WO2019043905A1

WO2019043905A1 - Scroll compressor and refrigeration cycle device

Info

Publication number: WO2019043905A1
Application number: PCT/JP2017/031565
Authority: WO
Inventors: 雄太郎岩本; 浩平達脇; 友寿松井; 修平小山; 祐司 ▲高▼村
Original assignee: 三菱電機株式会社
Priority date: 2017-09-01
Filing date: 2017-09-01
Publication date: 2019-03-07

Abstract

This scroll compressor is provided with a discharge valve mechanism disposed on a discharge chamber side of a fixed scroll, wherein the discharge valve mechanism has a lead valve, and has a valve seat which is provided on a surface on the discharge chamber side of the fixed scroll and on which the lead valve is seated around a discharge port that is open in the center portion. One or more cutouts are formed in the edge of the valve seat.

Description

Scroll compressor and refrigeration cycle apparatus

The present invention relates to a scroll compressor and a refrigeration cycle apparatus including a discharge valve mechanism disposed on the discharge chamber side of a fixed scroll.

On the discharge chamber side of the fixed scroll which is a component of the scroll compressor, a discharge valve mechanism for opening and closing the discharge port and a valve presser are provided. The discharge valve mechanism divides the high pressure space on the discharge chamber side from the low pressure space before compression of the refrigerant on the compression mechanism side using the fixed scroll.

The discharge valve mechanism comprises one reed valve. In addition, the discharge valve mechanism includes one valve seat on which the reed valve is seated around the discharge opening that opens in the central portion. In the discharge valve mechanism, an oil film is generated between the reed valve and the valve seat when the reed valve is seated. For this reason, when the valve is opened, the valve opening timing of the reed valve is delayed due to the oil film breakage resistance, over-compression occurs, and the performance of the scroll compressor is lowered.

In order to prevent the over-compression, a scroll compressor in which a groove is provided in a valve seat has been proposed (see, for example, Patent Document 1).

JP, 2001-221173, A

However, in the technique of Patent Document 1, refrigerant leakage loss from the high pressure space to the low pressure space occurs through the groove of the valve seat.

Further, in the case where the valve seat is not provided with the groove, it is necessary to prevent the delay in the valve opening timing due to the oil film breakage resistance.

The present invention is intended to solve the above problems, and the valve opening timing of the reed valve can be optimized to suppress over-compression, and the refrigerant leakage loss from the high pressure space to the low pressure space in the discharge valve mechanism is Provided are scroll compressors and refrigeration cycle devices that can be suppressed.

The scroll compressor according to the present invention includes a discharge valve mechanism disposed on the discharge chamber side of the fixed scroll, and the discharge valve mechanism is provided on one reed valve and a surface of the fixed scroll on the discharge chamber side. A scroll seat having one valve seat on which the reed valve is seated around a discharge opening opening in the center, wherein at least one notch is formed at an edge of the valve seat It is a thing.

A refrigeration cycle apparatus according to the present invention includes a scroll compressor.

According to the scroll compressor and the refrigeration cycle device of the present invention, at least one notch is formed at the edge of the valve seat. Therefore, the valve opening timing of the reed valve can be optimized to suppress over-compression, and the refrigerant leakage loss from the high pressure space to the low pressure space in the discharge valve mechanism can be suppressed.

1 is a schematic cross-sectional view showing a scroll compressor according to Embodiment 1 of the present invention. It is a schematic sectional drawing which shows the fixed scroll of the scroll compressor which concerns on Embodiment 1 of this invention. It is a schematic sectional drawing which shows the discharge valve mechanism of the scroll compressor which concerns on Embodiment 1 of this invention. It is a top view which shows the front-end | tip part of the reed valve of the scroll compressor which concerns on Embodiment 1 of this invention. It is a top view which shows the valve seat of the scroll compressor which concerns on Embodiment 1 of this invention. It is a top view which shows the valve seat of the scroll compressor which concerns on the modification of Embodiment 1 of this invention. It is explanatory drawing which shows the relationship of the oil film and pressure in the discharge valve mechanism of the scroll compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the relationship of the oil film and pressure in the discharge valve mechanism of the scroll compressor which concerns on the modification of Embodiment 1 of this invention. It is explanatory drawing which shows the relationship of the oil film and pressure in the discharge valve mechanism of the scroll compressor which concerns on a prior art. It is an explanatory view showing a relation of differential pressure and time to valve-opening in a discharge valve mechanism of a scroll compressor concerning Embodiment 1 of the present invention, a modification, and conventional technology. It is a top view which shows the valve seat of the scroll compressor which concerns on Embodiment 2 of this invention. It is a top view which shows the valve seat of the scroll compressor which concerns on Embodiment 3 of this invention. It is a refrigerant circuit figure showing the frozen cycle device to which the scroll compressor concerning Embodiment 4 of the present invention is applied.

Hereinafter, embodiments of the present invention will be described based on the drawings. In the drawings, the same reference numerals denote the same or corresponding parts, which are common to the whole text of the specification. Furthermore, the form of the component shown in the specification full text is an illustration to the last, and is not limited to these descriptions.

Embodiment 1
<Configuration of Scroll Compressor 100>
FIG. 1 is a schematic cross-sectional view showing a scroll compressor 100 according to Embodiment 1 of the present invention.

Scroll compressor 100 shown in FIG. 1 is applied to, for example, a refrigeration cycle apparatus 200 described later used for refrigeration or air conditioning applications such as a refrigerator or a freezer, an automatic vending machine, an air conditioner, a refrigeration apparatus, a water heater and the like. The scroll compressor 100 sucks in the refrigerant circulating in the refrigeration cycle, compresses the refrigerant, and discharges the refrigerant in a high temperature and high pressure state.

As shown in FIG. 1, the scroll compressor 100 includes a shell 2, an oil pump 3, a motor 4, a compression mechanism 5, a frame 6, and a shaft 7. Furthermore, the scroll compressor 100 includes a suction pipe 11, a discharge pipe 12, a discharge chamber 13, an Oldham ring 15, a slider 16, a sleeve 17, a first balancer 18, a second balancer 19, and a subframe 20 and an oil discharge pipe 21.

The shell 2 constitutes an outer shell of the scroll compressor 100, and has an oil sump 3a at the bottom. The shell 2 is cylindrical with a bottom, and the upper part is closed by the dome-shaped upper shell 2a. The lower part of the shell 2 is closed by the lower shell 2b.

The oil pump 3 is accommodated in the shell 2 and sucks the oil from the oil reservoir 3a. The oil pump 3 is provided at the lower part of the shell 2. Then, the oil pump 3 supplies the oil sucked from the oil reservoir 3a so as to lubricate a portion to be lubricated such as a bearing portion inside the scroll compressor 100. The oil after being sucked up by the oil pump 3 to lubricate the rocking bearing 8c is stored in the internal space 6d of the frame 6, and then passes through the radial oiling groove 6c provided in the thrust bearing 6b, and the Oldham ring space Flow to 15 b and lubricate Oldham ring 15. The oil drain pipe 21 is provided in the Oldham ring space 15b, and the oil is returned to the oil reservoir 3a through the oil drain pipe 21.

The motor 4 is installed between the frame 6 and the sub-frame 20 inside the shell 2 to rotate the shaft 7. The motor 4 has a rotor 4a and a stator 4b. The rotor 4 a is provided on the inner peripheral side of the stator 4 b and attached to the shaft 7. The rotor 4 a rotates the shaft 7 by rotating. The stator 4 b rotates the rotor 4 a by electric power supplied from an inverter (not shown).

The compression mechanism unit 5 includes a fixed scroll 30 and a swing scroll 40.

The fixed scroll 30 is fixed to a frame 6 fixedly supported in the shell 2 by a bolt or the like (not shown). The fixed scroll 30 has an end plate 30 a and a spiral portion 31 extending downward on the lower surface of the end plate 30 a. Further, a discharge port 32 for discharging the compressed fluid is formed in a central portion of the fixed scroll 30 so as to pass therethrough. Further, at the outlet portion of the discharge port 32 of the fixed scroll 30, a concave portion in which the discharge valve mechanism 50 is installed is formed. The discharge valve mechanism 50 is installed so as to cover the discharge port 32 and prevents backflow of fluid.

The rocking scroll 40 performs a revolving rotation movement, in other words, a rocking movement, with respect to the fixed scroll 30, and the rotation movement is restricted by the Oldham ring 15. The rocking scroll 40 has a mirror plate 40 a and a spiral portion 41 extending upward on the upper surface of the mirror plate 40 a.

The fixed scroll 30 and the swinging scroll 40 make the

spirals

31 and 41 face each other on the surfaces facing each other, and mesh the

spirals

31 and 41 with each other. A compression chamber 5a is formed in a space where the spiral portion 31 of the fixed scroll 30 and the spiral portion 41 of the oscillating scroll 40 are engaged. When the rocking scroll 40 is rocked by the shaft 7, the refrigerant in a gas state is compressed in the compression chamber 5a.

The frame 6 is fixed to the shell 2 and accommodates the compression mechanism 5. The frame 6 rotatably supports the shaft 7 via the main bearing 8a. In the frame 6, an intake port 6a is formed. The refrigerant in the gas state flows into the compression mechanism 5 through the suction port 6a.

The shaft 7 is supported by the frame 6. In the shaft portion 7, an oil passage 7a is formed inside, through which the oil sucked up by the oil pump 3 flows upward. The shaft portion 7 is connected to the motor 4 and the oscillating scroll 40, and transmits the rotational force of the motor 4 to the oscillating scroll 40.

The suction pipe 11 is provided on the side wall of the shell 2. The suction pipe 11 is a pipe for sucking the refrigerant in a gas state into the inside of the shell 2.

The discharge pipe 12 is provided on the top of the shell 2. The discharge pipe 12 is a pipe that discharges the compressed refrigerant to the outside of the shell 2.

The discharge chamber 13 is provided above the compression mechanism unit 5. The discharge chamber 13 accommodates the refrigerant compressed and discharged by the compression mechanism unit 5.

The slider 16 is a cylindrical member attached to the outer peripheral surface of the upper portion of the shaft 7. The slider 16 is located on the lower inner surface of the oscillating scroll 40. That is, the slider 16 attaches the swing scroll 40 to the shaft 7 via the slider 16. Thereby, the rocking scroll 40 rotates with the rotation of the shaft portion 7. A swing bearing 8 c is provided between the swing scroll 40 and the slider 16.

The sleeve 17 is a cylindrical member provided between the frame 6 and the main bearing 8a. The sleeve 17 absorbs the inclination of the frame 6 and the shaft 7.

The first balancer 18 is attached to the shaft 7. The first balancer 18 is located between the frame 6 and the rotor 4a. The first balancer 18 cancels the unbalance caused by the oscillating scroll 40 and the slider 16. The first balancer 18 is accommodated in the balancer cover 18a.

The second balancer 19 is attached to the shaft 7. The second balancer 19 is located between the rotor 4 a and the sub-frame 20 and attached to the lower surface of the rotor 4 a. The second balancer 19 cancels the unbalance caused by the oscillating scroll 40 and the slider 16.

The sub-frame 20 is provided below the motor 4 inside the shell 2 and rotatably supports the shaft portion 7 via the sub bearing 8 b.

The oil drain pipe 21 is a pipe that connects the space between the frame 6 and the oscillating scroll 40 and the space between the frame 6 and the sub frame 20. The oil discharge pipe 21 causes excess oil out of the oil flowing in the space between the frame 6 and the oscillating scroll 40 to flow out into the space between the frame 6 and the sub-frame 20. The oil that has flowed into the space between the frame 6 and the sub-frame 20 passes through the sub-frame 20 and returns to the oil sump 3a.

The Oldham ring 15 is disposed on a thrust surface which is a surface opposite to the upper surface of the rocking scroll 40 on which the spiral portion 41 is formed, and blocks the rotational movement of the rocking scroll 40. That is, the Oldham ring 15 functions to block the rotational movement of the rocking scroll 40 and to enable the rocking movement of the rocking scroll 40. The upper and lower surfaces of the Oldham ring 15 are formed with claws (not shown) protruding so as to be orthogonal to each other. The claws of the Oldham ring 15 are respectively inserted into Oldham grooves (not shown) formed in the rocking scroll 40 and the frame 6.

<Operation of Scroll Compressor 100>
When power is supplied to the stator 4b, the rotor 4a generates a torque, and the shaft 7 supported by the main bearing 8a and the auxiliary bearing 8b of the frame 6 rotates. The swing scroll 40 whose boss is driven by the eccentric portion of the shaft 7 is restricted in rotation by the Oldham ring 15 and revolves. That is, the boss portion of the rocking scroll 40 is driven by the eccentric portion of the shaft portion 7 in a state in which the rotation is restricted by the Oldham ring 15 that reciprocates in the Oldham groove direction of the frame 6. Exercise. As a result, the volume of the compression chamber 5a formed by the combination of the spiral portion 31 of the fixed scroll 30 and the spiral portion 41 of the oscillating scroll 40 is changed.

The refrigerant in a gas state that is sucked into the shell 2 from the suction pipe 11 with the rocking motion of the rocking scroll 40 is a compression chamber formed between the

spiral portions

31 and 41 of the fixed scroll 30 and the rocking scroll 40. It is taken into 5a and compressed toward the center. The compressed refrigerant is discharged from the discharge port 32 provided on the fixed scroll 30 with the discharge valve mechanism 50 opened and discharged from the discharge pipe 12 to the outside of the scroll compressor 100, that is, to the refrigerant circuit.

The unbalance due to the movement of the swing scroll 40 and the Oldham ring 15 is balanced by the first balancer 18 attached to the shaft 7 and the second balancer 19 attached to the rotor 4a. Further, the lubricating oil stored in the lower portion of the shell 2 is supplied from the oil passage 7a provided in the shaft portion 7 to each sliding portion such as the main bearing 8a, the sub bearing 8b and the thrust surface.

<Configuration of Discharge Valve Mechanism 50>
FIG. 2 is a schematic cross-sectional view showing fixed scroll 30 of scroll compressor 100 according to Embodiment 1 of the present invention. FIG. 3 is a schematic cross-sectional view showing the discharge valve mechanism 50 of the scroll compressor 100 according to Embodiment 1 of the present invention.

As shown in FIG. 2, the discharge valve mechanism 50 is disposed on the discharge chamber 13 side of the fixed scroll 30. The surface on the discharge chamber 13 side of the fixed scroll 30 in which the discharge valve mechanism 50 is disposed is a flat surface. The discharge valve mechanism 50 has one reed valve 51, one valve seat 52, and a valve presser 53.

The reed valve 51 is a long plate-like member, and is fixed to the fixed scroll 30 together with the valve presser 53 with the fixed end 51 a by a screw. The reed valve 51 has a tip 51b which is a free end extending longitudinally from the fixed end 51a. The tip 51 b of the reed valve 51 is seated on the valve seat 52 and serves as a seal between the high pressure space on the discharge chamber 13 side and the low pressure space on the compression chamber 5 a side before refrigerant compression. The reed valve 51 extends straight by connecting the fixed end 51 a and the tip 51 b in the longitudinal direction.

The valve seat 52 is provided on the surface of the fixed scroll 30 on the discharge chamber 13 side. In the valve seat 52, the leading end 51b of the reed valve 51 is seated around the discharge port 32 which opens in the central portion. The outer side of the outer peripheral edge 52 a of the valve seat 52 is recessed with respect to the plane of the surface of the fixed scroll 30 on the discharge chamber 13 side. That is, the valve seat 52 is formed by processing the groove 33 on the outer surface of the fixed scroll 30. As a result, the surface of the valve seat 52 on which the front end portion 51 b of the reed valve 51 is seated is flush with the surface of the fixed scroll 30 on the discharge chamber 13 side.

The valve presser 53 is a long plate-like member thicker than the reed valve 51, and the fixed end 53a is attached to the fixed scroll 30 together with the reed valve 51 by a screw. The valve presser 53 supports the reed valve 51 from the back when the reed valve 51 is opened, and protects the reed valve 51 so that the reed valve 51 is not deformed. The valve presser 53 connects the fixed end portion 53a and the tip end portion 53b in the longitudinal direction, and causes the tip end portion 53b to be warped toward the discharge chamber 13 side.

As shown in FIG. 3, when the leading end 51 b of the reed valve 51 is seated on the valve seat 52, an oil film is formed between the leading end 51 b and the valve seat 52. The oil film maintains the closed state in which the reed valve 51 seals, and prevents the backflow of the refrigerant from the high pressure space on the discharge chamber 13 side to the low pressure space on the compression chamber 5a side before the refrigerant compression.

<Configuration of Tip 51b of Reed Valve 51>
FIG. 4 is a top view showing a tip 51 b of the reed valve 51 of the scroll compressor 100 according to Embodiment 1 of the present invention.

As shown in FIG. 4, the reed valve 51 is formed in a circular shape that is wider than the intermediate portion 51 c that directs the tip end 51 b toward the fixed end 51 a. The reed valve 51 is formed in line symmetry with respect to a central axis X connecting the fixed end 51 a and the tip 51 b seated on the valve seat 52. The plan view projection line 51b1 at the outer peripheral edge of the tip 51b seated on the valve seat 52 of the reed valve 51 is outside the outer peripheral edge 52a of the valve seat 52 when the reed valve 51 is seated on the valve seat 52 It overlaps with the groove 33 which is a recessed area.

<Configuration of valve seat 52>
FIG. 5 is a top view showing a valve seat 52 of the scroll compressor 100 according to Embodiment 1 of the present invention.

The valve seat 52 is annular, and the outer peripheral edge 52 a and the inner peripheral edge 52 b are concentric circles. A discharge port 32 is concentrically formed in a circle on the inner side of the inner peripheral edge 52 b of the valve seat 52. An annular groove 33 is formed concentrically on the outer side of the outer peripheral edge 52 a of the valve seat 52.

<Structure of Notch 54>
As shown in FIG. 5, one notch 54 is formed in the inner peripheral edge 52 b of the valve seat 52. The shape of the notch 54 is an arc shape. The notch 54 is located on the tip 51 b side of the reed valve 51 with respect to the center of the valve seat 52. The notch 54 is formed in line symmetry with respect to a central axis X connecting the fixed end 51 a of the reed valve 51 and the tip 51 b seated on the valve seat 52. That is, the shape of the arc-shaped notch 54 is a line symmetrical with respect to the central axis X. The notch 54 is recessed from the surface of the valve seat 52 flush with the surface on the discharge chamber 13 side of the fixed scroll 30 toward the discharge chamber side. In FIG. 5, the central axis X is referred to as the X axis, and the orthogonal axis Y orthogonal to the central axis X through the center of the valve seat 52 is referred to as the Y axis.

The surface of the circumferential portion of the valve seat 52 where the notch 54 is formed is formed to be flush with the other circumferential portions. That is, the notch 54 does not extend from the inner peripheral edge 52 b to the outer peripheral edge 52 a of the valve seat 52, and does not connect the inner circumferential side and the outer circumferential side of the valve seat 52.

<Operation of Discharge Valve Mechanism 50>
In the discharge valve mechanism 50, the reed valve 51 is pressed against the valve seat 52 by the differential pressure between the high pressure space on the discharge chamber 13 side and the compression chamber 5a to close the valve. When the compression of the refrigerant proceeds in the compression chamber 5a, the pressure in the compression chamber 5a increases. When the pressure in the compression chamber 5a becomes higher than the pressure in the high pressure space, the reed valve 51 is pulled apart and opens from the valve seat 52. The opened reed valve 51 is supported by a valve retainer 53 at the back to prevent damage. When the discharge of the high-pressure refrigerant in the compression chamber 5a is completed, the reed valve 51 returns to the original flat plate-like state, and the valve is closed.

<Modification of valve seat 52>
FIG. 6 is a top view showing a valve seat 52 of the scroll compressor 100 according to a modification of the first embodiment of the present invention.

As shown in FIG. 6, the notch 54 may be formed in the outer peripheral edge 52 a of the valve seat 52. The shape and arrangement of the notches 54 are the same as the notches 54 of the first embodiment.

<Comparison of Embodiment 1 and Modifications>
FIG. 7 is an explanatory view showing a relationship between an oil film and pressure in the discharge valve mechanism 50 of the scroll compressor 100 according to Embodiment 1 of the present invention. FIG. 8 is an explanatory view showing a relationship between an oil film and pressure in the discharge valve mechanism 50 of the scroll compressor 100 according to a modification of the first embodiment of the present invention. FIG. 9 is an explanatory view showing a relationship between oil film and pressure in the discharge valve mechanism of the scroll compressor according to the prior art. FIG. 10 is an explanatory view showing the relationship between the differential pressure in the discharge valve mechanism 50 of the scroll compressor 100 and the time until the valve opens according to Embodiment 1 of the present invention, the modification and the prior art.

Even in the modification, the oil film formation region can be reduced and oil film breakage resistance of the reed valve 51 can be reduced, as compared with the conventional technique in which the notch 54 is not formed. In particular, in the first embodiment and the modification, the diameter of the valve seat 52 is not reduced in order to reduce the oil film formation area, but the notch 54 is formed to partially cut the valve seat. An unbalanced location is provided for oil film formation. This is characterized in that oil film breakage easily occurs. In the first embodiment shown in FIG. 7, the pressure receiving area where the reed valve 51 receives the differential pressure between the high pressure space and the compression chamber 5a is larger than the pressure receiving areas of the modified example shown in FIGS. .
That is, the force that the reed valve 51 receives from the high pressure space is defined as F = (pressure P × area A), the force that the reed valve 51 receives from the discharge port 32 is defined as F1, and the discharge pressure is defined as P1. The area where the reed valve 51 receives the outlet pressure is defined as A1, and the oil film break resistance is defined as W1,
F <F1 = P1 × A1-W1
Relationship is established. As a result, the reed valve 51 opens when the force F1 received from the discharge port 32 side is larger than the force F received from the high pressure space.
As shown in the first embodiment of FIG. 7, when the notch 54 is formed inside the valve seat 52, A1 is larger and W1 is smaller as compared with the conventional configuration of FIG. The pressure P1 for opening the valve can be small, and the compression loss can be reduced.
On the other hand, as shown in the modification of FIG. 8, when the notch 54 is formed on the outside of the valve seat 52, A1 is the same and W1 is smaller as compared with the conventional configuration of FIG. Although not as in the case of the first embodiment of FIG. 7, the pressure P1 at which the reed valve 51 opens becomes smaller.
Therefore, as shown in FIG. 10, in the discharge valve mechanism 50 according to the first embodiment, even if the differential pressure between the high pressure space and the compression chamber 5a is small, the reed valve 51 can be easily opened, and the valve opening timing can be advanced. The valve opening timing can be made appropriate. Even in the modification, as described above, this effect can not be obtained as compared with the first embodiment, but can be obtained as compared with the prior art.

<Effect of Embodiment 1>
According to the first embodiment, the scroll compressor 100 includes the discharge valve mechanism 50 disposed on the discharge chamber 13 side of the fixed scroll 30. The discharge valve mechanism 50 has one reed valve 51. The discharge valve mechanism 50 is provided on the surface of the fixed scroll 30 on the discharge chamber 13 side, and has one valve seat 52 on which the reed valve 51 is seated around the discharge port 32 opened in the central portion. One notch 54 is formed in the inner peripheral edge 52 b of the valve seat 52. One or more notches 54 may be formed in the edge including the inner peripheral edge 52 b and the outer peripheral edge 52 a of the valve seat 52.

According to this configuration, the notch 54 is formed, the oil film break resistance between the reed valve 51 and the valve seat 52 at the valve opening timing is reduced, and the overcompression loss at the valve opening timing can be reduced. Further, since the notch 54 is not connected to the inner peripheral side and the outer peripheral side around the discharge port 32 of the valve seat 52, refrigerant leakage from the high pressure space to the low pressure space can be suppressed when the reed valve 51 is seated. Furthermore, the notch 54 is locally formed in a part of the valve seat 52, and an increase in the amount of valve deformation when the reed valve 51 is seated and an increase in stress generated in the reed valve 51 can be minimized. Therefore, the valve opening timing of the reed valve 51 can be optimized to suppress over-compression, and the refrigerant leakage loss from the high pressure space to the low pressure space in the discharge valve mechanism 50 can be suppressed. Can be secured.

According to the first embodiment, the notch 54 is formed in the inner peripheral edge 52 b of the valve seat 52.

According to this configuration, it is possible to enlarge the pressure receiving area in which the reed valve 51 that is seated receives the differential pressure between the low pressure space and the high pressure space. Thus, the reed valve 51 can be easily opened, and the valve opening timing can be further optimized.

According to the first embodiment, the notch 54 is formed in the outer peripheral edge 52 a of the valve seat 52.

According to this configuration, the notch 54 is formed, the oil film break resistance between the reed valve 51 and the valve seat 52 at the valve opening timing is reduced, and the overcompression loss at the valve opening timing can be reduced. Further, since the notch 54 is not connected to the inner peripheral side and the outer peripheral side around the discharge port 32 of the valve seat 52, refrigerant leakage from the high pressure space to the low pressure space can be suppressed when the reed valve 51 is seated. Furthermore, the notch 54 is locally formed in a part of the valve seat 52, and an increase in the amount of valve deformation when the reed valve 51 is seated and an increase in stress generated in the reed valve 51 can be minimized.

According to the first embodiment, the notch 54 is formed in line symmetry with respect to the central axis X connecting the fixed end 51 a of the reed valve 51 and the tip 51 b seated on the valve seat 52.

According to this configuration, the valve opening operation of the reed valve 51 is not biased with respect to the central axis X, the reed valve 51 is not biased and deformed, and the durability of the reed valve 51 can be improved. That is, the amount of valve deformation when the reed valve 51 is seated and the stress generated in the reed valve 51 can be reduced, and the reliability of the strength of the reed valve 51 can be secured.

According to the first embodiment, the surface of the circumferential portion of the valve seat 52 in which the notch 54 is formed is formed as the same surface as other circumferential portions.

According to this configuration, since the notch 54 is not connected to the inner peripheral side and the outer peripheral side around the discharge port 32 of the valve seat 52, refrigerant leakage from the high pressure space to the low pressure space is suppressed when the reed valve 51 is seated. it can.

According to the first embodiment, the shape of the notch 54 is an arc shape in plan view on the surface of the valve seat 52.

According to this configuration, the notch 54 can be processed by casting, circular cutting, forging, or the like, and is easy to manufacture.

According to the first embodiment, the notch 54 is recessed from the surface of the valve seat 52 to the side opposite to the discharge chamber.

According to the first embodiment, the surface of the fixed scroll 30 on the discharge chamber 13 side is a flat surface. The outer side of the outer peripheral edge 52 a of the valve seat 52 is a groove 33 recessed with respect to the plane of the surface of the fixed scroll 30 on the discharge chamber 13 side. The surface of the valve seat 52 on which the reed valve 51 is seated is flush with the surface of the fixed scroll 30 on the discharge chamber 13 side.

According to this configuration, the valve seat 52 can be formed flush with the surface of the fixed scroll 30 on the discharge chamber 13 side by processing such that the outside of the outer peripheral edge 52a of the valve seat 52 is recessed in the groove 33. 52 is easy to manufacture. Further, the flat reed valve 51 is fixed in a state in which the fixed end 51 a to the tip 51 b are in contact with the surface of the fixed scroll 30 on the discharge chamber 13 side and the surface of the valve seat 52 flush with the surface. It suffices to fix the end 51a, the efficiency of assembling the discharge valve mechanism 50 is good, and the manufacture of the discharge valve mechanism 50 is easy.

According to the first embodiment, the plan view projection line 51b1 at the outer peripheral edge of the distal end 51b of the reed valve 51 which is seated on the valve seat 52 of the valve seat 52 when the reed valve 51 is seated on the valve seat 52. It overlaps with the area of the groove 33 that is recessed outside the outer peripheral edge 52a.

According to this configuration, the outer peripheral edge 52a of the valve seat 52 does not excessively expand the seating area of the valve seat 52, and the oil film breakage resistance between the reed valve 51 and the valve seat 52 at the valve opening timing is reduced. Overcompression loss at the valve opening timing can be reduced. Further, the outer peripheral edge portion 52a of the valve seat 52 does not excessively expand the seating area of the valve seat 52, and the increase in the amount of deformation of the valve when the reed valve 51 is seated and the increase in stress generated in the reed valve 51 can be minimized. .

Second Embodiment
<Configuration of valve seat 52>
FIG. 11 is a top view showing a valve seat 52 of the scroll compressor 100 according to Embodiment 2 of the present invention. In the second embodiment, features different from the above-described embodiment will be described, and the same description will be omitted.

As shown in FIG. 11, two notches 54 are formed in line symmetry with respect to the central axis X. The two notches 54 formed in line symmetry with respect to the central axis X have a mirror surface shape. The two notches 54 formed in line symmetry with respect to the central axis X are located on the tip 51 b side of the reed valve 51 with respect to the center of the valve seat 52. The shape and arrangement of the other notches 54 are the same as the notches 54 of the first embodiment.

<Effect of Second Embodiment>
According to the second embodiment, two notches 54 are formed in line symmetry with respect to central axis X.

According to this configuration, the valve opening operation of the reed valve 51 is not biased with respect to the central axis X, the reed valve 51 is not biased and deformed, and the durability of the reed valve 51 can be improved. Further, two notches 54 are formed, the oil film break resistance between the reed valve 51 and the valve seat 52 at the valve opening timing is reduced, and the over-compression loss at the valve opening timing can be reduced. Further, since the two notches 54 are not connected to the inner peripheral side and the outer peripheral side around the discharge port 32 of the valve seat 52, refrigerant leakage from the high pressure space to the low pressure space can be suppressed when the reed valve 51 is seated. Furthermore, the two notches 54 are locally formed in a part of the valve seat 52, and an increase in the amount of deformation of the valve when the reed valve 51 is seated and an increase in stress generated in the reed valve 51 can be minimized. .

According to the second embodiment, the two notches 54 formed in line symmetry with respect to the central axis X are located on the tip 51 b side of the reed valve 51 with respect to the center of the valve seat 52.

According to this configuration, the oil film breakage resistance between the reed valve 51 and the valve seat 52 at the valve opening timing is reduced at the tip portion 51b side of the larger reed valve 51, and the valve opening timing is more properly optimized. It can be done.

Third Embodiment
<Configuration of valve seat 52>
FIG. 12 is a top view showing a valve seat 52 of the scroll compressor 100 according to Embodiment 3 of the present invention. In the third embodiment, features different from the above-described embodiment will be described, and the same description will be omitted.

As shown in FIG. 12, three notches 54 are formed in line symmetry with respect to the central axis X. The two notches 54 are formed in line symmetry with respect to the central axis X on the side of the tip 51 b of the reed valve 51 with respect to the center of the valve seat 52. These two notches 54 are similar to the two notches 54 of the second embodiment. One notch 54 is formed on the central axis X that is axisymmetrical to the central axis X and on the fixed end 51 a side of the reed valve 51 with respect to the center of the valve seat 52. The one notch 54 is formed in addition to the two notches 54 of the second embodiment. The shape and arrangement of the other notches 54 are the same as the notches 54 of the first embodiment.

<Effect of Embodiment 3>
According to the third embodiment, one notch 54 is provided on the central axis X which is axisymmetrical to the central axis X and on the side of the fixed end 51 a of the reed valve 51 with respect to the center of the valve seat 52 It is formed.

According to this configuration, the valve opening operation of the reed valve 51 is not biased with respect to the central axis X, the reed valve 51 is not biased and deformed, and the durability of the reed valve 51 can be improved. Further, three notches 54 are formed, the oil film break resistance between the reed valve 51 and the valve seat 52 at the valve opening timing is reduced, and the over-compression loss at the valve opening timing can be reduced. Further, since the three notches 54 are not connected to the inner peripheral side and the outer peripheral side around the discharge port 32 of the valve seat 52, refrigerant leakage from the high pressure space to the low pressure space can be suppressed when the reed valve 51 is seated. Furthermore, the three notches 54 are locally formed in a part of the valve seat 52, and the increase in the amount of deformation of the valve when the reed valve 51 is seated and the increase in the stress generated in the reed valve 51 can be minimized. .

The present invention is not limited to the above first to third embodiments, and can be appropriately modified and applied without departing from the scope of the present invention. For example, although the shape of the notch 54 mentioned the circular arc shape as an example, an elliptical shape, a strip shape, a fan shape, etc. may be sufficient. The number of notches 54 may be four or more.

Fourth Embodiment
<Refrigeration cycle apparatus 200>
FIG. 13 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 200 to which the scroll compressor 100 according to Embodiment 4 of the present invention is applied.

As shown in FIG. 13, the refrigeration cycle apparatus 200 includes a scroll compressor 100, a condenser 201, an expansion valve 202 and an evaporator 203. The scroll compressor 100, the condenser 201, the expansion valve 202, and the evaporator 203 are connected by refrigerant pipes to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 203 is drawn into the scroll compressor 100 and becomes high temperature and high pressure. The high temperature and pressure refrigerant is condensed in the condenser 201 to become a liquid. The refrigerant that has become a liquid is decompressed and expanded by the expansion valve 202 and becomes a low-temperature low-pressure gas-liquid two phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 203.

The scroll compressor 100 according to the first to third embodiments can be applied to such a refrigeration cycle apparatus 200. For example, the refrigeration cycle apparatus 200 can be employed in an air conditioner, a refrigeration apparatus, a water heater, and the like.

<Effect of Fourth Embodiment>
The refrigeration cycle apparatus 200 includes the scroll compressor 100 described in the above first to third embodiments.

According to this configuration, in the refrigeration cycle apparatus 200 equipped with the scroll compressor 100, the valve opening timing of the reed valve 51 can be optimized to suppress over-compression and the high pressure space to the low pressure space in the discharge valve mechanism 50. Refrigerant leakage loss can be suppressed, and the reliability of the strength of the reed valve 51 can be secured.

Reference Signs List 2 shell 2a upper shell 2b lower shell 3 oil pump 3a oil reservoir 4 motor 4a rotor 4b stator 5 compression mechanism portion 5a compression chamber 6 frame 6a suction port 6b thrust bearing 6c oil groove , 6d internal space, 7 shaft portion, 7a oil passage, 8a main bearing, 8b sub bearing, 8c rocking bearing, 11 suction pipe, 12 discharge pipe, 13 discharge chamber, 15 oldham ring, 15b oldham ring space, 16 slider, Reference Signs List 17 sleeve 18 first balancer 18 a balancer cover 19 second balancer 20 sub frame 21 oil drain pipe 30 fixed scroll 30 a end plate 31 spiral portion 32 discharge port 33 groove portion 40 oscillating scroll 40 a End plate, 41 spiral parts, 5 Discharge valve mechanism, 51 reed valve, 51a fixed end, 51b tip, 51b1 projection line, 51c middle part, 52 valve seat, 52a outer peripheral part, 52b inner peripheral part, 53 valve retainer, 53a fixed end, 53b tip, 54 notches, 100 scroll compressor, 200 refrigeration cycle device, 201 condenser, 202 expansion valve, 203 evaporator, X central axis, Y orthogonal axis.

Claims

A discharge valve mechanism disposed on the discharge chamber side of the fixed scroll,
The discharge valve mechanism is a scroll having one reed valve, and one valve seat provided on the surface on the discharge chamber side of the fixed scroll and having the reed valve seated around a discharge opening opening in the center. A compressor,
The scroll compressor in which one or more notch is formed in the edge of said valve seat.
The scroll compressor according to claim 1, wherein the notch is formed in an inner peripheral edge portion of the valve seat.
The scroll compressor according to claim 1, wherein the notch is formed in an outer peripheral edge portion of the valve seat.
The scroll compression according to any one of claims 1 to 3, wherein the notch is formed in line symmetry with respect to a central axis connecting a fixed end of the reed valve and a tip end seated on the valve seat. Machine.
The scroll compressor according to claim 4, wherein two notches are formed in line symmetry with respect to the central axis.
The scroll compressor according to claim 5, wherein the two notches formed in line symmetry with respect to the central axis are located on the tip end side of the reed valve with respect to the center of the valve seat.
The scroll compressor according to claim 6, wherein the notch is further formed on the central axis and at the fixed end side of the reed valve with respect to the center of the valve seat.
The scroll compressor according to any one of claims 1 to 7, wherein the surface of the circumferential portion of the valve seat where the notches are formed is formed in the same plane as other circumferential portions.
The scroll compressor according to any one of claims 1 to 8, wherein a shape of the notch is an arc shape in a plan view on a surface of the valve seat.
The scroll compressor according to any one of claims 1 to 9, wherein the notch is recessed from the surface of the valve seat to the side opposite to the discharge chamber.
The surface of the fixed scroll on the discharge chamber side is a plane,
The outer side of the outer peripheral edge of the valve seat is a groove recessed with respect to the plane of the surface on the discharge chamber side of the fixed scroll,
The scroll compressor according to any one of claims 1 to 10, wherein a surface of the valve seat on which the reed valve is seated is formed flush with a surface of the surface on the discharge chamber side of the fixed scroll.
The scroll compression according to claim 11, wherein a plan view projection line at an outer peripheral edge portion of a tip end portion of the reed valve seated on the valve seat overlaps an area of the groove when the reed valve is seated on the valve seat. Machine.
A refrigeration cycle apparatus comprising the scroll compressor according to any one of claims 1 to 12.