EP2703648B1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
EP2703648B1
EP2703648B1 EP11864486.3A EP11864486A EP2703648B1 EP 2703648 B1 EP2703648 B1 EP 2703648B1 EP 11864486 A EP11864486 A EP 11864486A EP 2703648 B1 EP2703648 B1 EP 2703648B1
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EP
European Patent Office
Prior art keywords
hole
scroll
fixed scroll
lap
involute
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11864486.3A
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German (de)
English (en)
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EP2703648A4 (fr
EP2703648A1 (fr
Inventor
Tsutomu Kon
Satoshi Iitsuka
Akihiro Hayashi
Katsuki Akuzawa
Kenji Aida
Kazuyoshi Sugimoto
Yasunori Kiyokawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
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Publication of EP2703648A1 publication Critical patent/EP2703648A1/fr
Publication of EP2703648A4 publication Critical patent/EP2703648A4/fr
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Classifications

    • 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
    • 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
    • F04C18/0207—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 both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F04C18/0261—Details of the ports, e.g. location, number, geometry
    • 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
    • F04C18/0207—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 both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • 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
    • F04C18/0207—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 both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to scroll compressors and more particularly, to a scroll compressor which can be increased in the strength of a lap central portion without degradation in compression performance.
  • a scroll type compressor is known (for example, see Patent Literature 1).
  • the scroll type compressor 100 includes a compression vessel 110 which is formed in a cylindrical shape extending in the vertical direction and in which there are disposed on the upper side a compression element 114 for compressing a refrigerant and on the lower side an electrical driving element 115 for driving the compression element 114.
  • the compression element 114 includes a fixed scroll 119 and a rocking scroll 120, and laps 132 and 139 of the fixed scroll 119 and the rocking scroll 120 are meshed with each other so as to form a plurality of compression spaces 121 therebetween.
  • the fixed scroll 119 is secured to a casing.
  • the movable scroll 120 meshing with the fixed scroll 119 from below is integrally coupled to a driving shaft 123 by fitting an eccentric shaft section 123A of the driving shaft 123 into a bearing portion 122 provided on the lower surface. Then, the movable scroll 120 rotationally driven by drive force from a motor 127 revolves relative to the fixed scroll 119 without rotating, thereby reducing the volume of the compression spaces 121 formed between both the laps 132 and 139 so as to compress a refrigerant therein.
  • a refrigerant intake pipe 117 is directly connected to an intake port 111 of the compression element 114, and the compression vessel 110 includes a high-pressure side space 113 which is filled with a high-pressure refrigerant compressed by the compression element 114. Furthermore, the compression vessel 110 has a bottom portion serving as an oil reservoir 116 in which a lubricating oil for lubricating the compression element 114 and the like is stored. On the other hand, the compression vessel 110 is provided on the side thereof with a refrigerant intake pipe 117 for drawing the refrigerant into the aforementioned compression element 114 and a refrigerant discharge pipe 118 for discharging the refrigerant compressed by the compression element 114 out of the compressor.
  • an oil path 144 for allowing a lubricating oil to pass through a rotation axis 123 in order to supply the lubricating oil to the compression element 114 and bearings 128, 141, and 149 on the rotation axis 123.
  • the oil path 144 is formed in the axial direction of the rotation axis 123 and includes a lubricating oil intake port 145 formed at the lower end of the rotation axis 123 and a paddle 146 formed above the intake port 145.
  • the oil path 144 also includes oil feed ports 147 for supplying the lubricating oil to the position corresponding to the respective bearings.
  • the lubricating oil stored in the oil reservoir 116 enters the oil path 144 through the intake port 145 of the rotation axis 123 and is drawn up along the paddle 146 in the oil path 144. Then, the drawn lubricating oil lubricates each of the bearings 128, 141, and 149 through each oil feed port 147. Furthermore, the lubricating oil drawn up to a boss receiving section 142 is directed to the outer peripheral portion of a mainframe through a return pipe (not shown) formed in the mainframe and then discharged from a discharge port (not shown) formed in the outer peripheral portion, thereby allowing the lubricating oil to be fed back to the oil reservoir 116.
  • Patent Literature 1 Japanese Patent Application Laid-Open No. 2008-50986
  • Document JP 2000 045969 discloses a scroll compressor with the features of the preamble of independent claim 1 and can be considered as a closest prior art.
  • the compression portion surrounded by the lap of the fixed scroll and the lap of the movable scroll is composed of spaces formed by both the laps meshing with each other, where a discharge port that penetrates the end plate of the fixed scroll in the thickness direction is formed at the spiral center or the lap tip portion of the fixed scroll.
  • the spiral center at the tip portion surrounded by both the laps of the fixed scroll and the movable scroll is configured such that the refrigerant gas is compressed into a high-pressure state while being fed from peripheral compression portions to central compression portions.
  • the vicinity of the base of the spiral center of the lap relatively reduced in thickness on the end plate facing the discharge port is fragile in terms of strength and has an insufficient strength.
  • an object of the present invention is to provide a scroll compressor which can be enhanced in strength in the vicinity of the base of the lap tip portion of the fixed scroll on the end plate facing the through-hole, and hence enhanced in reliability and durability.
  • an end plate portion facing the through-hole in the vicinity of the base of the lap tip portion of the fixed scroll is formed to have an increased thickness, and by that amount of increase in thickness, the strength of the portion can be enhanced, and hence the reliability and durability of the fixed scroll can be advantageously enhanced.
  • the vertical wall of the through-hole erected from the peripheral portion facing the base of the lap tip portion of the fixed scroll is formed to have an increased height, whereby the end plate facing the through-hole at the root of the lap tip portion of the fixed scroll is increased in thickness, thus advantageously further enhancing the strength of the fixed scroll by that amount.
  • the height of the vertical wall of the through-hole is formed to be approximately two times the thickness of the portion of the lap of the fixed scroll facing the medium-pressure chamber, thus advantageously further enhancing the strength of the end plate facing the through-hole at the root of the lap tip portion of the fixed scroll.
  • the scroll compressor of (1) above it is possible to make, as long as possible, the distance to hole between the maximum proximity edge of the peripheral portion of the through-hole of the fixed scroll, the maximum proximity edge facing the base of the lap tip portion of the fixed scroll in the closest proximity thereto, and the base of the lap tip portion. This can further enhance the strength of the root of the lap tip portion of the fixed scroll on the end plate facing the through-hole and hence advantageously provide further enhanced reliability and durability for the fixed scroll.
  • the movable scroll is provided with the recess that forms the dummy port, thereby advantageously controlling the timing at which the refrigerant gas is discharged from the compression chamber.
  • Fig. 1 shows a scroll compressor 1 according to an embodiment of the present invention which provides a high internal pressure.
  • the compressor 1 is connected to a refrigerant circuit (not illustrated) in which a refrigerant is circulated to perform a refrigeration cycle and is configured to compress the refrigerant by inverter control.
  • the compressor 1 has a vertically elongated cylindrical enclosed dome-shaped casing 3.
  • the casing 3 with a hollow space provided therein has a pressure vessel which is constituted of: a casing body 5 which is a cylindrical barrel section having an axial line extending in the vertical direction; a bowl-shape upper cap 7 which is hermetically welded to and thereby integrated with the top end thereof and has a convex surface protruded upwardly; and a bowl-shaped lower cap 9 which is hermetically welded to and thereby integrated with the lower end of the casing body 5 and has a convex surface protruded downwardly.
  • the casing 3 includes a scroll compressor mechanism 11 for compressing the refrigerant and a driving motor 13 disposed below the scroll compressor mechanism 11.
  • the scroll compressor mechanism 11 and the driving motor 13 are connected to each other by a driving shaft 15 that is disposed to extend through the casing 3 in the vertical direction.
  • the scroll compressor mechanism 11 includes: a housing 21 being a generally bottomed cylindrical storage member which is opened upwardly; a fixed scroll 23 which is bolted to the upper surface of the housing 21 in a condition appressed thereto; and a movable scroll 25 disposed between the fixed scroll 23 and the housing 21 and meshing with the fixed scroll 23.
  • the housing 21 is secured, on the outer peripheral surface thereof, to the casing body 5.
  • the casing 3 is partitioned into the high-pressure space 17 below the housing 21 and a discharge space 29 above the housing 21, where the spaces 17 and 29 are in communication with each other through a vertical groove (not illustrated) which is formed to extend vertically through the outer periphery of the housing 21 and the fixed scroll 23.
  • the driving motor 13 includes an annular stator 13A secured to the inner wall surface of the casing 3 and a rotor 13B disposed rotatably inside the stator 13A.
  • the motor 13, which is a DC inverter-controlled motor, is configured such that the rotor 13B is drivingly connected with the movable scroll 25 of the scroll compressor mechanism 11 through the driving shaft 15.
  • the driving shaft 15 includes an oil supply path 15B that is formed as part of high-pressure oil supply means, and the oil supply path 15B is in communication with an oil chamber 52 behind the movable scroll 25.
  • the driving shaft 15 is connected at the lower end with a pickup (not illustrated), so that the pickup scoops up the oil stored in the inner bottom portion of the lower cap 9. The scooped oil is supplied through the oil supply path 15B of the driving shaft 15 to the oil chamber 52 behind the movable scroll 25.
  • the oil is supplied from the oil chamber 52 through a communication passage 51 and a communication hole 53 (refer to Fig. 7 ), to be discussed later, provided in the movable scroll 25, to an oil groove 23D on the side of the fixed scroll 23. Subsequently, the oil is supplied from the oil groove 23D to the respective sliding parts and a compression chamber 27 in the scroll compressor mechanism 11 (refer to Fig. 3 ).
  • the housing 21 includes a support section 21A in which an eccentric shaft section 15A of the driving shaft 15 is rotated and a radial bearing part 21B extending downwardly from the center of the lower surface of the support section 21A. Furthermore, the housing 21 is provided with a radial bearing 21C which penetrates between the lower end of the radial bearing part 21B and the bottom surface of the support section 21A. Furthermore, in the vicinity of the outer peripheral portion of the support section 21A toward the lower surface, a thin plate-shaped oil collector 24 for preventing a lubricating oil from entering into a discharge pipe (not illustrated) is vertically provided along the inner peripheral surface of the casing body 5.
  • the upper cap 7 of the casing 3 is provided with an intake pipe (not illustrated) for drawing the refrigerant in the refrigerant circuit into the scroll compressor mechanism 11 and the casing body 5 is provided with a discharge pipe for discharging the refrigerant in the casing 3 out of the casing 3, the pipes each hermetically secured thereto in a penetrating manner.
  • the intake pipe extends in the vertical direction in the discharge space 29, so that the inner end portion thereof penetrates through the fixed scroll 23 of the scroll compressor mechanism 11 so as to communicate with the compression chamber 27.
  • the intake pipe draws the refrigerant into the compression chamber 27.
  • the fixed scroll 23 is made up of: an end plate 23A; a spiral (involute) lap 23B formed on the lower surface of the end plate 23A; and a through hole 23C which is pierced through the end plate at the spiral (involute) center of the lap 23B and which forms the discharge port that is opened toward a discharge valve 22.
  • the top end face of the lap 23B of the fixed scroll 23 (a lower surface 233; refer to Fig. 4 ) particularly toward the refrigerant inlet has the oil groove 23D having a reduced width and engraved on the lower surface 233, the top end face slidingly facing an end surface 250 (refer to Fig. 1 ) that is the upper surface of the movable scroll 25.
  • the movable scroll 25 is made up of: an end plate 25A; a spiral (involute) lap 25B formed on the upper surface of the end plate 25A; and a recess 25D that constitutes a dummy port for controlling the timing at which a refrigerant gas in the compression chamber 27 under a high pressure is discharged toward the discharge space 29, the recess 25D being formed in a concave shape at the spiral (involute) center of the lap 25B. Then, the lap 23B of the fixed scroll 23 and the lap 25B of the movable scroll 25 mesh with each other, forming a plurality of compression chambers 27 between both the laps 23B and 25B (refer to Fig. 1 ).
  • the movable scroll 25 is configured such that a flow limiting member (pin member) 55 is inserted into the communication passage 51, to be discussed later.
  • the pin 55 is made up of a first pin 55A that is fitted into a pilot hole 51A located downstream of the communication passage 51 and a second pin 55B that is in contact with the first pin 55A and fitted into an insert hole 51B located upstream of the communication passage 51.
  • a screw with a hexagonal hole (not illustrated) is screwed into a female screw hole 51C so as to push the second pin 55B and the first pin 55A integrally against the downstream end, allowing the screw to block one end of the insert hole 51B (the left end in Fig. 4 ).
  • the screw is secured with an adhesive or the like to prevent the screw from loosening.
  • the movable scroll 25 is supported by the fixed scroll 23 with an Oldham ring 61 therebetween and provided with a bottomed cylindrical boss section 25C in a protruding manner at the center of the lower surface of the end plate 25A.
  • the driving shaft 15 is provided at the upper end thereof with the eccentric shaft section 15A, and the eccentric shaft section 15A is rotatably fitted into the boss section 25C of the movable scroll 25.
  • the movable scroll 25 is provided with the communication passage 51 that is formed in the end plate 25A and has one end opened outwardly and extending linearly inwardly.
  • the communication passage 51 forms the pilot hole 51A of the communication passage that has one end opened outwardly.
  • the pilot hole 51A is reamed from the one end to a predetermined depth so as to form the insert hole 51B of the predetermined depth.
  • the inlet port of the insert hole 51B is threaded to form the female screw hole 51C.
  • the other end (high-pressure opening) 51D of the communication passage 51 is in communication with the oil chamber (the high-pressure section in the hermetically sealed container) 52 behind the movable scroll 25 described above.
  • the communication passage 51 is provided on the inner peripheral surface of the inlet port thereof with the communication hole 53 that is an opening having a perfect circular shape.
  • the communication hole 53 is formed in the end plate 25A of the movable scroll 25 near the entrance facing a low-pressure section 27A of the compression chamber so as to penetrate in the thickness direction to the end surface 250, thus being opened to face the fixed scroll 23.
  • the driving shaft 15 below the radial bearing part 21B of the housing 21 is provided with a counterweight part 16 to keep the movable scroll 25 and the eccentric shaft section 15A in dynamic balance, so that the driving shaft 15 is rotated while being kept in weight balance by the counterweight part 16, thereby allowing the movable scroll 25 to revolve without rotating.
  • the compression chamber 27 is configured such that as the movable scroll 25 revolves, the volume between both the laps 23B and 25B is contracted toward the center, thereby compressing the refrigerant drawn through the intake pipe.
  • the fixed scroll 23 is provided at the center thereof with the through-hole 23C that constitutes the discharge port, so that the gas refrigerant discharged through the through-hole 23C is discharged into the discharge space 29 through the discharge valve 22. Then, the gas refrigerant is allowed to flow into a space out of the oil collector 24 in the high-pressure space 17 below the housing 21 through a vertical groove (not illustrated) provided in the outer periphery of each of the housing 21 and the fixed scroll 23. The high-pressure refrigerant is finally discharged out of the casing 3 through the discharge pipe provided on the casing body 5.
  • a characteristic structure of the present invention that is, the structure of the through-hole 23C as well as the spiral (involute) tip Z of the lap 23B of the fixed scroll 23, in other words, the shape near a point Z being the vertex of a convex curve S32 on a non-involute surface S3, to be discussed later, that is, the shape of the portion that faces the through-hole 23C.
  • 5 (A) is configured such that the portion equivalent to that mentioned above is provided with a significantly improved physical strength, the portion facing the through-hole 23C near the tip portion Z of the lap 23B in the closest proximity thereto (refer to Fig. 5(A) ).
  • symbols s1 and s2 denote an inner involute surface and an outer involute surface of the movable scroll 25, respectively.
  • symbols E1 and E2 denote the length of the major axis and the length of the minor axis orthogonal thereto of the through-hole 23C of the fixed scroll 23, respectively.
  • symbols e1 and e2 denote the length of the major axis of the recess 25D of the movable scroll 25 and the length of the orthogonal axis orthogonal thereto, respectively.
  • the lap 23B is formed to be greater in height (h + ⁇ h) than the height (h) of the one according to Specification 1 shown in Table 1, to be discussed later, so as to enable the compressor to provide higher output. Furthermore, as shown in Fig. 7 , the tip portion Z of the lap 23B has the non-involute surface S3 which is formed on a region ⁇ (refer to Fig. 5(A) ) between a start point P of an inner surface of two surfaces that constitute the lap 23B of the fixed scroll 23 (hereafter referred to as the "inner involute surface S1") and a start point Q of the outer surface of the two surfaces (hereafter referred to as the "outer involute surface S2"). Note that the non-involute surface S3 is formed without changing the positions of both the start points of the inner involute surface S1 and the outer involute surface S2.
  • the region from the point R through the point Z to the point Q is the convex surface portion, forming the convex curved surface S32 that is an outer non-involute surface of the non-involute surface S3.
  • the point Z corresponds to the vertex of the convex curved surface S32 that is the outer non-involute surface S3.
  • the point R is the start point of a common non-involute surface for the concave curved surface S31 being an inner non-involute surface and the convex curved surface S32 being an outer non-involute surface.
  • the non-involute surface S3 of the present invention is configured such that the entire concave curved surface S31, particularly from the start point R to the endpoint P of the concave curved surface S31, is formed in the shape of a curved surface having a reduced radius r of curvature (r ⁇ r' ; note that as shown in Fig. 5(B) , r' is the radius of curvature of the inner involute surface S'1 of the fixed scroll according to Specification 1 in Table 1 to be discussed later). That is, the concave curved surface S31 is formed in the shape denoted in Fig. 7 by the solid line which is shifted toward the through-hole 23C (rightward in the figure) with respect to the inner involute surface indicated by the broken line.
  • the convex curved surface S32 of the non-involute surface S3, that is, from the point R serving also as the start point of the convex curved surface S32 to the endpoint Q may have a curved surface which is appropriately shaped to be different from the inner involute surface, for example, any shape such as an arc-shaped curve which is outwardly shifted from the inner involute surface. Note that this embodiment employs an arc having an appropriate radius of curvature. As shown in Fig.
  • this allows the thickness T near the vertex Z of the convex curved surface S32 or the tip portion of the lap 23B of the fixed scroll 23 to be greater at least than a thickness T 0 near a tip portion Z 0 of the lap 25B of the movable scroll 25.
  • a length (hereafter referred to as the "distance to hole L") is designed to be as long as possible, where the distance to hole L is the length between the base on the end plate 23A particularly at the point Z being the tip portion of the lap 23B of the fixed scroll 23 (immediately below the portion denoted by the point Z in Fig. 5 (A) ), of the inner circumferential edge of the through-hole 23C constituting the discharge port formed at the spiral center being the tip portion of the lap 23B of the fixed scroll 23, and a maximum proximity edge U of the fixed scroll 23 facing the inner circumferential edge of the through-hole 23C in the closest proximity thereto from the base at the point Z being the tip portion of the lap 23B .
  • the distance to hole L of this embodiment is longer than L', that is, L > L', where for a generally typical through-hole, for example, the fixed scroll 23' shown in Fig. 5 (B) , the distance to hole L' is the length between the base on the end plate 23'A at the point Z' (immediately below the portion denoted by the point Z' in Fig. 5(B) ) being the tip portion of the lap 23'B and the maximum proximity edge U' of the fixed scroll 23' facing the inner circumferential edge of the through-hole 23'C in the closest proximity thereto from the base at the tip portion Z' of the lap 23'B.
  • the distance to hole L of the fixed scroll 23 can be increased when compared with the distance to hole L' of the fixed scroll 23' according to Specification 1 because the through hole 23C is reduced, for example, as compared with the through-hole 23'C of the fixed scroll 23' according to Specification 1 in Table 1.
  • a base surface 232 or the distance to hole L in particular, can be made longer on the end plate 23A.
  • this embodiment is configured as follows.
  • the through-hole 23C of this embodiment shown in Fig. 5(A) has an opening area reduced to about 80% to 90% (90% in this embodiment) when compared with the size of the through-hole 23' C opened on the fixed scroll 23' shown in Fig. 5(B) corresponding to Specification 1 in Table 1 (refer to Fig. 5(A) and Fig. 5(B) ). That is, the through-hole 23C in a close region ( ⁇ ) facing the concave curved surface S31 of the non-involute surface S3 is configured to be narrowed in the opening shape when compared with the opening shape of the through-hole 23'C of the fixed scroll 23' in a close region ( ⁇ '). For example, in this embodiment, the opening area is reduced by about 10%, thereby increasing the distance to hole L.
  • a curved surface which has an inner edge of a radius of curvature smaller than the radius r of curvature of the concave curved surface S31. That is, the opening edge portion in the close region ( ⁇ ) is shifted and retreated so as to come closer toward the center of the through-hole 23C (in Fig. 7 , the portion denoted by an alternate long and short dashed line is shifted rightward to the portion denoted by a bold line). In this manner, the hole is narrowed to thereby reduce the opening area.
  • the curved surface of this portion may be, for example, an arc which has a radius of curvature less than the radius r of curvature of the concave curved surface S31.
  • the opening shape of the through-hole 23C is configured such that the inner edge portion in the close region ( ⁇ ) facing the concave curved surface S31 of the non-involute surface S3 of the fixed scroll 23 is retreated and narrowed so as to be come closer toward the hole center as described above.
  • the opening shape has not been changed and thus the same as the shape of the through-hole 23'C of the fixed scroll 23' according to Specification 1. That is, communication with the compression chamber will start from the remaining region ( ⁇ ) of the through-hole 23C opposite to the lap.
  • two pairs of compression chambers discharge at the same timing.
  • the distance to hole ⁇ L can be expanded like the aforementioned distance to hole L because as shown in Fig. 6 , the width W of the through-hole 23C of the fixed scroll 23 on the cross section is narrowed when compared with the width W' of the corresponding portion of the through-hole 23'C of the fixed scroll 23' (note that W ⁇ W').
  • the through-hole 23C constituting the discharge port formed at the spiral center being the vertex Z serving also as the tip portion of the lap 23B of the fixed scroll 23 is configured such that as shown in Fig. 6(A) , on the inner circumferential surface of the through-hole 23C, the height H of a vertical wall 231 that is erected vertically particularly from the base surface 232 being a surface portion connected to the base of the lap 23B, of an end face 230 of the end plate 23A of the fixed scroll 23 is increased.
  • the through-hole 23'C of the fixed scroll 23' is configured such that as shownin Figs. 5(B) and 6(B) , the vertical wall 231' is formed from the base surface 232' so as to have a height H' generally the same as the width t' except for the tip portion of the lap 23'B of the fixed scroll 23' , that is, H' being approximately equal to t'.
  • the through-hole 23C of this embodiment is formed to have the vertical wall 231 that is higher than that for a generally typical through-hole, that is, the through-hole 23'C of the fixed scroll 23' according to Specification 1, the thickness of the end plate 23A in the vicinity of the point Z or the tip portion of the lap 23B is substantially increased, thus providing a significant increase in the structural strength.
  • the through hole 23C of this embodiment is smaller than the size of the recess 25D constituting the dummy port formed at the spiral center of the lap 25B of the movable scroll 25, that is, so as to satisfy the relation below: E 1 ⁇ e 1 and E 2 ⁇ e 2.
  • the through-hole 23C does not have the same area as that of the recess 25D, but has a narrower area than that.
  • the through-hole 23C of the fixed scroll 23 and the recess 25D of the movable scroll 25 are configured to have the relative positional relation of being 180 degrees out of phase with each other so as to be inverted in a point symmetric manner.
  • the "point symmetry” defines the geometric relation between two figures that can be superposed on each other when rotated 180 degrees about a symmetric center position.
  • the expression "in a point symmetric manner" is employed by taking into account the circumstances that the two figures are geometrically similar and have different sizes and thus not exactly superposed on each other.
  • the through-hole 23C By forming the through-hole 23C into such a shape, communication with the compression chamber starts from the remaining region ( ⁇ ; refer to Fig. 5 ) of the through-hole 23C opposite to the lap. Thus, it has not been changed that the two pairs of compression chambers discharge at the same timing. This allows for effectively avoiding generating an unnecessary load on the bearing, and as a result, it is possible to prevent the occurrence of adverse effects on such as noise, vibration, and durability.
  • the driving motor 13 When the driving motor 13 is driven, the rotor 13B is rotated relative to the stator 13A, thereby rotating the driving shaft 15.
  • the driving shaft 15 When the driving shaft 15 is rotated, the movable scroll 25 of the scroll compressor mechanism 11 revolves without rotating while the attitude thereof is being maintained constant relative to the fixed scroll 23. This causes a low-pressure refrigerant to be drawn through the intake pipe, fed from the periphery of the compression chamber 27 into the compression chamber 27, and compressed with volumetric change of the compression chamber 27.
  • the compressed refrigerant now under a high pressure, is discharged from the compression chamber 27 through the discharge valve 22 into the discharge space 29, and then flows out of the oil collector 24 toward the high-pressure space 17 below the housing 21 through the vertical groove (not illustrated) provided in the outer periphery of each of the housing 21 and the fixed scroll 23. Then, the high-pressure refrigerant is discharged out of the casing 3 through the discharge pipe (not illustrated) provided on the casing body 5.
  • the refrigerant having been discharged out of the casing 3 is circulated through the refrigerant circuit (not illustrated) and after that, drawn back into the compressor 1 through the intake pipe and then compressed, thus allowing the refrigerant to be repeatedly circulated.
  • the lubricating oil stored in the inner bottom portion of the lower cap 9 of the casing 3 is scooped up with the pickup (not illustrated) provided on the lower end of the driving shaft 15 shown in Fig. 1 , so that the resulting lubricating oil is supplied through the oil supply path 15B of the driving shaft 15 into the high-pressure oil chamber 52 behind the movable scroll 25. Furthermore, the lubricating oil is fed, with the help of a differential pressure, from the oil chamber 52 shown in Fig. 4 through the communication passage 51 and the communication hole 53 provided in the movable scroll 25 into the oil groove 23D (refer to Fig. 2 and Fig. 4 ) opened on the lower surface 233 being the top end face of the lap 23B of the fixed scroll 23, and then supplied to respective sliding parts of the scroll compressor mechanism 11 and the compression chamber 27.
  • the oil supplied to the compression chamber 27 moves to the center of both the scrolls which is a high-pressure compression chamber, and then along with the flow of the high-pressure refrigerant compressed here, the oil is discharged through the discharge valve 22 into the discharge space 29.
  • the lubricating oil discharged through the discharge valve 22 into the discharge space 29 in conjunction with the high-pressure refrigerant flows into the high-pressure space 17 below the housing 21 through the vertical groove (not illustrated) provided on the outer periphery of each of the housing 21 and the fixed scroll 23.
  • the oil is stored in the inner bottom portion of the lower cap 9 equivalent to the lower space 91 through the inner wall portion of the casing body 5 and a gap of the driving motor 13.
  • the high-pressure space 17 has the thin plate-shaped oil collector 24 and a cup 26, it is possible to collect the oil in the inner bottom portion of the lower cap 9 while preventing the oil from entering the discharge pipe.
  • the one according to Specification 5 corresponding to the fixed scroll of this embodiment is configured such that the scroll tooth height is increased by ⁇ h; the discharge hole area is reduced to 0.9 times; and the discharge hole vertical wall is increased to 2.5 times.
  • This structure provided the finding that it was possible to reduce 28% the force acting on the base of the tip portion Z of the fixed scroll at which the maximum stress occurred.
  • the compressor 1 of this embodiment that includes the fixed scroll according to Specification 5 showed that the strength of the end plate 23A near the base of the tip portion Z of the lap 23B of the fixed scroll 23 was enhanced.
  • the present invention is not limited to the aforementioned embodiment, but may be modified in a variety of ways without departing from the scope of the appended claims.
  • the fixed scroll of the present invention is not limited to the one according to Specification 5 in Table 1 above, but may also be any one according to Specifications 3, 4, and 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (2)

  1. Compresseur à spirale (1) comprenant : une spirale fixe (23) immobilisée à l'intérieur d'un carter (3) et une spirale mobile (25) s'engrenant avec la spirale fixe (23), le compresseur à spirale (1) comprimant un espace formé entre les deux recouvrements (23B, 25B) de ces spirales, la spirale fixe (23), située sur un bord de pointe de recouvrement, présentant une épaisseur supérieure à celle de la spirale mobile (25) sur un bord de pointe de recouvrement, où, sur une plaque terminale (23A) à la périphérie du trou traversant (23C) constituant l'orifice d'éjection et formé au centre de la spirale représentant le bord de pointe de la spirale fixe (23), une paroi verticale (231) érigée depuis un bord de proximité maximale (U) de la périphérie du trou traversant (23C) faisant face à la base de la pointe de recouvrement (Z) à la proximité la plus rapprochée de celle-ci et s'écartant vers l'intérieur avec une marche, caractérisé en ce que la hauteur (H) de la marche de la paroi verticale (231), érigée depuis la périphérie du trou traversant (23C), est formée pour valoir depuis deux fois jusqu'à deux fois et demi l'épaisseur (t) d'une partie du recouvrement (23B) de la spirale fixe (23) faisant face à un compartiment sous moyenne pression, sauf pour la pointe du recouvrement (23B) de la spirale fixe (23), une surface non développante (S3), qui est composée d'une surface interne non développante (S31), qui est une surface concave incurvée, et d'une surface externe non développante (S32), qui est une surface convexe incurvée, étant formée entre un point de début P d'une surface développante interne (S1) et un point de début Q d'une surface développante externe (S2), qui constituent le recouvrement de la spirale fixe (23) ; la surface non développante (S3) est configurée de telle sorte que la surface interne non développante (S31), qui est la surface concave incurvée, soit formée pour être une surface incurvée présentant un rayon de courbure plus petit pour être ainsi décalée vers le trou traversant (23C) par rapport à la surface interne développante (S1) ; et le trou traversant (23C) est formé de manière à ce que la forme de l'ouverture de celui-ci dans une zone fermée (ε) faisant face à la surface interne non développante (S31), qui est la surface concave incurvée, présente une surface incurvée dont le rayon de courbure est plus petit que celui de la surface interne non développante (S31), qui est la surface concave incurvée, afin de réduire ainsi la surface de l'ouverture du trou traversant (23C) de façon à renforcer la plaque terminale (23A) faisant face au trou traversant (23C) dans la proximité la plus rapprochée de celui-ci à proximité de la base de la pointe de recouvrement (Z).
  2. Compresseur à spirale (1) selon la revendication 1, dans lequel :
    la spirale mobile (25) inclut un évidement (25D) au niveau du centre de la spirale représentant la pointe de recouvrement (Z), l'évidement (25D) formant un orifice fictif avec au moins une partie de celle-ci chevauchant toujours le trou traversant (23C) de la spirale fixe (23) dans la direction axiale, et l'évidement (25D) étant formé pour être de taille supérieure à celle du trou traversant (23C), et
    le trou traversant (23C) de la spirale fixe (23) et l'évidement (25D) de la spirale mobile (25) étant géométriquement semblables et formés pour présenter une relation de position déphasée de 180 degrés l'un avec l'autre de façon à être inversés dans un symétrie ponctuelle.
EP11864486.3A 2011-04-28 2011-12-27 Compresseur à spirale Active EP2703648B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011101545A JP5879532B2 (ja) 2011-04-28 2011-04-28 スクロール型圧縮機
PCT/JP2011/080591 WO2012147239A1 (fr) 2011-04-28 2011-12-27 Compresseur à spirale

Publications (3)

Publication Number Publication Date
EP2703648A1 EP2703648A1 (fr) 2014-03-05
EP2703648A4 EP2703648A4 (fr) 2014-07-30
EP2703648B1 true EP2703648B1 (fr) 2016-07-06

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JP (1) JP5879532B2 (fr)
CN (1) CN103502646B (fr)
WO (1) WO2012147239A1 (fr)

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KR102318124B1 (ko) * 2017-04-24 2021-10-27 엘지전자 주식회사 스크롤 압축기
US10711782B2 (en) 2017-04-20 2020-07-14 Lg Electronics Inc. Scroll compressor with wrap contour modification
FR3070446B1 (fr) 2017-08-29 2020-02-07 Danfoss Commercial Compressors Un compresseur a spirales ayant un orifice de refoulement principal central et un orifice de refoulement auxiliaire
CN110307153B (zh) * 2018-03-27 2021-01-26 株式会社丰田自动织机 涡旋型压缩机
JP6739660B1 (ja) * 2019-03-19 2020-08-12 三菱電機株式会社 スクロール圧縮機
US20230349381A1 (en) * 2020-07-27 2023-11-02 Emerson Climate Technologies (Suzhou) Co., Ltd. Fixed Scroll and Scroll Compressor
CN114593048A (zh) * 2022-03-15 2022-06-07 松下压缩机(大连)有限公司 一种涡旋压缩机涡旋型线结构
CN114718863A (zh) * 2022-04-19 2022-07-08 广东美的环境科技有限公司 动涡旋盘、压缩组件和涡旋压缩机以及空调器

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JPS5923096A (ja) * 1982-07-30 1984-02-06 Toshiba Corp スクロ−ル・コンプレツサ
JP3711661B2 (ja) * 1996-10-24 2005-11-02 三菱電機株式会社 スクロール圧縮機
JP3774964B2 (ja) * 1996-12-10 2006-05-17 株式会社日立製作所 スクロール圧縮機
JP3766214B2 (ja) * 1998-08-03 2006-04-12 哲哉 ▲荒▼田 スクロール式流体機械
JP2005273453A (ja) * 2004-03-22 2005-10-06 Aisin Seiki Co Ltd スクロール圧縮機
JP4836712B2 (ja) 2006-08-24 2011-12-14 三洋電機株式会社 密閉型スクロール圧縮機
US7976296B2 (en) * 2008-12-03 2011-07-12 Emerson Climate Technologies, Inc. Scroll compressor having capacity modulation system
JP2010265756A (ja) * 2009-05-12 2010-11-25 Panasonic Corp スクロール圧縮機

Also Published As

Publication number Publication date
WO2012147239A1 (fr) 2012-11-01
JP5879532B2 (ja) 2016-03-08
CN103502646A (zh) 2014-01-08
EP2703648A4 (fr) 2014-07-30
JP2012233421A (ja) 2012-11-29
CN103502646B (zh) 2016-04-13
EP2703648A1 (fr) 2014-03-05

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