CN114729630A

CN114729630A - Compressor

Info

Publication number: CN114729630A
Application number: CN201980102516.8A
Authority: CN
Inventors: 达胁浩平; 增本浩二; 高村祐司
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2019-12-04
Filing date: 2019-12-04
Publication date: 2022-07-08
Anticipated expiration: 2039-12-04
Also published as: JPWO2021111546A1; JP7241915B2; WO2021111546A1

Abstract

The compressor according to the present invention includes: a compression mechanism unit for discharging the refrigerant compressed therein from the discharge port; a closed container which houses the compression mechanism and has a discharge chamber formed therein into which the refrigerant discharged from the discharge port flows; and a discharge valve mechanism that covers the discharge port so as to be openable and closable from the discharge chamber side, wherein the compression mechanism portion includes a valve seat on a peripheral edge of an end portion of the discharge port on the discharge chamber side, the discharge valve mechanism includes a leaf valve that extends from a fixed portion of the compression mechanism portion toward the discharge port and contacts the valve seat, and the leaf valve is configured to elastically deform with the fixed portion as a fixed end due to pressure of refrigerant discharged from the discharge port to communicate an inside of the compression mechanism portion with the discharge chamber, the leaf valve including: a 1 st plate thickness portion including a portion contacting the valve seat; and a 2 nd thick plate portion extending from the 1 st thick plate portion toward the fixing portion, wherein a maximum thickness of the 1 st thick plate portion is larger than a thickness of the 2 nd thick plate portion.

Description

Compressor

Technical Field

The present invention relates to a compressor for compressing a refrigerant.

Background

A compressor that compresses a refrigerant is used as one of devices constituting a refrigeration cycle apparatus. The refrigeration cycle device is mounted on, for example, an air conditioner and a refrigeration device.

As one type of compressor which is one of constituent devices constituting such a refrigeration cycle apparatus, there has been conventionally known a compressor as follows: the refrigerant discharged from the discharge port of the compression mechanism is temporarily discharged into a discharge chamber in the closed casing, and the refrigerant compressor is provided with a discharge valve mechanism covering the discharge port so as to be openable and closable from the discharge chamber. For example, a scroll compressor is known as an example of such a compressor (see patent document 1). More specifically, a conventional scroll compressor includes a scroll-type compression mechanism portion having a discharge port formed therein, and discharges a refrigerant compressed therein from the discharge port. Further, a conventional scroll compressor includes a sealed container in which a compression mechanism is housed, and a discharge chamber into which a refrigerant discharged from a discharge port of the compression mechanism flows is formed inside the sealed container. Further, the conventional scroll compressor further includes a discharge valve mechanism in the closed casing, the discharge valve mechanism covering a discharge port of the compression mechanism portion so as to be openable and closable from the discharge chamber side.

Specifically, the peripheral structure of the conventional discharge valve mechanism is described, and the compression mechanism portion includes a valve seat at the peripheral edge of the discharge chamber side end portion of the discharge port. The discharge valve mechanism includes a reed valve, a part of which is fixed to the compression mechanism. The reed valve is a plate-like member having the same thickness as a whole. The reed valve extends from a fixing portion with the compression mechanism portion toward the discharge port, and the tip end portion is in contact with the valve seat. The pressure of the refrigerant discharged from the discharge port acts on a portion of the reed valve that faces the discharge port. Therefore, when the pressure of the refrigerant discharged from the discharge port rises, the reed valve elastically deforms at a fixed end at a fixed position with respect to the compression mechanism due to the pressure of the refrigerant, and the tip end portion of the reed valve separates from the valve seat. Thereby, the discharge port is opened. The refrigerant compressed by the compression mechanism is discharged from the discharge port, passes between the valve seat and the reed valve, and flows into the discharge chamber. When the pressure of the refrigerant discharged from the discharge port decreases, the spring valve elastically deforms and returns, and the tip end portion of the spring valve comes into contact with the valve seat. Thereby, the discharge port is closed, and the inflow of the refrigerant from the discharge port into the discharge chamber is completed.

Patent document 1: japanese laid-open patent application No. 2001-221173

When the reed valve elastically deforms and recovers and the discharge port is closed by the reed valve, the contact portion of the reed valve with the valve seat is subjected to an impact when the contact portion collides with the valve seat. In order to suppress damage to the reed valve due to the impact, the thickness of the contact portion of the reed valve with the valve seat needs to be increased to some extent. Here, as described above, the conventional reed valve is a plate-like member having a uniform thickness as a whole. Therefore, if the thickness of the reed valve is increased to suppress damage to the reed valve, the rigidity of the reed valve is increased, and the reed valve is less likely to be elastically deformed. As a result, when the discharge port is opened, the gap between the valve seat and the reed valve is reduced, and the flow path resistance between the valve seat and the reed valve is increased. Therefore, in the conventional compressor including the discharge valve mechanism covering the discharge port so as to be openable and closable from the discharge chamber side, if the thickness of the reed valve is increased to suppress damage to the reed valve, the refrigerant compressed by the compression mechanism portion is difficult to flow into the discharge chamber, and the performance of the compressor is degraded.

Disclosure of Invention

The present invention has been made to solve the above problems, and an object of the present invention is to provide a compressor capable of suppressing damage to a reed valve and suppressing a decrease in performance.

The compressor according to the present invention includes: a compression mechanism part which is provided with a discharge port and discharges the refrigerant compressed inside from the discharge port; a closed container which houses the compression mechanism and has a discharge chamber formed therein into which the refrigerant discharged from the discharge port flows; and a discharge valve mechanism housed in the sealed container and covering the discharge port so as to be openable and closable from the discharge chamber side, wherein the compression mechanism portion includes a valve seat on a periphery of an end portion of the discharge port on the discharge chamber side, the discharge valve mechanism includes a reed valve extending from a fixed portion between the reed valve and the compression mechanism portion toward the discharge port and contacting the valve seat, the discharge valve mechanism is configured such that the reed valve is elastically deformed with the fixed portion as a fixed end by pressure of refrigerant discharged from the discharge port to communicate an inside of the compression mechanism portion with the discharge chamber, and the reed valve includes: a 1 st plate thickness portion including a portion that contacts the valve seat; and a 2 nd thick plate portion extending from the 1 st thick plate portion toward the fixing portion, wherein a maximum thickness of the 1 st thick plate portion is larger than a thickness of the 2 nd thick plate portion.

The maximum thickness of the 1 st thick plate part of the reed valve of the compressor related by the invention is thicker than the thickness of the 2 nd thick plate part. Therefore, even when the thickness of the 1 st plate thickness portion including the portion in contact with the valve seat is increased in order to suppress damage to the reed valve, the 2 nd plate thickness portion, which is thinner than the 1 st plate thickness portion, can suppress elastic deformation of the reed valve more easily than in the conventional art. Therefore, in the compressor according to the present invention, even when the thickness of the 1 st plate thickness portion including the portion in contact with the valve seat is increased in order to suppress damage to the reed valve, it is possible to suppress a decrease in performance as compared with the conventional compressor.

Drawings

Fig. 1 is a longitudinal sectional view of a compressor according to embodiment 1.

Fig. 2 is a vertical cross-sectional view showing the periphery of the discharge valve mechanism of the compressor according to embodiment 1.

Fig. 3 is a plan view of a reed valve of the discharge valve mechanism of the compressor according to embodiment 1.

Fig. 4 is a vertical cross-sectional view showing the periphery of a discharge valve mechanism of another example of the compressor according to embodiment 1.

Fig. 5 is a view of the periphery of the end portion of the valve pressing member shown in fig. 4, as viewed from below.

Fig. 6 is a vertical cross-sectional view showing the periphery of the discharge valve mechanism of the compressor according to embodiment 2, and is a view showing the valve seat and the periphery of the 1 st plate thickness portion of the reed valve.

Fig. 7 is a plan view showing the 1 st thick plate portion of the reed valve of fig. 6.

Fig. 8 is a vertical cross-sectional view showing the periphery of a discharge valve mechanism of another example of the compressor according to embodiment 2, and is a view showing the periphery of the 1 st plate thickness portion of the valve seat and the reed valve.

Fig. 9 is a plan view showing the 1 st thick plate portion of the reed valve of fig. 8.

Fig. 10 is a vertical cross-sectional view showing the periphery of a discharge valve mechanism of another example of the compressor according to embodiment 2, and is a view showing the periphery of the 1 st plate thickness portion of the valve seat and the reed valve.

Detailed Description

In the following embodiments, an example of a compressor according to the present invention will be described. The compressor according to the present invention is configured such that the refrigerant discharged from the discharge port of the compression mechanism is discharged into the discharge chamber in the closed casing, and is provided with a discharge valve mechanism that covers the discharge port so as to be openable and closable from the discharge chamber side. Conventionally, as a compressor provided with a discharge valve mechanism that openably and closably covers a discharge port from a discharge chamber side, various compressors such as a scroll compressor, a vane compressor, a rotary compressor, and a reciprocating compressor have been known. In the following embodiments, a scroll compressor is taken as an example, and an example of a compressor according to the present invention will be described. However, the present invention is not limited to the invention adopted for the scroll compressor. The present invention may be applied to compressors other than scroll compressors. In the drawings used in the following embodiments, the size of the components of the compressor according to the present invention may be different from the size of the components of the compressor actually manufactured by using the present invention.

Embodiment mode 1

A schematic configuration of a compressor 200 according to embodiment 1 will be described below with reference to fig. 1. The compressor 200 is one of constituent devices of a refrigeration cycle apparatus. More specifically, the compressor 200 sucks in a refrigerant circulating in the refrigeration cycle apparatus, compresses the refrigerant into a high-temperature and high-pressure state, and discharges the refrigerant. Refrigeration cycle devices are used in various industrial equipment such as refrigerators, freezers, vending machines, air conditioners, refrigeration devices, and hot water feeders.

The compressor 200 is a scroll compressor, and includes a scroll-type compression mechanism 10, a closed casing 1, and a discharge valve mechanism 100. The compression mechanism 10 is formed with a discharge port 32, and discharges the refrigerant compressed therein from the discharge port 32. The compression mechanism 10 is a scroll-type compression mechanism including a fixed scroll 11 and an oscillating scroll 21. The closed casing 1 houses a compression mechanism 10 and a discharge valve mechanism 100. Further, a discharge chamber 9 is formed inside the closed casing 1, and the refrigerant discharged from the discharge port 32 of the compression mechanism 10 flows into the discharge chamber 9. The discharge valve mechanism 100 openably and closably covers the discharge port 32 of the compression mechanism 10 from the discharge chamber 9 side. The compressor 200 according to embodiment 1 includes the motor 40 and the drive shaft 50 housed in the sealed container 1. The drive shaft 50 transmits the driving force of the motor 40 to the compression mechanism portion 10. Hereinafter, the structure of the compressor 200 will be described more specifically.

Hermetic container 1 constitutes an outer shell of compressor 200. In embodiment 1, the sealed container 1 includes a center case 2, an upper case 3, and a lower case 4. The center case 2 is a cylindrical member having an upper portion and a lower portion opened. The upper case 3 is a member that closes an opening in the upper portion of the center case 2. The lower case 4 is a member that closes the opening in the lower portion of the center case 2. Further, an oil reservoir is formed in the bottom of the sealed container 1. The oil reservoir stores refrigerating machine oil supplied to a sliding portion such as the compression mechanism 10.

The inside of the closed casing 1 is partitioned into an inflow chamber 8 and the discharge chamber 9 by a fixed scroll 11 of the compression mechanism 10 and a frame 60 described later. Specifically, as will be described later, the frame 60 is disposed below the fixed scroll 11. In the closed casing 1, a lower position of the frame 60 serves as an inflow chamber 8, and an upper position of the fixed scroll 11 serves as a discharge chamber 9. The sealed container 1 is provided with a suction pipe 6 communicating with the inflow chamber 8 and a discharge pipe 7 communicating with the discharge chamber 9. In embodiment 1, the suction pipe 6 is fixed to the center case 2 of the closed casing 1. The discharge pipe 7 is fixed to the upper case 3 of the closed casing 1.

The low-temperature low-pressure gas refrigerant flows into the inflow chamber 8 through the suction pipe 6. That is, the low-temperature low-pressure gas refrigerant to be compressed in the compression mechanism 10 flows into the inflow chamber 8. The high-temperature and high-pressure gas refrigerant compressed in the compression mechanism 10 and discharged from the discharge port 32 flows into the discharge chamber 9. Therefore, the inflow chamber 8 is a space of a lower pressure than the discharge chamber 9. In other words, the discharge chamber 9 is a higher pressure space than the inflow chamber 8. The high-temperature high-pressure gaseous refrigerant flowing into the discharge chamber 9 flows out of the compressor 200 through the discharge pipe 7.

The frame 60 and the sub-frame 65 are housed in the closed casing 1 so as to face each other with the motor 40 interposed therebetween in the axial direction of the drive shaft 50. The frame 60 holds the compression mechanism portion 10. The frame 60 is disposed above the motor 40 and between the motor 40 and the compression mechanism 10. The sub-frame 65 is located on the lower side of the motor 40. The frame 60 and the sub-frame 65 are fixed to the inner peripheral surface of the center case 2 of the closed casing 1 by means of shrink fitting or the like.

The drive shaft 50 transmits the driving force of the motor 40 to the orbiting scroll 21. The orbiting scroll 21 is eccentrically coupled to the drive shaft 50 and is combined with the frame 60 via a cross ring 70. That is, the cross ring 70 is disposed between the orbiting scroll 21 and the frame 60. Specifically, the cross ring 70 is disposed between a platen 22 of the orbiting scroll 21, which will be described later, and the frame 60. The cross ring 70 includes a ring portion 71, a pair of keys 72 provided on an upper surface of the ring portion 71, and a pair of keys 73 provided on a lower surface of the ring portion 71. On the other hand, a pair of key grooves 26 into which a pair of keys 72 are slidably inserted are formed in the lower surface 22a of the platen 22 of the orbiting scroll 21. Further, the frame 60 is formed with a pair of key grooves 61 into which the pair of keys 73 are slidably inserted. When the orbiting scroll 21 tries to rotate by the driving force of the motor 40, the rotation of the orbiting scroll 21 is restricted by the cross ring 70. Therefore, when the orbiting scroll 21 tries to rotate by the driving force of the motor 40, the orbiting scroll 21 orbits without rotating. That is, the oscillating scroll 21 performs an oscillating motion.

The compression mechanism 10 includes the fixed scroll 11 and the orbiting scroll 21 as described above. Fixed scroll 11 includes a platen 12 and a worm tooth 13. The worm teeth 13 are arranged on the lower surface of the platen 12. The fixed scroll 11 is fixed to the frame 60 by bolts or the like not shown.

Oscillating scroll 21 includes a platen 22 and an orbital tooth 23. The upper surface of the platen 22 is opposed to the fixed scroll 11. The worm teeth 23 are substantially the same shape as the worm teeth 13, and are provided on the upper surface of the platen 22. Further, the orbiting scroll 21 is provided with a hollow cylindrical projection 24 on the lower surface of the platen 22.

The oscillating scroll 21 and the fixed scroll 11 are arranged in the closed casing 1 in a state of being combined with the wrap 23 and the wrap 13. In a state where the worm teeth 23 and the worm teeth 13 are combined, the winding direction of the worm teeth 23 is opposite to the winding direction of the worm teeth 13. Thus, by combining the worm tooth 13 of the fixed scroll 11 and the worm tooth 23 of the oscillating scroll 21, a compression chamber 30 that compresses refrigerant is formed between the worm tooth 13 and the worm tooth 23. The volume of the compression chamber 30 changes due to the oscillating movement of the oscillating scroll 21. Further, a seal member 14 is provided at the tip of the inner wrap 13 of the fixed scroll 11 to reduce leakage of refrigerant from between the inner wrap 13 and a platen 22 of the oscillating scroll 21. Also, a seal member 27 is provided at the tip of the worm 23 of the oscillating scroll 21 to reduce leakage of refrigerant from between the worm 23 and the platen 12 of the fixed scroll 11.

A communication port 15 for communicating the inside and outside of the compression chamber 30 is formed at a substantially central position of the platen 12 of the fixed scroll 11. That is, the refrigerant compressed in the compression chamber 30 flows out from the inside of the compression chamber 30 to the outside of the compression chamber 30 through the communication port 15. The compression mechanism 10 of the compressor 200 according to embodiment 1 includes the discharge chamber 31. The discharge chamber 31 covers the communication port 15 on the outer side of the compression chamber 30. The discharge chamber 31 is fixed to the upper surface of the platen 12 of the fixed scroll 11 by bolts or the like. Further, the discharge chamber 31 is formed with a discharge port 32. Therefore, in embodiment 1, the refrigerant compressed in the compression chamber 30 is discharged from the communication port 15 into the discharge chamber 31, and thereafter flows into the discharge chamber 9 from the discharge port 32. That is, in embodiment 1, the discharge valve mechanism 100 that openably covers the discharge port 32 of the compression mechanism section 10 from the discharge chamber 9 side is attached to the discharge chamber 31. The discharge valve mechanism 100 prevents the refrigerant from flowing backward from the discharge chamber 9 to the discharge port 32. The details of the discharge valve mechanism 100 will be described later.

The frame 60 has a surface facing the lower surface 22a of the platen 22 of the orbiting scroll 21 from below. This surface is a surface that supports the orbiting scroll 21 so as to be able to oscillate, and supports a load acting on the orbiting scroll 21 during compression of the refrigerant. Therefore, a thrust plate 25 is provided on the lower surface 22a of the platen 22 of the orbiting scroll 21 for the purpose of improving the slidability with this surface. The frame 60 is formed with a flow path, not shown, for guiding the refrigerant flowing into the inlet chamber 8 into the compression mechanism 10.

The motor 40 that supplies a driving force to the drive shaft 50 has a stator 41 and a rotor 42. The stator 41 is fixed to the inner peripheral surface of the center housing 2 of the closed casing 1 by shrink fitting or the like. The stator 41 is electrically connected to the power supply terminal 5, and power is supplied from the power supply terminal 5. The rotor 42 is disposed on the inner peripheral side of the stator 41, and is connected to a later-described main shaft portion 51 of the drive shaft 50 by means of shrink fitting or the like.

The drive shaft 50 includes a main shaft portion 51 and an eccentric shaft portion 52 provided at the upper end of the main shaft portion 51. The upper portion of the main shaft 51 is rotatably supported by a main bearing 62, and the main bearing 62 is provided to the frame 60. The lower portion of the main shaft portion 51 is rotatably supported by a sub-bearing 66, and the sub-bearing 66 is provided on the sub-frame 65. Further, a displacement pump 53 is provided in the sub-frame 65. The refrigerating machine oil stored in the oil reservoir of the closed casing 1 is pumped up by the pump 53 and supplied to the sliding portion such as the compression mechanism portion 10 through the oil supply hole 54 formed in the drive shaft 50.

When the main shaft 51 rotates, the eccentric shaft 52 eccentric with respect to the main shaft 51 rotates with respect to the main shaft 51 at a radius that is the distance between the axis of the main shaft 51 and the axis of the eccentric shaft 52. As a result, the orbiting scroll 21 connected to the eccentric shaft portion 52 attempts to rotate with the radius described above with respect to the main shaft portion 51. In other words, the orbiting scroll 21 is intended to orbit with the radius described above with respect to the fixed scroll 11. At this time, as described above, the orbiting scroll 21 is restricted from rotating by the oldham ring 70. Therefore, the oscillating scroll 21 oscillates with the radius described above with respect to the fixed scroll 11.

The compressor 200 according to embodiment 1 includes the 1 st balance weight 55 and the 2 nd balance weight 56 to cancel out the imbalance of the load due to the oscillation of the orbiting scroll 21. The 1 st balance weight 55 is attached to the main shaft 51 at a position between the frame 60 and the rotor 42 by shrink fitting or the like. The 2 nd balance weight 56 is installed at the lower portion of the rotor 42.

Fig. 2 is a vertical cross-sectional view showing the periphery of the discharge valve mechanism of the compressor according to embodiment 1. Fig. 3 is a plan view of a reed valve of the discharge valve mechanism of the compressor according to embodiment 1. In fig. 3, the position of the outer peripheral portion 35a of the valve seat 35 in a state where the reed valve 110 is in contact with the valve seat 35 is indicated by a two-dot chain line as a virtual line. Hereinafter, the structure around the discharge valve mechanism 100 and the detailed structure of the discharge valve mechanism 100 will be described with reference to fig. 2 and 3.

The discharge chamber 31 of the compression mechanism 10 includes, for example, a valve seat 35 having a substantially annular shape in plan view on the periphery of the end of the discharge port 32 on the discharge chamber 9 side. The discharge valve mechanism 100 includes a reed valve 110 that openably covers the discharge port 32 of the compression mechanism 10 from the discharge chamber 9 side. The reed valve 110 is fixed to the discharge chamber 31 at a fixed position. In embodiment 1, the end 111 of the reed valve 110 is a fixed portion between the reed valve 110 and the discharge chamber 31. In embodiment 1, the reed valve 110 is fixed to the discharge chamber 31 using the fixing member 101 as a bolt. Specifically, a through hole 113 is formed in the end 111 of the reed valve 110. The reed valve 110 is fixed to the discharge chamber 31 by screwing the fixing member 101 inserted into the through hole 113 into a female screw portion formed in the discharge chamber.

The reed valve 110 extends from an end 111 as a fixing portion toward the discharge port 32. Also, the end 112 is in contact with the valve seat 35. In other words, the end 112 is seated on the valve seat 35. When the pressure of the refrigerant discharged from the discharge port 32 is applied to the end portion 112, the end portion 111 becomes a fixed end and the end portion 112 becomes a free end, and the reed valve 110 is elastically deformed. Thereby, the interior of the compression mechanism 10 communicates with the discharge chamber 9. More specifically, when the pressure of the refrigerant discharged from the discharge port 32 increases, the reed valve 110 elastically deforms by the pressure of the refrigerant with the end portion 111 as a fixed end, and the end portion 112 separates from the valve seat 35. Thereby, the discharge port 32 is opened. Then, the refrigerant compressed in the compression mechanism 10 is discharged from the discharge port 32, passes between the valve seat 35 and the reed valve 110, and flows into the discharge chamber 9. When the pressure of the refrigerant discharged from the discharge port 32 decreases, the elastic deformation of the reed valve 110 is restored, and the end 112 of the reed valve 110 comes into contact with the valve seat 35. Thereby, the discharge port 32 is closed, and the inflow of the refrigerant from the discharge port 32 into the discharge chamber 9 is completed. In addition, this prevents the refrigerant from flowing backward from the discharge chamber 9 to the discharge port 32.

The discharge valve mechanism 100 according to embodiment 1 includes a valve holder 120. The valve presser 120 contacts the reed valve 110 when the reed valve 110 is elastically deformed by the pressure of the refrigerant discharged from the discharge port 32, thereby preventing the reed valve 110 from being excessively bent. Specifically, the valve pressing member 120 is disposed above the reed valve 110. A through hole 123 is formed in the end 121 of the valve pressing member 120. The valve pressing member 120 is fixed to the discharge chamber 31 together with the reed valve 110 by screwing the fixing member 101 inserted into the through hole 123 into a female screw portion formed in the discharge chamber. Further, the end 122 of the valve pressing member 120 is disposed above the end 112 of the reed valve 110. Further, in a state where the reed valve 110 is not elastically deformed, the gap between the reed valve 110 and the valve pressing piece 120 gradually becomes wider as going from the end 121 toward the end 122. Accordingly, when the reed valve 110 is elastically deformed by the pressure of the refrigerant discharged from the discharge port 32, the reed valve 110 contacts the valve holder 120, and the reed valve 110 can be prevented from being excessively bent.

Here, the conventional reed valve is a plate-like member having a uniform thickness as a whole. On the other hand, the reed valve 110 according to embodiment 1 has a different thickness depending on the location. Specifically, a portion including a portion contacting the valve seat 35 on the end 112 side becomes the 1 st thickness portion 114 having the thickness T1. A portion extending from the 1 st thick plate portion 114 toward the end portion 111 as the fixed portion is a 2 nd thick plate portion 115 having a thickness T2. Further, the thickness T1 of the 1 st plate thickness portion 114 is thicker than the thickness T2 of the 2 nd plate thickness portion 115. Further, as described later in embodiment 2, in the case where the 1 st thick plate portion 114 is formed with the concavity and convexity, the thickness T1 of the 1 st thick plate portion 114 indicates the maximum thickness of the 1 st thick plate portion 114.

In embodiment 1, when the 1 st thick plate portion 114 and the valve seat 35 are viewed in the direction in which the 1 st thick plate portion 114 faces the valve seat 35, the outer peripheral portion 114b of the 1 st thick plate portion 114 is disposed outward of the outer peripheral portion 35a of the valve seat 35. In other words, when the 1 st thick plate portion 114 and the valve seat 35 are viewed in the vertical direction, the outer peripheral portion 114b of the 1 st thick plate portion 114 is disposed outside the outer peripheral portion 35a of the valve seat 35.

Next, the operation of the compressor 200 will be described.

When the power supply terminal 5 is energized, a current flows through the electric wire portion of the stator 41, and a magnetic field is generated. The magnetic field operates to rotate the rotor 42. That is, torque is generated in the rotor 42, and the rotor 42 rotates. When the rotor 42 rotates, the drive shaft 50 connected to the rotor 42 also rotates. When the drive shaft 50 rotates, the orbiting scroll 21 whose rotation is restricted by the cross ring 70 performs an orbiting motion. Thereby, the compressor 200 starts the compression of the refrigerant by a well-known compression principle. Further, when the rotor 42 rotates, the imbalance of the load due to the oscillation of the orbiting scroll 21 is cancelled by the 1 st balance weight 55 and the 2 nd balance weight 56.

When the compression of the refrigerant is started, the low-temperature low-pressure gas refrigerant flows into the inflow chamber 8 in the closed casing 1 through the suction pipe 6. A part of the low-temperature low-pressure gas refrigerant flowing into the inflow chamber 8 passes through a flow path, not shown, formed in the frame 60 and is sucked into the compression chamber 30 from the outer peripheral side of the compression mechanism 10. The remaining part of the low-temperature low-pressure gaseous refrigerant flowing into the inflow chamber 8 cools the refrigerating machine oil, the motor 40, and the like stored in the oil reservoir of the sealed container 1.

The compression chamber 30 is reduced in volume when moving toward the center of the orbiting scroll 21 by the orbiting motion of the orbiting scroll 21. In this step, the low-temperature low-pressure gas refrigerant sucked into the compression chamber 30 is compressed into a high-temperature high-pressure gas refrigerant. The refrigerant thus compressed flows into the discharge chamber 31 through the communication port 15 of the fixed scroll 11. When the pressure of the refrigerant flowing into and accumulated in the discharge chamber 31 increases, that is, the pressure of the refrigerant discharged from the discharge port 32 increases, the reed valve 110 is elastically deformed by the pressure of the refrigerant with the end portion 111 as a fixed end, and the end portion 112 is separated from the valve seat 35. Thereby, the discharge port 32 is opened. Then, the refrigerant compressed in the compression mechanism 10 is discharged from the discharge port 32, passes between the valve seat 35 and the reed valve 110, and flows into the discharge chamber 9. The high-temperature high-pressure gaseous refrigerant flowing into the discharge chamber 9 passes through the discharge pipe 7 and flows out of the compressor 200.

When the pressure of the refrigerant discharged from the discharge port 32 decreases, the elastic deformation of the reed valve 110 is restored, and the end 112 of the reed valve 110 comes into contact with the valve seat 35. Thereby, the discharge port 32 is closed, and the inflow of the refrigerant from the discharge port 32 into the discharge chamber 9 is completed. In addition, this prevents the refrigerant from flowing backward from the discharge chamber 9 to the discharge port 32.

However, when the discharge port 32 is closed by the reed valve 110 as the elastic deformation of the reed valve 110 is restored, the contact portion of the reed valve 110 that is in contact with the valve seat 35 is applied with an impact at the time of collision against the valve seat 35. In order to suppress damage to the reed valve 110 due to the impact, the thickness of the contact portion of the reed valve 110 with the valve seat 35 needs to be increased to some extent. Therefore, in the reed valve 110 according to embodiment 1, the thickness T1 of the 1 st thick plate portion 114 including the contact portion with the valve seat 35 is also set to a thickness that can suppress damage to the 1 st thick plate portion 114 when the reed valve collides with the valve seat 35.

Here, the conventional reed valve is a plate-like member having the same thickness as a whole as described above. Therefore, in the conventional reed valve, if the thickness of the reed valve is increased in order to suppress damage to the reed valve, the rigidity of the reed valve is increased, and the reed valve is less likely to be elastically deformed. As a result, when the discharge port is opened, the gap between the valve seat and the reed valve is reduced, and the flow path resistance between the valve seat and the reed valve is increased. Therefore, in the conventional compressor including the discharge valve mechanism covering the discharge port so as to be openable and closable from the discharge chamber side, if the thickness of the reed valve is increased to suppress damage to the reed valve, the refrigerant compressed in the compression mechanism portion is less likely to flow into the discharge chamber, and the performance of the compressor is reduced.

On the other hand, in the reed valve 110 of the compressor 200 according to embodiment 1, the thickness T1 of the 1 st plate thickness portion 114 is thicker than the thickness T2 of the 2 nd plate thickness portion 115. In other words, the thickness T2 of the 2 nd thick plate portion 115 is thinner than the thickness T1 of the 1 st thick plate portion 114. Therefore, even when the thickness T1 of the 1 st thick plate portion 114 including the portion in contact with the valve seat 35 is increased in order to suppress damage to the reed valve 110, the 2 nd thick plate portion 115 that is thinner than the 1 st thick plate portion 114 can suppress elastic deformation of the reed valve 110 more difficult than in the related art. Therefore, in the compressor 200 according to embodiment 1, even when the thickness T1 of the 1 st thick plate portion 114 including the portion in contact with the valve seat 35 is increased to suppress damage to the reed valve 110, performance can be suppressed from being lowered as compared with the conventional compressor.

In addition, in the reed valve 110 according to embodiment 1, the thickness T2 of the 2 nd thick plate portion 115 is made smaller than the thickness T1 of the 1 st thick plate portion 114, so that the impact at the time of collision of the 1 st thick plate portion 114 against the valve seat 35 can be suppressed as compared with the conventional reed valve formed of a plate-shaped member having the same thickness as a whole. Therefore, the compressor 200 according to embodiment 1 can suppress damage to the reed valve 110 more than before.

In addition, in the reed valve 110 according to embodiment 1, when the 1 st thick plate portion 114 and the valve seat 35 are viewed in the direction in which the 1 st thick plate portion 114 faces the valve seat 35, the outer peripheral portion 114b of the 1 st thick plate portion 114 is disposed outward of the outer peripheral portion 35a of the valve seat 35. When the 1 st thick plate portion 114 collides against the valve seat 35, the outer peripheral portion 114b of the 1 st thick plate portion 114 is most easily damaged. In the compressor 200 according to embodiment 1, since the outer peripheral portion 114b of the 1 st thick plate portion 114 is disposed outside the outer peripheral portion 35a of the valve seat 35, the outer peripheral portion 114b of the 1 st thick plate portion 114 can be prevented from colliding with the valve seat 35, and damage to the reed valve 110 can be further suppressed.

Further, some conventional scroll compressors do not include the discharge chamber 31. The compressor 200 according to embodiment 1 may not include the discharge chamber 31. In this case, the refrigerant compressed in the compression mechanism 10 is discharged from the communication port 15 of the fixed scroll 11 to the discharge chamber 9. That is, the communication port 15 functions as a discharge port. In the case where the compressor 200 is configured without the discharge chamber 31 as described above, the valve seat 35 may be provided on the peripheral edge of the end portion of the communication port 15 functioning as the discharge port on the discharge chamber 9 side. The discharge valve mechanism 100 may be attached to, for example, the platen 12 of the fixed scroll 11.

In addition, in the case where the reed valve 110 is configured as in embodiment 1, as shown in fig. 2, a surface portion 114a of the 1 st thick plate portion 114 facing the valve pressing piece 120 may protrude toward the valve pressing piece 120 side than a surface portion 115a of the 2 nd thick plate portion 115 facing the valve pressing piece 120. In this case, the valve pressing member 120 may be configured as shown in fig. 4.

Fig. 4 is a vertical sectional view showing the periphery of a discharge valve mechanism of another example of the compressor according to embodiment 1. Fig. 5 is a view of the periphery of the end portion of the valve pressing member shown in fig. 4, as viewed from below. Fig. 5 is a view showing the periphery of the end portion 122 of the valve pressing member 120. In fig. 5, the 1 st thick plate portion 114 and the 2 nd thick plate portion 115 of the reed valve 110 when they are in contact with the valve pressing member 120 are indicated by two-dot chain lines as imaginary lines.

In the valve pressing member 120 shown in fig. 4, a valve pressing member recess 124 is formed in a surface portion 120a opposed to the reed valve 110 at a portion opposed to the 1 st thick plate portion 114 when the reed valve 110 is in contact with the valve pressing member 120, and the valve pressing member recess 124 allows the 1 st thick plate portion 114 to enter when the reed valve 110 is in contact with the valve pressing member 120. The amount of depression of the valve pressing recess 124 is substantially the same as the amount of protrusion of the surface portion 114a of the 1 st plate thickness portion 114 from the surface portion 115a of the 2 nd plate thickness portion 115. By configuring the valve pressing member 120 in this manner, when the reed valve 110 is elastically deformed and comes into contact with the valve pressing member 120, both the 1 st thick plate portion 114 and the 2 nd thick plate portion 115 come into contact with the valve pressing member 120, and the entire reed valve 110 can be substantially uniformly pressed by the valve pressing member 120. This can further suppress damage to the reed valve 110.

As described above, the compressor 200 according to embodiment 1 includes the compression mechanism 10, the closed casing 1, and the discharge valve mechanism 100. The compression mechanism 10 is a scroll-type compression mechanism in which a discharge port 32 is formed and a refrigerant compressed therein is discharged from the discharge port 32. The closed casing 1 houses the compression mechanism 10 and has a discharge chamber 9 formed therein into which the refrigerant discharged from the discharge port 32 flows. The discharge valve mechanism 100 is housed in the closed casing 1, and covers the discharge port 32 from the discharge chamber 9 side so as to be openable and closable. The compression mechanism 10 includes a valve seat 35 at a peripheral edge of an end of the discharge port 32 on the discharge chamber 9 side. The discharge valve mechanism 100 further includes a reed valve 110, and the reed valve 110 extends from a fixed portion with the compression mechanism 10 toward the discharge port 32 and contacts the valve seat 35. The discharge valve mechanism 10 is configured such that the reed valve 110 is elastically deformed at the fixed end as the fixed end by the pressure of the refrigerant discharged from the discharge port 32, and the interior of the compression mechanism portion 10 communicates with the discharge chamber 9. Further, the reed valve 110 includes: a 1 st plate thickness portion 114 including a portion that contacts the valve seat 35; and a 2 nd thick plate portion 115 extending from the 1 st thick plate portion 114 toward the above-described fixing site. Further, the thickness T1 of the 1 st plate thickness portion 114 is thicker than the thickness T2 of the 2 nd plate thickness portion 115.

In embodiment 1 configured as described above, even when the thickness T1 of the 1 st thick plate portion 114 including the portion in contact with the valve seat 35 is increased in order to suppress damage to the reed valve 110, the 2 nd thick plate portion 115 that is thinner than the 1 st thick plate portion 114 can suppress elastic deformation of the reed valve 110 more easily than in the related art. Therefore, in the compressor 200 according to embodiment 1, even when the thickness T1 of the 1 st thick plate portion 114 including the portion in contact with the valve seat 35 is increased to suppress damage to the reed valve 110, performance can be suppressed from being lowered as compared with the conventional compressor.

Embodiment mode 2

The reed valve 110 is not limited to the structure described in embodiment 1. In embodiment 2, several examples of the reed valve 110 will be described. Note that in embodiment 2, items not specifically described are described with the same reference numerals as in embodiment 1 with respect to the same functions and structures as those in embodiment 1.

Fig. 6 is a vertical cross-sectional view showing the periphery of the discharge valve mechanism of the compressor according to embodiment 2, and is a view showing the valve seat and the periphery of the 1 st plate thickness portion of the reed valve. Fig. 7 is a plan view showing the 1 st thick plate portion of the reed valve of fig. 6.

In the 1 st thick plate portion 114 of the reed valve 110 shown in fig. 6 and 7, a reed valve recess 116 recessed in the direction of facing the 1 st thick plate portion 114 and the valve seat 35 is formed at a portion facing the discharge port 32. By forming the reed valve recess 116 in the 1 st plate thickness portion 114, the 1 st plate thickness portion 114 can be made lighter in weight. Further, by making the 1 st thick plate portion 114 lightweight, the impact at the time of collision of the 1 st thick plate portion 114 against the valve seat 35 can be reduced. Therefore, by forming the reed valve recess 116 in the 1 st thick plate portion 114, damage to the reed valve 110 can be further suppressed.

In embodiment 2, in consideration of ease of processing the reed valve 110 and the like, the thickness T3 of the portion of the 1 st thick plate portion 114 where the reed valve recess 116 is formed is the same as the thickness T2 of the 2 nd thick plate portion 115. However, the thickness T3 of the 1 st thick plate portion 114 at the location where the reed valve recess 116 is formed may be different from the thickness T2 of the 2 nd thick plate portion 115. For example, the thickness T3 of the 1 st plate thickness portion 114 where the reed valve recess 116 is formed may be smaller than the thickness T2 of the 2 nd plate thickness portion 115. By configuring the reed valve 110 in this manner, the 1 st thick plate portion 114 can be further reduced in weight, and damage to the reed valve 110 can be further suppressed. For example, the thickness T2 of the 2 nd thick plate portion 115 may be thinner than the thickness T3 of the 1 st thick plate portion 114 where the reed valve recess 116 is formed. By configuring the reed valve 110 in this manner, since the rigidity of the 2 nd thick plate portion 115 is reduced, the impact when the 1 st thick plate portion 114 collides against the valve seat 35 can be suppressed, and the damage of the reed valve 110 can be further suppressed.

In addition, in the case where the 1 st thick plate portion 114 forms the reed valve recess 116, the position where the reed valve recess 116 is formed is preferably the position shown in fig. 6. Specifically, when the 1 st thick plate portion 114 and the discharge port 32 are viewed in the direction in which the 1 st thick plate portion 114 faces the valve seat 35, the reed valve recess 116 is preferably formed inside the peripheral edge portion 32a of the discharge port 32. By forming the reed valve recess 116 in this manner, a portion of the 1 st plate thickness portion 114 that contacts the valve seat 35 becomes a portion having a thickness T1. Therefore, by forming the reed valve recess 116 in this way, damage to the reed valve 110 can be further suppressed.

Here, as shown in fig. 6, the discharge port 32 according to embodiment 2 is formed by a through hole 33 that communicates the inside and the outside of the compression mechanism portion 10, and a tapered portion 34 formed at the peripheral edge of the end portion of the through hole 33 on the discharge chamber 9 side. That is, the peripheral edge 32a of the discharge port 32 is the peripheral edge on the outer periphery side of the tapered portion 34. In the discharge port 32 having such a configuration, when the reed valve recess 116 is formed at a position inside the peripheral edge portion 32a of the discharge port 32, the position at which the reed valve recess 116 is formed is more preferably as follows. When the 1 st thick plate portion 114 and the discharge port 32 are viewed in the direction in which the 1 st thick plate portion 114 faces the valve seat 35, the peripheral edge portion 116a of the reed valve recess 116 is more preferably disposed inside the peripheral edge portion 32a on the outer peripheral side of the tapered portion 34 and outside the peripheral edge portion 33a of the through hole 33. By forming the reed valve recess 116 in this way, the portion of the 1 st thick plate portion 114 that contacts the valve seat 35 becomes the portion of the thickness T1, and the reed valve recess 116 can be formed large. Therefore, by forming the reed valve recess 116 in this way, damage to the reed valve 110 can be further suppressed.

Fig. 8 is a vertical cross-sectional view showing the periphery of a discharge valve mechanism of another example of the compressor according to embodiment 2, and is a view showing the periphery of the 1 st plate thickness portion of the valve seat and the reed valve. Fig. 9 is a plan view showing the 1 st thick plate portion of the reed valve of fig. 8.

The recess formed in the 1 st thick plate portion 114 of the reed valve 110 is not limited to one recess, and for example, as shown in fig. 8 and 9, a plurality of recesses may be formed in the 1 st thick plate portion 114. Specifically, in the 1 st thick plate portion 114 of the reed valve 110 shown in fig. 8 and 9, a 2 nd reed valve recess 117 recessed in the direction in which the 1 st thick plate portion 114 faces the valve seat 35 is formed inside the reed valve recess 116. By configuring the reed valve 110 in this manner, the 1 st thick plate portion 114 can be further reduced in weight, and damage to the reed valve 110 can be further suppressed.

The bottom of the reed valve recess 116 is flat. In other words, in the 1 st thick plate portion 114 in which the above-described reed valve recess 116 is formed, the thickness of the portion in which the reed valve recess 116 is formed is the same. However, the bottom of the reed valve recess 116 may be curved. For example, as shown in fig. 10, the thickness of the portion of the 1 st plate thickness portion 114 where the reed valve recess 116 is formed may be continuously reduced from the peripheral edge portion 116a of the reed valve recess 116 toward the center portion of the reed valve recess 116. The shape of the bottom of the 2 nd reed valve recess 117 is not limited to a flat shape, and may be a curved shape. When the bottom of the reed valve recess 116 is curved, the thickness T3 indicates the thickness of the portion having the smallest thickness among the thicknesses of the portions of the 1 st thick plate portion 114 where the reed valve recess 116 is formed.

As described above, although the compressor 200 described in embodiment 1 and embodiment 2 is a scroll compressor, the compressor 200 is not limited to the scroll compressor. Conventionally, as a compressor provided with a discharge valve mechanism covering a discharge port so as to be openable and closable from a discharge chamber side, various compressors such as a vane compressor, a rotary compressor, and a reciprocating compressor have been known in addition to a scroll compressor. The compressor 200 may be a compressor other than a scroll compressor, such as a vane compressor, a rotary compressor, or a reciprocating compressor. In this case, the valve seat 350 may be provided on the periphery of the discharge chamber side end of the discharge port of the compression mechanism. The discharge valve mechanism 100 described above may be provided in the discharge chamber of the closed casing. As a result, the compressor 200 can obtain the effects described in embodiment 1 and embodiment 2 even if it is a compressor other than a scroll compressor.

Description of the reference numerals

Sealing the container; a central housing; an upper housing; a lower housing; a power terminal; a suction tube; a discharge pipe; flowing into a chamber; a discharge chamber; a compression mechanism portion; a fixed scroll; a platen; a mosquito coil tooth; a sealing member; a communication port; an oscillating scroll; a platen; a lower surface; a, winding teeth; a protrusion; a thrust plate; a keyway; a sealing member; a compression chamber; discharging the chamber; an exhaust port; a peripheral edge portion; a through hole; a peripheral edge portion; a cone; a valve seat; a peripheral portion; a motor; a stator; a rotor; a drive shaft; a main shaft portion; an eccentric shaft portion; 53.. a pump; an oil feed hole; 1 st balance weight; 56.. 2 nd balance weight; a frame; 61... keyway; a main bearing; 65.. subframe; 66.. a secondary bearing; a cross-ring; 71.. a ring; a key; 73... key; a discharge valve mechanism; a fixture; a reed valve; an end portion; an end portion; a through hole; 1 st panel thickness; a surface portion; a peripheral portion; a 2 nd panel thickness portion; a surface portion; a reed valve recess; a peripheral edge portion; a 2 nd reed valve recess; a valve press; a surface portion; an end portion; an end portion; a through hole; a valve press recess; 200.. a compressor; thickness; thickness; thickness.

Claims

1. A compressor, wherein,

the compressor is provided with:

a compression mechanism part which is provided with a discharge port and discharges the refrigerant compressed inside from the discharge port;

a closed container which houses the compression mechanism and has a discharge chamber formed therein into which the refrigerant discharged from the discharge port flows; and

a discharge valve mechanism housed in the sealed container and covering the discharge port from the discharge chamber side so as to be openable and closable,

the compression mechanism portion includes a valve seat at a peripheral edge of the discharge chamber-side end portion of the discharge port,

the discharge valve mechanism includes a reed valve extending from a fixed portion between the discharge valve mechanism and the compression mechanism portion toward the discharge port and contacting the valve seat,

the discharge valve mechanism is configured such that the reed valve is elastically deformed at the fixed portion as a fixed end by the pressure of the refrigerant discharged from the discharge port, and the inside of the compression mechanism portion communicates with the discharge chamber,

the reed valve includes:

a 1 st plate thickness portion including a portion that contacts the valve seat; and

a 2 nd thick plate portion extending from the 1 st thick plate portion toward the fixing portion,

the maximum thickness of the 1 st plate thickness portion is thicker than the thickness of the 2 nd plate thickness portion.

2. The compressor of claim 1,

the discharge valve mechanism includes a valve pressing member that comes into contact with the reed valve when the reed valve is elastically deformed by a pressure of the refrigerant discharged from the discharge port,

a surface portion of the 1 st thick plate portion opposed to the valve pressing member protrudes toward the valve pressing member side than a surface portion of the 2 nd thick plate portion opposed to the valve pressing member,

a valve pressing recess into which the 1 st plate thickness portion enters when the reed valve comes into contact with the valve pressing member is formed in a surface portion of the valve pressing member that faces the reed valve at a portion that faces the 1 st plate thickness portion when the reed valve comes into contact with the valve pressing member.

3. The compressor of claim 1 or 2,

when the 1 st plate thickness portion and the valve seat are viewed in the opposing direction of the 1 st plate thickness portion and the valve seat,

an outer peripheral portion of the 1 st thick plate portion is disposed outward of an outer peripheral portion of the valve seat.

4. A compressor according to any one of claims 1 to 3,

in the 1 st plate thickness portion, a reed valve recess portion that is recessed in an opposing direction of the 1 st plate thickness portion and the valve seat is formed at a portion opposing the discharge port.

5. The compressor of claim 4,

the thickness of the 1 st plate thickness portion where the reed valve recess is formed is thinner than the thickness of the 2 nd plate thickness portion.

6. The compressor of claim 4,

the thickness of the 2 nd thick plate portion is thinner than the thickness of the 1 st thick plate portion at a portion where the reed valve recess is formed.

7. A compressor according to any one of claims 4 to 6,

when the reed valve recess and the discharge port are viewed in the direction in which the 1 st plate thickness portion faces the valve seat, the reed valve recess is formed inward of the peripheral edge portion of the discharge port.

8. The compressor of claim 7,

the discharge port is formed by a through hole for communicating the inside of the compression mechanism with the outside, and a tapered portion formed at a peripheral edge of the discharge chamber side end of the through hole,

when the reed valve recess and the discharge port are viewed in the opposite direction of the 1 st plate thickness portion to the valve seat,

the peripheral edge of the reed valve recess is disposed inside the peripheral edge on the outer periphery of the tapered portion and outside the peripheral edge of the through hole.

9. The compressor according to any one of claims 4 to 8,

in the 1 st plate thickness portion, a 2 nd reed valve recess portion is formed inside the reed valve recess portion, the 2 nd reed valve recess portion being recessed in an opposing direction of the 1 st plate thickness portion and the valve seat.

10. The compressor according to any one of claims 4 to 9,

the thickness of the 1 st plate thickness portion at the position where the reed valve recess is formed becomes continuously thinner from the peripheral edge portion of the reed valve recess toward the central portion of the reed valve recess.

11. The compressor according to any one of claims 1 to 10,

the compression mechanism part is a scroll type compression mechanism part,

the compression mechanism includes:

a fixed scroll having a communication port formed therein for communicating the interior of the compression chamber with the exterior; and

a discharge chamber that covers the communication port on an outer side of the compression chamber and is formed with the discharge port,

the discharge valve mechanism is mounted to the discharge chamber.

12. The compressor according to any one of claims 1 to 10,

the compression mechanism part is a scroll type compression mechanism part,

the compression mechanism part is provided with a fixed scroll which is provided with the discharge port,

the discharge valve mechanism is mounted to the fixed scroll.