WO2023166604A1 - 圧縮機 - Google Patents

圧縮機 Download PDF

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Publication number
WO2023166604A1
WO2023166604A1 PCT/JP2022/008847 JP2022008847W WO2023166604A1 WO 2023166604 A1 WO2023166604 A1 WO 2023166604A1 JP 2022008847 W JP2022008847 W JP 2022008847W WO 2023166604 A1 WO2023166604 A1 WO 2023166604A1
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WO
WIPO (PCT)
Prior art keywords
valve
reed valve
valve seat
convex portion
chamber
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.)
Ceased
Application number
PCT/JP2022/008847
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English (en)
French (fr)
Japanese (ja)
Inventor
奨 齊田
貴也 木本
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 Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2022/008847 priority Critical patent/WO2023166604A1/ja
Priority to JP2024504082A priority patent/JP7693085B2/ja
Publication of WO2023166604A1 publication Critical patent/WO2023166604A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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 disclosure relates to a compressor having a reed valve in a discharge hole of a compression mechanism.
  • Some compressors have a reed valve in the discharge hole of the compression mechanism that compresses the gas.
  • the reed valve is pushed up to open the discharge hole when the pressure in the compression chamber of the compression mechanism exceeds a certain level. At this time, the gas is discharged to the outside of the compression mechanism through the discharge hole. Further, the reed valve closes the discharge hole when the gas is discharged and the pressure in the compression chamber drops below a certain level, thereby preventing the discharged gas from returning to the compression chamber.
  • closing delay if the reed valve is not closed (hereinafter also referred to as closing delay) at the timing when the discharge space and the suction chamber communicate with each other in the compression mechanism, the discharged gas flows back from the discharge hole to the suction chamber. The back-flowing gas re-expands in the compression chamber, reducing the performance of the compressor.
  • Compressors have a variety of operating conditions, and the factors that affect reed valve closing delays, such as discharge gas flow rate and rotation speed, also change depending on the operating conditions. It is difficult to solve by just adjusting. Therefore, an effective means is to shape the flow path around the discharge hole into a shape that facilitates discharge but prevents reverse flow.
  • a compressor with a modified shape around the discharge hole there is a technique in which a plurality of valve seats contacting the reed valve are formed in a substantially concentric shape with the discharge hole on the bottom surface of the valve housing chamber formed so as to be recessed in the plate. (see, for example, Patent Document 1).
  • the valve seat portion provided around the discharge hole in Patent Document 1 has a second valve seat surface and a first valve seat surface provided outside the second valve seat surface via an annular groove. .
  • valve seat portion of Patent Document 1 is provided so that both the first valve seat surface and the second valve seat surface are in contact with the reed valve when the reed valve is closed.
  • the gas that is discharged and flows toward the outer peripheral side along the first valve seat surface and the second valve seat surface tends to flow horizontally or upward as it is. Therefore, when the gas is discharged, it is difficult for the gas to flow below the valve seat surface, i.e., to the bottom side of the valve chamber, and the escape of the discharged gas is restricted, so that the gas is less likely to be discharged from the discharge hole. Therefore, even if the compressor of Patent Document 1 can suppress the backflow of gas to the suction chamber by the double valve seat surface at the time of backflow, it is not configured to sufficiently discharge gas at the time of discharge. Machine performance may be degraded.
  • the present disclosure has been made to solve the problems described above, and aims to provide a compressor that suppresses deterioration in compressor performance due to deterioration in gas discharge performance.
  • a compressor according to the present disclosure includes a closed container, and a compression mechanism section installed in the closed container and provided with a compression chamber for compressing gas therein, wherein the compression mechanism section constitutes a part of the wall of the compression chamber and includes a plate formed with a discharge hole for discharging the gas compressed in the compression chamber to the outside of the compression chamber; and a plate covering the discharge side of the discharge hole.
  • a reed valve disposed on the plate and capable of freely opening and closing the discharge hole
  • the plate is formed on a surface opposite to the compression chamber so as to be recessed toward the compression chamber, and a valve seat surface which is formed on the bottom surface of the valve storage chamber at the periphery of the opening of the discharge hole so as to protrude from the bottom surface and contacts the reed valve in the closed state.
  • a groove is formed between the valve seat portion and the valve seat surface, protruding from the bottom surface of the valve accommodating chamber, and provided along the outer periphery of the valve seat portion, and is separated from the reed valve in the closed state. and are provided.
  • the convex portion protruding from the bottom surface of the valve housing chamber forms a groove with the valve seat surface and is provided along the outer periphery of the valve seat portion, and the convex portion is in the closed state. Since it is separated from the reed valve, the discharged gas also flows below the valve seat surface, that is, on the bottom surface side, in the valve accommodating chamber during discharge. Therefore, as compared with the conventional configuration, the space in which the discharged gas escapes is widened, so that the gas can be easily discharged from the discharge hole, and the deterioration of the performance of the compressor due to the deterioration of the gas discharge performance can be suppressed.
  • FIG. 1 is a longitudinal sectional view showing the configuration of a rotary compressor as an example of a compressor according to Embodiment 1;
  • FIG. FIG. 2 is a transverse sectional view showing the AA section of the compressor of FIG. 1;
  • FIG. 2 is a plan view of the upper plate in the compressor of FIG. 1 viewed from above in the axial direction;
  • FIG. 4 is a partial cross-sectional view showing the BB cross section of the plate of FIG. 3;
  • FIG. 4 is a partial cross-sectional view showing the CC cross section of the plate of FIG. 3;
  • FIG. 4 is a plan view showing a state in which a reed valve is arranged on the plate of FIG.
  • FIG. 3 4 is a partial cross-sectional view showing a BB cross section when the reed valve and the valve guard are fixed to the plate of FIG. 3 and the reed valve is in an open state;
  • FIG. 4 is a partial cross-sectional view showing a BB cross section when the reed valve and the valve guard are fixed to the plate of FIG. 3 and the reed valve is in a closed state;
  • FIG. FIG. 8 is an explanatory view showing the direction in which gas flows when the gas is discharged from the compression chamber P in FIG. 7;
  • FIG. 8 is an explanatory view showing the direction of gas flow when the gas flows back into the compression chamber P in FIG. 7;
  • FIG. 11 is a partial cross-sectional view when the reed valve and the valve guard are fixed to the upper plate of the compressor according to Embodiment 3 and the reed valve is in the open state;
  • FIG. 11 is a partial cross-sectional view showing a modification of the compressor according to Embodiment 3;
  • FIG. 12 is a partial cross-sectional view of the compressor according to Embodiment 4 when the reed valve and the valve guard are fixed to the upper plate and the reed valve is in the open state;
  • FIG. 11 is a partial cross-sectional view showing a modification of the compressor according to Embodiment 4;
  • FIG. 1 is a vertical cross-sectional view showing the configuration of a rotary compressor, which is an example of a compressor 100 according to Embodiment 1.
  • a rotary compressor as an example of a compressor 100.
  • Compressor 100 may include reed valve 80 in compression mechanism section 10, and may be, for example, a vane compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.
  • a positive displacement compressor in which the volume of the compression chamber changes is suitable as the compressor of the first embodiment.
  • the compressor 100 of Embodiment 1 can be used for compressing refrigerant gas in a heat pump device that utilizes the latent heat of refrigerant.
  • the compressor 100 includes a closed container 1 and a compression mechanism section 10 installed inside the closed container 1 .
  • the compression mechanism section 10 has a compression chamber P (see FIG. 2 described later) for compressing gas therein.
  • the pressure of the gas is higher than the atmospheric pressure, and the sealed container 1 is configured to hold the high-pressure gas.
  • the sealed container 1 in FIG. 1 is composed of a cylindrical portion 1b and two circular lids 1a1 and 1a2 arranged on both sides of the cylindrical portion 1b, and both ends of the cylinder are closed by the lids 1a1 and 1a2. have.
  • the cylindrical portion 1b of the sealed container 1 is connected to a suction pipe 60 for introducing the gas to be compressed inside and a discharge pipe 70 for discharging the compressed gas to the outside. Since the closed container 1 is generally installed in the outdoor unit of the heat pump device, legs (not shown) are installed on the lid 1a2 forming the bottom of the closed container 1 so that the closed container 1 can stand on its own.
  • An electric motor 20 that drives the compression mechanism 10 is housed inside the closed container 1 .
  • the electric motor 20 is composed of a rotor 22 and a stator 21 surrounding the rotor 22 .
  • a terminal 30 is attached to the lid 1a1 of the closed container 1, and the terminal 30 and the stator 21 are connected by a lead wire (not shown).
  • the compression mechanism 10 is arranged in the lower part of the cylindrical part 1b
  • the electric motor 20 is arranged in the upper part of the cylindrical part 1b
  • the terminal 30 is attached to the upper lid 1a1.
  • the stator 21 generates magnetic force due to current supplied from the outside through the terminals 30 .
  • the rotor 22 is rotated by the magnetic force generated by the stator 21 .
  • Rotating force of the rotor 22 is transmitted to the compression mechanism section 10 by the rotating shaft 11 .
  • the rotating shaft 11 is a rod-shaped member extending along the rotation center axis Ax of the rotor 22 .
  • the rotary shaft 11 is formed with an eccentric shaft portion 12 eccentric at a predetermined distance from the rotation center axis Ax of the rotor 22 in a part of its longitudinal direction.
  • the eccentric shaft portion 12 is a columnar portion having a central axis that is parallel to and displaced from the rotation central axis Ax by a certain distance.
  • an oil reservoir space Sb in which lubricating oil is stored.
  • the direction in which the rotating shaft 11 extends is defined as the axial direction, and the direction perpendicular to the axial direction is defined as the radial direction.
  • the compression mechanism 10 is a machine configured to reduce the volume of gas by power.
  • the compression mechanism section 10 includes a cylinder 13 having a cylinder chamber 13a therein, a piston 16 rolling inside the cylinder chamber 13a, plates 14 and 15 covering them from the axial direction, In addition, it is composed of a vane 18 (see FIG. 2 to be described later) or the like that partitions the cylinder chamber 13a.
  • the compression mechanism section 10 also includes a reed valve 80 installed on the plate 14 .
  • the cylinder chamber 13a is a cylindrical space coaxial with the rotating shaft 11.
  • the piston 16 is a cylindrical member smaller than the cylinder chamber 13a.
  • a cylindrical space is formed inside the piston 16, and the eccentric shaft portion 12 of the rotating shaft 11 is inserted into the space.
  • a slight gap (not shown) is provided between the piston 16 and the eccentric shaft portion 12 , and the piston 16 is rotatable around the center of the eccentric shaft portion 12 .
  • the cylinder chamber 13a is closed axially by plates 14 and 15. As shown in FIG.
  • a plurality of compression units consisting of the cylinder 13, the plate 14, the plate 15, the piston 16, the eccentric shaft portion 12, and the vane 18 may be provided in the axial direction. 4 shows an example of a formed configuration.
  • the two eccentric shaft portions 12 are installed in phases reversed by 180°.
  • one plate 15 can partition the two cylinder chambers 13a.
  • the space outside the piston 16 in the cylinder chamber 13a is closed on both sides in the axial direction by plates 14 and 15, and is used for gas compression.
  • this space is also referred to as a compressed space.
  • the sizes of the eccentric shaft portion 12 and the piston 16 are set so that the outer peripheral surface 16o of the piston 16 is in contact with part of the inner peripheral surface 13ai of the cylinder chamber 13a.
  • the piston 16 rolls in the cylinder chamber 13a such that the position where the outer peripheral surface 16o of the piston 16 and the inner peripheral surface 13ai of the cylinder chamber 13a are in contact with each other rotates due to the rotation of the rotary shaft 11 .
  • the height of the piston 16 in the axial direction (in the direction of the arrow Z) is made equal to the height of the cylinder chamber 13a so that the upper and lower ends of the piston 16 slide on the plates 14 and 15 when the piston 16 rolls. be.
  • a low-pressure gas is drawn into the compressor 100 through the suction pipe 60 in the refrigerant circuit of the heat pump device.
  • the cylinder 13 is formed with a suction hole 13c for drawing low-pressure gas to be compressed into the cylinder chamber 13a.
  • One of the suction holes 13c is connected to the suction pipe 60, and the other is connected to the inside of the cylinder chamber 13a.
  • the plate 14 has an annular portion facing the upper surface of the cylinder 13, and a substantially cylindrical bearing 14g provided in the central portion of the annular portion so as to extend upward.
  • a bearing hole 14h into which the rotating shaft 11 is inserted is formed in the bearing 14g, and the rotating shaft 11 rotates inside the bearing hole 14h.
  • either of the plates 14 and 15 may have the bearing 14g.
  • the bearing 14g can be a slide bearing, a rolling bearing, or the like.
  • a part of the annular portion of the plate 14 is formed with a discharge hole 14a (see FIG. 3 to be described later) for discharging the gas compressed in the compression space.
  • a channel groove 14b is formed.
  • the plate 14 is generally flat except for the bearing 14g and the portion where the channel groove 14b is formed.
  • the surface of the flat plate portion on the side of the cylinder chamber 13a is defined as a first surface 14x
  • the surface of the flat plate portion on the side opposite to the cylinder chamber 13a in the first embodiment, the bearing 14g is
  • the surface on the side where the second surface 14y is formed is defined as the second surface 14y.
  • the lower surface of the upper plate 14 is the first surface 14x
  • the upper surface of the upper plate 14 is the second surface 14y.
  • the first surface 14x of the plate 14 has a flat surface that slides on the upper end of the piston 16 in the axial direction. Note that if the first surface 14x is not a sliding surface due to the structure of the compressor 100, the first surface 14x may not necessarily be flat.
  • the bearing 14g is formed to protrude from the second surface 14y.
  • the channel groove 14b is formed to be recessed in a region including the discharge-side opening peripheral edge portion 14a1 (see FIG. 3) of the discharge hole 14a (see FIG. 3) on the second surface 14y.
  • the bearing hole 14 h and the discharge hole 14 a are provided through the plate 14 .
  • a reed valve 80 is installed on the second surface 14y side of the plate 14 so as to cover the discharge side of the discharge hole 14a.
  • the reed valve 80 opens and closes the discharge hole 14a.
  • a detailed configuration of the plate 14 will be described later.
  • a muffler 50 is installed on the second surface 14y side of the plate 14 so as to be fixed to the plate 14 .
  • the muffler 50 covers the plate 14 so that a space Sm is formed between the plate 14 and the muffler 50 .
  • High-pressure gas compressed in the cylinder chamber 13a is discharged into the space Sm formed between the plate 14 and the muffler 50 through a discharge hole 14a (see FIG. 3 described later) of the plate 14.
  • FIG. The muffler 50 has a muffler hole (not shown) that allows the high-pressure gas that has been compressed in the compression chamber P and flowed into the space Sm to flow into a space outside the muffler 50 (hereinafter also referred to as a discharge space So) in the sealed container 1. formed.
  • the purpose of the muffler 50 is to reduce noise by passing the discharged high-pressure gas through a space Sm having an appropriate volume. It is used for the purpose of preventing inflow through the hole 14a. Note that the muffler 50 may be omitted when there is no need to reduce noise and there is no risk of inflow of lubricating oil.
  • the muffler 50 is provided so as to cover the reed valve 80 installed on the plate 14 .
  • FIG. 1 shows a structural example in which the muffler 50 has a bell shape and the side surface of the annular portion of the plate 14 enters the lower portion of the muffler 50 . Note that the shape and installation location of the muffler 50 may be changed as appropriate. However, when the muffler 50 is made of a metal material, it is necessary to secure a certain or more insulation distance from the stator 21 .
  • a shaft hole in which the bearing 14g of the plate 14 is arranged is formed through the muffler 50 (the upper muffler 50 in the example of FIG. 1) on the side facing the electric motor 20 in the axial direction.
  • FIG. 2 is a cross-sectional view showing the AA section of the compressor 100 of FIG.
  • the cylinder 13 has an outer diameter larger than that of the plate 14 and is fixed to the inner surface of the closed container 1 (see FIG. 1).
  • a through hole 13f is formed in the outer peripheral portion of the cylinder 13 so as to communicate between the oil reservoir space Sb below the cylinder 13 and the discharge space So above the cylinder 13 .
  • the through hole 13f serves as a passage for the oil in the gas discharged into the discharge space So above the cylinder 13 to return to the oil reservoir space Sb below the cylinder 13.
  • the through hole 13f may be a recess formed in the outer peripheral surface of the cylinder 13 so as to form a gap with respect to the sealed container 1 (see FIG. 1).
  • a suction port 13d and a discharge port 13e are formed at different positions in the rotation direction (arrow R direction) in the cylinder chamber 13a.
  • the suction port 13 d is a port connected to the suction pipe 60 .
  • the suction port 13d is connected to the suction pipe 60 via a suction hole 13c radially penetrating through the cylinder 13 .
  • the cross-sectional shape of the suction hole 13c is circular, for example.
  • the cross-sectional shape of the suction hole 13c may not be circular, and may be oval or rectangular, for example. Also, the cross-sectional shape of the suction hole 13c may change along the direction of the flow path.
  • the discharge port 13e is a port connected to the discharge pipe 70 via the discharge space So inside the sealed container 1 shown in FIG.
  • FIG. 2 shows an example in which the discharge port 13e is locally formed as a depression in the inner peripheral surface 13ai of the cylinder chamber 13a.
  • the discharge port 13e is formed on the plate 14 side of the inner peripheral surface 13ai of the cylinder chamber 13a.
  • the discharge port 13e is provided apart from the vane groove 13b formed in the cylinder 13, but a part of the discharge port 13e may be formed so as to communicate with the vane groove 13b.
  • the gas compressed in the cylinder chamber 13a passes through the discharge port 13e, the plate 14, the muffler 50, and the discharge space So in the sealed container 1, and is discharged out of the sealed container 1 through the discharge pipe 70.
  • the positions of the suction port 13d and the discharge port 13e, and the configuration of the suction port 13d and the discharge port 13e may be changed as appropriate.
  • one discharge port 13e is formed on the plate 14 side in FIG.
  • a vane groove 13b is formed in the radial direction between the suction port 13d and the discharge port 13e of the cylinder chamber 13a.
  • a vane 18 is slidably inserted into the vane groove 13b.
  • the compression mechanism section 10 has a vane spring 19 that presses the vane 18 against the piston 16, and the axial upper and lower ends of the vane 18 slide on the sliding surfaces of the plates 14 and 15. It is said that The vane 18 partitions the space formed between the inner peripheral surface 13ai of the cylinder chamber 13a and the outer peripheral surface 16o of the piston 16 .
  • the vane 18 is configured to follow the rolling motion of the piston 16 and always come into contact with the outer peripheral surface 16 o of the piston 16 .
  • FIG. 2 shows a structural example in which a housing hole 13g for housing the vane spring 19 is formed in the cylinder 13, and a communication hole 13h for communicating the housing hole 13g and the discharge space So in the sealed container 1 is formed. .
  • Lubricating oil is supplied to the sliding groove of the vane 18 through the communication hole 13h, and the pressure inside the closed container 1 is applied to the opposite side of the vane 18 from the cylinder chamber 13a.
  • the compression space is a space between the inner peripheral surface 13ai of the cylinder chamber 13a and the outer peripheral surface 16o of the piston 16, and is sealed by being covered with plates 14 and 15 on both sides in the axial direction.
  • the compression space is partitioned by the vane 18 into a low pressure side suction chamber Q connected to the suction port 13d and a high pressure side compression chamber P connected to the discharge port 13e.
  • the suction port 13d and the discharge port 13e are located close to each other in the circumferential direction, but are located on opposite sides of the vane 18 from each other.
  • the suction chamber Q is a space surrounded by an inner peripheral surface 13ai of the cylinder chamber 13a, one surface of the vane 18, an outer peripheral surface 16o of the piston 16, and plates 14 and 15 covering both axial ends of the cylinder chamber 13a.
  • the compression chamber P is a space surrounded by an inner peripheral surface 13ai of the cylinder chamber 13a, the other surface of the vane 18, an outer peripheral surface 16o of the piston 16, and plates 14 and 15 covering both axial ends of the cylinder chamber 13a. .
  • the volumes of the suction chamber Q and the compression chamber P change as the piston 16 rolls. When the volume of the suction chamber Q expands due to the rolling of the piston 16, gas is sucked from the suction port 13d.
  • the compression mechanism section 10 has therein a compression chamber P for compressing gas and a suction chamber Q for sucking gas. and compression process are performed one by one.
  • the eccentric distance which is the distance between the center of the rotating shaft 11 and the center of the eccentric shaft portion 12, is the distance between the piston 16 and the inner peripheral surface 13ai of the cylinder chamber 13a.
  • a fixed distance The piston 16 rolls inside the cylinder 13 due to the eccentric rotation of the eccentric shaft portion 12 .
  • a contact portion S is formed between the outer peripheral surface 16o of the piston 16 and the inner peripheral surface 13ai of the cylinder chamber 13a in the axial direction (the arrow Z direction). As the piston 16 rolls, the contact portion S moves in the circumferential direction along the inner peripheral surface 13ai of the cylinder chamber 13a.
  • the contact portion S partitions the space between the inner peripheral surface 13ai of the cylinder chamber 13a and the outer peripheral surface 16o of the piston 16 together with the vane 18 .
  • the volume of the compression chamber P decreases as the position of the contact portion S moves due to rolling of the piston 16, and the pressure inside the compression chamber P increases.
  • the volume of the suction chamber Q expands as the position of the contact portion S moves due to the rolling of the piston 16, and sucks the external gas from the suction port 13d. Further, the position of the contact portion S moves, the volume of the compression chamber P becomes minimal, and when the contact portion S passes the vane 18 and the suction port 13d, the compression chamber P up to that point disappears.
  • a reciprocating compressor can be used for compression.
  • a compressor in which the chamber P and the suction chamber Q are temporally switched by using a valve or the like may be used.
  • FIG. 3 is a plan view of the upper plate 14 of the compressor 100 of FIG. 1 as seen from above in the axial direction (direction of arrow Z).
  • FIG. 4 is a partial sectional view showing the BB section of the plate 14 of FIG.
  • FIG. 5 is a partial sectional view showing the CC section of the plate 14 of FIG. 6 is a plan view showing a state in which the reed valve 80 is arranged on the plate 14 of FIG. 3.
  • FIG. FIG. 7 is a partial cross-sectional view showing the BB section when the reed valve 80 and the valve retainer 81 are fixed to the plate 14 of FIG. 3 and the reed valve 80 is in the open state.
  • FIG. 4 is a partial sectional view showing the BB section of the plate 14 of FIG.
  • the BB cross section is a cross section along a plane parallel to the rotation center axis Ax including the center axis 14ac of the discharge hole 14a and the center axis 14dc of the fixing hole 14d.
  • the BB cross section is also a plane along the longitudinal direction of the reed valve 80 .
  • a CC cross section is a cross section taken along a plane parallel to the rotation center axis Ax including the center axis 14ac of the discharge hole 14a and the center axis 14lc of the intermediate step portion 14l.
  • FIG. 1 the plate 14 forms part of the wall of the compression space in the compression mechanism section 10.
  • the upper plate 14 constitutes the upper wall of the upper compression space.
  • the channel groove 14b of the plate 14 includes a valve storage chamber 14j in which the reed valve 80 (see FIG. 6) is stored and a specific direction of the valve storage chamber 14j (example in FIG. 3).
  • a middle stage portion 14l shallower than the valve accommodating chamber 14j is provided on the front side in the rotational direction (on the left side in the drawing).
  • the discharge hole 14a is formed through the bottom wall 14jw of the valve housing chamber 14j in the plate 14, and is connected to the discharge port 13e of the cylinder 13 shown in FIG. . 2 and the discharge hole 14a of the plate 14 shown in FIG. are communicated.
  • the reed valve 80 is housed in the valve housing chamber 14j and opens and closes the discharge hole 14a.
  • the reed valve 80 is formed of a thin plate member.
  • the reed valve 80 has a circular valve tip portion 80a that covers the discharge hole 14a, a valve base portion 80b that is fixed to the plate 14, and a valve intermediate portion 80c that connects the valve tip portion 80a and the valve base portion 80b.
  • a fixing hole 80d into which a fastening part 82 (see FIG. 8) is inserted is formed in the valve base 80b.
  • the valve intermediate portion 80c and the valve base portion 80b are provided so as to extend in one direction from the valve tip portion 80a.
  • the valve housing chamber 14j is formed around the discharge hole 14a. and a strip-shaped second space 14j2 extending along the longitudinal direction of the reed valve 80 from the space 14j1. As shown in FIG. 7, the valve intermediate portion 80c and the valve base portion 80b of the reed valve 80 are arranged in the second space 14j2.
  • a fixing surface 14p higher than the bottom surface 14js of the valve housing chamber 14j is provided on the side of the second space 14j2 far from the first space 14j1, ie, the side on which the valve base 80b is arranged.
  • a fixing hole 14d into which a fastening part 82 (see FIG. 7) is inserted is formed in the fixing surface 14p.
  • the valve storage chamber 14j is formed in the plate 14 so that the height from the bottom surface 14js of the valve storage chamber 14j to the fixed surface 14p is the same as the height D1 of the valve seat surface 14f1 described later.
  • a valve guard 81 is arranged on the opposite side of the reed valve 80 to the discharge hole 14a (the upper side of the reed valve 80 in FIG. 7). are fixed to the plate 14 by fasteners 82 such as screws.
  • the valve base portion 80b is fixed to the fixing surface 14p of the plate 14 by the fastening member 82, and the reed valve 80 is elastically deformed, thereby opening and closing the discharge side of the discharge hole 14a by the valve tip portion 80a.
  • the reed valve 80 when the reed valve 80 is closed, the volume of the compression chamber P is reduced by the rolling of the piston 16 (see FIG.
  • the reed valve 80 opens as shown in FIG. 7, and the compressed gas is discharged into the space Sm through the discharge hole 14a.
  • the valve guard 81 regulates the maximum opening degree of the reed valve 80 by coming into contact with the valve intermediate portion 80c and the valve tip portion 80a of the reed valve 80 when the reed valve 80 is opened.
  • a valve seat portion 14f protruding from the bottom surface 14js of the valve accommodating chamber 14j is provided in an annular shape at the opening peripheral edge portion 14a1 of the discharge hole 14a.
  • the valve seat portion 14f has an annular valve seat surface 14f1 that contacts the reed valve 80 in the closed state, and an inclined surface 14f2 that connects the outer edge of the valve seat surface 14f1 and the bottom surface 14js of the valve storage chamber 14j.
  • the inclined surface 14f2 which is the outer peripheral surface of the valve seat portion 14f, has a cylindrical shape like a side surface of a truncated cone whose diameter increases as it approaches the first surface 14x from the second surface 14y side in the axial direction (arrow Z direction).
  • valve seat portion 14f is formed so that its outer diameter increases as it approaches the compression chamber P. As shown in FIG. Since the valve seat portion 14f has the inclined surface 14f2, the contact area between the plate 14 and the reed valve 80 at the opening peripheral edge portion 14a1 on the discharge side of the discharge hole 14a can be reduced. Sticking to the portion 14f can be reduced.
  • the reed valve 80 sticks to the valve seat portion 14f, the gas pressure in the compression chamber P required to open the reed valve 80 increases. That is, the inside of the compression chamber P is overcompressed, the required power increases, and the performance of the compressor 100 deteriorates.
  • the reed valve 80 and the valve seat portion 14f that is less likely to stick, deterioration in the performance of the compressor 100 can be suppressed.
  • the bottom surface 14js provided on the outer side of the inclined surface 14f2 is axially (in the direction of the arrow Z) so that the bottom surface 14js provided on the outside of the closed reed valve 80 does not come into contact with the first surface 14x and the valve seat surface 14f1. formed between
  • the bottom surface 14ls of the middle stage portion 14l of the flow channel 14b is formed between the bottom surface 14js of the valve accommodating chamber 14j and the second surface 14y in the axial direction (direction of arrow Z). be.
  • the flow channel 14b may have a plurality of intermediate step portions 14l.
  • the portion 14l may be omitted.
  • the inner side surface of the channel groove 14b formed in the plate 14 may be an inclined surface smoothly connecting the bottom surface 14js of the valve housing chamber 14j to the second surface 14y.
  • the inner side surface of the channel groove 14b is an inclined surface
  • the inner side surface may be a uniformly inclined inclined surface or an inclined surface whose inclination angle changes along the way.
  • the flow channel 14b may branch into a plurality of parts on the way.
  • the discharge hole 14a is provided through the plate 14 from the valve seat surface 14f1 to the first surface 14x in the axial direction (arrow Z direction), and has the same cross section in the axial direction (arrow Z direction).
  • the discharge-side opening peripheral edge portion 14 a 1 of the discharge hole 14 a is circular with an opening radius R 1 smaller than the radius R 2 of the valve tip portion 80 a of the reed valve 80 . If the discharge hole 14a is smaller than the valve tip portion 80a of the reed valve 80, the cross-sectional shape of the discharge hole 14a may not be circular.
  • the cross-sectional shape, size, and cross-sectional center position of the discharge hole 14a may change from the valve seat surface 14f1 side toward the first surface 14x.
  • the discharge hole 14a is preferably formed so as to overlap the recess when viewed from the axial direction (direction of arrow Z).
  • the discharge hole 14a only needs to be connected to the discharge port 13e, and the positions and shapes of the discharge port 13e and the discharge hole 14a are not limited to those described above.
  • valve tip portion 80a should be large enough to block the discharge hole 14a when the reed valve 80 is closed.
  • the valve tip portion 80a is formed larger than the discharge-side opening peripheral portion 14a1 of the discharge hole 14a so that the valve seat surface 14f1 and the valve tip portion 80a can come into contact with each other.
  • the valve tip portion 80a is too large, it interferes with the flow of gas discharged from the discharge hole 14a into the muffler 50 (see FIG. 1). It should be slightly larger than the outer edge.
  • valve intermediate portion 80c connecting the valve base portion 80b and the valve tip portion 80a functions as a leaf spring when the reed valve 80 opens and closes.
  • the closer the portion is to the valve base portion 80b, the greater the bending stress that acts upon opening and closing. Therefore, the thickness t80 (see FIG. 7) of the reed valve 80 and the width W80c (see FIG. 6) of the valve intermediate portion 80c are formed to dimensions that do not damage the reed valve 80 when opened and closed.
  • the thickness t80 of the reed valve 80 and the width W80c of the valve intermediate portion 80c are too large, the inside of the compression chamber P may be overcompressed when the reed valve 80 is opened, and the performance of the compressor 100 may deteriorate. , the size should be such that the reed valve 80 will not be damaged and its closing will not be delayed.
  • the valve guard 81 is formed of a plate-like member.
  • the valve guard 81 extends from one end of the tip portion 81a provided above the discharge hole 14a so as to form a gap with the reed valve 80 in the closed state, and the lead valve 81 between the plate 14 and the tip portion 81a. and a base portion 81b fixed to the plate 14 so as to sandwich the valve 80 therebetween.
  • the tip portion 81a of the valve guard 81 contacts the valve tip portion 80a and the valve intermediate portion 80c of the reed valve 80 in the open state. As shown in FIG.
  • the thickness t81 of the valve guard 81 is equal to the thickness t80 of the reed valve 80. It should be sufficiently thick compared to .
  • a fixing hole 81d into which the fastening part 82 is inserted is formed in the base portion 81b of the valve guard 81 .
  • the base portion 81 b of the valve guard 81 sandwiches the valve base portion 80 b of the reed valve 80 with the plate 14 .
  • the valve guard 81 is composed of a combination of an arcuately extending tip portion 81a and a linearly extending base portion 81b.
  • the tip portion 81a of the valve guard 81 is inclined with respect to the base portion 81b so that the gap between the valve guard 81 and the reed valve 80 increases toward the tip side of the valve guard 81 .
  • the shape of the valve guard 81 is not limited to the shape described above, and may be, for example, a shape combining a plurality of arcs. 7, a fixing hole 81d is provided in the base portion 81b of the valve guard 81, and the base portion 81b is fixed to the plate 14 together with the reed valve 80 by the fastening part 82.
  • the base portion 81b of the valve guard 81 is welded to the plate 14. may be fixed to
  • a through hole 81c is provided in the tip portion 81a of the valve guard 81 in a direction perpendicular to the surface with which the reed valve 80 contacts (the lower surface of the tip portion 81a in FIG. 8).
  • FIG. 9 is an explanatory diagram showing the direction of gas flow when the gas is discharged from the compression chamber P in FIG.
  • the operation of the compressor 100, the operation of the reed valve 80, and the flow of gas during discharge will be described below with reference to FIGS. 1 to 9.
  • FIG. When a current flows from the terminal 30 shown in FIG. 1 to the electric motor 20 and a magnetic force is generated in the stator 21 of the electric motor 20, the rotor 22 rotates due to the generated magnetic force, and the rotation shaft 11 rotates as the rotor 22 rotates. Rotate.
  • the piston 16 rolls inside the cylinder 13, and gas is sucked into the suction chamber Q (see FIG. 2) from outside the sealed container 1.
  • FIG. After that, as the piston 16 rolls, the suction chamber Q is switched to the compression chamber P, the volume of the compression chamber P is reduced, and the gas pressure is increased.
  • the pressure in the space (for example, space Sm) outside the plate 14 in the sealed container 1 is applied to the portion of the reed valve 80 (see FIG. 8) that closes the discharge hole 14a. and the pressure in the compression chamber P acts toward the compression chamber P side, so that the reed valve 80 maintains the closed state.
  • the piston 16 moves and the volume of the compression chamber P becomes smaller, and the pressure in the compression chamber P becomes sufficiently higher than the pressure in the space Sm outside the plate 14, the gas in the compression chamber P is released into the reed valve.
  • the force pushing up the reed valve 80 becomes larger than the force of the gas in the space Sm pressing the reed valve 80 toward the compression chamber P side, the reed valve 80 separates from the valve seat surface 14f1 (see FIG. 7), and the reed valve 80 begins to open. .
  • the reed valve 80 opens, the gas in the compression chamber P exits the compression mechanism 10 and flows into the space Sm.
  • the pressure in the compression chamber P decreases, and when the force applied to the reed valve 80 by the gas in the compression chamber P becomes smaller than the restoring force of the reed valve 80, the reed valve 80 closes.
  • By closing the reed valve 80 it is possible to suppress the gas in the space Sm from returning to the compression mechanism section 10 and being recompressed.
  • the arrows in FIG. 9 indicate the direction of gas flow.
  • gas from the compression chamber P passes through the discharge hole 14a and collides with the valve tip portion 80a.
  • the valve tip portion 80a collides with the valve tip portion 80a.
  • the main flow of gas thus formed is directed from the center of the valve tip portion 80a to the opposite side (left side in FIG. 9) to the direction toward the valve base portion 80b.
  • the center of the valve tip portion 80a to the valve base portion 80b the right side in FIG.
  • FIG. 9 shows only the flow of gas in the longitudinal direction of the reed valve 80, since the valve tip portion 80a is provided in a circular shape as shown in FIG. , along the lower surface of the reed valve 80 in 360° directions.
  • the main flow that has flowed along the lower surface of the reed valve 80 flows into the space Sm inside the muffler 50 along the inner surface of the flow channel 14b.
  • the gas that has flowed into the space Sm is discharged into the space (discharge space So) outside the muffler 50 inside the sealed container 1 through a muffler hole (not shown) provided in the muffler 50, and flows through the discharge pipe 70 into the compressor 100. It flows to the outside (for example, the condenser in a heat pump system).
  • the second surface 14y side of the plate 14 is provided with a protrusion 14n protruding from the bottom surface 14js of the valve storage chamber 14j.
  • the convex portion 14n is annularly provided so as to surround the discharge hole 14a.
  • the convex portion 14n does not need to be provided on the entire circumference of the valve seat portion 14f, and may be provided in an arc along a part of the outer circumference of the valve seat portion 14f.
  • the convex portion 14n includes an annular upper surface 14n1, a cylindrical inner peripheral surface 14n3 connecting the inner peripheral end of the upper surface 14n1 and the bottom surface 14js of the valve accommodating chamber 14j, and the outer peripheral end of the upper surface 14n1 and the valve accommodating chamber 14j. and a cylindrical outer peripheral surface 14n2 connected to the bottom surface 14js of the chamber 14j.
  • the upper surface 14n1 of the convex portion 14n is a surface parallel to the valve seat surface 14f1, and the inner peripheral surface 14n3 and the outer peripheral surface 14n2 of the convex portion 14n share the central axis 14ac of the discharge hole 14a. They are provided concentrically.
  • the inner peripheral surface 14n3 and the outer peripheral surface 14n2 are each provided substantially perpendicularly (that is, in the axial direction) to the bottom surface 14js.
  • the structure of the convex part 14n is not limited to said structure.
  • the convex portion 14n is provided outside the valve seat surface 14f1 with a distance from the outer peripheral end of the valve seat surface 14f1.
  • An annular groove 14r is formed between the .
  • the convex portion 14n is provided outside the inclined surface 14f2 of the valve seat portion 14f via the bottom surface 14js.
  • a groove 14r is formed between the valve seat surface 14f1 and the convex portion 14n by the inclined surface 14f2 of the valve seat portion 14f, the bottom surface 14js of the valve accommodating chamber 14j, and the inner peripheral surface 14n3 of the convex portion 14n.
  • the convex portion 14n may be provided outside the valve seat surface 14f1 so as to form a groove 14r with the valve seat surface 14f1. It may be provided so as to hang on the inclined surface 14f2.
  • a groove 14r having a c-shaped cross section is formed by the inclined surface 14f2 of the valve seat portion 14f and the inner peripheral surface 14n3 of the convex portion 14n.
  • the convex portion 14n is formed integrally with the plate 14, but the convex portion 14n may be formed separately from the plate 14 and fixed to the plate 14.
  • the convex portion 14n is formed such that the height D2 of the convex portion 14n is smaller than the height D1 of the valve seat portion 14f.
  • the height D1 of the valve seat portion 14f and the height D2 of the convex portion 14n are the axial heights relative to the bottom surface 14js of the valve accommodating chamber 14j. That is, the height D1 of the valve seat portion 14f is the height from the bottom surface 14js of the valve storage chamber 14j to the valve seat surface 14f1, and the height D2 of the convex portion 14n is the height from the bottom surface 14js of the valve storage chamber 14j. It is the height up to the upper surface 14n1 of the convex portion 14n. Therefore, as shown in FIG. 8, the closed reed valve 80 contacts the valve seat surface 14f1 but does not contact the convex portion 14n.
  • FIG. 10 is an explanatory diagram showing the direction of gas flow when the gas flows back into the compression chamber P in FIG. Arrows in FIG. 10 indicate directions in which gas flows when the reed valve 80 is delayed in closing. The gas flow in the channel groove 14b when the reed valve 80 is delayed in closing and the gas flows back will be described with reference to FIG.
  • the bottom flow path portion 14m into which the gas hardly flows when the gas is discharged also functions as an effective flow path when the gas flows backward.
  • the bottom channel portion 14m is a space formed between the valve seat surface 14f1 and the bottom surface 14js in the channel groove 14b.
  • the convex portion 14n extending from the bottom surface 14js of the valve accommodating chamber 14j toward the reed valve 80 becomes a wall that blocks the flow path of the gas that flows backward from the outside of the convex portion 14n toward the discharge hole 14a. Therefore, a vortex W is generated in a direction opposite to the flow toward the suction chamber Q on the outside of the convex portion 14n. As a result, the amount of backflow gas that reaches the discharge hole 14a is reduced, and the amount of backflow gas that enters the suction chamber Q is also reduced, so that the deterioration of the performance of the compressor 100 due to re-expansion of the backflow gas can be suppressed.
  • the greater the height D2 see FIG.
  • the height D2 of the convex portion 14n should be large within the range where D2 ⁇ D1 is satisfied.
  • the projection 14n shown in FIGS. 6 to 8 is formed to have a constant height D2 over the entire circumference, and the portion 14nc overlapping the closed reed valve 80 in plan view in FIG. Both the portion 14nc provided between the reed valve 80 in the closed state and the bottom surface 14js) and the portion 14ne exposed from the reed valve 80 in the closed state are formed at a position lower than the valve seat surface 14f1. .
  • the height D2 of the convex portion 14n does not need to be lower than the height D1 of the valve seat portion 14f over the entire circumference of the convex portion 14n. D2 should be smaller than the height D1 of the valve seat portion 14f.
  • a portion 14ne of the convex portion 14n exposed from the reed valve 80 may be provided so as to be higher than the valve seat portion 14f.
  • a portion 14ne of the convex portion 14n exposed from the reed valve 80 preferably has a height D2 large enough to fit within the bottom channel portion 14m (see FIG. 10).
  • the opening degree of the reed valve 80 becomes small, the ratio of the flow passage area where the convex portion 14n can block the flow of the reverse flow passage including the bottom flow passage portion 14m increases, and the performance of the compressor 100 is reduced. suppressing effect is increased.
  • the position or angle of the outer peripheral surface 14n2 of the convex portion 14n is particularly important in order to facilitate the generation of the vortex W outside the convex portion 14n as shown in FIG. If the position of the outer peripheral surface 14n2 of the convex portion 14n is far away from the discharge hole 14a, the effect of preventing the flow toward the suction chamber Q may be reduced. For example, when the width of the convex portion 14n is increased, the position of the outer peripheral surface 14n2 of the convex portion 14n becomes farther from the discharge hole 14a.
  • the distance Ln from the opening peripheral edge portion 14a1 of the discharge hole 14a to the outer peripheral surface 14n2 of the projection 14n is approximately the same as the opening radius R1 of the discharge hole 14a, or It is desirable to be about 1.5 times or less of R1. Also, when processing to install or form the projection 14n on the plate 14, the distance Ln from the opening peripheral edge 14a1 of the discharge hole 14a to the outer peripheral surface 14n2 of the projection 14n is approximately the same as the opening radius R1 of the discharge hole 14a. (For example, 0.5 times or more and 1.5 times or less of the opening radius R1) facilitates processing.
  • the outer peripheral surface 14n2 of the convex portion 14n is a surface that rises sharply from the bottom surface 14js of the valve accommodating chamber 14j and is substantially perpendicular to the bottom surface 14js. Specifically, it is desirable that the outer peripheral surface 14n2 of the convex portion 14n is provided at an angle of, for example, 70 degrees or more with respect to the bottom surface 14js of the valve accommodating chamber 14j.
  • the gas passing through the discharge hole 14a flows mainly from the compression chamber P in a direction perpendicular to the first surface 14x (upward in FIG. 9) along the discharge hole 14a.
  • the flow in the direction along the valve seat surface 14f1 perpendicular to this flow is small.
  • the gas discharged in the lateral direction at the time of gas discharge flows along the first valve seat surface and the second valve seat surface. Easy to flow.
  • the performance of the compressor may be degraded due to the restriction of the amount of gas that can be discharged at the time of discharge, compared to the configuration in which one valve seat surface is provided in the flow path.
  • the space on the bottom side of the valve seat surface that is, the bottom flow path portion 14m shown in FIG.
  • the compressor 100 includes a closed container 1 and a compression mechanism section 10 installed in the closed container 1 and provided with a compression chamber P for compressing gas therein.
  • the compression mechanism 10 includes a plate 14 forming a part of the wall of the compression chamber P, and a plate 14 having a discharge hole 14a for discharging the gas compressed in the compression chamber P to the outside of the compression chamber P.
  • a reed valve 80 is provided on the plate 14 so as to cover the discharge side and can open and close the discharge hole 14a.
  • the surface (second surface 14y) opposite to the compression chamber P is formed so as to be recessed toward the compression chamber P side, and a valve storage chamber 14j in which the reed valve 80 is accommodated;
  • a valve seat portion 14f having a valve seat surface 14f1 which is formed so as to protrude from the bottom surface 14js and contacts the reed valve 80 in the closed state is provided on the opening peripheral edge portion 14a1 of the discharge hole 14a at the bottom surface 14js of the valve 14j.
  • the plate 14 of the present disclosure protrudes from the bottom surface 14js of the valve accommodating chamber 14j, forms a groove 14r between it and the valve seat surface 14f1, and is provided along the outer periphery of the valve seat portion 14f.
  • a protruding portion 14n separated from the reed valve 80 is provided.
  • the convex portion 14n separated from the reed valve 80 in the closed state is provided. Since it becomes easier to flow into the flow path portion 14m than in the conventional case, the space in which the discharged gas escapes is widened, and the discharge performance of the gas from the discharge holes 14a is improved.
  • the convex portion 14n is provided away from the valve seat surface along the outer periphery of the valve seat portion 14f, even if gas flows backward due to delay in closing of the reed valve 80, the outer periphery of the valve seat portion 14f is At least in part, before the gas reaches the discharge hole 14a, it collides with the convex portion 14n to generate a vortex W, and the inflow of the gas into the compression chamber P is suppressed. Therefore, in the compressor 100 of the present disclosure, it is possible to suppress the reverse flow of gas while improving the discharge performance of the gas, so that deterioration of the performance of the compressor 100 can be suppressed more than in the past.
  • the convex portion 14n is provided in an annular shape along the outer periphery of the valve seat portion 14f. At least the height D2 of the portion 14nc of the convex portion 14n provided between the reed valve 80 and the bottom surface 14js in the closed state from the bottom surface 14js is greater than the height D1 of the valve seat surface 14f1 from the bottom surface 14js. small. As a result, a vortex W is generated around the entire periphery of the valve seat, making it difficult for the gas to flow back. Since the convex portion 14n does not come into contact with the reed valve 80, it is possible to obtain the above effect of improving the ejection property.
  • FIG. 11 is a plan view showing a state where reed valve 80 is arranged on upper plate 14 of compressor 100 according to the second embodiment.
  • FIG. 12 is a partial sectional view showing the DD section when the reed valve 80 and the valve guard 81 are fixed to the plate 14 of FIG. 11 and the reed valve 80 is in the open state.
  • the DD cross section is a cross section along a plane parallel to the rotation center axis Ax including the center axis 14ac of the discharge hole 14a and the center axis 14dc of the fixing hole 14d.
  • the DD section is also a plane along the longitudinal direction of the reed valve 80 .
  • the shape of the convex portion 14n is different from that in the first embodiment, and other configurations are the same as in the first embodiment.
  • the same reference numerals are given to the same parts as in the first embodiment, and the explanation will focus on the differences from the first embodiment.
  • the convex portions 14n have different heights in the circumferential direction.
  • the protrusion 14n is provided outside the valve seat surface 14f1 so as to form a groove 14r with the valve seat surface 14f1.
  • the convex portion 14n is provided in an annular shape so as to surround the entire circumference of the valve seat portion 14f.
  • a portion 14nc (in FIG. 12, a portion 14nc provided between the reed valve 80 and the bottom surface 14js in FIG. 12) covered by the reed valve 80 in the circumferential direction of the convex portion 14n and a portion 14nc exposed from the reed valve 80
  • the height is different between the portion 14ne where the Specifically, as shown in FIG. 12, the height D2 of the portion 14nc of the convex portion 14n covered by the reed valve 80 is smaller than the height D3 of the portion 14ne exposed from the reed valve 80 in the convex portion 14n.
  • the height D2 of the portion 14nc of the convex portion 14n covered by the reed valve 80 is smaller than the height D1 of the valve seat portion 14f, that is, the height of the valve seat surface 14f1.
  • the height D3 of the portion 14ne exposed from the reed valve 80 in the convex portion 14n is greater than the height D1 of the valve seat portion 14f.
  • each of the heights D1, D2 and D3 is the height in the axial direction based on the bottom surface 14js of the valve storage chamber 14j.
  • a step 14ns is provided at the boundary between the portion 14nc covered by the reed valve 80 and the portion 14ne exposed from the reed valve 80 in the circumferential direction of the convex portion 14n.
  • the height D2 of the portion 14nc should be smaller than the height D1 of the valve seat portion 14f so that the entire portion 14nc of the convex portion 14n covered with the reed valve 80 does not come into contact with the reed valve 80 . That is, it is sufficient that the convex portion 14n, including the portion 14nc covered with the reed valve 80, is provided so as to be separated from the reed valve 80 in the closed state. Therefore, as shown in FIG.
  • the step 14ns may be provided outside the reed valve 80 relative to the portion immediately below the reed valve 80 in the circumferential direction of the convex portion 14n. Also, instead of providing the step 14ns at the boundary between the two portions 14nc and 14ne having different heights, the portions 14nc and 14ne may be connected by a smooth inclined portion. Moreover, the convex portion 14n may be formed so that the height of the convex portion 14n varies along the circumferential direction.
  • the reed valve 80 in the closed state is in contact with the valve seat surface 14f1 as in the case of the first embodiment.
  • the portion 14n is not contacted. Therefore, in the second embodiment as well, the same effect as in the case of the first embodiment can be obtained.
  • the height D3 of the portion 14ne of the convex portion 14n exposed from the reed valve 80 in the closed state from the bottom surface 14js is equal to the height D3 of the valve seat surface 14f1. It is larger than the height D1 from the bottom surface 14js.
  • the height of the projection 14n from the bottom surface 14js of the valve housing chamber 14j can be partially increased without contact between the reed valve 80 and the projection 14n. barriers can be increased. Therefore, the backflow can be further reduced, and the performance of the compressor 100 is improved.
  • the gap between the reed valve 80 and the plate 14 becomes large especially on the tip side of the reed valve 80 in the longitudinal direction (the left side in FIG. 12).
  • the reverse flow can be efficiently reduced.
  • FIG. 13 is a plan view showing a modification of the plate 14 of the compressor 100 according to Embodiment 2.
  • FIG. 14 is a partial cross-sectional view showing the EE cross section when the reed valve 80 and the valve guard 81 are fixed to the plate 14 of FIG. 13 and the reed valve 80 is in the open state. 13 and 14, the
  • the height D2 of the convex portion 14n is smaller than the height D1 of the valve seat portion 14f.
  • the convex portion 14n is not provided directly below the reed valve 80 on the bottom surface 14js of the valve accommodating chamber 14j, but is provided only in a region exposed from the reed valve 80 in the closed state.
  • the height D2 may be greater than or equal to the height D1 of the valve seat portion 14f.
  • the convex portion 14n is provided only in the area exposed from the reed valve 80 in the closed state on the outer periphery of the valve seat portion 14f.
  • the convex portion 14n reduces the backflow while reducing the backflow. 14n members can be reduced.
  • FIG. 15 is a partial cross-sectional view when reed valve 80 and valve guard 81 are fixed to upper plate 14 of compressor 100 according to Embodiment 3 and reed valve 80 is in an open state.
  • the third embodiment is different from the first embodiment in that multiple projections 14n are provided on the outer side of the valve seat portion 14f.
  • the same reference numerals are given to the same parts as in the first embodiment, and the explanation will focus on the differences from the first embodiment.
  • the bottom surface 14js of the valve housing chamber 14j formed in the plate 14 is provided with multiple projections in the outward direction from the central axis 14ac of the discharge hole 14a. That is, two protrusions 14na and 14nb protruding from the bottom surface 14js are provided outside the valve seat portion 14f in the valve storage chamber 14j. In FIG. 15, multiple protrusions are provided only in a specific direction of the valve seat portion 14f. Specifically, similarly to the convex portion 14n of the first embodiment, the convex portion 14na is annularly provided outside the valve seat portion 14f so as to surround the entire circumference of the valve seat portion 14f.
  • the convex portion 14nb is provided in an arc shape outside the convex portion 14na.
  • the outer convex portion 14nb is provided in a region covered with the reed valve 80 on the bottom surface 14js between the inner convex portion 14na and the fixing surface 14p to which the reed valve 80 is fixed.
  • the height D2 of the outer convex portion 14nb and the inner convex portion 14na are the same and smaller than the height D1 of the valve seat portion 14f.
  • the shape and arrangement of the outer convex portion 14nb and the inner convex portion 14na are not limited to the above case.
  • the outer convex portion 14nb may be configured such that the height from the bottom surface 14js changes in the circumferential direction.
  • the two protrusions 14nb and 14na may be provided only in a specific direction.
  • three or more protrusions may be provided in the outward direction from the central axis 14ac of the discharge hole 14a.
  • FIG. 16 is a partial cross-sectional view showing a modification of the compressor 100 according to Embodiment 3.
  • FIG. 16 both the inner convex portion 14na and the outer convex portion 14nb are annularly formed so as to surround the entire circumference of the valve seat portion 14f.
  • the convex portion is provided in multiples on the bottom surface 14js in the outward direction from the central axis 14ac of the discharge hole 14a.
  • the barrier increases when the gas flows back into the compression chamber P, and the generation of the vortex W in the back flow is promoted, so that the back flow can be further reduced, and the performance of the compressor 100 is improved.
  • FIG. 17 is a partial cross-sectional view when reed valve 80 and valve guard 81 are fixed to upper plate 14 of compressor 100 according to Embodiment 4 and reed valve 80 is in an open state.
  • the cross-sectional shape of the convex portion 14n is different from that in the first embodiment, and the rest of the configuration is the same as in the first embodiment.
  • the same reference numerals are given to the same parts as in the first embodiment, and the explanation will focus on the differences from the first embodiment.
  • the convex portion 14n has a slope portion whose height from the bottom surface 14js gradually increases toward the outer peripheral side.
  • the height of the convex portion 14n is the height in the axial direction based on the bottom surface 14js of the valve accommodating chamber 14j.
  • the convex portion 14n has an outer peripheral surface 14n2 substantially perpendicular to the bottom surface 14js, an inner peripheral surface 14n3 inclined with respect to the outer peripheral surface 14n2, and has a right-angled triangular cross-sectional shape.
  • the inner peripheral surface 14n3 of the convex portion 14n forms the inclined portion of the convex portion 14n.
  • the height D2 of the convex portion 14n that is, the height from the bottom surface 14js of the valve chamber 14j to the top of the convex portion 14n is smaller than the height D1 of the valve seat portion 14f.
  • FIG. 18 is a partial cross-sectional view showing a modification of compressor 100 according to Embodiment 4.
  • the convex portion 14n has a slope portion whose height from the bottom surface 14js gradually increases toward the outer peripheral side.
  • the convex portion 14n has an outer peripheral surface 14n2 substantially perpendicular to the bottom surface 14js, an inner peripheral surface 14n3 lower than the outer peripheral surface 14n2 and substantially perpendicular to the bottom surface 14js, and an inclined upper surface 14n1, and has a trapezoidal shape.
  • the convex portion 14n of the modified example has a cross-sectional shape of That is, in the convex portion 14n of the modified example, the height D4 of the inner peripheral surface 14n3 is smaller than the height D5 of the outer peripheral surface 14n2.
  • the upper surface 14n1 of the convex portion 14n forms the slope of the convex portion 14n.
  • the height of the convex portion 14n that is, the height D5 of the outer peripheral surface 14n2 of the convex portion 14n is smaller than the height D1 of the valve seat portion 14f.
  • At least the convex portion 14n is provided between the closed reed valve 80 and the bottom surface 14js of the valve accommodating chamber 14j. It suffices if D5 ⁇ D1 in the portion where the That is, a portion may be formed in the circumferential direction of the convex portion 14n so that the height of the convex portion 14n is higher than the height D1 of the valve seat portion 14f.
  • the convex portion 14n is a slanted portion whose height from the bottom surface 14js gradually increases toward the outer peripheral side of the convex portion 14n (inner It has a peripheral surface 14n3 and an upper surface 14n1 in FIG.
  • the inclined portion of the convex portion 14n is formed such that the distance from the bottom surface 14js increases from the central axis 14ac of the discharge hole 14a toward the outside (that is, the outer peripheral side) so as to follow the gas flow during discharge. Therefore, even when the height of the convex portion 14n is increased, the effect on the ease of gas flow can be reduced.
  • the outer peripheral surface 14n2 of the convex portion 14n which is substantially perpendicular to the flow direction of the gas flowing backward along the bottom surface 14js of the valve housing chamber 14j, acts as a barrier to reduce the reverse flow. The effect is achievable. Therefore, the performance of the compressor 100 is improved.

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DE102024103000A1 (de) 2024-02-02 2025-08-07 Schaeffler Technologies AG & Co. KG Kältemittelverdichter

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0281973A (ja) * 1988-09-19 1990-03-22 Hitachi Ltd 圧縮機の吐出弁装置
JP2001082337A (ja) * 1999-09-16 2001-03-27 Toshiba Kyaria Kk 圧縮機の吐出弁装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0281973A (ja) * 1988-09-19 1990-03-22 Hitachi Ltd 圧縮機の吐出弁装置
JP2001082337A (ja) * 1999-09-16 2001-03-27 Toshiba Kyaria Kk 圧縮機の吐出弁装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102024103000A1 (de) 2024-02-02 2025-08-07 Schaeffler Technologies AG & Co. KG Kältemittelverdichter

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