EP3376032B1 - Verdichter - Google Patents

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Publication number
EP3376032B1
EP3376032B1 EP18161496.7A EP18161496A EP3376032B1 EP 3376032 B1 EP3376032 B1 EP 3376032B1 EP 18161496 A EP18161496 A EP 18161496A EP 3376032 B1 EP3376032 B1 EP 3376032B1
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EP
European Patent Office
Prior art keywords
discharge
side hole
hole portion
discharge side
compression
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
EP18161496.7A
Other languages
English (en)
French (fr)
Other versions
EP3376032A1 (de
EP3376032B8 (de
EP3376032C0 (de
Inventor
Hajime Sato
Yoshiaki Miyamoto
Yoshiyuki Kimata
Masahiro Taniguchi
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3376032A1 publication Critical patent/EP3376032A1/de
Application granted granted Critical
Publication of EP3376032B1 publication Critical patent/EP3376032B1/de
Publication of EP3376032C0 publication Critical patent/EP3376032C0/de
Publication of EP3376032B8 publication Critical patent/EP3376032B8/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04C23/008—Hermetic pumps
    • 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
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves

Definitions

  • the present invention relates to a compressor.
  • a compressor for compressing a fluid such as a refrigerant is provided in an air conditioner, a refrigerator, and the like.
  • a scroll compressor, a rotary compressor, or the like which are types of compressors, a discharge valve mechanism using a reed valve or the like is provided between a compression side on which a refrigerant is compressed and a discharge side which discharges a compressed refrigerant.
  • a refrigerant compressor disclosed in Patent Document 1 is configured so that the refrigerant compressed by a compression element on the compression side is discharged from the discharge port equipped with the discharge valve mechanism to the discharge side.
  • a discharge port is provided to pass through a main bearing or the like which partitions the compression side and the discharge side, and the discharge port can be opened and closed by a valve seat and a valve body provided on the discharge side.
  • the valve body is easily deformed or misaligned in the state in which the valve body is closed, the sealing property is easily lowered, and the valve strength is easily lowered.
  • the present invention has been made to solve the aforementioned problems, and an object of the present invention is to provide a compressor capable of reducing a pressure loss at a discharge port, without lowering the sealing property and the valve strength in a state in which the valve body is closed.
  • a compressor as defined in claim 1.
  • the valve body Since only the one end of the valve body is fixed to the base portion, when the discharge port is opened, the valve body is obliquely disposed from the one end toward the other end with respect to the base portion. Accordingly, the compressed fluid discharged from the discharge port is guided by the surface of the obliquely disposed valve body to flow obliquely from the one end toward the other end.
  • bulging portion spaced apart from the one end of the valve body further than the inner circumferential surface of the compression side hole portion is provided on the inner circumferential surface of the discharge side hole portion in a plan view. Therefore, the discharge direction of the compressed fluid introduced into the compression side hole portion and discharged from the discharge side hole portion can be made to coincide with the direction along the valve body.
  • the other side of the valve body is elastically deformed obliquely to open the discharge port, and it is possible to discharge the compressed fluid toward the side on which the valve body is more greatly separated from the discharge port by discharging the compressed fluid discharged from the discharge side hole portion toward the other end side of the valve body. Therefore, it is possible to reduce the pressure loss at the time of discharge of the compressed fluid from the discharge port.
  • the distance from the one end of the valve body to the discharge port is long. Therefore, the length from one end of the valve body fixed to the base portion to the opening and closing portion of the discharge opening becomes longer. As a result, the valve body is easily elastically deformed, and the pressure loss of the compressed fluid at the time of discharge can be further reduced. Moreover, since the valve body is easily elastically deformed, the durability of the valve body is enhanced. Accordingly, it is possible to avoid the degradation of the sealing property of the discharge port due to long-term use.
  • the discharge side hole portion may be formed to have a smaller diameter than the compression side hole portion, the center of the discharge side hole portion may be disposed on a side separated from the one end of the valve body further than the center of the compression side hole portion, and the bulging portion may be part of the inner circumferential surface of the discharge side hole portion.
  • the discharge opening of the discharge side hole portion can be made smaller than the opening of the compression side hole portion. Further, by increasing the opening of the compression side hole portion, it is possible to reduce the pressure loss when the compressed fluid is introduced into the compression side hole portion. On the other hand, by decreasing the discharge opening of the discharge side hole portion, it is possible to suppress deformation (deflection of the valve body into the discharge port, etc.) of the valve body when the discharge port is closed by the valve body. Therefore, it is possible to easily ensure a sufficient sealing property when the discharge opening is closed by the valve body and to suppress a decrease in valve strength.
  • an opening area of a communication portion between the compression side hole portion and the discharge side hole portion is formed to be equal to or larger than a cross-sectional area of the discharge side hole portion.
  • the opening area of the communication portion between the compression side hole portion and the discharge side hole portion is formed to be equal to or larger than the cross-sectional area of the discharge side hole portion, it is possible to reduce the pressure loss at the communication portion. If the compression side hole portion and the discharge side hole portion are made to eccentrically communicate with each other, a portion having an angular shape and having a small opening area is easily generated in the communication portion. Therefore, by securing the opening area of the communication portion, it is possible to greatly reduce the pressure loss of the compressed fluid flowing in the communication portion.
  • the base portion may have a base portion main body, and a seating plate which is attachable to and detachable from the base portion main body at a position where the valve body is provided and which is made of a harder material than the base portion main body, and the discharge side hole portion may be provided in the seating plate.
  • the surface of the side of the base portion of the valve body abuts on the seating plate and is supported by the seating plate. Therefore, the valve body does not abut on the base portion main body at the time of opening and closing, and breakage of the base portion main body can be avoided.
  • a chamfered portion may be formed at an edge portion of a communication portion between the compression side hole portion and the discharge side hole portion.
  • the compressor of the present invention it is possible to provide a compressor capable of reducing the pressure loss at the discharge port without lowering the sealing property or the valve strength in a state in which the valve body is closed.
  • the compressor A is a vertical type scroll compressor provided in an air conditioner, a refrigerator, or the like.
  • the compressor A of the present embodiment includes a housing 1, an electric motor 2 provided in the housing 1, and a scroll compression mechanism 3 which is similarly provided in the housing 1 and compresses a fluid such as a refrigerant by the driving of the electric motor 2.
  • the housing 1 is formed to include a cylindrical housing main body 1a, an upper cover 1b which closes an opening of an upper end of the housing main body 1a, and a lower cover 1c which closes an opening of a lower end of the housing main body 1a.
  • a suction pipe 4 for supplying a fluid such as a refrigerant from the accumulator or the like into the housing 1 is provided on the side surface of the housing main body 1a, and a discharge pipe 5 for discharging the fluid compressed by the scroll compression mechanism 3 to the outside is provided in the upper cover 1b.
  • the electric motor 2 includes a stator 6 and a rotor 7 and is configured such that power is supplied from a power source to the stator 6 and the rotor 7 rotates in one direction around an axis O1 extending in a vertical direction S1.
  • a rotary shaft 8 is integrally attached to the rotor 7 with its axis O1 direction oriented in the vertical direction S 1.
  • the upper end side of the rotary shaft 8 in the direction of the axis O1 is supported by an upper bearing 10, and the lower end side thereof is pivotally supported by a lower bearing 11.
  • the rotary shaft 8 is provided to rotate around the axis O1 together with the rotation of the rotor 7.
  • the upper bearing 10 and the lower bearing 11 are integrally fixed to the housing main body 1a.
  • An eccentric pin 12 is integrally provided on the upper end portion of the rotary shaft 8 with its axis O2 oriented in the vertical direction S1 and is eccentric (offset) with respect to the axis O1 of the rotary shaft 8.
  • the scroll compression mechanism 3 includes a fixed scroll 15 (base portion), an orbiting scroll 16 that revolves and turns eccentrically with respect to the fixed scroll 15 by the electric motor 2, and a discharge cover 17 (base portion).
  • the fixed scroll 15 includes a disk-shaped end plate 15a, and a fixed wrap 15b protruding downward from the lower surface of the end plate 15a and disposed in a spiral shape.
  • the fixed scroll 15 is fixedly installed in the housing 1 by being bolt-joined to the upper bearing 10.
  • the orbiting scroll 16 is formed to include a disk-shaped end plate 16a, and an orbiting wrap 16b protruding upward from the upper surface of the end plate 16a and disposed in a spiral shape.
  • the orbiting wrap 16b of the orbiting scroll 16 is accommodated between the fixed wraps 15b of the fixed scroll 15.
  • a boss 20 is integrally provided on the lower surface of the end plate 16a of the orbiting scroll 16, and the eccentric pin 12 is fitted to the boss 20.
  • the orbiting scroll 16 is provided to be eccentrically connected to the rotary shaft 8, and to follow the rotation about the axis O1 of the rotary shaft 8 and rotates (revolves) about the eccentric distance from the axis (axial center) O1 of the rotary shaft 8 as a radius. Further, the orbiting scroll 16 is configured to revolve without rotating.
  • the fixed scroll 15 and the orbiting scroll 16 mesh with the fixed wrap 15b and the orbiting wrap 16b to overlap vertically.
  • the fixed scroll 15 and the orbiting scroll 16 are eccentric to each other by a predetermined amount, the fixed wrap 15b and the orbiting wrap 16b mesh with each other with phases shifted 180 degrees, and the fixed wrap 15b and the orbiting wrap 16b are in contact with each other at a plurality of places in accordance with the rotation angle of the orbiting scroll 16.
  • the compression chamber 21 is formed in point symmetry with respect to the center portion of the spiral of the fixed wrap 15b and the orbiting wrap 16b, and the compression chamber 21 gradually transitions to the inner circumference side, while reducing the volume in accordance with the orbiting motion of the orbiting scroll 16, thereby compressing the fluid to the maximum at the center portion of the spiral.
  • a discharge port 15c formed to penetrate the end plate 15a of the fixed scroll 15 to allow the upper and lower spaces to communicate with each other is provided in the end plate 15a at a position corresponding to the center portion of the compression chamber 21, and a discharge valve mechanism C is configured on the upper surface side of the discharge port 15c.
  • the discharge valve mechanism C is a mechanism which opens and closes the discharge opening 15d of the discharge port 15c in accordance with a pressure difference between the intermediate chamber 19 between the fixed scroll 15 and the discharge cover 17 and the compression chamber 21.
  • the discharge cover 17 is disposed above the fixed scroll 15, and partitions and divides the interior of the housing 1 into a space on a lower side to which the suction pipe 4 is connected and an intermediate chamber 19, and a discharge chamber 22 on an upper side to which the discharge pipe 5 is connected.
  • a discharge port 17c through which upper and lower spaces communicate with each other is provided to penetrate the discharge cover 17, and a discharge valve mechanism B is formed on the upper surface side of the discharge port 17c.
  • the discharge valve mechanism B is a mechanism which opens and closes the discharge port 17d of the discharge port 17c in accordance with a pressure difference between the intermediate chamber 19 and the discharge chamber 22.
  • the discharge valve mechanism B and the discharge valve mechanism C include discharge ports 15c and 17c which penetrate the end plate 15a of the fixed scroll 15 or the discharge cover 17, valve seats 15e and 17e provided on the end plate 15a of the fixed scroll 15 or the upper surface of the discharge cover 17, a valve body 25 which closes to face the discharge openings 15d and 17d of the discharge ports 15c and 17c, and a retainer 26 disposed over the valve body 25 and the discharge port 17d to overlap.
  • the discharge port 17c of the discharge valve mechanism B and the discharge port 15c of the discharge valve mechanism C have compression side hole portions 15f and 17f provided on the compression chamber 21 side, and discharge side hole portions 15g and 17g provided on the discharge chamber 22 side and having the discharge openings 15d and 17d.
  • the compression side hole portions 15f and 17f and the discharge side hole portions 15g and 17g are bottomed holes having circular cross sections and are formed to opposite directions to each other. That is, the compression side hole portions 15f and 17f are formed in the end plate 15a of the fixed scroll 15 or the discharge cover 17 from the compression side, and the discharge side hole portions 15g and 17g are formed on the end plate 15a of the fixed scroll 15 or the discharge cover 17 from the discharge side, for example, by a drill.
  • the cross-sectional areas of the discharge side hole portions 15g and 17g are smaller than the cross-sectional areas of the compression side hole portions 15f and 17f, and the discharge side hole portions 15g and 17g are formed to be smaller in diameter than the compression side hole portions 15f and 17f.
  • the cross-sectional area referred to here is a cross-sectional area in a plane orthogonal to the center line at each hole portion and is the maximum cross-sectional area at each hole portion.
  • the centers of the discharge side hole portions 15g and 17g are eccentric with respect to the centers of the compression side hole portions 15f and 17f, and the centers of the discharge side hole portions 15g and 17g are separated from one end 25a of the valve body 25 further than the centers of the compression side hole portions 15f and 17f. Due to the eccentricity of the discharge side hole portions 15g and 17g with respect to the compression side hole portions 15f and 17f, some parts of the inner circumferential surfaces of the discharge side hole portions 15g and 17g are bulging portions 15h and 17h bulging to the side separated from one end 25a of the valve body 25 further than the inner circumferential surfaces of the compression side hole portions 15f and 17f as viewed in a plan view.
  • communication portions 15i and 17i through which the compression side hole portions 15f and 17f communicate with the discharge side hole portions 15g and 17g communicate with each other, are provided.
  • the opening areas of the communication portions 15i and 17i are formed to be equal to or larger than the cross-sectional areas of the discharge side hole portions 15g and 17g.
  • the opening areas of the communication portions 15i and 17i are the areas of the portion surrounded by a boundary line X (see FIG. 3 ) between the compression side hole portions 15f and 17f and the discharge side hole portions 15g and 17g.
  • a chamfered portion such as an R surface or a C surface may be provided on the edge portion forming the boundary line X in the communication portions 15i and 17i.
  • valve seats 15e and 17e are directly formed on the upper surface of the end plate 15a of the fixed scroll 15 and the upper surface of the discharge cover 17.
  • the valve seats 15e and 17e have a surface shape corresponding to the surface shape of the opposite valve body 25, and the valve seats 15e and 17e are formed in a planar shape in substantially the entire region facing the valve body 25 in this embodiment.
  • the valve body 25 includes a reed valve, and one end 25a thereof is fixed to the end plate 15a of the fixed scroll 15 or the upper surface of the discharge cover 17.
  • the other end 25b closes the discharge ports 15c and 17c in a state in which it abuts the valve seats 15e and 17e.
  • the valve body 25 is provided to be elastically deformable in a direction in which it approaches and separates from the end plate 15a or the upper surface of the discharge cover 17 with one end 25a fixed to the end plate 15a of the fixed scroll 15 or the upper surface of the discharge cover 17 as a fulcrum.
  • One end side of the retainer 26 is fixed to and supported by the discharge cover 17, and the retainer 26 is inclined upward toward the other end side to overlap the upper part of the valve body 25 and the discharge opening 17d. Since the retainer 26 is formed to be inclined from one end side to the other end side, the valve body 25 is elastically deformed by the pressure difference and restricts the lift amount of each position during lifting.
  • valve body 25 and the retainer 26 are fastened together at one end 25a to the end plate 15a of the fixed scroll 15 or the discharge cover 17.
  • the discharge valve mechanism B when the pressure in the compression chamber 21 is equal to or lower than the pressure of the intermediate chamber 19, the other end 25b side is kept in a state in which the discharge opening 17d is closed. Further, when the pressure of the compression chamber 21 becomes larger than the pressure of the intermediate chamber 19, the discharge valve mechanism B is elastically deformed in accordance with the pressure difference with the fixed portion (bolt 30) on the one end 25a side as a fulcrum, and the other end 25b side is lifted up from the valve seat 15e to open the discharge opening 17d. As a result, the compressed fluid is fed from the intermediate chamber 19 to the compression chamber 21 through the discharge opening 17d. When the pressure of the compression chamber 21 becomes equal to or lower than the pressure of the intermediate chamber 19, the other end 25b side of the valve body 25 restores to its original state to close the discharge opening 17d.
  • the discharge valve mechanism C when the pressure of the intermediate chamber 19 is lower than the pressure of the discharge chamber 22, the other end 25b side is kept in a state in which the discharge opening 17d is closed. Further, when the pressure of the intermediate chamber 19 becomes greater than the pressure of the discharge chamber 22, the discharge valve mechanism C is elastically deformed in accordance with the pressure difference with the fixed portion (bolt 30) on the one end 25a side as a fulcrum, and the other end 25b side is lifted up from the valve seat 15e to open the discharge opening 17d. As a result, compressed fluid is supplied from the intermediate chamber 19 to the discharge chamber 22 through the discharge opening 17d. When the pressure of the compression chamber 21 becomes equal to or lower than the pressure of the intermediate chamber 19, the other end 25b side of the valve body 25 returns to its original state to close the discharge opening 17d.
  • the compressed fluid is sequentially discharged from the discharge pipe 5 for use.
  • valve body 25 since only the one end 25a of the valve body 25 is fixed to the end plate 15a or the discharge cover 17, when the discharge openings 15d and 17d are opened, the valve body 25 is obliquely disposed from the one end 25a toward the other end 25b with respect to the end plate 15a or the discharge cover 17. Accordingly, the compressed fluid discharged from the discharge openings 15d and 17d is guided by the surface of the obliquely disposed valve body 25 to flow obliquely from one end 25a toward the other end 25b.
  • bulging portions 15h and 17h spaced apart from one end 25a of the valve body 25 from the inner circumferential surface of the compression side hole portions 15f and 17f are provided on the inner circumferential surfaces of the discharge side hole portions 15g and 17g in a plan view. Therefore, the discharge direction of the compressed fluid introduced into the compression side hole portions 15f and 17f and discharged from the discharge side hole portions 15g and 17g can be made to coincide with the direction along the valve body 25 (see arrow Y of FIG. 3 ).
  • the valve body 25 is elastically deformed obliquely by separating the other end 25b from the discharge openings 15d and 17d while the one end 25a is fixed, thereby opening the discharge openings 15d and 17d. Therefore, by discharging the compressed fluid discharged from the discharge side hole portions 15g and 17g toward the other end 25b side of the valve body 25 in the direction of the arrow Y, it is possible to discharge the compressed fluid toward the side on which the valve body 25 is more greatly separated from the discharge openings 15d and 17d. Therefore, it is possible to reduce the pressure loss at the time of discharge of the compressed fluid.
  • the distance from the one end 25a of the valve body 25 to the discharge openings 15d and 17d is longer than the distance from the one end 25a to the compression side hole portions 15f and 17f. Therefore, the length from one end 25a of the valve body 25 to the opening and closing portion of the discharge openings 15d and 17d becomes longer. As a result, the valve body 25 is easily elastically deformed, the discharge openings 15d and 17d can be opened to a greater extent, and the pressure loss of the compressed fluid at the time of discharge can be further reduced.
  • valve body 25 is easily elastically deformed, the durability of the valve body 25 is enhanced. Thus, it is possible to avoid the degradation of the sealing property of the discharge openings 15d and 17d due to long-term use.
  • the compressor A of the present claimed invention by increasing the opening areas of the compression side hole portions 15f and 17f compared to the opening areas of the discharge openings 15d and 17d of the discharge side hole portions 15g and 17g, it is possible to reduce the pressure loss when the compressed fluid is introduced into the compression side hole portions 15f and 17f.
  • the discharge openings 15d and 17d of the discharge side hole portions 15g and 17g are reduced, it is possible to avoid the valve body 25 from being deformed (flexural deformation such as fitting to the discharge openings 15d and 17d) when the discharge openings 15d and 17d are closed by the valve body 25.
  • the end plate 15a of the fixed scroll 15 or the discharge cover 17 around the discharge openings 15d and 17d can be easily brought into contact with the valve body 25 with a sufficient area. Therefore, it is possible to easily ensure sufficient sealing property when the discharge openings 15d and 17d are closed by the valve body 25.
  • the compression side hole portions 15f and 17f and the discharge side hole portions 15g and 17g are made eccentric to communicate with each other, a part having a small opening area with an angular shape is likely to occur at the communication portions 15i and 17i.
  • the opening areas of the communication portions 15i and 17i between the compression side hole portions 15f and 17f and the discharge side hole portions 15g and 17g are formed to be equal to or greater than the cross-sectional areas of the discharge side hole portions 15g and 17g, the opening areas of the communication portions 15i and 17i can be sufficiently secured to reduce the pressure loss in the communication portions 15i and 17i, and a decrease in valve strength can be suppressed.
  • the compression side hole portions 15f and 17f and the discharge side hole portions 15g and 17g are not necessarily formed using a drill.
  • a drill for example, as illustrated in FIG. 4 , it is also possible to form the discharge side hole' portions 15g and 17g with an end mill.
  • the end plate 15a of the fixed scroll 15 or the discharge cover 17 may have the main body portions 35 and 37, and seating plate 31 detachably provided in the main body portions 35 and 37.
  • the seating plate 31 is disposed between the main body portions 35 and 37 and the valve body 25 at a position on which the valve body 25 is provided.
  • the seating plate 31 is made of a material harder than the main body portions 35 and 37.
  • the main body portions 35 and 37 are made of cast iron, and the seating plate 31 is made of metal such as carbon tool steel material (SK material).
  • the valve body 25 is made of, for example, stainless steel.
  • Compression side hole portions 15f and 17f are formed in the main body portion 35 and 37, and discharge side hole parts 15g and 17g are formed in the seating plate 31. That is, the communication portions 15i and 17i are provided between the seating plate 31 and the main body portions 35 and 37. Further, in the communication portions 15i and 17i, a chamfered portion 41 is formed on the opening edge portion on the compression side of the discharge side hole portions 15g and 17g which are the edge portions. Further, a chamfered portion 42 is formed on the opening edge portion on the discharge side of the compression side hole portions 15f and 17f.
  • the surface of the valve body 25 abuts on the seating plate 31 and is supported by the seating plate 31. Therefore, since the valve body 25 does not abut on the main body portions 35 and 37 at the time of opening and closing, breakage of the main body portions 35 and 37 can be avoided.
  • discharge side hole portions 15g and 17g can be provided on the seating plate 31, the discharge side hole portions 15g and 17g can be provided by being easily offset with respect to the compression side hole portions 15f and 17f.
  • the opening area can be increased at the portions of the chamfered portions 41 and 42, which leads to a further reduction in pressure loss. Further, the chamfered portions 41 and 42 may not be necessarily provided.
  • a center P3 of the discharge side hole portions 15g and 17g may not be disposed on a straight line which connects a center P1 of the fixed portion (bolt 30) of the one end 25a and a center P2 of the compression side hole portions 15f and 15f.
  • the compression side hole portions 15f and 17f and the discharge side hole portions 15g and 17g are formed in a circular form
  • the shapes of the compression side hole portions 15f and 17f, the discharge side hole portions 15g and 17g, the discharge ports 15c and 17c and the like are not particularly limited, and may be a long hole, an elliptical hole, a rectangular hole, or the like.

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

Claims (5)

  1. Verdichter (A), umfassend:
    ein Basisabschnitt (15, 17), der eine Druckseite (21) und eine Auslassseite (22) trennt;
    einen Auslassanschluss (15c, 17c), der in den Basisabschnitt (15, 17) eindringt; und
    einen Ventilkörper (25), bei dem ein Ende (25a) an dem Basisabschnitt (15, 17) befestigt ist, das andere Ende (25b) des Auslassanschlusses (15c, 17c) zugewandt ist, um den Auslassanschluss (15c, 17c) zu schließen, und wenn ein Druck auf der Druckseite (21) größer wird als ein Druck auf der Auslassseite (22), das andere Ende elastisch verformt wird, um den Auslassanschluss (15c, 17c) zu öffnen,
    wobei der Auslassanschluss (15c, 17c) einen verdichtungsseitigen Lochabschnitt (15f, 17f), der auf der Verdichtungsseite (21) bereitgestellt ist, und einen auslassseitigen Lochabschnitt (15g, 17g), der auf der Auslassseite (22) bereitgestellt ist, aufweist, wobei der auslassseitige Lochabschnitt (15g, 17g) durch einen Verbindungsabschnitt (15i, 17i), der an der Unterseite des verdichtungsseitigen Lochabschnitts (15f, 17f) und der Unterseite des auslassseitigen Lochabschnitts (15g, 17g) bereitgestellt ist, mit dem verdichtungsseitigen Lochabschnitt (15f, 17) in Verbindung ist, und der auslassseitige Lochabschnitt (15g, 17g) eine Auslassöffnung (15d, 17d) aufweist,
    dadurch gekennzeichnet, dass der auslassseitige Lochabschnitt (15g, 17g) an einem Endabschnitt auf der Auslassseite (22) einen Wulstabschnitt (15h, 17h) aufweist, wobei der Wulstabschnitt (15h, 17h) zu einer Seite gewölbt ist, die von dem einen Ende des Ventilkörpers (25), der an dem Basisabschnitt (15, 17) befestigt ist, weiter als eine innere Umfangsfläche des verdichtungsseitige Lochabschnitts (15f, 17f) in einer Draufsicht orthogonal zu der Mittellinie des auslassseitigen Lochabschnitts (15g, 17g) in einem Abschnitt einer inneren Umfangsfläche des auslassseitigen Lochabschnitts (15g, 17g) entfernt ist, und
    eine Öffnungsfläche des verdichtungsseitigen Lochabschnitts (15f, 17f) größer ist als eine Öffnungsfläche der Auslassöffnung (15d, 17d) des auslassseitigen Lochabschnitts (15g, 17g),
    und dass die Öffnungsfläche des Verbindungsabschnitts (15i, 17i), die die Fläche des Abschnitts ist, der von einer Grenzlinie (X) zwischen dem verdichtungsseitigen Lochabschnitt (15f, 17f) und dem auslassseitigen Lochabschnitt (15g, 17g) umgeben ist, gebildet ist, um gleich wie oder größer als die Querschnittsfläche des auslassseitigen Lochabschnitts (15g, 17g) ist.
  2. Verdichter (A) nach Anspruch 1, wobei der auslassseitige Lochabschnitt (15g, 17g) gebildet ist, um einen kleineren Durchmesser als der verdichtungsseitige Lochabschnitt (15f, 17f) aufzuweisen, und die Mitte des auslassseitigen Lochabschnitts (15g, 17g) auf einer Seite angeordnet ist, die von dem einen Ende des Ventilkörpers (25) weiter entfernt ist als die Mitte des verdichtungsseitigen Lochabschnitts (15f, 17f), und
    der Wulstabschnitt (15h, 17h) Teil der inneren Umfangsfläche des auslassseitigen Lochabschnitts (15g, 17g) ist.
  3. Verdichter (A) nach Anspruch 1 oder 2, wobei der Basisabschnitt (15, 17) einen Basisabschnitthauptkörper (35, 37), der aus Gusseisen gefertigt ist, und eine Sitzplatte (31) aufweist, die an einer Position, an der der Ventilkörper (25) bereitgestellt ist, an dem Basisabschnitthauptkörper (35) anbringbar und davon abnehmbar ist und die aus einem Kohlenstoff-Werkzeugstahlmaterial hergestellt ist, das härter ist als der Basisabschnitthauptkörper (35), und
    der verdichtungsseitige Lochabschnitt (15g, 17g) in der Sitzplatte (31) bereitgestellt ist.
  4. Verdichter (A) nach einem der Ansprüche 1 bis 3, wobei in dem Verbindungsabschnitt (15i, 17i) an einem Öffnungsrandabschnitt auf der Verdichtungsseite (21) des verdichtungsseitigen Lochabschnitts (15g, 17g), der der Randabschnitt ist, ein abgeschrägter Abschnitt (41) gebildet ist, und ein abgeschrägter Abschnitt (42) an einem Öffnungsrandabschnitt auf der Auslassseite (22) des verdichtungsseitigen Lochabschnitts (15f, 17f) gebildet ist.
  5. Verdichter (A) nach einem der Ansprüche 1 bis 4, wobei die Mitte des auslassseitigen Lochabschnitts (15g, 17g) in Bezug auf die Mitte des verdichtungsseitigen Lochabschnitts (15f, 17f) exzentrisch ist, und die Mitte des auslassseitigen Lochabschnitts (15g, 17g) weiter von dem feststehenden Ende (25a) des Ventilkörpers (25) entfernt ist als die Mitte des verdichtungsseitigen Lochabschnitts (15f, 17f).
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JPH0331597A (ja) * 1989-06-28 1991-02-12 Matsushita Refrig Co Ltd 回転圧縮機
SI1413758T1 (sl) * 2002-10-15 2006-06-30 Bitzer Kuehlmaschinenbau Gmbh Spiralni zgoscevalnik z lovilnikom olja

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JPS5851093U (ja) * 1981-10-05 1983-04-06 三菱電機株式会社 回転式電動圧縮機
JPH05106580A (ja) * 1991-10-14 1993-04-27 Daikin Ind Ltd 容積形圧縮機
JP2000110744A (ja) * 1998-09-30 2000-04-18 Fujitsu General Ltd スクロール圧縮機
JP2001099066A (ja) * 1999-09-28 2001-04-10 Sanyo Electric Co Ltd 冷媒圧縮機
US20060269433A1 (en) * 2005-05-31 2006-11-30 Skinner Robin G Discharge port for a scroll compressor
EP2565460B1 (de) * 2010-04-28 2019-06-26 Panasonic Corporation Rotationsverdichter
JP6147605B2 (ja) * 2013-08-02 2017-06-14 三菱重工業株式会社 圧縮機
KR102166427B1 (ko) * 2014-05-02 2020-10-15 엘지전자 주식회사 스크롤 압축기

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6179889A (ja) * 1984-09-26 1986-04-23 Matsushita Electric Ind Co Ltd 密閉形回転式電動圧縮機の吐出口装置
JPH0331597A (ja) * 1989-06-28 1991-02-12 Matsushita Refrig Co Ltd 回転圧縮機
SI1413758T1 (sl) * 2002-10-15 2006-06-30 Bitzer Kuehlmaschinenbau Gmbh Spiralni zgoscevalnik z lovilnikom olja

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EP3376032B8 (de) 2023-12-20
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JP2018155202A (ja) 2018-10-04
EP3376032C0 (de) 2023-11-15

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