Compressor

Abstract

This compressor is provided with a sealed container and a compression mechanism unit that is provided in the sealed container and has a compression chamber to compress gas therein. The compression mechanism unit includes: a plate that constitutes a part of the walls of the compression chamber and has an ejection hole formed therein to eject gas compressed inside the compression chamber to the outside of the compression chamber; and a reed valve that is disposed on the plate so as to cover the ejection side of the ejection hole and is capable of opening and closing the ejection hole. The plate is provided with: a valve accommodation chamber that is formed on a surface of the plate on the side opposite to the compression chamber so as to be recessed toward the compression chamber, and that accommodates the reed valve; a valve seat part that is formed on a bottom surface of the valve accommodation chamber so as to protrude from the bottom surface at the opening peripheral edge of the ejection hole, and that has a valve seat surface that contacts the reed valve in a closed state; and a protruding part that protrudes from the bottom surface of the valve accommodation chamber, is provided along the outer periphery of the valve seat part with a groove formed between the protruding part and the seat surface, and is separated from the reed valve in the closed state.

Description

Technical Field

[0001] The present disclosure relates to a compressor having a reed valve at a discharge hole of a compression mechanism section.

Background Art

[0002] In a compressor, there is one in which a reed valve is provided at a discharge hole of a compression mechanism section that compresses gas. The reed valve is pushed up and opens the discharge hole when the pressure in the compression chamber of the compression mechanism section becomes a certain level or higher. At this time, gas is discharged to the outside of the compression mechanism section through the discharge hole. Further, the reed valve closes the discharge hole when the gas is discharged and the pressure in the compression chamber becomes a certain level or lower, preventing the discharged gas from returning to the compression chamber. However, when the reed valve is not closed (hereinafter also referred to as a closing delay) at the timing when the discharge space and the suction chamber communicate with each other in the compression mechanism section, the discharged gas flows backward from the discharge hole into the suction chamber. The gas that has flowed backward expands again in the compression chamber, degrading the performance of the compressor.

[0003] There are various operating conditions for the compressor, and since factors that affect the closing delay of the reed valve such as the discharge gas flow rate and the rotational speed also change depending on the operating conditions, the problem of backflow is difficult to solve only by adjusting the specifications of the reed valve such as the spring constant. Therefore, it has been regarded as an effective means to make the flow path shape around the discharge hole a shape that is easy to discharge but difficult for backflow. As a compressor in which the shape around the discharge hole is changed, a technique is disclosed in which a plurality of valve seat surfaces with which the reed valve contacts are formed substantially concentrically with the discharge hole on the bottom surface of a valve housing chamber formed to be recessed in a 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.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] However, since the valve seat portion of Patent Document 1 is provided such that both the first valve seat surface and the second valve seat surface come into contact with the reed valve when the reed valve is closed, when the gas is discharged, the gas discharged and flowing toward the outer peripheral side along the first valve seat surface and the second valve seat surface easily flows horizontally or upward as it is. Therefore, when the gas is discharged, it is difficult for the gas to flow to the lower side of the valve seat surface, that is, the bottom surface side in the valve housing chamber, and the escape space for the discharged gas is limited, so it is difficult for the gas to be discharged from the discharge hole. Accordingly, even if the compressor of Patent Document 1 can suppress the backflow of gas into the suction chamber by the double valve seat surfaces during backflow, it is not configured to be able to sufficiently discharge the gas during discharge, and the performance of the compressor may deteriorate.

[0006] The present disclosure has been made to solve the above problems, and an object thereof is to provide a compressor that suppresses a decrease in the performance of the compressor due to a decrease in the dischargeability of gas.

Means for Solving the Problems

[0007] The compressor of the present disclosure is a compressor including a sealed container and a compression mechanism portion installed in the sealed container and provided with a compression chamber for compressing gas therein, wherein the compression mechanism portion 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 reed valve disposed on the plate so as to cover the discharge side of the discharge hole and capable of opening and closing the discharge hole. The plate is formed on the surface opposite to the compression chamber so as to be recessed toward the compression chamber side, and has a valve housing chamber for housing the reed valve, and a valve seat portion formed on the bottom surface of the valve housing chamber so as to protrude from the bottom surface at the opening peripheral edge of the discharge hole and having a valve seat surface that contacts the reed valve in the closed state. And a convex portion protruding from the bottom surface of the valve housing chamber, forming a groove between the convex portion and the valve seat surface and provided along the outer periphery of the valve seat portion, and being separated from the reed valve in the closed state. The aforesaid is provided and protrudes from the bottom surface of the valve housing chamber, forms a groove between the convex portion and the valve seat surface and is provided along the outer periphery of the valve seat portion, and is separated from the reed valve in the closed state. and the convex portion is provided only in a region exposed from the reed valve in the closed state on the outer periphery of the valve seat portion. Moreover, the compressor of the present disclosure is a compressor including a sealed container and a compression mechanism portion installed in the sealed container and provided with a compression chamber for compressing gas therein, wherein the compression mechanism portion constitutes a part of the wall of the compression chamber, and includes a plate in which a discharge hole for discharging the gas compressed in the compression chamber to the outside of the compression chamber is formed, and a reed valve disposed on the plate so as to cover the discharge side of the discharge hole and capable of opening and closing the discharge hole. The plate is formed to be recessed toward the compression chamber side on the surface opposite to the compression chamber, and has a valve accommodation chamber for accommodating the reed valve, and a valve seat portion formed on the bottom surface of the valve accommodation chamber so as to project from the bottom surface at the opening peripheral edge of the discharge hole and having a valve seat surface that contacts the reed valve in the closed state. A convex portion is provided so as to project from the bottom surface of the valve accommodation chamber, form a groove with the valve seat surface, and extend along the outer periphery of the valve seat portion, and be separated from the reed valve in the closed state. The convex portion is provided in multiple layers in a direction from the center of the discharge hole toward the outside on the bottom surface. Moreover, the compressor of the present disclosure is a compressor including a sealed container and a compression mechanism portion installed in the sealed container and provided with a compression chamber for compressing gas therein, wherein the compression mechanism portion constitutes a part of the wall of the compression chamber, and includes a plate in which a discharge hole for discharging the gas compressed in the compression chamber to the outside of the compression chamber is formed, and a reed valve disposed on the plate so as to cover the discharge side of the discharge hole and capable of opening and closing the discharge hole. The plate is formed to be recessed toward the compression chamber side on the surface opposite to the compression chamber, and has a valve accommodation chamber for accommodating the reed valve, and a valve seat portion formed on the bottom surface of the valve accommodation chamber so as to project from the bottom surface at the opening peripheral edge of the discharge hole and having a valve seat surface that contacts the reed valve in the closed state. A convex portion is provided so as to project from the bottom surface of the valve accommodation chamber, form a groove with the valve seat surface, and extend along the outer periphery of the valve seat portion, and be separated from the reed valve in the closed state. The convex portion has a slope surface whose height from the bottom surface gradually increases toward the outer peripheral side of the convex portion.

Advantages of the Invention

[0008] In the compressor of the present disclosure, a convex portion protruding from the bottom surface of the valve housing chamber forms a groove between the valve seat surface and is provided along the outer periphery of the valve seat portion, and the convex portion is separated from the reed valve in the closed state. Therefore, at the time of discharge, the discharged gas also flows to the lower side, that is, the bottom surface side, of the valve seat surface in the valve housing chamber. Thus, compared with the conventional configuration, the space for the discharged gas to escape becomes wider, so that the gas is easily discharged from the discharge hole, and a decrease in the performance of the compressor due to a decrease in the gas discharge property can be suppressed.

Brief Description of the Drawings

[0009]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14

Figure 15

Figure 16

Figure 17

Figure 18

Embodiments for Carrying Out the Invention

[0010] Hereinafter, embodiments of the compressor according to the present disclosure will be described with reference to the drawings. In different embodiments, common elements are denoted by the same reference numerals, and detailed descriptions made in other embodiments are omitted without repetition. Note that the drawings are schematically drawn, and the present disclosure is not limited only to the form of the drawings. Also, the present disclosure is not limited only to the embodiments described below. For example, combinations of different embodiments and configurations formed by partial substitutions may be used as long as there is no technical contradiction.

[0011] Embodiment 1. FIG. 1 is a longitudinal sectional view showing the configuration of a rotary compressor, which is an example of the compressor 100 according to Embodiment 1. As shown in FIG. 1, in Embodiment 1, a rotary compressor is used as an example of the compressor 100 for explanation. Note that the compressor 100 only needs to be provided with a reed valve 80 in the compression mechanism portion 10, and may be, for example, a vane compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like. As the compressor of Embodiment 1, a positive displacement compressor in which the volume of the compression chamber changes is suitable. The compressor 100 of Embodiment 1 can be used to compress the gas of the refrigerant in a heat pump apparatus that utilizes the latent heat of the refrigerant.

[0012] As shown in FIG. 1, the compressor 100 includes a sealed container 1 and a compression mechanism portion 10 installed in the sealed container 1. The compression mechanism portion 10 has a compression chamber P (see FIG. 2 described later) for compressing gas inside. Generally, in a heat pump apparatus that utilizes the latent heat of the gas-liquid phase change, the pressure of the gas is higher than the atmosphere, 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 lid-shaped lids 1a1 and 1a2 arranged on both sides of the cylindrical portion 1b, and has a shape in which both ends of the cylinder are closed by the lids 1a1 and 1a2. An intake pipe 60 for guiding the gas to be compressed into the sealed container 1 and a discharge pipe 70 for discharging the compressed gas to the outside are connected to the cylindrical portion 1b of the sealed container 1. Since the sealed container 1 is generally installed in the outdoor unit of the heat pump apparatus, legs (not shown) are installed on the lid 1a2 forming the bottom of the sealed container 1 so that the sealed container 1 can stand on its own.

[0013] An electric motor 20 for driving the compression mechanism portion 10 is housed inside the sealed 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 sealed container 1, and the terminal 30 and the stator 21 are connected by a lead wire (not shown). In the example shown in FIG. 1, the compression mechanism portion 10 is arranged at the lower part inside the cylindrical portion 1b, the electric motor 20 is arranged at the upper part inside the cylindrical portion 1b, and the terminal 30 is attached to the upper lid 1a1.

[0014] The stator 21 generates magnetic force by the current supplied from the outside through the terminal 30. The rotor 22 rotates by the magnetic force generated by the stator 21. The rotating force of the rotor 22 is transmitted to the compression mechanism portion 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. A part of the rotating shaft 11 in its longitudinal direction is formed with an eccentric shaft portion 12 that is eccentric by a predetermined distance from the rotation center axis Ax of the rotor 22. The eccentric shaft portion 12 is a columnar portion having a central axis that is displaced by a constant distance parallel to the rotation center axis Ax. Below the compression mechanism portion 10 of the sealed container 1, there is an oil sump space Sb for storing lubricating oil, and the lubricating oil is used for lubricating the bearings of the rotating shaft 11, the inside of the compression mechanism portion 10, etc. In the following description, the extending direction of the rotating shaft 11 will be described as the axial direction, and the direction perpendicular to the axial direction will be described as the radial direction.

[0015] The compression mechanism portion 10 is a machine configured to reduce the volume of gas by power. When the compressor 100 is a rotary compressor, the compression mechanism portion 10 includes a cylinder 13 having a cylinder chamber 13a inside, a piston 16 that rolls inside the cylinder chamber 13a, plates 14 and 15 that cover them from the axial direction, and a vane 18 (see FIG. 2 described later) that partitions the cylinder chamber 13a, etc. Further, the compression mechanism portion 10 includes a reed valve 80 installed on the plate 14.

[0016] The cylinder chamber 13a is a cylindrical space coaxial with the rotation axis 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 rotation axis 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 axial direction of the cylinder chamber 13a is closed by the plates 14 and 15. There may be a plurality of compression units including the cylinder 13, the plates 14, the plate 15, the piston 16, the eccentric shaft portion 12, and the vane 18 in the axial direction. In FIG. 1, a configuration example in which two compression units are formed in the axial direction (arrow Z direction) is shown. When two compression units are formed in the axial direction, the two eccentric shaft portions 12 are installed in phases inverted by 180°. In the configuration including two cylinder chambers 13a in the axial direction as shown in FIG. 1, the two cylinder chambers 13a can be partitioned by one plate 15.

[0017] The space outside the piston 16 in the cylinder chamber 13a is closed by the plate 14 and the plate 15 on both axial sides and is used for gas compression. Hereinafter, this space is also referred to as a compression space. Since the eccentric shaft portion 12 is inserted into the piston 16, the piston 16 is at an eccentric position with respect to the cylinder chamber 13a. 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 contacts a part of the inner peripheral surface 13ai of the cylinder chamber 13a. The piston 16 rolls in the cylinder chamber 13a so that the position where the outer peripheral surface 16o of the piston 16 contacts the inner peripheral surface 13ai of the cylinder chamber 13a rotates due to the rotation of the rotation axis 11. The height of the piston 16 in the axial direction (arrow Z direction) is set to be the same as 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.

[0018] In the refrigerant circuit of the heat pump device, low-pressure gas is sucked into the compressor 100 through the suction pipe 60. In the cylinder 13, a suction hole 13c for sucking the low-pressure gas to be compressed into the cylinder chamber 13a is formed. One side of the suction hole 13c is connected to the suction pipe 60, and the other side is connected to the inside of the cylinder chamber 13a.

[0019] The plate 14 has an annular portion facing the upper surface of the cylinder 13 and a substantially cylindrical bearing 14g provided so as to extend upward at the central portion of the annular portion. 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. In the configuration where only one compression unit is formed in the compressor 100, either the plate 14 or 15 may have the bearing 14g. For example, the plate 15 facing the lower surface of the cylinder 13 may have the bearing 14g. Further, the bearing 14g can be a sliding bearing, a rolling bearing, or the like.

[0020] A discharge hole 14a (see FIG. 3 described later) for discharging the gas compressed in the compression space is formed in a part of the annular portion of the plate 14, and a flow path groove 14b is formed around the discharge hole 14a including the discharge hole 14a. The plate 14 is generally flat except for the bearing 14g and the portion where the flow path groove 14b is formed. Hereinafter, the surface on the cylinder chamber 13a side of the flat portion is defined as the first surface 14x, and the surface on the side opposite to the cylinder chamber 13a (the surface on the side where the bearing 14g is formed in the first embodiment) of the flat portion is defined as the second surface 14y for explanation. In the example of FIG. 1, the lower surface of the upper plate 14 is the first surface 14x, and the upper surface of the upper plate 14 is the second surface 14y.

[0021] The first surface 14x of the plate 14 has a flat surface that slides against the axial upper end of the piston 16. Note that if the first surface 14x is not a sliding surface due to the structure of the compressor 100, the first surface 14x does not necessarily have to be flat. The bearing 14g is formed to protrude from the second surface 14y. The flow path groove 14b is formed to be recessed in a region on the second surface 14y that includes the discharge-side opening peripheral edge 14a1 (see FIG. 3) of the discharge hole 14a (see FIG. 3). The bearing hole 14h and the discharge hole 14a are provided through the plate 14.

[0022] On the second surface 14y side of the plate 14, a reed valve 80 is installed so as to cover the discharge side of the discharge hole 14a. The reed valve 80 opens and closes the discharge hole 14a. The detailed configuration of the plate 14 will be described later. On the second surface 14y side of the plate 14, a muffler 50 is installed in a fixed manner to the plate 14.

[0023] The muffler 50 covers the plate 14 so that a space Sm is formed between the muffler 50 and the plate 14. In the space Sm formed between the plate 14 and the muffler 50, the high-pressure gas compressed in the cylinder chamber 13a is discharged through the discharge hole 14a (see FIG. 3 to be described later) of the plate 14. The muffler 50 is formed with a muffler hole (not shown) for allowing the high-pressure gas compressed in the compression chamber P and flowing into the space Sm to flow into the space outside the muffler 50 in the sealed container 1 (hereinafter also referred to as the discharge space So). The muffler 50 is used for the purpose of reducing noise by allowing the discharged high-pressure gas to pass through a space Sm with an appropriate volume, and for the purpose of preventing the lubricating oil stored in the oil reservoir space Sb in the sealed container 1 from flowing into the cylinder chamber 13a through the discharge hole 14a. Note that the muffler 50 may be omitted when there is no need to reduce noise and there is no risk of lubricating oil flowing in.

[0024] The muffler 50 is provided so as to cover the reed valve 80 installed on the plate 14. FIG. 1 shows an example of a structure in which the muffler 50 has a bell shape and the side surface of the annular portion of the plate 14 enters the lower part 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 formed of a metal material, it is necessary to secure an insulation distance of a certain level or more from the stator 21. Further, in the muffler 50 on the side facing the motor 20 (the upper muffler 50 in the example of FIG. 1), a shaft hole through which the bearing 14g of the plate 14 is disposed is formed to penetrate in the axial direction.

[0025] FIG. 2 is a cross-sectional view showing an A-A cross section of the compressor 100 in FIG. 1. The cylinder 13 has an outer diameter larger than that of the plate 14 and is fixed to the inner surface of the sealed container 1 (see FIG. 1). A through hole 13f is formed in the outer peripheral portion of the cylinder 13 so as to communicate the oil sump 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 sump space Sb below the cylinder 13. Note that the through hole 13f may be a recess formed on the outer peripheral surface of the cylinder 13 so as to form a gap with the sealed container 1 (see FIG. 1).

[0026] In the cylinder chamber 13a, an intake port 13d and a discharge port 13e are formed at different positions in the rotational direction (arrow R direction). The intake port 13d is a port connected to the intake pipe 60. The intake port 13d is connected to the intake pipe 60 through an intake hole 13c penetrating the cylinder 13 in the radial direction. The cross-sectional shape of the intake hole 13c is, for example, circular. Note that the cross-sectional shape of the intake hole 13c does not have to be circular, and may be, for example, elliptical or rectangular. Further, the cross-sectional shape of the intake hole 13c may change along the flow path direction.

[0027] The discharge port 13e is a port that connects to the discharge pipe 70 via the discharge space So in the sealed container 1 shown in FIG. 1. FIG. 2 shows an example in which the discharge port 13e is formed as a depression in a local area of the inner peripheral surface 13ai of the cylinder chamber 13a. The discharge port 13e is formed on the plate 14 side on the inner peripheral surface 13ai of the cylinder chamber 13a. In the example of FIG. 2, 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 to communicate with the vane groove 13b. The gas compressed in the cylinder chamber 13a is discharged from the discharge port 13e, passes through the plate 14, the muffler 50, and the discharge space So in the sealed container 1 shown in FIG. 1, and is discharged outside the sealed container 1 from the discharge pipe 70. Note that the positions of the suction port 13d and the discharge port 13e, and the configurations of the suction port 13d and the discharge port 13e may be changed as appropriate. Also, in FIG. 2, one discharge port 13e is formed on the plate 14 side, but a plurality of discharge ports may be formed, or they may be formed on both sides of the plates 14 and 15.

[0028] Between the suction port 13d and the discharge port 13e of the cylinder chamber 13a, a vane groove 13b is formed in the radial direction. Inside the vane groove 13b, a vane 18 is slidably inserted. In the example shown in FIG. 2, the compression mechanism portion 10 has a vane spring 19 that presses the vane 18 against the piston 16, and the upper and lower ends of the vane 18 in the axial direction are configured to slide on the sliding surfaces of the plates 14 and 15. 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 always contact the outer peripheral surface 16o of the piston 16 following the rolling of the piston 16. For example, the vane 18 is biased by the vane spring 19 toward the center of the cylinder chamber 13a (the same position as the rotation center axis Ax), so that it always contacts the piston 16. However, when the lubricating oil and the condensed working fluid are compressed in the cylinder chamber 13a and the pressure in the cylinder chamber 13a abnormally increases, the vane 18 can separate from the piston 16 and relieve the pressure. 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 with the discharge space So in the sealed container 1 is formed. Through the communication hole 13h, lubricating oil is supplied to the sliding groove of the vane 18, and the pressure in the sealed container 1 is applied to the opposite side of the vane 18 from the cylinder chamber 13a.

[0029] The compression space is the 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 covering both axial sides with the plates 14 and 15. The compression space is partitioned by the vane 18 into a low-pressure suction chamber Q connected to the suction port 13d and a high-pressure 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.

[0030] The suction chamber Q is a space surrounded by the inner peripheral surface 13ai of the cylinder chamber 13a, one surface of the vane 18, the outer peripheral surface 16o of the piston 16, and the plates 14 and 15 covering both axial ends of the cylinder chamber 13a. The compression chamber P is a space surrounded by the inner peripheral surface 13ai of the cylinder chamber 13a, the other surface of the vane 18, the outer peripheral surface 16o of the piston 16, and the 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 due to the rolling of the piston 16. 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, and when the volume of the compression chamber P shrinks as the volume of the suction chamber Q expands, the gas is compressed. Thus, the compression mechanism portion 10 has a compression chamber P for compressing gas therein and a suction chamber Q for sucking gas, and one suction process and one compression process are each performed during one rotation of the rotating shaft 11.

[0031] The eccentricity, which is the distance between the center of the rotating shaft 11 and the center of the eccentric shaft portion 12, is set to a constant distance while a part of the outer peripheral surface 16o of the piston 16 is in contact with the inner peripheral surface 13ai of the cylinder chamber 13a and the piston 16 rolls. The piston 16 rolls inside the cylinder 13 due to the eccentric rotation of the eccentric shaft portion 12. A contact portion S that contacts each other along the axial direction (arrow Z direction) is formed between the outer peripheral surface 16o of the piston 16 and the inner peripheral surface 13ai of the cylinder chamber 13a. The contact portion S moves in the circumferential direction along the inner peripheral surface 13ai of the cylinder chamber 13a as the piston 16 rolls. 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.

[0032] Next, the compression operation caused by the rolling of the piston 16 will be briefly described. The volume of the compression chamber P decreases as the position of the contact portion S moves due to the rolling of the piston 16, and the pressure inside the compression chamber P increases. On the other hand, the volume of the suction chamber Q increases as the position of the contact portion S moves due to the rolling of the piston 16, and external gas is sucked in from the suction port 13d. Further, as the position of the contact portion S moves and the volume of the compression chamber P becomes extremely small, and when the contact portion S exceeds the positions of the vane 18 and the suction port 13d, the compression chamber P up to that point disappears. Further, when the position of the contact portion S moves and the suction chamber Q is no longer connected to the suction port 13d, the space that was the suction chamber Q switches to the compression chamber P connected to the discharge port 13e. On the other hand, on the side opposite to the compression chamber P with the contact portion S in between, a new suction chamber Q connected to the suction port 13d is formed. In this way, the suction and compression operations are performed so that the suction chamber Q and the compression chamber P are sequentially switched.

[0033] In addition, as the compressor 100 of Embodiment 1, in addition to a compressor configured such that the compression chamber P and the suction chamber Q are spatially partitioned and replaced like a rotary compressor, a compressor in which the compression chamber P and the suction chamber Q are switched temporally, such as by using a valve like a reciprocating compressor, may be used.

[0034] FIG. 3 is a plan view of the upper plate 14 in the compressor 100 of FIG. 1 as viewed from above in the axial direction (arrow Z direction). FIG. 4 is a partial cross-sectional view showing the B-B cross-section of the plate 14 of FIG. 3. FIG. 5 is a partial cross-sectional view showing the C-C cross-section of the plate 14 of FIG. 3. FIG. 6 is a plan view showing a state in which the reed valve 80 is disposed on the plate 14 of FIG. 3. FIG. 7 is a partial cross-sectional view showing the B-B cross-section when the reed valve 80 is in an open state with the reed valve 80 and the valve retainer 81 fixed to the plate 14 of FIG. 3. FIG. 8 is a partial cross-sectional view showing the B-B cross-section when the reed valve 80 is in a closed state with the reed valve 80 and the valve retainer 81 fixed to the plate 14 of FIG. 3. Here, the B-B cross-section is a cross-section in a plane parallel to the rotation center axis Ax and including the central axis 14ac of the discharge hole 14a and the central axis 14dc of the fixing hole 14d. The B-B cross-section is also a plane along the longitudinal direction of the reed valve 80. Further, the C-C cross-section is a cross-section in a plane parallel to the rotation center axis Ax and including the central axis 14ac of the discharge hole 14a and the central axis 14lc of the middle section 14l.

[0035] Hereinafter, based on FIGS. 1 to 8, the configurations of the plate 14 and the reed valve 80 will be described in detail. As shown in FIG. 1, the plate 14 forms a part of the wall of the compression space in the compression mechanism section 10. In the compressor 100 of FIG. 1, the upper plate 14 forms the upper wall of the upper compression space.

[0036] As shown in FIGS. 3 to 5, the flow path groove 14b of the plate 14 has a valve housing chamber 14j in which the reed valve 80 (see FIG. 6) is housed, and a middle section 14l that is shallower than the valve housing chamber 14j and is provided in a specific direction of the valve housing chamber 14j (in the example of FIG. 3, the front side in the rotation direction, the left side in the drawing). As shown in FIGS. 4 and 5, the discharge hole 14a is formed so as to penetrate 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. That is, the discharge port 13e of the cylinder 13 shown in FIG. 2 and the discharge hole 14a of the plate 14 shown in FIG. 4 communicate the compression chamber P and the inside of the flow path groove 14b formed on the second surface 14y side of the plate 14.

[0037] As shown in FIGS. 6 and 8, 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-like member. The reed valve 80 has a circular valve tip portion 80a that covers the discharge hole 14a, a valve base portion 80b 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 component 82 (see FIG. 8) is inserted is formed in the valve base portion 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.

[0038] As shown in FIGS. 3 and 4, the valve housing chamber 14j is formed around the discharge hole 14a and has a circular first space 14j1 in which the valve tip portion 80a (see FIG. 7) is disposed, and a strip-shaped second space 14j2 that extends from the first space 14j1 along the longitudinal direction of the reed valve 80. As shown in FIG. 7, the valve intermediate portion 80c and the valve base portion 80b of the reed valve 80 are disposed in the second space 14j2. On the side of the second space 14j2 that is far from the first space 14j1, that is, the side where the valve base portion 80b is disposed, a fixing surface 14p that is higher than the bottom surface 14js of the valve housing chamber 14j is provided. A fixing hole 14d into which a fastening component 82 (see FIG. 7) is inserted is formed in the fixing surface 14p. The valve housing chamber 14j is formed in the plate 14 such that the height from the bottom surface 14js of the valve housing chamber 14j to the fixing surface 14p is the same as the height D1 of a valve seat surface 14f1 described later.

[0039] As shown in FIGS. 7 and 8, a valve retainer 81 is disposed on the side opposite to the discharge hole 14a of the reed valve 80 (the upper side of the reed valve 80 in FIG. 7), and the reed valve 80 and the valve retainer 81 are fixed to the plate 14 by fastening components 82 such as screws. The valve base portion 80b is fixed to the fixing surface 14p of the plate 14 by the fastening component 82, and the reed valve 80 is elastically deformed, so that the discharge side of the discharge hole 14a is opened and closed by the valve tip portion 80a. In the state where the reed valve 80 is closed as shown in FIG. 8, when the volume of the compression chamber P is reduced by the rolling of the piston 16 (see FIG. 2) and the pressure difference between the gas in the compression chamber P and the gas in the space outside the plate 14 (that is, the space Sm and the discharge space So) becomes sufficiently large, 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 retainer 81 defines the maximum opening degree of the reed valve 80 by contacting the valve intermediate portion 80c and the valve tip portion 80a of the reed valve 80 when the reed valve 80 opens.

[0040] As shown in FIGS. 6 to 8, on the opening peripheral edge portion 14a1 of the discharge hole 14a at the bottom surface 14js of the valve housing chamber 14j, a valve seat portion 14f protruding from the bottom surface 14js is provided in an annular shape. 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 housing chamber 14j. The inclined surface 14f2, which is the outer peripheral surface of the valve seat portion 14f, has a cylindrical shape like the 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). That is, the valve seat portion 14f is formed so that the outer diameter increases as it approaches the compression chamber P. 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 discharge-side opening peripheral edge portion 14a1 of the discharge hole 14a can be reduced, and the adhesion of the reed valve 80 to the valve seat portion 14f via the lubricating oil can be reduced.

[0041] When the reed valve 80 adheres 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 becomes an over-compressed state, the required power increases, and the performance of the compressor 100 deteriorates. On the other hand, the present disclosure includes a valve seat portion 14f that is difficult to adhere to the reed valve 80, so that a decrease in the performance of the compressor 100 can be suppressed.

[0042] As shown in FIG. 8, the bottom surface 14js provided outside the inclined surface 14f2 is formed between the first surface 14x and the valve seat surface 14f1 in the axial direction (arrow Z direction) so as not to contact the closed reed valve 80.

[0043] Also, as shown in FIG. 5, the bottom surface 14ls of the middle section 14l in the flow path groove 14b is formed between the bottom surface 14js of the valve housing chamber 14j and the second surface 14y in the axial direction (arrow Z direction). In FIG. 3, only one middle section 14l is provided in a specific direction of the valve housing chamber 14j in the flow path groove 14b, but there may be a plurality of middle sections 14l in the flow path groove 14b, or there may be no middle section 14l. Further, the inner surface of the flow path groove 14b formed in the plate 14 may be an inclined surface that is smoothly connected from the bottom surface 14js of the valve housing chamber 14j to the second surface 14y. When the inner surface of the flow path groove 14b is an inclined surface, this inner surface may be an inclined surface with a uniform inclination or an inclined surface whose inclination angle changes midway. Also, the flow path groove 14b may branch into a plurality of paths midway.

[0044] In FIGS. 6 to 8, the discharge hole 14a is provided so as to penetrate axially (in the direction of arrow Z) from the valve seat surface 14f1 of the plate 14 to the first surface 14x, and has the same cross-section in the axial direction (in the direction of arrow Z). In FIG. 6, the opening peripheral edge portion 14a1 on the discharge side of the discharge hole 14a is circular with an opening radius R1 smaller than the radius R2 of the valve tip portion 80a of the reed valve 80. Note that 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 does not have to be circular. Further, the cross-sectional shape, size, and central position of the cross-section of the discharge hole 14a may change from the valve seat surface 14f1 side toward the first surface 14x. When the discharge port 13e is formed as a depression in the cylinder 13 as shown in FIG. 2, the discharge hole 14a may be formed so as to overlap the depression when viewed in the axial direction (in the direction of arrow Z). Note that the discharge hole 14a only needs to be connected to the discharge port 13e, and the positions of the discharge port 13e and the discharge hole 14a and the shapes of both are not limited to those described above.

[0045] As shown in FIGS. 6 and 8, the valve tip portion 80a only needs to have a size such that it can close the discharge hole 14a in the closed state of the reed valve 80. In FIG. 6, the valve tip portion 80a is formed larger than the opening peripheral edge portion 14a1 on the discharge side 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. However, if the valve tip portion 80a is too large, it will obstruct the flow of the gas discharged from the discharge hole 14a into the muffler 50 (see FIG. 1), so the size of the valve tip portion 80a is preferably slightly larger than the outer edge of the valve seat surface 14f1.

[0046] As shown in FIGS. 7 to 8, the 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 of the valve intermediate portion 80c is to the valve base portion 80b, the greater the bending stress acting during opening and closing. Therefore, the thickness t80 of the reed valve 80 (see FIG. 7) and the width W80c of the valve intermediate portion 80c (see FIG. 6) are formed to be dimensions such that the reed valve 80 does not break when opening and closing. However, if the thickness t80 of the reed valve 80 and the width W80c of the valve intermediate portion 80c are too large, there is a risk that the inside of the compression chamber P will be overcompressed when opening the reed valve 80, resulting in a decrease in the performance of the compressor 100. Therefore, it is advisable to set the dimensions such that the reed valve 80 does not break and there is no delay in closing.

[0047] As shown in FIG. 8, the valve retainer 81 is formed of a plate-like member. The valve retainer 81 has a tip portion 81a provided above the discharge hole 14a so as to form a gap with the closed reed valve 80, and a base portion 81b that extends from one end of the tip portion 81a and is fixed to the plate 14 so as to sandwich the reed valve 80 between the base portion 81b and the plate 14. The tip portion 81a of the valve retainer 81 contacts the valve tip portion 80a and the valve intermediate portion 80c of the open reed valve 80. As shown in FIG. 7, when the reed valve 80 is in the open state, a collision force of the reed valve 80 acts on the valve retainer 81. Therefore, the thickness t81 of the valve retainer 81 is preferably made sufficiently thicker than the thickness t80 of the reed valve 80. A fixing hole 81d into which a fastening component 82 is inserted is formed in the base portion 81b of the valve retainer 81. The base portion 81b of the valve retainer 81 sandwiches the valve base portion 80b of the reed valve 80 between the base portion 81b and the plate 14. In the example shown in FIG. 6, the valve retainer 81 is composed of a combination of a tip portion 81a extending in an arc shape and a base portion 81b extending in a straight line. The tip portion 81a of the valve retainer 81 is inclined with respect to the base portion 81b so that the gap with the reed valve 80 becomes larger toward the tip side of the valve retainer 81.

[0048] Note that the shape of the valve retainer 81 is not limited to the above shape, and for example, it may be a shape combining a plurality of arcs. Further, in FIG. 7, a fixing hole 81d is provided in the base portion 81b of the valve retainer 81, and the base portion 81b together with the reed valve 80 is fixed to the plate 14 by a fastening component 82, but the base portion 81b of the valve retainer 81 may be fixed to the plate 14 by welding.

[0049] Further, a through hole 81c is provided in the tip portion 81a of the valve retainer 81 in a direction perpendicular to the surface (the lower surface of the tip portion 81a in FIG. 8) with which the reed valve 80 contacts. By providing the through hole 81c, the contact area between the reed valve 80 and the valve retainer 81 can be reduced, and the adhesion of the reed valve 80 to the valve retainer 81 via the lubricating oil can be suppressed.

[0050] FIG. 9 is an explanatory diagram showing the direction in which gas flows when gas is discharged from the compression chamber P in FIG. 7. Hereinafter, with reference to FIGS. 1 to 9, the operation of the compressor 100, the operation of the reed valve 80, and the gas flow at the time of discharge will be described. When an electric 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 rotating shaft 11 rotates along with the rotation of the rotor 22. When the rotating shaft 11 rotates, 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. Thereafter, as the piston 16 rolls, the suction chamber Q is switched to the compression chamber P, the volume of the compression chamber P decreases, and the pressure of the gas increases.

[0051] Here, when the volume of the compression chamber P is large, a force due to the differential pressure between the pressure in the space (e.g., space Sm) outside the plate 14 in the sealed container 1 and the pressure in the compression chamber P acts toward the compression chamber P on the portion closing the discharge hole 14a of the reed valve 80 (see FIG. 8), so that the reed valve 80 maintains the closed state. Thereafter, when the piston 16 moves and the volume of the compression chamber P decreases, and the pressure in the compression chamber P becomes sufficiently higher than the pressure in the space Sm outside the plate 14, the force with which the gas in the compression chamber P pushes up the reed valve 80 becomes larger than the force with which the gas in the space Sm presses the reed valve 80 toward the compression chamber P, the reed valve 80 separates from the valve seat surface 14f1 (see FIG. 7), and the reed valve 80 begins to open. When the reed valve 80 opens, the gas in the compression chamber P exits from the compression mechanism portion 10 and flows into the space Sm. When the gas in the compression chamber P flows out, the pressure in the compression chamber P decreases, and when the force received by the reed valve 80 from the gas in the compression chamber P becomes smaller than the restoring force of the reed valve 80, the reed valve 80 closes. By the reed valve 80 closing, it is possible to suppress the gas in the space Sm from returning to the compression mechanism portion 10 and being recompressed.

[0052] The arrow in Fig. 9 indicates the direction in which the gas flows. As shown in Fig. 9, when the reed valve 80 is open, the gas from the compression chamber P passes through the discharge hole 14a and impinges on the valve tip 80a. At this time, in the open reed valve 80, the valve tip 80a is inclined with respect to the first surface 14x so as to be far from the valve base 80b with respect to the first surface 14x. Therefore, the main flow of the gas impinging on the valve tip 80a is directed to the side opposite to the direction facing the valve base 80b from the center of the valve tip 80a (the left side in Fig. 9). On the other hand, in the direction from the center of the valve tip 80a to the valve base 80b (the right side in Fig. 9), the remaining gas that cannot be completely discharged as the main flow flows as a sub-flow. Note that Fig. 9 shows only the gas flow in the longitudinal direction of the reed valve 80. However, as shown in Fig. 6, since the valve tip 80a is provided in a circular shape, the discharged gas flows in a 360° direction along the lower surface of the reed valve 80 from the center of the valve tip 80a. The main flow that has flowed along the lower surface of the reed valve 80 flows into the space Sm in the muffler 50 along the inner surface of the flow path groove 14b. The gas that has flowed into the space Sm is discharged into the space (discharge space So) outside the muffler 50 in the sealed container 1 through a muffler hole (not shown) provided in the muffler 50, and flows outside the compressor 100 (for example, into a condenser in a heat pump device) through the discharge pipe 70.

[0053] Incidentally, when the contact portion S shown in Fig. 2 moves near the vane 18 and the discharge port 13e and the suction chamber Q communicate with each other, and the reed valve 80 shown in Fig. 9 is not closed, that is, when the reed valve 80 closes late, the gas in the space Sm outside the plate 14 flows back into the suction chamber Q. Once the discharged gas flows back into the suction chamber Q, the gas is recompressed, so the performance of the compressor 100 deteriorates. Hereinafter, based on Figs. 6 to 8, a structure for suppressing the backflow of gas will be described.

[0054] As shown in Fig. 7, on the second surface 14y side of the plate 14, a convex portion 14n protruding from the bottom surface 14js of the valve housing chamber 14j is provided. In the example shown in Fig. 6, the convex portion 14n is provided in an annular shape so as to surround the discharge hole 14a. Note that 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 shape along a part of the outer circumference of the valve seat portion 14f.

[0055] In FIG. 7, the convex portion 14n has 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 accommodation chamber 14j, and a cylindrical outer peripheral surface 14n2 connecting the outer peripheral end of the upper surface 14n1 and the bottom surface 14js of the valve accommodation chamber 14j. In FIG. 7, 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 are provided concentrically with the central axis 14ac of the discharge hole 14a as a common axis. In the cross-section of FIG. 7, the inner peripheral surface 14n3 and the outer peripheral surface 14n2 are each provided substantially perpendicular to (i.e., in the axial direction) the bottom surface 14js. Note that the configuration of the convex portion 14n is not limited to the above configuration.

[0056] As shown in FIGS. 6 and 7, the convex portion 14n is provided outside the valve seat surface 14f1 at a distance from the outer peripheral end of the valve seat surface 14f1, and an annular groove 14r is formed between the valve seat surface 14f1 and the upper surface 14n1 of the convex portion 14n. In FIGS. 6 and 7, 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 accommodation chamber 14j, and the inner peripheral surface 14n3 of the convex portion 14n.

[0057] Note that the convex portion 14n only needs to be provided outside the valve seat surface 14f1 so as to form a groove 14r between the convex portion 14n and the valve seat surface 14f1. For example, a part of the convex portion 14n may be provided so as to overlap the inclined surface 14f2 of the valve seat portion 14f. In this case, 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. Also, in FIG. 7, the convex portion 14n is integrally formed with the plate 14, but the convex portion 14n may be formed separately from the plate 14 and fixed to the plate 14.

[0058] Also, as shown in FIG. 7, 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. Here, the height D1 of the valve seat portion 14f and the height D2 of the convex portion 14n are the axial heights with respect to the bottom surface 14js of the valve accommodation chamber 14j, respectively. That is, the height D1 of the valve seat portion 14f is the height from the bottom surface 14js of the valve accommodation 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 accommodation chamber 14j 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.

[0059] FIG. 10 is an explanatory diagram showing the direction in which gas flows when gas flows backward into the compression chamber P in FIG. 7. The arrow in FIG. 10 indicates the direction in which gas flows when the reed valve 80 closes slowly. Based on FIG. 10, the gas flow in the flow path groove 14b when the reed valve 80 closes slowly and gas flows backward will be described.

[0060] Since the surface of the plate 14 excluding the first surface 14x is covered with the same high-pressure gas as that in the sealed container 1 and the discharge space So, when the reed valve 80 closes slowly, gas flows backward from all directions into the discharge hole 14a along the surface on the second surface 14y side of the plate 14. In the flow path groove 14b, the bottom flow path portion 14m, where gas hardly flows in when gas is discharged, also functions as an effective flow path when gas flows backward. Here, the bottom flow path portion 14m is a space formed between the valve seat surface 14f1 and the bottom surface 14js in the flow path groove 14b.

[0061] When the gas flows backward, the convex portion 14n extending from the bottom surface 14js of the valve housing chamber 14j toward the reed valve 80 side becomes a wall that stands in the flow path of the gas flowing backward from the outside of the convex portion 14n toward the discharge hole 14a. Therefore, a vortex W is generated outside the convex portion 14n in a direction opposite to the flow toward the suction chamber Q. As a result, the amount of the backward-flowing gas reaching the discharge hole 14a decreases, so that the amount of the backward-flowing gas entering the suction chamber Q also decreases, and a decrease in the performance of the compressor 100 due to the re-expansion of the backward-flowing gas can be suppressed. The greater the height D2 (see FIG. 8) of the convex portion 14n, the greater the effect of inhibiting the backward flow. Therefore, in the portion 14nc provided between the reed valve 80 in the closed state and the bottom surface 14js of the valve housing chamber 14j in the convex portion 14n, it is preferable to increase the height D2 of the convex portion 14n within the range satisfying D2 < D1.

[0062] In the convex portion 14n illustrated in FIGS. 6 to 8, it is formed so as to have a constant height D2 over the entire circumference, and a portion 14nc that overlaps the reed valve 80 in the closed state in the plan view of FIG. 6 (that is, the portion 14nc provided between the reed valve 80 in the closed state and the bottom surface 14js in FIG. 8) and a portion 14ne exposed from the reed valve 80 in the closed state are both formed at positions lower than the valve seat surface 14f1. Note that it is not necessary for the height D2 of the convex portion 14n to be lower than the height D1 of the valve seat portion 14f over the entire circumference of the convex portion 14n. It is sufficient that at least the height D2 of the portion 14nc covered by the reed valve 80 in the convex portion 14n is smaller than the height D1 of the valve seat portion 14f. The 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. The portion 14ne of the convex portion 14n exposed from the reed valve 80 is preferably increased in height D2 within the range that fits into the bottom flow path portion 14m (see FIG. 10). In particular, when the opening degree of the reed valve 80 decreases, the ratio of the flow path area where the convex portion 14n can inhibit the flow in the backward-flow path including the bottom flow path portion 14m increases, and the effect of suppressing the decrease in the performance of the compressor 100 becomes greater.

[0063] As shown in FIG. 10, in order to easily generate a vortex W outside the convex portion 14n, in particular, the position or angle of the outer peripheral surface 14n2 of the convex portion 14n is important. If the position of the outer peripheral surface 14n2 of the convex portion 14n is greatly separated 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. Therefore, although it depends on the size of the valve seat portion 14f, it is desirable that the distance Ln from the opening peripheral edge portion 14a1 of the discharge hole 14a to the outer peripheral surface 14n2 of the convex portion 14n is approximately the same as the opening radius R1 of the discharge hole 14a or is about 1.5 times or less of the opening radius R1. Also, even during the processing of installing or forming the convex portion 14n on the plate 14, the processing is easy if the distance Ln from the opening peripheral edge portion 14a1 of the discharge hole 14a to the outer peripheral surface 14n2 of the convex portion 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). Further, the outer peripheral surface 14n2 of the convex portion 14n is preferably a surface that rises steeply from the bottom surface 14js of the valve housing 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 housing chamber 14j.

[0064] Incidentally, when the gas is discharged as shown in FIG. 9, the gas passing through the discharge hole 14a mainly flows out along the discharge hole 14a in a direction perpendicular to the first surface 14x from the compression chamber P (upward in FIG. 9), and the flow in a direction along the valve seat surface 14f1 perpendicular to this flow (lateral direction in FIG. 9) is small. In the configuration where the valve seat surface is provided in a double structure as in the conventional case, the gas discharged laterally during gas discharge flows along the first valve seat surface and the second valve seat surface, so it easily flows in the horizontal direction. Therefore, in the conventional configuration, when the gas is discharged, it is difficult for the gas to flow into the space on the bottom surface side of the valve seat surface (i.e., the bottom flow path portion 14m shown in FIG. 10), so the escape space for the discharged gas is limited. Therefore, in the conventional compressor, compared with the configuration in which one valve seat surface is provided in the flow path, the amount of gas that can be discharged during discharge is limited, which may reduce the performance of the compressor. In the conventional compressor, the space on the bottom surface side of the valve seat surface (i.e., the bottom flow path portion 14m shown in FIG. 10) is not a flow path when the gas is discharged from the compression chamber P, and in this space, the gas existing in the muffler stays, or a part of the main flow along the reed valve 80 collides with the flow path groove 14b to form a vortex.

[0065] On one hand, the compressor 100 according to Embodiment 1 includes a sealed container 1 and a compression mechanism unit 10 installed in the sealed container 1 and provided with a compression chamber P for compressing gas therein. The compression mechanism unit 10 includes a plate 14 that forms a part of the wall of the compression chamber P and has a discharge hole 14a formed therein for discharging the gas compressed in the compression chamber P to the outside of the compression chamber P, and a reed valve 80 that is disposed on the plate 14 so as to cover the discharge side of the discharge hole 14a and is capable of opening and closing the discharge hole 14a. The plate 14 is formed with a valve housing chamber 14j that is recessed toward the compression chamber P on the surface (second surface 14y) opposite to the compression chamber P and houses the reed valve 80, and a valve seat portion 14f that is formed on the bottom surface 14js of the valve housing chamber 14j so as to protrude from the bottom surface 14js to the opening peripheral edge portion 14a1 of the discharge hole 14a and has a valve seat surface 14f1 that contacts the reed valve 80 in the closed state. Further, the plate 14 of the present disclosure is provided with a convex portion 14n that protrudes from the bottom surface 14js of the valve housing chamber 14j, forms a groove 14r between the convex portion 14n and the valve seat surface 14f1, and is provided along the outer periphery of the valve seat portion 14f and is separated from the reed valve 80 in the closed state.

[0066] In the compressor 100 of the present disclosure, by providing the convex portion 14n that is separated from the reed valve 80 in the closed state, when discharging, the discharged gas flows more easily into the bottom flow path portion 14m on the bottom surface 14js side rather than the valve seat surface 14f1 in the valve housing chamber 14j, so the escape space for the discharged gas becomes wider, and the gas dischargeability from the discharge hole 14a is improved. Further, since the convex portion 14n is provided along the outer periphery of the valve seat portion 14f and is separated from the valve seat surface, even when gas flows back due to the delayed closing of the reed valve 80, at least a part of the outer periphery of the valve seat portion 14f causes the gas to collide with the convex portion 14n and generate a vortex W before the gas reaches the discharge hole 14a, suppressing the inflow of gas into the compression chamber P. Therefore, in the compressor 100 of the present disclosure, it is possible to suppress the decrease in the performance of the compressor 100 compared with the prior art because it can improve the gas dischargeability while suppressing the reverse flow amount of the gas.

[0067] Further, the convex portion 14n is provided annularly along the outer periphery of the valve seat portion 14f. And, at least the height D2 from the bottom surface 14js of the portion 14nc provided between the reed valve 80 and the bottom surface 14js in the closed state among the convex portions 14n is smaller than the height D1 from the bottom surface 14js of the valve seat surface 14f1. Thereby, a vortex W is generated over the entire circumference of the valve seat, making it difficult for the gas to flow backward. Since the convex portion 14n does not contact the reed valve 80, the above-described effect of improving the discharge performance can also be obtained.

[0068] Embodiment 2. FIG. 11 is a plan view showing a state in which a reed valve 80 is disposed on the upper plate 14 of the compressor 100 according to Embodiment 2. FIG. 12 is a partial cross-sectional view showing a D-D cross section when the reed valve 80 and the valve retainer 81 are fixed to the plate 14 of FIG. 11 and the reed valve 80 is in an open state. Here, the D-D cross section is a cross section in a plane parallel to the rotation center axis Ax including the central axis 14ac of the discharge hole 14a and the central axis 14dc of the fixing hole 14d. The D-D cross section is also a plane along the longitudinal direction of the reed valve 80. In Embodiment 2, the shape of the convex portion 14n is different from that in Embodiment 1, and other configurations are the same as those in Embodiment 1. In Embodiment 2, the same reference numerals are given to the same portions as those in Embodiment 1, and the description will be centered on the differences from Embodiment 1.

[0069] As shown in FIGS. 11 to 12, in Embodiment 2, the convex portion 14n has different heights in the circumferential direction. In the example shown in FIGS. 11 and 12, as in the case of Embodiment 1, the convex portion 14n is provided outside the valve seat surface 14f1 so as to form a groove 14r between the convex portion 14n and the valve seat surface 14f1. The convex portion 14n is provided annularly so as to surround the entire circumference of the valve seat portion 14f.

[0070] As shown in FIG. 11, the height is different between a portion 14nc covered by the reed valve 80 in the circumferential direction of the convex portion 14n (in FIG. 12, the portion 14nc provided between the reed valve 80 and the bottom surface 14js) and a portion 14ne exposed from the reed valve 80. Specifically, as shown in FIG. 12, the height D2 of the portion 14nc covered by the reed valve 80 in the convex portion 14n is smaller than the height D3 of the portion 14ne exposed from the reed valve 80 in the convex portion 14n. Further, the height D2 of the portion 14nc covered by the reed valve 80 in the convex portion 14n is smaller than the height D1 of the valve seat portion 14f, that is, the height of the valve seat surface 14f1. On the other hand, the height D3 of the portion 14ne exposed from the reed valve 80 in the convex portion 14n is larger than the height D1 of the valve seat portion 14f. Here, each of the heights D1, D2, and D3 is the axial height with respect to the bottom surface 14js of the valve housing chamber 14j.

[0071] As shown in FIG. 11, 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. As long as the height D2 of the portion 14nc is smaller than the height D1 of the valve seat portion 14f so that the entire portion 14nc covered by the reed valve 80 in the convex portion 14n does not contact the reed valve 80. That is, the convex portion 14n may be provided so that the portion 14nc covered by the reed valve 80 is included and the whole is separated from the closed reed valve 80. Therefore, as shown in FIG. 11, the step 14ns may be provided outside the reed valve 80 rather than directly below the reed valve 80 in the circumferential direction of the convex portion 14n. Further, 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. Further, the convex portion 14n may be formed such that the height of the convex portion 14n changes over the circumferential direction.

[0072] As described above, also in the compressor 100 of the second embodiment shown in FIGS. 11 to 12, similar to the case of the first embodiment, the closed reed valve 80 contacts the valve seat surface 14f1 but does not contact the convex portion 14n. Therefore, also in the second embodiment, the same effect as in the case of the first embodiment can be obtained.

[0073] Also, in the compressor 100 of Embodiment 2 shown in FIGS. 11 to 12, the height D3 from the bottom surface 14js of the exposed portion 14ne of the convex portion 14n from the lead valve 80 in the closed state is larger than the height D1 from the bottom surface 14js of the valve seat surface 14f1. Thereby, without the lead valve 80 and the convex portion 14n coming into contact, the height of the convex portion 14n from the bottom surface 14js of the valve accommodation chamber 14j can be partially increased, and the barrier when gas flows backward in the portion 14ne can be increased. Therefore, the reverse flow rate can be further reduced, improving the performance of the compressor 100.

[0074] When the lead valve 80 closes slowly, the gap between the lead valve 80 and the plate 14 becomes particularly large on the tip side in the longitudinal direction of the lead valve 80 (the left side in FIG. 12). In the present disclosure, since the height of the convex portion 14n is high on the side where this gap becomes large (the left side in FIG. 12), the reverse flow rate can be efficiently reduced.

[0075] FIG. 13 is a plan view showing a modified example of the plate 14 of the compressor 100 according to Embodiment 2. FIG. 14 is a partial cross-sectional view showing an E - E cross-section when the lead valve 80 and the valve retainer 81 are fixed to the plate 14 of FIG. 13 and the lead valve 80 is in the open state. In the modified example shown in FIGS. 13 to 14, the height D2 of the portion 14nc covered by the lead valve 80 in FIGS. 11 to 12 is set to D2 = 0. That is, in the modified example, no convex portion 14n is provided between the lead valve 80 in the closed state and the bottom surface 14js of the valve accommodation chamber 14j on the outer periphery of the valve seat portion 14f, and the convex portion 14n is formed in an arc shape. In FIG. 14, the height D2 of the convex portion 14n is smaller than the height D1 of the valve seat portion 14f. Note that in the modified example, the convex portion 14n is not provided directly below the lead valve 80 on the bottom surface 14js of the valve accommodation chamber 14j, but is provided only in the region exposed from the lead valve 80 in the closed state, so the height D2 of the convex portion 14n may be equal to or greater than the height D1 of the valve seat portion 14f.

[0076] As described above, in the modified example shown in FIGS. 13 to 14, the convex portion 14n is provided only in the region exposed from the reed valve 80 in the closed state on the outer periphery of the valve seat portion 14f. Thereby, when the reed valve 80 closes slowly, the convex portion 14n reduces the reverse flow rate at the tip side of the reed valve 80 (the left side in FIG. 14) where the gap between the reed valve 80 and the plate 14 increases, and the members of the convex portion 14n can be reduced.

[0077] Embodiment 3. FIG. 15 is a partial cross-sectional view when the reed valve 80 and the valve retainer 81 are fixed to the upper plate 14 of the compressor 100 according to Embodiment 3 and the reed valve 80 is in the open state. In Embodiment 3, in that multiple convex portions 14n are provided outside the valve seat portion 14f, it is different from the case of Embodiment 1, and other configurations are the same as those in the case of Embodiment 1. In Embodiment 3, the same reference numerals are given to the same parts as those in Embodiment 1, and the description will be centered on the differences from Embodiment 1.

[0078] In the example shown in FIG. 15, multiple convex portions are provided on the bottom surface 14js of the valve housing chamber 14j formed in the plate 14 in a direction outward from the central axis 14ac of the discharge hole 14a. That is, in the valve housing chamber 14j, outside the valve seat portion 14f, two convex portions 14na and 14nb protruding from the bottom surface 14js are provided. In FIG. 15, multiple convex portions are provided only in a specific direction of the valve seat portion 14f. Specifically, the convex portion 14na is provided annularly so as to surround the entire circumference of the valve seat portion 14f outside the valve seat portion 14f, similar to the convex portion 14n of Embodiment 1. On the other hand, the convex portion 14nb is provided in an arc shape outside the convex portion 14na. The outer convex portion 14nb is provided in the region covered by 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. In FIG. 15, the heights D2 of the outer convex portion 14nb and the inner convex portion 14na are the same and are smaller than the height D1 of the valve seat portion 14f.

[0079] Note that the shapes and arrangements of the outer convex portion 14nb and the inner convex portion 14na are not limited to the above cases. For example, the outer convex portion 14nb may be configured such that the height from the bottom surface 14js varies in the circumferential direction, like the convex portion 14n of the second embodiment. Also, for example, the two convex portions 14nb and 14na may be provided only in a specific direction. Further, triple or more convex portions may be provided in the direction outward from the central axis 14ac of the discharge hole 14a.

[0080] FIG. 16 is a partial cross-sectional view showing a modified example of the compressor 100 according to the third embodiment. In the modified example shown in FIG. 16, both the inner convex portion 14na and the outer convex portion 14nb are formed in an annular shape so as to surround the entire circumference of the valve seat portion 14f.

[0081] As described above, in the third embodiment and the modified example of the third embodiment, the convex portions are provided multiply in the direction outward from the central axis 14ac of the discharge hole 14a on the bottom surface 14js. Thereby, the barriers when the gas flows back into the compression chamber P increase, and the generation of the vortex W in the backflow path is promoted. Therefore, the backflow rate can be further reduced, and the performance of the compressor 100 is improved.

[0082] Fourth Embodiment. FIG. 17 is a partial cross-sectional view when the reed valve 80 and the valve retainer 81 are fixed to the upper plate 14 of the compressor 100 according to the fourth embodiment and the reed valve 80 is in an open state. In the fourth embodiment, the cross-sectional shape of the convex portion 14n is different from that in the first embodiment, and the other configurations are the same as those in the first embodiment. In the fourth embodiment, the same reference numerals are given to the same portions as in the first embodiment, and the description will be centered on the differences from the first embodiment.

[0083] In Embodiment 4, the convex portion 14n has a sloped surface whose height from the bottom surface 14js gradually increases toward the outer peripheral side. Here, the height of the convex portion 14n is the axial height with respect to the bottom surface 14js of the valve accommodation chamber 14j. In the example shown in FIG. 17, the convex portion 14n has an outer peripheral surface 14n2 substantially perpendicular to the bottom surface 14js and an inner peripheral surface 14n3 inclined with respect to the outer peripheral surface 14n2, and has a cross-sectional shape of a right triangle. In FIG. 17, 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 accommodation chamber 14j to the apex of the convex portion 14n, is smaller than the height D1 of the valve seat portion 14f.

[0084] Note that the cross-sectional shape of the convex portion 14n is not limited to the above case. FIG. 18 is a partial cross-sectional view showing a modified example of the compressor 100 according to Embodiment 4. Also in the modified example shown in FIG. 18, the convex portion 14n has a sloped surface whose height from the bottom surface 14js gradually increases toward the outer peripheral side. In the modified example, 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 cross-sectional shape. 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. In the modified example, the upper surface 14n1 of the convex portion 14n forms the inclined portion 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.

[0085] Note that also in Embodiment 4 and the modified example of Embodiment 4, similar to the case of Embodiment 1, it is sufficient that D5 < D1 in at least the portion provided between the lead valve 80 in the closed state and the bottom surface 14js of the valve accommodation chamber 14j in the convex portion 14n. That is, in the circumferential direction of the convex portion 14n, a portion where the height of the convex portion 14n becomes higher than the height D1 of the valve seat portion 14f may be formed.

[0086] As described above, in Embodiment 4 and the modification of Embodiment 4, the convex portion 14n has a slope surface (inner peripheral surface 14n3 in FIG. 17, upper surface 14n1 in FIG. 18) whose height from the bottom surface 14js gradually increases toward the outer peripheral side of the convex portion 14n. Thereby, the inclined portion of the convex portion 14n is formed such that the distance from the bottom surface 14js increases toward the outside (i.e., the outer peripheral side) from the central axis 14ac of the discharge hole 14a along the gas flow during discharge. Therefore, even when the height of the convex portion 14n is increased, the influence on the ease of gas flow can be reduced. Further, when the reed valve 80 closes slowly and gas flows backward, 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, serves as a barrier, and the effect of reducing the reverse flow amount can be realized. Therefore, the performance of the compressor 100 is improved.

Explanation of Signs

[0087] 1 Sealed container, 1a1, 1a2 Lids, 1b Cylindrical part, 10 Compression mechanism part, 11 Rotating shaft, 12 Eccentric shaft part, 13 Cylinder, 13a Cylinder chamber, 13ai Inner peripheral surface, 13b Vane groove, 13c Suction hole, 13d Suction port, 13e Discharge port, 13f Through hole, 13g Accommodation hole, 13h Communication hole, 14 Plate, 14a Discharge hole, 14a1 Opening peripheral edge part, 14ac Central axis, 14b Flow path groove, 14d Fixing hole, 14dc Central axis, 14f Valve seat part, 14f1 Valve seat surface, 14f2 Inclined surface, 14g Bearing, 14h Bearing hole, 14j Valve accommodation chamber, 14j1 First space, 14j2 Second space, 14js Bottom surface, 14jw Bottom wall, 14l Middle part, 14lc Central axis, 14ls Bottom surface, 14m Bottom flow path part, 14n Protrusion, 14n1 Upper surface, 14n2 Outer peripheral surface, 14n3 Inner peripheral surface, 14na Protrusion, 14nb Protrusion, 14nc Part, 14ne Part, 14ns Step, 14p Fixing surface, 14r Groove, 14x First surface, 14y Second surface, 15 Plate, 16 Piston, 16o Outer peripheral surface, 18 Vane, 19 Vane spring, 20 Electric motor, 21 Stator, 22 Rotor, 30 Terminal, 50 Muffler, 60 Suction pipe, 70 Discharge pipe, 80 Reed valve, 80a Valve tip part, 80b Valve base part, 80c Valve middle part, 80d Fixing hole, 81 Valve presser, 81a Tip part, 81b Base part, 81c Through hole, 81d Fixing hole, 82 Fastening part, 100 Compressor, Ax Rotation center axis, D1 Height, D2 Height, D3 Height, D4 Height, D5 Height, Ln Distance, P Compression chamber, Q Suction chamber, R Arrow, R1 Opening radius, R2 Radius, S Contact part, Sb Oil sump space, Sm Space, So Discharge space, W Vortex, W80c Width, Z Arrow, js Bottom surface, t80 Thickness, t81 Thickness.

Claims

1. A compressor comprising a sealed container and a compression mechanism unit installed inside the sealed container and provided with a compression chamber for compressing gas therein, wherein the compression mechanism unit includes a plate that forms part of the wall of the compression chamber and has a discharge hole formed therein for discharging the gas compressed in the compression chamber to the outside of the compression chamber, and a reed valve disposed on the plate so as to cover the discharge side of the discharge hole and capable of opening and closing the discharge hole. On the plate, a valve housing chamber is formed so as to be recessed toward the compression chamber on the surface opposite to the compression chamber, and the reed valve is housed therein, and a valve seat portion is formed on the bottom surface of the valve housing chamber so as to project from the bottom surface at the opening peripheral edge of the discharge hole and has a valve seat surface that contacts the reed valve in the closed state. A convex portion projects from the bottom surface of the valve housing chamber, forms a groove between the convex portion and the valve seat surface, and is provided along the outer periphery of the valve seat portion and is spaced apart from the reed valve in the closed state. The convex portion is provided only in a region exposed from the reed valve in the closed state on the outer periphery of the valve seat portion. Compressor.

2. A compressor comprising a sealed container and a compression mechanism unit installed inside the sealed container and provided with a compression chamber for compressing gas therein, wherein the compression mechanism unit includes a plate that forms part of the wall of the compression chamber and has a discharge hole formed therein for discharging the gas compressed in the compression chamber to the outside of the compression chamber, and a reed valve disposed on the plate so as to cover the discharge side of the discharge hole and capable of opening and closing the discharge hole. On the plate, a valve housing chamber is formed so as to be recessed toward the compression chamber on the surface opposite to the compression chamber, and the reed valve is housed therein, A valve seat portion is formed on the bottom surface of the valve accommodation chamber so as to project from the bottom surface at the opening peripheral edge of the discharge hole, and has a valve seat surface that contacts the lead valve in the closed state. A convex portion is provided which projects from the bottom surface of the valve accommodation chamber, forms a groove between the convex portion and the valve seat surface, is provided along the outer periphery of the valve seat portion, and is spaced apart from the lead valve in the closed state. The convex portions are provided in multiple layers in a direction from the center of the discharge hole toward the outside on the bottom surface. Compressor.

3. A compressor comprising a sealed container and a compression mechanism portion installed in the sealed container and provided with a compression chamber for compressing gas therein, wherein the compression mechanism portion a plate that constitutes a part of the wall of the compression chamber and has a discharge hole formed therein for discharging the gas compressed in the compression chamber to the outside of the compression chamber; a lead valve that is disposed on the plate so as to cover the discharge side of the discharge hole and is capable of opening and closing the discharge hole; on the plate, a valve accommodation chamber that is formed to be recessed toward the compression chamber side on the surface opposite to the compression chamber and in which the lead valve is accommodated; a valve seat portion that is formed on the bottom surface of the valve accommodation chamber so as to project from the bottom surface at the opening peripheral edge of the discharge hole and has a valve seat surface that contacts the lead valve in the closed state; a convex portion is provided which projects from the bottom surface of the valve accommodation chamber, forms a groove between the convex portion and the valve seat surface, is provided along the outer periphery of the valve seat portion, and is spaced apart from the lead valve in the closed state; the convex portion has a sloped surface whose height from the bottom surface gradually increases toward the outer peripheral side of the convex portion. Compressor.

4. The convex portion is provided in an annular shape along the outer periphery of the valve seat portion. At least the height of the portion of the convex portion provided between the lead valve and the bottom surface in the closed state from the bottom surface is smaller than the height of the valve seat surface from the bottom surface. The compressor according to claim 2 or 3.

5. The convex portion is provided annularly or arcuately along the outer periphery of the valve seat portion. The compressor according to any one of claims 1 to 4.

6. The height from the bottom surface of the exposed portion of the convex portion from the reed valve in the closed state is greater than the height from the bottom surface of the valve seat surface. The compressor according to any one of claims 1 to 5.

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