WO2023181727A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2023181727A1
WO2023181727A1 PCT/JP2023/005393 JP2023005393W WO2023181727A1 WO 2023181727 A1 WO2023181727 A1 WO 2023181727A1 JP 2023005393 W JP2023005393 W JP 2023005393W WO 2023181727 A1 WO2023181727 A1 WO 2023181727A1
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WO
WIPO (PCT)
Prior art keywords
pin
thrust
distance
thrust plate
axis
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Application number
PCT/JP2023/005393
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English (en)
Japanese (ja)
Inventor
淳夫 手島
泰造 佐藤
拓樹 増山
Original Assignee
サンデン株式会社
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Publication date
Application filed by サンデン株式会社 filed Critical サンデン株式会社
Publication of WO2023181727A1 publication Critical patent/WO2023181727A1/fr

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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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00

Definitions

  • the present invention relates to a scroll compressor.
  • Scroll compressors have been known that compress gas in a compression chamber formed by the fixed scroll and the orbiting scroll by rotating the orbiting scroll around the axis of a rotating shaft with respect to a fixed scroll fixed to a housing.
  • Scroll compressors are generally used in air conditioners such as refrigerators and car air conditioners, and are driven by a motor housed in a housing.
  • the housing of the scroll compressor is formed with a gas intake port and a gas discharge port. Gas is drawn into the housing through the suction port, introduced into a compression chamber disposed near the discharge port, compressed in the compression chamber, and then discharged from the discharge port to the outside of the housing.
  • the amount of thermal expansion increases after the compressor starts operating. However, if there is a difference in the amount of thermal expansion between the components, for example, components that should not be in contact with each other may come into contact with each other, causing phenomena such as moving parts getting stuck. This may occur and may impede the operation of the scroll compressor.
  • the present invention provides a scroll compressor that can operate stably without being affected by differences in thermal expansion between component parts.
  • a scroll compressor includes a suction side space in which gas is guided, a compression space in which the gas passing through the suction side space is compressed, and the compressed gas is discharged from the compression space.
  • a housing having a discharge side space formed therein, a rotating shaft rotatably arranged around an axis in the suction side space, and a rotary shaft provided in the suction side space of the housing so that the rotating shaft can be rotated.
  • a bearing supported on the rotating shaft, and provided on the rotating shaft such that the bearing is disposed on the side of the compression space with respect to a position where the bearing supports the rotating shaft, and revolves around the axis as the rotating shaft rotates.
  • an orbiting scroll and a compression chamber that is fixed to the housing from the discharge side space in the housing toward the compression space in a posture facing the orbiting scroll, and compresses the gas in a gap between the orbiting scroll and the orbiting scroll.
  • a fixed scroll formed in the space; and a fixed scroll provided integrally with or separate from the housing and fixed in the suction side space, and with respect to the vicinity of the periphery of the orbiting scroll, A thrust receiving portion facing each other with a thrust gap serving as a gap left therebetween, and an annular plate member disposed in the thrust gap with the rotating shaft inserted therein, the plate member facing toward the discharge side space.
  • a pin arrangement hole having an inner diameter larger than an outer diameter and into which the positioning pin is loosely fitted is provided so that the thrust plate can move relative to the thrust receiver in the direction of the axis, and
  • the distance between the pin center of the positioning pin and the axis is defined as d1
  • the distance between the pin placement hole center of the pin placement hole and the axis is defined as d2.
  • a plurality of the positioning pins and the pin arrangement holes are arranged at intervals in the circumferential direction of the rotating shaft, and the distance d1 is the same between the plurality of positioning pins. , the distance d2 may be the same between the plurality of pin arrangement holes.
  • the one of the thrust receiving portion and the thrust plate is provided with a pin fitting hole into which the positioning pin is fitted so as to be immovable relative to the one;
  • the positioning pin is fixed when the distance between the center of the pin fitting hole and the axis is defined as d3 when the thrust receiving part and the thrust plate are at room temperature and under the same temperature environment.
  • d3 ⁇ d2 may be satisfied
  • d3>d2 may be satisfied.
  • a scroll compressor includes a suction side space in which gas is guided, a compression space in which the gas is compressed via the suction side space, and a compressed gas that is compressed from the compression space.
  • a housing having a discharge side space formed therein, a rotating shaft disposed in the suction side space so as to be rotatable about an axis, and a rotary shaft provided in the suction side space of the housing to rotate the rotating shaft.
  • a bearing that can support the rotating shaft; and a bearing that is provided on the rotating shaft so as to be disposed on the side of the compression space with respect to a position where the bearing supports the rotating shaft, and that revolves around the axis as the rotating shaft rotates.
  • an orbiting scroll that is fixed to the housing in a position facing the orbiting scroll from the discharge side space in the housing toward the compression space, and a compression chamber that compresses the gas is provided in a gap between the orbiting scroll and the orbiting scroll; a fixed scroll formed in the compression space; and a fixed scroll provided integrally with or separate from the housing and fixed in the suction side space, and arranged in the direction of the axis with respect to the vicinity of the periphery of the orbiting scroll.
  • a thrust receiving portion facing each other with a thrust gap therebetween, and an annular plate member disposed in the thrust gap with the rotating shaft inserted therein, the plate member having a side facing toward the discharge side space; a thrust plate whose discharge side surface faces the orbiting scroll and whose suction side surface faces the suction side space faces the thrust receiver; and one of the thrust receiver and the thrust plate.
  • a positioning pin that is integrally or separately provided and fixed to one of the two and extends toward the other, the other of the thrust receiving portion and the thrust plate having the positioning pin; has an inner diameter larger than an outer diameter, and the positioning pin is loosely fitted so that the thrust plate can move relative to the thrust receiver in the direction of the axis, and is smaller than the circumferential direction of the rotating shaft.
  • a long elongated pin placement hole is provided in the radial direction of the rotating shaft, and the contact range of the positioning pin with the pin placement hole when the thrust receiving portion and the thrust plate are at room temperature and in the same temperature environment is provided.
  • the distance between the outermost part of the pin, which is the outermost part in the radial direction of the rotating shaft, and the axis is defined as d4, and the outermost part in the radial direction in the contact range with the positioning pin of the pin arrangement hole.
  • the positioning pin is fixed. If the one of the thrust receiving parts is the thrust receiving part, d6>d7 is satisfied.
  • the distance d6 and the distance d7 satisfy d6>d7
  • the one to which the positioning pin is fixed is the thrust plate.
  • the distance d4 and the distance d5 may satisfy d4 ⁇ d5.
  • a plurality of the positioning pins and the pin arrangement holes are respectively arranged at intervals in the circumferential direction of the rotating shaft, and when the one to which the positioning pin is fixed is the thrust plate.
  • the distance d4 is the same between the plurality of positioning pins
  • the distance d5 is the same between the plurality of pin arrangement holes
  • the one to which the positioning pin is fixed is the same as the one of the positioning pins.
  • the distance d6 may be the same between the plurality of positioning pins
  • the distance d7 may be the same between the plurality of pin arrangement holes.
  • the one of the thrust receiving portion and the thrust plate is provided with a pin fitting hole into which the positioning pin is fitted so as to be immovable relative to the one;
  • the distance between the outermost part of the pin fitting hole, which is the outermost part of the pin fitting hole in the radial direction, and the axis is d8.
  • the coefficient of linear expansion of the material of the thrust plate may be 0.75 times or more greater than the coefficient of linear expansion of the material of the thrust receiving portion.
  • the scroll compressor may further include a biasing member that is provided between the suction side surface of the thrust plate and the thrust receiving portion, and biases the thrust plate toward the orbiting scroll.
  • the biasing member may be an annular rubber seal ring through which the rotating shaft is inserted.
  • FIG. 1 is a longitudinal cross-sectional view of a scroll compressor according to a first embodiment of the present invention. It is a top view of the thrust receiving part in the scroll compressor based on the said 1st embodiment. It is a top view of the thrust plate in the scroll compressor concerning the said first embodiment.
  • FIG. 3 is a cross-sectional view including the axis of the thrust plate and the thrust receiver in the scroll compressor according to the first embodiment, in which (a) shows the state at normal temperature, and (b) shows the start of operation of the scroll compressor. Indicates the medium condition (conditions where the temperature is higher than normal temperature).
  • FIG. 2 is an enlarged view of a main part showing the positional relationship between a positioning pin and a pin arrangement hole in the scroll compressor according to the first embodiment.
  • FIG. 3 is a cross-sectional view including the axis of the thrust plate and the thrust receiver in a scroll compressor according to a modification of the first embodiment, in which (a) shows the state at room temperature, and (b) shows the scroll compressor. Indicates the state during the start of operation. It is a top view of the thrust receiving part in the scroll compressor based on 2nd embodiment of this invention.
  • FIG. 4 is a sectional view including the axis of the thrust plate and the thrust receiver in the scroll compressor according to the second embodiment, in which (a) shows the state at normal temperature, and (b) shows the start of operation of the scroll compressor. Indicates the state inside. It is a top view of the thrust plate in the scroll compressor based on the modification of the said second embodiment.
  • FIG. 4 is a cross-sectional view including the axis of the thrust plate and the thrust receiver in a scroll compressor according to a modification of the second embodiment, in which (a) shows the state at room temperature, and (b) shows the scroll compressor. Indicates the state during the start of operation.
  • the scroll compressor 100 is a compressor suitably used, for example, when compressing refrigerant gas (hereinafter simply referred to as gas) in a heat pump type air conditioner, refrigerator, or the like.
  • gas refrigerant gas
  • the scroll compressor 100 includes a housing 1, a rotating shaft 2 provided in the housing 1, a bearing 3, an orbiting scroll 4, a fixed scroll 5, a thrust receiving part 6, and a thrust plate 7. , and a positioning pin 8.
  • the rotating shaft 2 has a cylindrical shape centered on the axis O. At one end of the rotating shaft 2 in the direction of the axis O, there is an eccentric axis O1 centered at a position shifted in the radial direction of the rotating shaft 2 (hereinafter referred to as the shaft radial direction) with respect to the axis O. As such, an eccentric shaft portion 2a formed in a cylindrical shape is provided. An orbiting scroll 4, which will be described later, is provided on the eccentric shaft portion 2a.
  • the housing 1 defines an internal space through which gas flows.
  • This internal space includes a suction side space A1 in which gas is guided toward one side in the direction of the axis O, a compression space A2 in which the gas that has passed through the suction side space A1 is compressed, and a compression space in which the compressed gas is A discharge side space A3 flowing from A2 is formed in this order toward one side in the direction of the axis O. Therefore, the housing 1 is formed with an inlet 1a that communicates with the inlet space A1 at a position on the other side in the direction of the axis O and for inhaling gas from the outside of the housing 1.
  • a discharge port 1b for discharging gas to the outside of the housing 1 through the discharge side space A3 is formed at a position on one side in the direction of.
  • a compression chamber C which will be described later, is arranged in the compression space A2.
  • an electric motor M serving as a drive device is provided in the suction side space A1 of the housing 1.
  • a rotating shaft 2 is connected to the electric motor M, and the rotating shaft 2 is rotated by the electric motor M. Gas sucked into the suction side space A1 from the suction port 1a passes around the electric motor M and heads toward the compression space A2.
  • the housing 1 is further provided with an inverter In on the other side in the direction of the axis O with respect to the suction side space A1.
  • the bearing 3 is provided in the suction side space A1 of the housing 1 and rotatably supports the rotating shaft. More specifically, in this embodiment, the bearings 3 include a first bearing 3a provided on the other side of the axis O with respect to the electric motor M, and a first bearing 3a provided on the other side of the axis O with respect to the electric motor M. A second bearing 3b provided with a position is provided.
  • the orbiting scroll 4 is disposed on the compression space A2 side with respect to the position where the second bearing 3b supports the rotation shaft 2, that is, between the suction side space A1 and the compression space A2, and is arranged on the eccentric shaft portion of the rotation shaft 2. 2a.
  • the orbiting scroll 4 includes an orbiting side bottom plate 4a having a disk shape, and an orbiting side wrap 4b protruding from the orbiting side bottom plate 4a toward the compression space A2.
  • the orbiting scroll 4 is configured to revolve around the axis O as the rotating shaft 2 rotates.
  • the orbiting scroll 4 is configured to revolve around the axis O while its rotation is suppressed by the rotation prevention mechanism.
  • This rotation prevention mechanism is constituted by, for example, a rotation prevention pin 10 extending from a thrust plate 7, which will be described later.
  • the fixed scroll 5 is arranged facing the orbiting scroll 4 from the discharge side space A3 toward the compression space A2 in the housing 1, and is fixed to the housing 1.
  • the fixed scroll 5 has a disk-shaped fixed bottom plate 5a centered on the axis O, and a fixed wrap 5b protruding from the fixed bottom plate 5a toward the compression space A2.
  • the fixed side wrap 5b meshes with the rotating side wrap 4b of the orbiting scroll 4, and is a region sandwiched between the rotating side bottom plate 4a and the fixed side bottom plate 5a, and a compression chamber for compressing gas is provided in the gap between the wraps 4b and 5b. It forms C.
  • This compression chamber C is arranged in the compression space A2 of the housing 1.
  • a discharge port P1 communicating with the discharge port 1b of the housing 1 is formed in the fixed side bottom plate 5a. Between the fixed side bottom plate 5a of the fixed scroll 5 and the discharge port 1b of the housing 1, the discharge port P1 and the discharge port 1b are communicated with each other in the discharge side space A3 of the housing 1, and the gas compressed in the compression chamber C is provided. A discharge chamber C1 is formed into which the gas flows. Further, a suction port (not shown) for sucking gas into the compression chamber C is formed in the fixed side bottom plate 5a.
  • the thrust receiving part 6 is provided separately from the housing 1 and fixed in the suction side space A1, and is arranged in the direction of the axis O with respect to the vicinity of the circumferential edge of the orbiting scroll 4 (near the outer edge in the circumferential direction). They face each other with a thrust gap.
  • the thrust receiving portion 6 is formed of an alloy such as ADC12, and the linear expansion coefficient of the material of the thrust receiving portion 6 is 21 ⁇ 10 ⁇ 6 /°C.
  • the thrust receiving part 6 has a plate shape, is arranged on the compression space A2 side with respect to the electric motor M in the suction side space A1, and has the rotating shaft 2 inserted therethrough, and is called a center plate.
  • the thrust receiving portion 6 includes a first annular recess 11 having an annular shape centered on the axis O that is recessed in the direction of the axis O from the side of the compression space A2 toward the electric motor M, and an electric motor from the bottom of the first annular recess 11.
  • a second annular recess 12 having an annular shape centered on the axis O extending toward the motor M is formed.
  • the inner diameter of the second annular recess 12 is smaller than the inner diameter of the first annular recess 11, and the second bearing 3b is disposed in the second annular recess 12.
  • the bottom surface of the first annular recess 11 is a discharge side facing surface 11a facing the discharge side space A3, and the inner surface (the surface facing inward in the axial radial direction) of the first annular recess 11 is radially opposed. This is the surface 11b.
  • the discharge side facing surface 11a and the radial direction facing surface 11b face the outer surface of the thrust plate 7, which will be described in detail later.
  • the thrust receiving portion 6 partitions the suction side space A1 of the housing 1 in the direction of the axis O.
  • the suction side space A1 in the suction pressure region X1 on the electric motor M side, which is the other side of the thrust receiving part 6 in the direction of the axis O, the pressure of the gas (suction pressure )
  • the thrust receiving portion 6 is exposed to gas at a pressure and temperature equivalent to that of Note that the gas temperature in the suction pressure region X1 is approximately ⁇ 40° C. to 50° C. while the scroll compressor 100 is operating.
  • the back pressure area Y1 on the side of the orbiting scroll 4, which is on one side of the thrust receiving part 6 in the direction of the axis O, is arranged inside the fixed side bottom plate 5a of the fixed scroll 5.
  • the thrust receiving portion 6 is exposed to gas having a higher pressure and higher temperature than the suction pressure region X1.
  • the gas temperature in the back pressure region Y1 is approximately ⁇ 40° C. to 100° C. while the scroll compressor 100 is operating.
  • the thrust receiving portion 6 has a plurality of (mains) spaced apart from each other in the circumferential direction of the rotating shaft 2 (hereinafter referred to as the axial circumferential direction) on the discharge side facing surface 11a which is the bottom surface of the first annular recess 11.
  • the axial circumferential direction the discharge side facing surface 11a which is the bottom surface of the first annular recess 11.
  • two pin placement holes 6x are provided.
  • each pin arrangement hole 6x has a perfect circular shape, and is formed so as to be recessed from the discharge side facing surface 11a of the first annular recess 11 toward the suction pressure region X1 in the direction of the axis O. (See Figure 1).
  • the distance between the pin arrangement hole center Oh and the axis O is defined as d2
  • the distance d2 at each pin arrangement hole 6x are identical to each other.
  • a range of -40° C. to 50° C. is defined as the normal temperature. Therefore, the above-mentioned "at room temperature and under the same temperature environment” means conditions where the temperature is the same in the range of -40°C to 50°C.
  • the pin arrangement hole centers Oh are arranged at positions 180 degrees apart in the axial circumferential direction. The inner diameter of the pin arrangement hole 6x is larger than the outer diameter of the positioning pin 8, which will be described in detail later.
  • the thrust plate 7 is disposed within the first annular recess 11 of the thrust receiving portion 6 in the back pressure region Y1 of the suction side space A1 of the housing 1, and the rotating shaft 2 is inserted therethrough. That is, the thrust plate 7 is an annular plate member disposed in the thrust gap between the thrust receiving portion 6 and the orbiting scroll 4.
  • a discharge side surface 7a of the thrust plate 7 facing the discharge side space A3 (compression space A2 side) faces the orbiting side bottom plate 4a of the orbiting scroll 4, and a suction side surface 7b facing the suction side space A1. is opposed to the discharge side facing surface 11a of the thrust receiving portion 6.
  • the outer circumferential surface 7c of the thrust plate 7 facing outward in the axial radial direction faces the radially opposing surface 11b of the thrust receiving portion 6.
  • a gap is always formed between the outer circumferential surface 7c of the thrust plate 7 and the radially opposing surface 11b of the thrust receiving portion 6, thereby allowing the diameter of the thrust plate 7 to expand due to thermal expansion. ing.
  • the entire thrust plate 7 is disposed in the back pressure region Y1, and when the scroll compressor 100 is in operation, the entire thrust plate 7 is exposed to gas at a higher pressure and higher temperature than in the suction pressure region X1.
  • the thrust plate 7 is made of an alloy such as AC4CH, and the linear expansion coefficient of the material of the thrust plate 7 is 21.5 ⁇ 10 ⁇ 6 /°C. From the ratio of the maximum linear expansion coefficient of 24 ⁇ 10 -6 /°C and the minimum linear expansion coefficient of 18 ⁇ 10 -6 /°C for the material of the thrust receiving part 6 and the material of the thrust plate 7, the material of the thrust receiving part 6 is determined. The coefficient of linear expansion of the material of the thrust plate 7 is 0.75 to 1.33 times the coefficient of linear expansion of the material of the thrust plate 7.
  • the thrust plate 7 is provided with a plurality of (two in this embodiment) pin fitting holes 7y at intervals in the axial direction.
  • the pin fitting hole 7y has a perfect circular shape and passes through the thrust plate 7 in the direction of the axis O.
  • the thrust receiving part 6 and the thrust plate 7 are at room temperature (-40°C to 50°C) and under the same temperature environment, and the distance between the pin fitting hole center Ok and the axis O is defined as d3, each The distances d3 in the pin fitting holes 7y are the same.
  • the pin fitting hole centers Ok are located 180 degrees apart in the axial direction, and are formed at positions corresponding to the pin arrangement holes 6x described above.
  • the inner diameter of the pin fitting hole 7y is formed to be equal to or slightly smaller than the outer diameter of a positioning pin 8, which will be described later.
  • the inner diameter of the pin fitting hole 7y and the outer diameter of the positioning pin 8 are approximately the same size.
  • the thrust plate 7 is provided with a plurality of rotation-preventing pin holes 7z spaced apart in the circumferential direction of the shaft at positions radially inside the pin fitting hole 7y.
  • the rotation prevention pins 10 rotation prevention mechanism, see FIG. 1
  • the rotation prevention pins 10 described above are inserted into these rotation prevention pin holes 7z.
  • the positioning pin 8 has a perfect circular cross section, is provided separately from the thrust plate 7 and is fixed to the thrust plate 7, and is directed toward the suction pressure region X1 in the direction of the axis O. , that is, it extends toward the thrust receiving portion 6. More specifically, as shown in FIGS. 4(a) and 4(b), the positioning pin 8 is fitted into the pin fitting hole 7y so that it cannot move relative to the thrust plate 7, and the positioning pin The pin center Op of No. 8 is approximately aligned with the pin fitting hole center Ok. Therefore, a plurality of positioning pins 8 (two in this embodiment) are provided at intervals in the axial circumferential direction.
  • each The distances d1 of the positioning pins 8 are the same.
  • the respective pin centers Op are provided at positions separated by 180 degrees in the axial circumferential direction.
  • the distance d1 between the pin center Op of the positioning pin 8 and the axis O, and the distance d2 between the pin arrangement hole center Oh of the pin arrangement hole 6x and the axis O satisfy d1 ⁇ d2. Further, the distance d1 and the distance d3 between the pin fitting hole center Ok and the axis O in the pin fitting hole 7y satisfy d3 ⁇ d2.
  • the inner diameter of the pin arrangement hole 6x is formed larger than the outer diameter of the positioning pin 8, so that the thrust plate 7 can move relative to the thrust receiving part 6 in the direction of the axis O.
  • the positioning pin 8 is loosely fitted into the pin arrangement hole 6x.
  • 1/2 of the difference between the outer diameter of the positioning pin 8 and the inner diameter of the pin arrangement hole 6x along the axial radial direction was defined as the pin gap s, and the absolute value of the difference between the distance d1 and the distance d2 was defined as ⁇ d.
  • s> ⁇ d is satisfied.
  • the pin gap s is, for example, about 10 [ ⁇ m] to 20 [ ⁇ m], preferably 15 [ ⁇ m].
  • biasing member Between the suction side surface 7b of the thrust plate 7 and the discharge side facing surface 11a of the thrust receiving part 6, there is provided a biasing force that urges the thrust plate 7 toward the orbiting side bottom plate 4a of the orbiting scroll for the purpose of improving compression efficiency.
  • a force member 9 is provided.
  • the biasing member 9 is a seal ring formed of an elastically deformable material such as rubber and having an annular shape centered on the axis O.
  • the thrust plate 7 is arranged in the back pressure region Y1, and during the operation of the scroll compressor 100, the thrust plate 7 is smaller than the thrust receiving part 6. You will be exposed to hot gas. Therefore, the thrust plate 7 expands in diameter in the axial direction, and thermally expands relatively to the thrust receiving part 6.
  • the thrust plate 7 is movable relative to the thrust receiver 6 in the direction of the axis O.
  • the thrust plate 7 will stick to the thrust receiving part 6 and the thrust
  • the plate 7 cannot move in the direction of the axis O.
  • the thrust plate 7 becomes stuck with the thrust plate 7 pressing the orbiting scroll 4 more than necessary, abnormal contact will occur between the orbiting scroll 4 and the fixed scroll 5, and the operation of the compressor will be affected. It is possible that problems may occur.
  • the distance d1 between the pin center Op of the positioning pin 8 and the axis O, and the distance d2 between the pin arrangement hole center Oh and the axis O of the pin arrangement hole 6x satisfy d1 ⁇ d2
  • the distance d1 and the distance d3 between the pin fitting hole center Ok and the axis O in the pin fitting hole 7y satisfy d3 ⁇ d2.
  • the thrust plate 7 and the thrust receiving part 6 since the absolute value of the difference between the distance d1 and the distance d2, ⁇ d, and the pin gap s satisfy s> ⁇ d, when assembling the thrust plate 7 and the thrust receiving part 6, the thrust plate The positioning pin 8 fitted into the pin 7 can be smoothly inserted into the pin arrangement hole 6x without coming into contact with the inner surface of the pin arrangement hole 6x. Therefore, the work when assembling the component parts can be facilitated.
  • a plurality of positioning pins 8 and pin arrangement holes 6x are provided at intervals in the axial direction, the distance d1 is the same between the plurality of positioning pins 8, and the distance d2 is the same between the plurality of pin arrangement holes. It is the same between 6x. Therefore, the thrust plate 7 is reliably positioned by the plurality of positioning pins 8, and when the thrust plate 7 thermally expands, each positioning pin 8 moves without contacting each pin arrangement hole 6x, and the thrust plate Even if a difference in thermal expansion occurs between the thrust plate 7 and the thrust receiving part 6, stacking of the thrust plate 7 can be reliably avoided.
  • the thrust plate 7 since the coefficient of linear expansion of the material of the thrust plate 7 is 0.75 times or more that of the material of the thrust receiving part 6, under the operating conditions of the general scroll compressor 100, the thrust The amount of thermal expansion of the plate 7 is larger than that of the thrust receiving portion 6, and by satisfying d1 ⁇ d2 and d3 ⁇ d2 as described above, it is possible to avoid stacking of the thrust plate 7.
  • the scroll compressor 100 is operated with the thrust plate 7 always pressing the orbiting scroll 4 toward the fixed scroll 5. .
  • stacking of the thrust plate 7 can be avoided by satisfying d1 ⁇ d2 and d3 ⁇ d2 as described above, and while the urging member 9 is provided to improve compression efficiency, the orbiting scroll 4
  • the biasing member 9 is a seal ring, it is possible to ensure sealing performance and reduce the risk of abnormal contact between the orbiting scroll 4 and the fixed scroll 5.
  • the positioning pin 8 may be fixed to the thrust receiving portion 6 side.
  • the thrust receiving portion 6 is provided with a pin fitting hole 6y
  • the thrust plate 7 is provided with a pin placement hole 7x.
  • the distance d1 between the pin center Op of the positioning pin 8 and the axis O, and the distance d2 between the pin arrangement hole center Oh and the axis O of the pin arrangement hole 7x satisfy d1>d2.
  • the distance d1 and the distance d3 between the pin fitting hole center Ok and the axis O in the pin fitting hole 6y satisfy d3>d2.
  • the cross-sectional shape of the positioning pin 8 does not have to be a perfect circle, as long as it has a shape that can at least define the pin center Op.
  • the cross-sectional shape of the positioning pin 8 may be a regular polygon, a cross, a star, or the like.
  • the pin arrangement holes 6x and 7x are not particularly limited as long as they have a shape that can similarly define the pin arrangement hole center Oh.
  • the scroll compressor 100A of this embodiment differs from the scroll compressor 100 of the first embodiment in that the pin arrangement hole 60x has an elongated hole shape. (Pin placement hole) As shown in FIG. 7, the pin arrangement hole 60x has an oval (including elliptical) shape that is longer in the radial direction than in the circumferential direction.
  • the positioning pin 8 As shown in FIGS. 8(a) and 8(b), when the thrust receiving part 60 and the thrust plate 7 (described later) are at room temperature (-40°C to 50°C) and under the same temperature environment, the positioning pin 8 The distance between the pin outermost part 81, which is the outermost part in the shaft radial direction in the contact range with the pin arrangement hole 60x, and the axis O is defined as d4, and the distance in the contact range with the positioning pin 8 of the pin arrangement hole 60x is defined as d4.
  • the distance d4 at each positioning pin 8 is the same, and each pin arrangement
  • the distances d5 in the holes 60x are also the same. Further, d4 ⁇ d5 is satisfied.
  • the axial radial direction in the contact range with the pin arrangement hole 60x of the positioning pin 8 is
  • the distance between the pin innermost part 82, which is the innermost part, and the axis O is defined as d6
  • the distance between the pin arrangement hole 60x, which is the innermost part in the axial radial direction in the contact range with the positioning pin 8 is defined as d6.
  • the respective pin arrangement holes 60x are arranged at positions 180 degrees apart in the axial direction.
  • the inner diameter of the pin arrangement hole 60x is larger than the outer diameter of the positioning pin 8 at each position in the circumferential direction of the pin arrangement hole 60x, and the positioning pin 8 is loosely fitted into the pin arrangement hole 60x.
  • the minimum gap between the positioning pin 8 and the pin arrangement hole 60x is, for example, about 10 [ ⁇ m] to 20 [ ⁇ m], preferably 15 [ ⁇ m].
  • the positioning pin 8 does not come into contact with the inner surface of the pin placement hole 60x and
  • the outermost portion 81 moves outward in the axial radial direction relative to the outermost pin placement hole portion 61 so that the outermost portion 81 approaches the outermost portion 61 of the pin placement hole.
  • the thrust plate 7 and the thrust receiving portion 6 are assembled.
  • the positioning pin 8 fitted into the thrust plate 7 can be smoothly inserted into the pin arrangement hole 60x without coming into contact with the innermost pin arrangement hole part 62 of the pin arrangement hole 60x. Therefore, the work when assembling the component parts can be facilitated.
  • the pin placement hole 60x is an elongated hole that is long in the radial direction of the shaft, movement of the positioning pin 8 in the circumferential direction of the shaft within the pin placement hole 60x is restricted to some extent, while movement in the radial direction of the shaft is prevented. It is possible to avoid the thrust plate 7 from stacking and to suppress the shaking of the thrust plate 7 in the axial circumferential direction.
  • a plurality of positioning pins 8 and pin arrangement holes 60x are provided at intervals in the axial direction, the distance d4 is the same between the plurality of positioning pins 8, and the distance d5 is the same between the plurality of positioning pins 8. It is the same between 60x. Therefore, the thrust plate 7 is reliably positioned by the plurality of positioning pins 8, and when the thrust plate 7 thermally expands, each positioning pin 8 moves without contacting each pin arrangement hole 60x, and the thrust plate Even if a difference in thermal expansion occurs between the thrust plate 7 and the thrust receiving part 6, stacking of the thrust plate 7 can be reliably avoided.
  • the positioning pin 8 may be fixed to the thrust receiving portion 6 side.
  • a pin arrangement hole 70x is provided in the thrust plate 70, as shown in FIG.
  • a pin fitting hole 6y is provided in the thrust receiving part 6, and the distance d6 between the innermost pin part 82 and the axis O and the innermost part of the pin arrangement hole are 62 and the axis O satisfies d6>d7, and the distance d4 between the outermost pin part 81 and the axis O and the distance d5 between the outermost pin placement hole part 61 and the axis O satisfy d4 ⁇ d5. satisfy.
  • the pin fitting hole 6y is the innermost portion in the axial radial direction.
  • the distance between the innermost hole part 68 and the axis O is defined as d9
  • the distances d9 in each pin fitting hole 6y are the same.
  • the distance d9 and the distance d7 between the innermost portion 62 of the pin arrangement hole and the axis O satisfy d9>d7.
  • the positioning pin 8 does not come into contact with the inner surface of the pin placement hole 70x.
  • the pin innermost portion 82 moves inward in the axial radial direction relative to the pin placement hole innermost portion 62 so as to be close to the pin placement hole innermost portion 72 .
  • the thrust plate 7 can be prevented from becoming stuck.
  • the thrust plate 70 and the thrust receiver 6 are assembled. At this time, it is possible to smoothly insert the positioning pin 8 into the pin arrangement hole 70x without the positioning pin 8 fitted into the thrust receiving part 6 coming into contact with the outermost part 71 of the pin arrangement hole 70x. can.
  • a plurality of positioning pins 8 and pin arrangement holes 70x are provided at intervals in the axial circumferential direction, the distance d6 is the same between the plurality of positioning pins 8, and the distance d7 is the same between the plurality of positioning pins 8. It is the same between 70x. Therefore, the thrust plate 70 is reliably positioned by the plurality of positioning pins 8, and when the thrust plate 70 expands thermally, each positioning pin 8 moves without contacting each pin arrangement hole 70x, and the thrust plate Even if a difference in thermal expansion occurs between the thrust plate 70 and the thrust receiving portion 6, stacking of the thrust plate 7 can be reliably avoided.
  • the pin arrangement holes 60x and 70x do not have to have an elliptical shape, but may have a rectangular shape, for example, and at least in the radial direction of the rotating shaft 2 rather than in the circumferential direction of the rotating shaft 2. It is not particularly limited as long as it has a long shape.
  • the positioning pin 8 may also serve as the rotation prevention mechanism (rotation prevention pin 10) described above. That is, the positioning pin 8 may pass through the thrust plates 7 and 70 and extend toward the orbiting side bottom plate 4a of the orbiting scroll 4.
  • the positioning pin 8 does not need to be separate from the thrust receiving part 6 or the thrust plate 7, and may be formed integrally with the thrust receiving part 6 or the thrust plate 7.
  • the thrust receiving parts 6 and 60 do not need to be provided separately from the housing 1, and may be molded integrally with the housing 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

[Problème] Fournir un compresseur à spirale permettant un fonctionnement stable, sans être affecté par des différences de quantités de dilatation thermique entre des composants. [Solution] Une broche de positionnement (8) est fixée à une plaque de poussée (7), un palier de butée (6) est pourvu d'un trou d'agencement de broche (6x) qui présente un diamètre interne qui est plus grand qu'un diamètre externe de la broche de positionnement (8), et dans lequel la broche de positionnement (8) s'ajuste de manière lâche de telle sorte que la plaque de poussée (7) est apte à un déplacement relatif dans une direction d'axe O par rapport au palier de butée (6), et dans un environnement dans lequel le palier de butée (6) et la plaque de poussée (7) sont à température ambiante et sont à la même température, si une distance entre un centre de broche (Op) de la broche de positionnement (8) et l'axe O est définie comme étant d1 et une distance entre un centre de trou d'agencement de broche (Oh) du trou d'agencement de broche (6x) et l'axe O est définie comme étant d2, la relation d1<d2 est satisfaite.
PCT/JP2023/005393 2022-03-24 2023-02-16 Compresseur à spirale WO2023181727A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022-047834 2022-03-24
JP2022047834A JP2023141488A (ja) 2022-03-24 2022-03-24 スクロール圧縮機

Publications (1)

Publication Number Publication Date
WO2023181727A1 true WO2023181727A1 (fr) 2023-09-28

Family

ID=88100506

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2023/005393 WO2023181727A1 (fr) 2022-03-24 2023-02-16 Compresseur à spirale

Country Status (2)

Country Link
JP (1) JP2023141488A (fr)
WO (1) WO2023181727A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000220582A (ja) * 1999-01-29 2000-08-08 Sanyo Electric Co Ltd スクロール流体機械
JP2003035283A (ja) * 2001-07-25 2003-02-07 Nippon Soken Inc スクロール型ポンプ
JP2007291878A (ja) * 2006-04-21 2007-11-08 Sanden Corp スクロール型流体機械
JP2008248817A (ja) * 2007-03-30 2008-10-16 Hitachi Ltd スクロール式流体機械
JP2017172504A (ja) * 2016-03-24 2017-09-28 サンデンホールディングス株式会社 スクロール圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000220582A (ja) * 1999-01-29 2000-08-08 Sanyo Electric Co Ltd スクロール流体機械
JP2003035283A (ja) * 2001-07-25 2003-02-07 Nippon Soken Inc スクロール型ポンプ
JP2007291878A (ja) * 2006-04-21 2007-11-08 Sanden Corp スクロール型流体機械
JP2008248817A (ja) * 2007-03-30 2008-10-16 Hitachi Ltd スクロール式流体機械
JP2017172504A (ja) * 2016-03-24 2017-09-28 サンデンホールディングス株式会社 スクロール圧縮機

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