment is the same as that of the first embodiment.
- FIG. 8 is a diagram showing an outer curve of the scroll in the scroll compressor according to the third embodiment of the present invention.
- the value of ⁇ is fixed to 0.2 and the value of N is fixed to 1.
- the interval reduction rate is the ratio P1/P2 between the winding start interval P1 and the winding end interval P2, as shown in FIG. Therefore, from FIG. 8, as ⁇ is increased to 0 or more, the reduction rate of the interval increases.
- the reduction ratio of the wall thickness of the spiral body also increases as ⁇ increases to 0 or more like the reduction ratio of the interval.
- the reduction ratio of the wall thickness is the ratio of the wall thickness at the winding start portion to the wall thickness at the winding end portion of the spiral body.
- ⁇ takes a value of 0 or more.
- the value of (1- ⁇ ) in formula (3) decreases as the expansion angle ⁇ increases. Therefore, as is clear from FIG. 6, the value of w( ⁇ )/a ⁇ becomes smaller every ⁇ /2 of the expansion angle ⁇ .
- w( ⁇ )/a ⁇ is about 1.46 when the expansion angle ⁇ is ⁇ /2, but w( ⁇ )/a ⁇ when the expansion angle ⁇ is 3 ⁇ /2. Is about 1.39, which is small.
- w( ⁇ )/a ⁇ is large, it means that the spiral body has a large wall thickness. Therefore, when the extension arm length w( ⁇ ) changes as shown in FIG. The thickness of the spiral body is reduced at each expansion angle ⁇ from the beginning to the end of winding. The effects obtained by this configuration will be described below.
- the pressure difference between the compression chambers 71 formed in the compression mechanism portion 8 becomes larger in the central portion where the pressure is increased by compressing the refrigerant, that is, in the central portion of the spiral body. That is, the pressure difference between the compression chambers 71 is larger at the winding start portion of the spiral body than at the winding end portion. Therefore, when designing the wall thickness of the spiral body, it is necessary to design the wall thickness to withstand the pressure difference generated at the central portion of the spiral body.
- the wall thickness of the spiral body is constant from the start of winding to the end of winding so as to withstand the pressure difference generated at the center of the spiral body, the end of winding with a small pressure difference between the compression chambers 71 In the vicinity of the part, the strength is overdesigned. That is, since the thickness of the spiral body is formed to be thicker than necessary, the volume of the compression chamber 71 at the time of completion of suction, that is, the suction volume is unnecessarily reduced.
- the reduction ratio of the wall thickness from the winding start portion to the winding end portion can be arbitrarily set.
- ⁇ the wall thickness of the strength required at the beginning of winding can be reduced while the wall thickness at the end of winding is reduced, and
- the reduction ratio of the wall thickness increases. Therefore, when the pressure difference between the compression chambers 71 in the central portion of the spiral body is large, the value of ⁇ is increased. However, when the pressure difference between the compression chambers 71 at the center of the spiral body is small, the value of ⁇ may be reduced.
- the same effect as that of the first embodiment is obtained, and by changing the value of ⁇ , the reduction ratio of the wall thickness of the spiral body is arbitrarily set. It becomes possible.
- the third embodiment it is possible to define a specific mathematical expression capable of arbitrarily setting the flatness ratio of the contour of the spiral body and the reduction ratio of the wall thickness, and to define the spiral body on the base plate.
- the degree of freedom in designing the spiral shape can be improved.
- the flatness of the contour of the spiral body is set according to the shape of the base plate, and ⁇ is set according to the specifications and operating conditions of the compressor, thereby optimizing the contour of the spiral body. It is possible to increase the suction volume while improving the packaging density. This makes it possible to improve the compression function without increasing the size of the compressor. Alternatively, it is possible to reduce the size of the compressor with the same compression function.
- FIG. 9 is a diagram showing a spiral shape of a spiral body in the scroll compressor according to the fourth embodiment of the present invention.
- 9A to 9D are, in order, the functional formula of the extension arm length w( ⁇ ), the formula (3) shown in the first embodiment, and the following formulas (4) to The shapes of the fixed spiral body 1b and the swinging spiral body 2b in the case of (6) are described.
- FIG. 10: is a figure which shows the characteristic of the extension arm length w ((theta)) which specifies the spiral shape of the spiral body in the scroll compressor which concerns on Embodiment 4 of this invention.
- FIGS. 10(a) to 10(d) correspond to FIGS.
- the vertical axis of FIG. 10 represents the ratio of w( ⁇ ) to the product of the basic circle radius a and the expansion angle ⁇ .
- the horizontal axis of FIG. 10 indicates the extension angle ⁇ [rad]. Further, in FIGS. 9 and 10, the value of ⁇ is 0.1, the value of ⁇ is 0, and the value of N is 1.
- the contours of the fixed spiral body 1b and the swing spiral body 2b can be arbitrarily set by changing the functional expression of the extension arm length w( ⁇ ).
- Embodiments 1 to 4 the low-pressure shell type scroll compressor in which the closed container 100 is filled with the low-pressure refrigerant has been described.
- the high-pressure shell type scroll compressor in which the closed container 100 is filled with the high-pressure refrigerant is described. Even in the case, the same effect can be obtained.
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Abstract
Description
x=a・cоsθ+w(θ)・sinθ ・・・(1)
y=a・sinθ-w(θ)・cоsθ ・・・(2) A scroll compressor according to the present invention includes a fixed scroll in which a fixed scroll is erected on a fixed base plate and a swing scroll in which a swing scroll is set up on a swing base plate. In a scroll compressor that compresses refrigerant in a compression chamber formed by meshing with an oscillating scroll, one of the outer curve and the inner curve of each of the fixed scroll and the oscillating scroll is used to extend the base circle. A curve that is an open line and is defined by the formula (1) and the formula (2) using the expansion angle θ and the basic circle radius a in the x and y coordinate systems, and the formula (1) and the formula ( 2) The length w(θ) of the extended arm is a function that increases while changing in a sine wave or cosine wave with π[rad] as one cycle with respect to the angle of extension θ.
x=a·cos θ+w(θ)·sin θ (1)
y=a·sin θ−w(θ)·cos θ (2)
x=a・cоsθ+w(θ)・sinθ ・・・(1)
y=a・sinθ-w(θ)・cоsθ ・・・(2) According to the present invention, the spiral shape of the spiral body is defined by the formulas (1) and (2) using the expansion angle θ and the basic circle radius a in the x and y coordinate systems, and also the formulas (1) and The extension arm length w(θ) in Expression (2) is a function that increases while changing in a sine wave shape or a cosine wave shape with π [rad] as one cycle with respect to the extension angle θ. Accordingly, the spiral shape of the spiral body having a flat contour can be defined by an equation.
x=a·cos θ+w(θ)·sin θ (1)
y=a·sin θ-w(θ)·cos θ (2)
図1は、本発明の実施の形態1に係るスクロール圧縮機の全体構成の概略縦断面図である。
実施の形態1のスクロール圧縮機は、圧縮機構部8と、圧縮機構部8を回転軸6を介して駆動する電動機構部110と、その他の構成部品とを有し、これらが外郭を構成する密閉容器100の内部に収納された構成を有する。
FIG. 1 is a schematic vertical cross-sectional view of the overall configuration of a scroll compressor according to
The scroll compressor according to the first embodiment includes a
図2は、本発明の実施の形態1に係るスクロール圧縮機の圧縮機構部の横断面図である。図3は、本発明の実施の形態1に係るスクロール圧縮機の圧縮機構部の固定渦巻体と揺動渦巻体とを示した平面図である。なお、図2および図3では、固定スクロール1の固定渦巻体1bと揺動スクロール2の揺動渦巻体2bとの区別を容易にするため、揺動スクロール2の揺動渦巻体2bにハッチングを施してある。後述の図においても同様である。 Next, the component arrangement of the
FIG. 2 is a cross-sectional view of the compression mechanism portion of the scroll compressor according to the first embodiment of the present invention. FIG. 3 is a plan view showing a fixed spiral body and an oscillating spiral body of the compression mechanism portion of the scroll compressor according to
実施の形態2では、上記式(3)におけるαの値に応じた、渦巻体の輪郭の扁平率の変化について説明する。以下、実施の形態2が実施の形態1と異なる構成を中心に説明するものとし、実施の形態2で説明されない構成は実施の形態1と同様である。
In the second embodiment, a change in flatness of the contour of the spiral body according to the value of α in the above formula (3) will be described. Hereinafter, the second embodiment will be described focusing on the configuration different from that of the first embodiment, and the configuration not described in the second embodiment is the same as that of the first embodiment.
実施の形態3では、上記式(3)においてβの値に応じた、渦巻体の肉厚の縮小率の変化について説明する。以下、実施の形態3が実施の形態1と異なる構成を中心に説明するものとし、実施の形態3で説明されない構成は実施の形態1と同様である。 Embodiment 3.
In the third embodiment, the change in the reduction ratio of the wall thickness of the spiral body according to the value of β in the above formula (3) will be described. Hereinafter, the third embodiment will be described focusing on the configuration different from the first embodiment, and the configuration not described in the third embodiment is the same as that of the first embodiment.
実施の形態4では、伸開腕長さw(θ)の特性に応じた渦巻形状の変化について説明する。以下、実施の形態4が実施の形態1と異なる構成を中心に説明するものとし、実施の形態4で説明されない構成は実施の形態1と同様である。 Fourth Embodiment
In the fourth embodiment, a change in the spiral shape according to the characteristic of the extension arm length w(θ) will be described. Hereinafter, the configuration in which the fourth embodiment is different from the configuration in the first embodiment will be mainly described, and the configuration not described in the fourth embodiment is the same as that in the first embodiment.
Claims (8)
- 固定台板に固定渦巻体が立設された固定スクロールと、揺動台板に揺動渦巻体が立設された揺動スクロールとを備え、前記固定渦巻体と前記揺動渦巻体とが噛み合うことで形成される圧縮室内で冷媒を圧縮するスクロール圧縮機において、
前記固定渦巻体および前記揺動渦巻体のそれぞれの外側曲線および内側曲線のいずれか一方を、基礎円の伸開線である曲線であって、x、y座標系において伸開角θおよび基礎円半径aを用いて式(1)および式(2)で定義される曲線とし、前記式(1)および前記式(2)における伸開腕長さw(θ)を、伸開角θに対してπ[rad]を1周期とした正弦波状または余弦波状に変化しながら増加する関数としたスクロール圧縮機。
One of the outer curve and the inner curve of each of the fixed spiral body and the oscillating spiral body is a curve that is an expansion line of a basic circle, and an expansion angle θ and a basic circle in an x, y coordinate system. A curve defined by the formula (1) and the formula (2) using the radius a, and the extension arm length w(θ) in the formula (1) and the formula (2) with respect to the extension angle θ. A scroll compressor having a function of increasing while changing in a sine wave shape or a cosine wave shape with π [rad] as one cycle.
- 係数βを0以上とした請求項2~請求項5のいずれか一項に記載のスクロール圧縮機。 The scroll compressor according to any one of claims 2 to 5, wherein the coefficient β is 0 or more.
- 前記式(1)および前記式(2)で定義された曲線が前記外側曲線であるとき、前記固定渦巻体および前記揺動渦巻体のそれぞれの前記内側曲線は、前記外側曲線を前記基礎円の中心を基準としてπ[rad]回転させた曲線上に中心を有する、半径が前記揺動スクロールの揺動半径と等しい円群の外側包絡線であり、
前記式(1)および前記式(2)で定義された曲線が前記内側曲線であるとき、前記固定渦巻体および前記揺動渦巻体のそれぞれの前記外側曲線は、前記内側曲線を前記基礎円の中心を基準としてπ[rad]回転させた曲線上に中心を有する、半径が前記揺動スクロールの揺動半径と等しい円群の内側包絡線とする請求項1~請求項6のいずれか一項に記載のスクロール圧縮機。 When the curves defined by the formula (1) and the formula (2) are the outer curves, the inner curves of the fixed spiral body and the oscillating spiral body respectively correspond to the outer curve of the basic circle. An outer envelope of a group of circles having a radius equal to the swing radius of the orbiting scroll and having a center on a curve rotated by π [rad] with respect to the center,
When the curves defined by the formula (1) and the formula (2) are the inner curves, the outer curves of the fixed spiral body and the oscillating spiral body respectively correspond to the inner curve of the basic circle. 7. The inner envelope of a group of circles having a radius equal to the swing radius of the orbiting scroll and having a center on a curve rotated by π [rad] with the center as a reference. Scroll compressor described in. - 前記揺動台板は、外形形状が扁平形状である請求項1~請求項7のいずれか一項に記載のスクロール圧縮機。 The scroll compressor according to any one of claims 1 to 7, wherein the swing base plate has a flat outer shape.
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Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05223071A (en) * | 1991-12-20 | 1993-08-31 | Hitachi Ltd | Scroll type fluid machine, scroll member and method for working the same |
JPH0849670A (en) * | 1994-08-05 | 1996-02-20 | Toyota Autom Loom Works Ltd | Scroll type compressor |
JP2017089491A (en) * | 2015-11-10 | 2017-05-25 | 三菱重工オートモーティブサーマルシステムズ株式会社 | Scroll Type Fluid Machine |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57186085A (en) * | 1981-05-12 | 1982-11-16 | Nippon Soken Inc | Scroll type compressor |
JPS5990789A (en) * | 1982-11-16 | 1984-05-25 | Nippon Soken Inc | Scroll pump |
JPH0612044B2 (en) * | 1985-10-14 | 1994-02-16 | 三菱重工業株式会社 | Rotary fluid machinery |
JP3360303B2 (en) * | 1991-09-13 | 2002-12-24 | ダイキン工業株式会社 | Scroll type fluid machine |
JP4007271B2 (en) * | 1991-12-20 | 2007-11-14 | 株式会社日立製作所 | Scroll type fluid machinery |
JPH05288169A (en) * | 1992-04-09 | 1993-11-02 | Hitachi Ltd | Scroll compressor |
JP2910457B2 (en) * | 1992-09-11 | 1999-06-23 | 株式会社日立製作所 | Scroll fluid machine |
JPH06159269A (en) * | 1992-11-18 | 1994-06-07 | Hitachi Ltd | Scroll compressor |
JP3194076B2 (en) * | 1995-12-13 | 2001-07-30 | 株式会社日立製作所 | Scroll type fluid machine |
JP3690881B2 (en) * | 1996-08-12 | 2005-08-31 | 株式会社日本自動車部品総合研究所 | Scroll compressor |
CN2397283Y (en) * | 1999-09-30 | 2000-09-20 | 钱永贵 | High efficient static vortex dish for vortex compressor |
JP3599005B2 (en) * | 2001-07-30 | 2004-12-08 | 株式会社日立製作所 | Scroll fluid machine |
-
2019
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Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05223071A (en) * | 1991-12-20 | 1993-08-31 | Hitachi Ltd | Scroll type fluid machine, scroll member and method for working the same |
JPH0849670A (en) * | 1994-08-05 | 1996-02-20 | Toyota Autom Loom Works Ltd | Scroll type compressor |
JP2017089491A (en) * | 2015-11-10 | 2017-05-25 | 三菱重工オートモーティブサーマルシステムズ株式会社 | Scroll Type Fluid Machine |
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