WO2021111546A1

WO2021111546A1 - Compressor

Info

Publication number: WO2021111546A1
Application number: PCT/JP2019/047423
Authority: WO
Inventors: 浩平達脇; 増本　浩二; 祐司 ▲高▼村
Original assignee: 三菱電機株式会社
Priority date: 2019-12-04
Filing date: 2019-12-04
Publication date: 2021-06-10
Also published as: JP7241915B2; CN114729630A; JPWO2021111546A1; CN114729630B

Abstract

A compressor according to the present invention is provided with: a compression mechanism part that ejects a refrigerant compressed therein from an ejection port; a sealing container in which the compression mechanism part is accommodated and an ejection chamber in which the refrigerant ejected from the ejection port flows is formed; and an ejection valve mechanism that covers the ejection port from a side of the ejection chamber to be freely openable and closable. The compression mechanism part is provided with a valve seat at a rim of an end on the side of the ejection chamber of the ejection port. The ejection valve mechanism is provided with a reed valve that extends to the ejection port from a fixation spot with the compression mechanism part and contacts the valve seat. The reed valve elastically deforms using the fixation spot as a fixation end due to pressure of the refrigerant ejected from the ejection port. The inside of the compression mechanism part communicates with the ejection chamber. The reed valve is provided with a first plate thickness part including a spot that contacts the valve seat and a second plate thickness part that extends to the fixation spot from the first plate thickness part. The maximum thickness of the first plate thickness part is larger than that of the second plate thickness part.

Description

Compressor

The present invention relates to a compressor that compresses a refrigerant.

The compressor that compresses the refrigerant is used as one of the devices that make up the refrigeration cycle device. Further, the refrigerating cycle device is mounted on, for example, an air conditioner and a refrigerating device.

As one of the types of compressors that are one of the constituent devices of such a refrigeration cycle device, conventionally, the refrigerant discharged from the discharge port of the compression mechanism unit is once discharged to the discharge chamber in the closed container. A compressor equipped with a discharge valve mechanism that covers the discharge port from the discharge chamber side so as to be openable and closable is known. For example, a scroll compressor is known as an example of such a compressor (see Patent Document 1). Specifically, the conventional scroll compressor is provided with a scroll-type compression mechanism unit in which a discharge port is formed and the internally compressed refrigerant is discharged from the discharge port. Further, the conventional scroll compressor includes a closed container in which the compression mechanism unit is housed and a discharge chamber into which the refrigerant discharged from the discharge port of the compression mechanism unit flows in is formed inside. Further, the conventional scroll compressor also includes a discharge valve mechanism in the closed container that covers the discharge port of the compression mechanism portion from the discharge chamber side so as to be openable and closable.

Specifically explaining the configuration around the conventional discharge valve mechanism, the compression mechanism unit is provided with a valve seat on the peripheral edge of the end portion of the discharge port on the discharge chamber side. Further, the discharge valve mechanism includes a reed valve whose part is fixed to the compression mechanism portion. The reed valve is a plate-shaped member having a uniform thickness throughout. The reed valve extends from a fixed portion with the compression mechanism portion toward the discharge port, and the tip portion is in contact with the valve seat. The pressure of the refrigerant discharged from the discharge port acts on the portion of the reed valve facing the discharge port. Therefore, when the pressure of the refrigerant discharged from the discharge port rises, the reed valve elastically deforms at the fixed end with the compression mechanism due to the pressure of the refrigerant, and the tip of the reed valve separates from the valve seat. .. As a result, the discharge port is opened. Then, the refrigerant compressed by the compression mechanism unit is discharged from the discharge port, passes between the valve seat and the reed valve, and flows into the discharge chamber. Further, when the pressure of the refrigerant discharged from the discharge port decreases, the elastic deformation of the reed valve returns, and the tip of the reed valve comes into contact with the valve seat. As a result, the discharge port is closed, and the inflow of the refrigerant from the discharge port into the discharge chamber is completed.

Japanese Unexamined Patent Publication No. 2001-221173

When the elastic deformation of the reed valve returns and the discharge port is closed by the reed valve, the impact when it collides with the valve seat is applied to the contact point of the reed valve with the valve seat. In order to prevent the reed valve from being damaged by this impact, it is necessary to increase the thickness of the contact portion of the reed valve with the valve seat to some extent. Here, as described above, the conventional reed valve is a plate-shaped member having a uniform thickness throughout. Therefore, 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 becomes smaller, and the flow path resistance between the valve seat and the reed valve increases. Therefore, in a conventional compressor equipped with a discharge valve mechanism that covers the discharge port from the discharge chamber side so as to be openable and closable, if the thickness of the reed valve is increased in order to suppress damage to the reed valve, the refrigerant compressed by the compression mechanism portion is used. There is a problem that it becomes difficult for the compressor to flow into the discharge chamber, and the performance of the compressor deteriorates.

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

In the compressor according to the present invention, a discharge port is formed, and a compression mechanism unit that discharges the internally compressed refrigerant from the discharge port and the compression mechanism unit are housed, and the refrigerant discharged from the discharge port flows in. A closed container having a discharge chamber formed inside and a discharge valve mechanism that is housed in the closed container and covers the discharge port from the discharge chamber side so as to be openable and closable. A valve seat is provided on the peripheral edge of the end portion on the discharge chamber side, and the discharge valve mechanism includes a lead valve extending from a fixed portion with the compression mechanism portion to the discharge port and coming into contact with the valve seat, and the discharge port. The lead valve is elastically deformed with the fixed portion as a fixed end due to the pressure of the refrigerant discharged from the compressor, and the inside of the compression mechanism portion and the discharge chamber communicate with each other. A first plate thickness portion including a contact portion and a second plate thickness portion extending from the first plate thickness portion toward the fixed portion are provided, and the maximum thickness of the first plate thickness portion is the second plate. It is thicker than the thickness of the thick part.

In the lead valve of the compressor according to the present invention, the maximum thickness of the first plate thickness portion is thicker than the thickness of the second plate thickness portion. Therefore, even if the thickness of the first plate thickness portion including the portion that comes into contact with the valve seat is increased in order to suppress damage to the reed valve, the lead valve is provided by the second plate thickness portion that is thinner than the first plate thickness portion. Can be suppressed from being less likely to be elastically deformed than before. Therefore, the compressor according to the present invention suppresses deterioration of performance more than before even when the thickness of the first plate thick portion including the portion in contact with the valve seat is increased in order to suppress damage to the reed valve. Can be done.

It is a vertical cross-sectional view of the compressor which concerns on Embodiment 1. It is a vertical cross-sectional view which shows the periphery of the discharge valve mechanism of the compressor which concerns on Embodiment 1. It is a top view of the reed valve of the discharge valve mechanism of the compressor which concerns on Embodiment 1. It is a vertical cross-sectional view which shows the periphery of the discharge valve mechanism of another example of the compressor which concerns on Embodiment 1. It is a figure which looked at the periphery of the end of the valve retainer shown in FIG. 4 from below. It is a vertical cross-sectional view which shows the periphery of the discharge valve mechanism of the compressor which concerns on Embodiment 2, and is the figure which shows the periphery of the 1st plate thickness part of a valve seat and a lead valve. It is a top view which shows the 1st plate thickness part of the reed valve of FIG. It is a vertical cross-sectional view which shows the periphery of the discharge valve mechanism of another example of the compressor which concerns on Embodiment 2, and is the figure which shows the periphery of the 1st plate thickness part of a valve seat and a reed valve. It is a top view which shows the 1st plate thickness part of the reed valve of FIG. It is a vertical cross-sectional view which shows the periphery of the discharge valve mechanism of another example of the compressor which concerns on Embodiment 2, and is the figure which shows the periphery of the 1st plate thickness part of a valve seat and a reed valve.

An example of the compressor according to the present invention will be described in each of the following embodiments. The compressor according to the present invention has a configuration in which the refrigerant discharged from the discharge port of the compression mechanism unit is once discharged into the discharge chamber in the closed container, and covers the discharge port so as to be openable and closable from the discharge chamber side. It is a compressor equipped with a discharge valve mechanism. Conventionally, various types of compressors such as scroll compressors, vane compressors, rotary compressors, and reciprocating compressors are known as compressors provided with a discharge valve mechanism that can open and close the discharge port from the discharge chamber side. ing. In each of the following embodiments, an example of the compressor according to the present invention will be described by taking a scroll compressor as an example. However, the present invention is not limited to the invention adopted in the scroll compressor. The present invention may be adopted for a compressor other than the scroll compressor. Further, in each of the drawings used in the following embodiments, the size of the component of the compressor according to the present invention is different from the size of the component of the compressor actually manufactured by using the present invention. There is.

Embodiment 1.
FIG. 1 is a vertical cross-sectional view of the compressor according to the first embodiment.
Hereinafter, the schematic configuration of the compressor 200 according to the first embodiment will be described with reference to FIG. The compressor 200 is one of the constituent devices of the refrigeration cycle device. More specifically, the compressor 200 sucks in the refrigerant circulating in the refrigeration cycle device, compresses it, and discharges it in a high temperature and high pressure state. Refrigerating cycle devices are used in various industrial machines such as refrigerators, freezers, vending machines, air conditioners, refrigerating devices, and water heaters.

The compressor 200 is a scroll compressor, and includes a scroll type compression mechanism unit 10, a closed container 1, and a discharge valve mechanism 100. The compression mechanism unit 10 has a discharge port 32 formed therein, and discharges the internally compressed refrigerant from the discharge port 32. The compression mechanism unit 10 is a scroll-type compression mechanism unit including a fixed scroll 11 and a swing scroll 21. The compression mechanism portion 10 and the discharge valve mechanism 100 are housed in the closed container 1. Further, inside the closed container 1, a discharge chamber 9 into which the refrigerant discharged from the discharge port 32 of the compression mechanism portion 10 flows is formed. The discharge valve mechanism 100 covers the discharge port 32 of the compression mechanism unit 10 so as to be openable and closable from the discharge chamber 9 side. Further, the compressor 200 according to the first embodiment includes an electric motor 40 and a drive shaft 50 housed in a closed container 1. The drive shaft 50 transmits the driving force of the electric motor 40 to the compression mechanism unit 10. Hereinafter, the configuration of the compressor 200 will be described in more detail.

The closed container 1 constitutes the outer shell of the compressor 200. In the first embodiment, the closed container 1 includes a center shell 2, an upper shell 3, and a lower shell 4. The center shell 2 is a tubular member having an open upper portion and a lower portion. The upper shell 3 is a member that closes the upper opening of the center shell 2. The lower shell 4 is a member that closes the opening at the lower part of the center shell 2. An oil sump is formed at the bottom of the closed container 1. Refrigerating machine oil to be supplied to sliding parts such as the compression mechanism part 10 is stored in the oil pool.

The inside of the closed container 1 is divided into an inflow chamber 8 and a discharge chamber 9 described above by a fixed scroll 11 of the compression mechanism portion 10 and a frame 60 described later. Specifically, as will be described later, the frame 60 is arranged below the fixed scroll 11. In the closed container 1, the position below the frame 60 is the inflow chamber 8, and the position above the fixed scroll 11 is the discharge chamber 9. The closed 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 the first embodiment, the suction pipe 6 is fixed to the center shell 2 of the closed container 1. The discharge pipe 7 is fixed to the upper shell 3 of the closed container 1.

Low temperature and low pressure gaseous refrigerant flows into the inflow chamber 8 through the suction pipe 6. That is, the low-temperature low-pressure gaseous refrigerant compressed by the compression mechanism unit 10 flows into the inflow chamber 8. The high-temperature and high-pressure gaseous refrigerant compressed by the compression mechanism unit 10 and discharged from the discharge port 32 flows into the discharge chamber 9. Therefore, the inflow chamber 8 is a lower pressure chamber than the discharge chamber 9. In other words, the discharge chamber 9 is a higher pressure chamber than the inflow chamber 8. The high-temperature and high-pressure gaseous refrigerant that has flowed into the discharge chamber 9 flows out of the compressor 200 through the discharge pipe 7.

Inside the closed container 1, a frame 60 and a subframe 65 are further housed so as to face each other with the motor 40 in the axial direction of the drive shaft 50. The frame 60 holds the compression mechanism unit 10. The frame 60 is arranged above the electric motor 40 and is located between the electric motor 40 and the compression mechanism portion 10. The subframe 65 is located below the motor 40. The frame 60 and the subframe 65 are fixed to the inner peripheral surface of the center shell 2 of the closed container 1 by shrink fitting or the like.

The drive shaft 50 transmits the driving force of the motor 40 to the swing scroll 21. The swing scroll 21 is eccentrically connected to the drive shaft 50 and is combined with the frame 60 via the old dam ring 70. That is, the old dam ring 70 is arranged between the swing scroll 21 and the frame 60. Specifically, the old dam ring 70 is arranged between the base plate 22 and the frame 60, which will be described later, of the swing scroll 21. The oldam ring 70 includes a ring portion 71, a pair of keys 72 provided on the upper surface of the ring portion 71, and a pair of keys 73 provided on the 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 on the lower surface 22a of the base plate 22 of the swing scroll 21. Further, the frame 60 is formed with a pair of key grooves 61 into which a pair of keys 73 are slidably inserted. When the swing scroll 21 tries to rotate due to the driving force of the electric motor 40, the rotation of the swing scroll 21 is regulated by the old dam ring 70. Therefore, when the swing scroll 21 tries to rotate due to the driving force of the electric motor 40, the swing scroll 21 revolves without rotating. That is, the rocking scroll 21 swings.

The compression mechanism unit 10 includes a fixed scroll 11 and a swing scroll 21 as described above. The fixed scroll 11 includes a base plate 12 and spiral teeth 13. The spiral teeth 13 are provided on the lower surface of the base plate 12. The fixed scroll 11 is fixed to the frame 60 by a bolt or the like (not shown).

The swing scroll 21 includes a base plate 22 and spiral teeth 23. The upper surface of the base plate 22 faces the fixed scroll 11. The spiral tooth 23 has substantially the same shape as the spiral tooth 13 and is provided on the upper surface of the base plate 22. Further, the swing scroll 21 is provided with a hollow cylindrical boss portion 24 on the lower surface of the base plate 22.

The swing scroll 21 and the fixed scroll 11 are arranged in the closed container 1 in a state where the spiral teeth 23 and the spiral teeth 13 are combined. In the state where the spiral tooth 23 and the spiral tooth 13 are combined, the winding direction of the spiral tooth 23 and the winding direction of the spiral tooth 13 are opposite to each other. By combining the spiral teeth 13 of the fixed scroll 11 and the spiral teeth 23 of the swing scroll 21 in this way, a compression chamber 30 for compressing the refrigerant is formed between the spiral teeth 13 and the spiral teeth 23. .. The volume of the compression chamber 30 changes due to the swinging motion of the swinging scroll 21. A seal member 14 is provided at the tip of the spiral tooth 13 of the fixed scroll 11 in order to reduce refrigerant leakage from between the spiral tooth 13 and the base plate 22 of the swing scroll 21. Similarly, a seal member 27 is provided at the tip of the spiral tooth 23 of the swing scroll 21 in order to reduce refrigerant leakage from between the spiral tooth 23 and the base plate 12 of the fixed scroll 11.

A communication port 15 for communicating the inside and the outside of the compression chamber 30 is formed at a substantially central position of the base plate 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 portion 10 of the compressor 200 according to the first embodiment includes a 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 base plate 12 of the fixed scroll 11 with bolts or the like. Further, a discharge port 32 is formed in the discharge chamber 31. Therefore, in the first embodiment, the refrigerant compressed in the compression chamber 30 is discharged from the communication port 15 into the discharge chamber 31, and then flows into the discharge chamber 9 from the discharge port 32. .. That is, in the first embodiment, the discharge valve mechanism 100 that covers the discharge port 32 of the compression mechanism unit 10 so as to be openable and closable from the discharge chamber 9 side is attached to the discharge chamber 31. The discharge valve mechanism 100 prevents the backflow of the refrigerant from the discharge chamber 9 to the discharge port 32. Details of the discharge valve mechanism 100 will be described later.

The frame 60 has a surface facing the lower surface 22a of the base plate 22 of the rocking scroll 21 from below. This surface is a surface that swingably supports the rocking scroll 21, and is a surface that supports the load acting on the rocking scroll 21 in the process of compressing the refrigerant. Therefore, a thrust plate 25 is provided on this surface for the purpose of improving the slidability of the rocking scroll 21 with the lower surface 22a of the base plate 22. Further, the frame 60 is formed with a flow path (not shown) that guides the refrigerant flowing into the inflow chamber 8 into the compression mechanism portion 10.

The electric motor 40 that supplies the 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 shell 2 of the closed container 1 by shrink fitting or the like. Further, 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 arranged on the inner peripheral side of the stator 41, and is connected to the spindle portion 51 of the drive shaft 50, which will be described later, by shrink fitting or the like.

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

When the spindle portion 51 rotates, the eccentric shaft portion 52 that is eccentric with respect to the spindle portion 51 becomes the distance between the axis of the spindle portion 51 and the axis of the eccentric shaft portion 52 with respect to the spindle portion 51. Rotate with a radius. As a result, the swing scroll 21 connected to the eccentric shaft portion 52 tends to rotate with respect to the spindle portion 51 with the above-mentioned radius. In other words, the swing scroll 21 attempts to rotate with respect to the fixed fixed scroll 11 with the above-mentioned radius. At this time, as described above, the rotation of the swing scroll 21 is regulated by the old dam ring 70. Therefore, the swing scroll 21 swings with respect to the fixed scroll 11 with the above-mentioned radius.

Further, the compressor 200 according to the first embodiment includes a first balance weight 55 and a second balance weight 56 in order to offset the imbalance of the load caused by the swinging of the swing scroll 21. The first balance weight 55 is attached to the spindle portion 51 at a position between the frame 60 and the rotor 42 by shrink fitting or the like. The second balance weight 56 is attached to the lower part 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 the first embodiment. FIG. 3 is a plan view of the reed valve of the discharge valve mechanism of the compressor according to the first embodiment. Note that FIG. 3 shows 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 by a two-dot chain line which is an imaginary line. Hereinafter, the configuration around the discharge valve mechanism 100 and the detailed configuration of the discharge valve mechanism 100 will be described with reference to FIGS. 2 and 3.

The discharge chamber 31 of the compression mechanism unit 10 is provided with, for example, a valve seat 35 having a substantially annular shape in a plan view on the peripheral edge of the end portion of the discharge port 32 on the discharge chamber 9 side. The discharge valve mechanism 100 includes a reed valve 110 that covers the discharge port 32 of the compression mechanism unit 10 so as to be openable and closable from the discharge chamber 9 side. The reed valve 110 is fixed to the discharge chamber 31 at the fixing point. In the first embodiment, the end 111 of the reed valve 110 is a fixed portion of the reed valve 110 with the discharge chamber 31. Further, in the first embodiment, the reed valve 110 is fixed to the discharge chamber 31 by using a fixture 101 which is a bolt. Specifically, a through hole 113 is formed at the end 111 of the reed valve 110. The lead valve 110 is fixed to the discharge chamber 31 by screwing the fixture 101 inserted into the through hole 113 into the female screw portion formed in the discharge chamber.

The reed valve 110 extends from the end portion 111, which is a fixed portion, toward the discharge port 32. Then, the end portion 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 of the reed valve 110, the end portion 111 becomes a fixed end and the end portion 112 becomes a free end and elastically deforms. As a result, the inside of the compression mechanism unit 10 and the discharge chamber 9 communicate with each other. More specifically, when the pressure of the refrigerant discharged from the discharge port 32 increases, the reed valve 110 elastically deforms with the end 111 as a fixed end due to the pressure of the refrigerant, and the end 112 separates from the valve seat 35. .. As a result, the discharge port 32 is opened. Then, the refrigerant compressed by the compression mechanism unit 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. Further, when the pressure of the refrigerant discharged from the discharge port 32 decreases, the elastic deformation of the reed valve 110 returns, and the end portion 112 of the reed valve 110 comes into contact with the valve seat 35. As a result, the discharge port 32 is closed, and the inflow of the refrigerant from the discharge port 32 into the discharge chamber 9 is completed. Further, this prevents the backflow of the refrigerant from the discharge chamber 9 to the discharge port 32.

Further, the discharge valve mechanism 100 according to the first embodiment includes a valve retainer 120. The valve retainer 120 prevents the reed valve 110 from bending too much due to contact with the reed valve 110 when the reed valve 110 is elastically deformed by the pressure of the refrigerant discharged from the discharge port 32. Specifically, the valve retainer 120 is arranged above the lead valve 110. A through hole 123 is formed in the end portion 121 of the valve retainer 120. The valve retainer 120 is fixed to the discharge chamber 31 together with the reed valve 110 by screwing the fixture 101 inserted into the through hole 123 into the female screw portion formed in the discharge chamber. Further, the end portion 122 of the valve retainer 120 is arranged above the end portion 112 of the reed valve 110. When the reed valve 110 is not elastically deformed, the gap between the reed valve 110 and the valve retainer 120 gradually widens from the end 121 to the end 122. As a result, when the reed valve 110 is elastically deformed by the pressure of the refrigerant discharged from the discharge port 32, the reed valve 110 and the valve retainer 120 come into contact with each other, and the reed valve 110 can be prevented from bending too much.

Here, the conventional reed valve is a plate-shaped member having a uniform thickness throughout. On the other hand, the reed valve 110 according to the first embodiment has a different thickness depending on the location. Specifically, the portion on the end 112 side that includes the portion that comes into contact with the valve seat 35 is the first plate thick portion 114 having a thickness T1. Further, a portion extending from the first plate thick portion 114 toward the end portion 111 which is a fixed portion is a second plate thick portion 115 having a thickness T2. The thickness T1 of the first plate thick portion 114 is thicker than the thickness T2 of the second plate thick portion 115. When unevenness is formed on the first plate thickness portion 114 as described later in the second embodiment, the thickness T1 of the first plate thickness portion 114 represents the maximum thickness of the first plate thickness portion 114. To do.

Further, in the first embodiment, when the first plate thickness portion 114 and the valve seat 35 are observed in the direction opposite to the first plate thickness portion 114 and the valve seat 35, the outer peripheral portion 114b of the first plate thickness portion 114 is formed. , It is arranged outside the outer peripheral portion 35a of the valve seat 35. In other words, when observing the first plate thickness portion 114 and the valve seat 35 in the vertical direction, the outer peripheral portion 114b of the first plate thickness portion 114 is arranged 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 to generate a magnetic field. This magnetic field acts 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 accordingly. When the drive shaft 50 rotates, the swing scroll 21 whose rotation is regulated by the old dam ring 70 swings. As a result, the compressor 200 starts compressing the refrigerant according to a known compression principle. When the rotor 42 rotates, the first balance weight 55 and the second balance weight 56 cancel the imbalance of the load caused by the swing of the swing scroll 21.

When the compression of the refrigerant is started, the low-temperature low-pressure gaseous refrigerant flows into the inflow chamber 8 in the closed container 1 through the suction pipe 6. A part of the low-temperature and low-pressure gaseous refrigerant that has flowed into the inflow chamber 8 is sucked into the compression chamber 30 from the outer peripheral side of the compression mechanism portion 10 through a flow path (not shown) formed in the frame 60. Further, the remaining part of the low-temperature low-pressure gaseous refrigerant that has flowed into the inflow chamber 8 cools the refrigerating machine oil, the electric motor 40, and the like stored in the oil sump of the closed container 1.

The volume of the compression chamber 30 shrinks as it moves to the center of the rocking scroll 21 due to the rocking motion of the rocking scroll 21. By this step, the low-temperature low-pressure gaseous refrigerant sucked into the compression chamber 30 is compressed into the high-temperature and high-pressure gaseous refrigerant. The refrigerant compressed in this way flows into the discharge chamber 31 through the communication port 15 of the fixed scroll 11. Then, when the pressure of the refrigerant flowing into and stored in the discharge chamber 31 rises, that is, when the pressure of the refrigerant discharged from the discharge port 32 rises, the pressure of the refrigerant causes the lead valve 110 to end. The 111 is elastically deformed with the fixed end, and the end 112 is separated from the valve seat 35. As a result, the discharge port 32 is opened. Then, the refrigerant compressed by the compression mechanism unit 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 and high-pressure gaseous refrigerant that has flowed into the discharge chamber 9 flows out of the compressor 200 through the discharge pipe 7.

Further, when the pressure of the refrigerant discharged from the discharge port 32 decreases, the elastic deformation of the reed valve 110 returns, and the end 112 of the reed valve 110 comes into contact with the valve seat 35. As a result, the discharge port 32 is closed, and the inflow of the refrigerant from the discharge port 32 into the discharge chamber 9 is completed. Further, this prevents the backflow of the refrigerant from the discharge chamber 9 to the discharge port 32.

By the way, when the elastic deformation of the reed valve 110 returns and the discharge port 32 is closed by the reed valve 110, an impact when the reed valve 110 collides with the valve seat 35 is applied to the contact point with the valve seat 35. In order to prevent the reed valve 110 from being damaged by this impact, it is necessary to increase the thickness of the contact portion of the reed valve 110 with the valve seat 35 to some extent. Therefore, also in the reed valve 110 according to the first embodiment, when the thickness T1 of the first plate thickness portion 114 including the contact portion with the valve seat 35 collides with the valve seat 35, the first plate thickness portion 114 The thickness is set so that damage can be suppressed.

Here, as described above, the conventional reed valve is a plate-shaped member having a uniform thickness throughout. 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 becomes smaller, and the flow path resistance between the valve seat and the reed valve increases. Therefore, in a conventional compressor provided with a discharge valve mechanism that covers the discharge port from the discharge chamber side so as to be openable and closable, if the thickness of the reed valve is increased in order to suppress damage to the reed valve, compression is performed by the compression mechanism portion. It becomes difficult for the refrigerant to flow into the discharge chamber, and the performance of the compressor deteriorates.

On the other hand, in the reed valve 110 of the compressor 200 according to the first embodiment, the thickness T1 of the first plate thickness portion 114 is thicker than the thickness T2 of the second plate thickness portion 115. In other words, the thickness T2 of the second plate thickness portion 115 is thinner than the thickness T1 of the first plate thickness portion 114. Therefore, even if the thickness T1 of the first plate thickness 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 second plate thickness is thinner than that of the first plate thickness portion 114. The portion 115 can prevent the reed valve 110 from being less likely to be elastically deformed than before. Therefore, the compressor 200 according to the first embodiment has a performance even when the thickness T1 of the first plate thick 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 decrease can be suppressed more than before.

Further, in the reed valve 110 according to the first embodiment, the thickness T2 of the second plate thickness portion 115 is thinner than the thickness T1 of the first plate thickness portion 114, so that the thickness T2 is uniform throughout. Compared with the conventional reed valve which is a thick plate-shaped member, the impact when the first plate thick portion 114 collides with the valve seat 35 can be suppressed. Therefore, the compressor 200 according to the first embodiment can further suppress damage to the reed valve 110 as compared with the conventional one.

Further, in the reed valve 110 according to the first embodiment, when the first plate thickness portion 114 and the valve seat 35 are observed in the direction opposite to the first plate thickness portion 114 and the valve seat 35, the first plate thickness portion is observed. The outer peripheral portion 114b of 114 is arranged outside the outer peripheral portion 35a of the valve seat 35. When the first plate thickness portion 114 collides with the valve seat 35, the outer peripheral portion 114b of the first plate thickness portion 114 is most likely to be damaged. In the compressor 200 according to the first embodiment, since the outer peripheral portion 114b of the first plate thick portion 114 is arranged outside the outer peripheral portion 35a of the valve seat 35, the outer peripheral portion 114b of the first plate thick portion 114 The collision between the valve seat 35 and the valve seat 35 can be prevented, and damage to the lead valve 110 can be further suppressed.

Note that some conventional scroll compressors do not have a discharge chamber 31. The compressor 200 according to the first embodiment may also have a configuration that does not include the discharge chamber 31. In this case, the refrigerant compressed by the compression mechanism unit 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. When the compressor 200 is not provided with 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. Then, the discharge valve mechanism 100 may be attached to, for example, the base plate 12 of the fixed scroll 11.

Further, when the reed valve 110 is configured as in the first embodiment, as shown in FIG. 2, the surface portion 114a facing the valve retainer 120 in the first plate thickness portion 114 is formed in the second plate thickness portion 115. The surface portion 115a facing the valve retainer 120 may protrude toward the valve retainer 120. In such a case, the valve retainer 120 may be configured as shown in FIG.

FIG. 4 is a vertical cross-sectional view showing the periphery of the discharge valve mechanism of another example of the compressor according to the first embodiment. FIG. 5 is a view of the periphery of the end of the valve retainer shown in FIG. 4 as viewed from below. Note that FIG. 5 is a diagram showing the periphery of the end portion 122 of the valve retainer 120. Further, in FIG. 5, the first plate thickness portion 114 and the second plate thickness portion 115 of the reed valve 110 when it comes into contact with the valve retainer 120 are shown by an alternate long and short dash line, which is an imaginary line.

In the valve retainer 120 shown in FIG. 4, the reed valve 110 is provided on the surface portion 120a facing the reed valve 110 at a position facing the first plate thick portion 114 when the reed valve 110 comes into contact with the valve retainer 120. A valve holding recess 124 is formed in which the first plate thick portion 114 enters when it comes into contact with the valve holding 120. The recessed amount of the valve holding recess 124 is substantially the same as the protruding amount of the surface portion 114a of the first plate thick portion 114 protruding from the surface portion 115a of the second plate thick portion 115. By configuring the valve retainer 120 in this way, when the reed valve 110 is elastically deformed and comes into contact with the valve retainer 120, both the first plate thickness portion 114 and the second plate thickness portion 115 come into contact with the valve retainer 120. , The entire reed valve 110 can be pressed substantially uniformly by the valve retainer 120. As a result, damage to the reed valve 110 can be further suppressed.

As described above, the compressor 200 according to the first embodiment includes a compression mechanism unit 10, a closed container 1, and a discharge valve mechanism 100. The compression mechanism unit 10 is a scroll-type compression mechanism unit in which a discharge port 32 is formed and the internally compressed refrigerant is discharged from the discharge port 32. In the closed container 1, the compression mechanism portion 10 is housed, and a discharge chamber 9 into which the refrigerant discharged from the discharge port 32 flows is formed inside. The discharge valve mechanism 100 is housed in a closed container 1 and covers the discharge port 32 so as to be openable and closable from the discharge chamber 9 side. Further, the compression mechanism unit 10 is provided with a valve seat 35 on the peripheral edge of the end portion of the discharge port 32 on the discharge chamber 9 side. Further, the discharge valve mechanism 100 includes a reed valve 110 that extends from a fixed portion with the compression mechanism portion 10 to the discharge port 32 and comes into contact with the valve seat 35. Further, the discharge valve mechanism 100 has a configuration in which the lead valve 110 is elastically deformed with the fixed portion as a fixed end due to the pressure of the refrigerant discharged from the discharge port 32, and the inside of the compression mechanism portion 10 and the discharge chamber 9 communicate with each other. It has become. Further, the reed valve 110 includes a first plate thickness portion 114 including a portion in contact with the valve seat 35, and a second plate thickness portion 115 extending from the first plate thickness portion 114 toward the fixing portion. The thickness T1 of the first plate thickness portion 114 is thicker than the thickness T2 of the second plate thickness portion 115.

In the first embodiment configured as described above, even when the thickness T1 of the first plate thickness 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 first The second plate thickness portion 115, which is thinner than the plate thickness portion 114, can prevent the reed valve 110 from becoming less likely to be elastically deformed than before. Therefore, the compressor 200 according to the first embodiment has a performance even when the thickness T1 of the first plate thick 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 decrease can be suppressed more than before.

Embodiment 2.
The reed valve 110 is not limited to the configuration shown in the first embodiment. In the second embodiment, some examples of the reed valve 110 will be introduced. In the second embodiment, items not particularly described will be the same as those in the first embodiment, and the same functions and configurations as those in the first embodiment will be described using the same reference numerals.

FIG. 6 is a vertical cross-sectional view showing the periphery of the discharge valve mechanism of the compressor according to the second embodiment, and is a diagram showing the periphery of the first plate thick portion of the valve seat and the reed valve. FIG. 7 is a plan view showing a first plate thickness portion of the reed valve of FIG.
The first plate thickness portion 114 of the lead valve 110 shown in FIGS. 6 and 7 has a lead valve recess 116 recessed in the direction opposite to the first plate thickness portion 114 and the valve seat 35 at a position facing the discharge port 32. It is formed. By forming the reed valve recess 116 in the first plate thickness portion 114, the weight of the first plate thickness portion 114 can be reduced. Then, by reducing the weight of the first plate thick portion 114, the impact when the first plate thick portion 114 collides with the valve seat 35 can be reduced. Therefore, by forming the reed valve recess 116 in the first plate thick portion 114, damage to the reed valve 110 can be further suppressed.

In the second embodiment, the thickness T3 of the first plate thickness portion 114 and the thickness T3 of the second plate thickness portion 115 of the portion where the reed valve recess 116 is formed are taken into consideration in consideration of ease of processing of the reed valve 110 and the like. The thickness of T2 is the same as that of T2. However, the thickness T3 of the first plate thickness portion 114 and the thickness T2 of the second plate thickness portion 115 at the location where the reed valve recess 116 is formed may be different. For example, the thickness T3 of the first plate thickness portion 114 at the portion where the reed valve recess 116 is formed may be thinner than the thickness T2 of the second plate thickness portion 115. By configuring the reed valve 110 in this way, the thickness of the first plate thick portion 114 can be further reduced, and damage to the reed valve 110 can be further suppressed. Further, for example, the thickness T2 of the second plate thick portion 115 may be thinner than the thickness T3 of the first plate thick portion 114 where the reed valve recess 116 is formed. By configuring the reed valve 110 in this way, the rigidity of the second plate thickness portion 115 is reduced, so that the impact when the first plate thickness portion 114 collides with the valve seat 35 can be suppressed, and the reed valve 110 is damaged. Can be further suppressed.

Further, when the reed valve recess 116 is formed in the first plate thick portion 114, the position where the reed valve recess 116 is formed is preferably the position shown in FIG. Specifically, when observing the first plate thickness portion 114 and the discharge port 32 in the direction opposite to the first plate thickness portion 114 and the valve seat 35, the lead valve recess 116 is larger than the peripheral edge portion 32a of the discharge port 32. It is preferably formed at an inner position. By forming the reed valve recess 116 in this way, the portion of the first plate thick portion 114 that comes into contact with the valve seat 35 becomes a thick 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 the second embodiment has a through hole 33 for communicating the inside and the outside of the compression mechanism portion 10 and an end of the through hole 33 on the discharge chamber 9 side. It is formed by a tapered portion 34 formed on the peripheral edge of the portion. That is, the peripheral edge portion 32a of the discharge port 32 becomes the peripheral edge portion on the outer peripheral 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 following positions are more preferable for the formation position of the reed valve recess 116. When observing the first plate thickness portion 114 and the discharge port 32 in the direction opposite to the first plate thickness portion 114 and the valve seat 35, the peripheral edge portion 116a of the reed valve recess 116 is the peripheral edge portion 32a on the outer peripheral side of the tapered portion 34. It is more preferable that the position is located on the inside of the through hole 33 and on the outside of the peripheral edge portion 33a of the through hole 33. By forming the reed valve recess 116 in this way, the portion of the first plate thick portion 114 that comes into contact with the valve seat 35 becomes a portion having a thickness T1, and the reed valve recess 116 can also be formed to be 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 the discharge valve mechanism of another example of the compressor according to the second embodiment, and is a diagram showing the periphery of the first plate thick portion of the valve seat and the reed valve. FIG. 9 is a plan view showing a first plate thickness portion of the reed valve of FIG.
The recess formed in the first plate thickness portion 114 of the reed valve 110 is not limited to one recess, and for example, as shown in FIGS. 8 and 9, a plurality of recesses are formed in the first plate thickness portion 114. You may. Specifically, the first plate thickness portion 114 of the lead valve 110 shown in FIGS. 8 and 9 has a second lead recessed inside the lead valve recess 116 in the direction in which the first plate thickness portion 114 and the valve seat 35 face each other. A valve recess 117 is formed. By configuring the reed valve 110 in this way, the thickness of the first plate thick portion 114 can be further reduced, and damage to the reed valve 110 can be further suppressed.

FIG. 10 is a vertical cross-sectional view showing the periphery of the discharge valve mechanism of another example of the compressor according to the second embodiment, and is a diagram showing the periphery of the first plate thick portion of the valve seat and the reed valve.
The bottom of the reed valve recess 116 described above had a flat shape. In other words, in the first plate thick portion 114 in which the above-mentioned reed valve recess 116 is formed, the thickness of the portion where the reed valve recess 116 is formed is uniform. Not limited to this, the bottom portion of the lead valve recess 116 may have a curved surface shape. For example, as shown in FIG. 10, the thickness of the first plate thick portion 114 at the portion where the reed valve recess 116 is formed is continuous from the peripheral edge portion 116a of the reed valve recess 116 toward the central portion of the reed valve recess 116. The configuration may be thin. The shape of the bottom of the second reed valve recess 117 is not limited to a flat shape, but may be a curved shape. When the bottom of the reed valve recess 116 has a curved surface shape, the above-mentioned thickness T3 is the smallest of the thicknesses of the first plate thick portion 114 where the reed valve recess 116 is formed. It shall represent the thickness of.

As described above, the compressor 200 shown in the first and second embodiments is a scroll compressor, but the compressor 200 is not limited to the scroll compressor. Conventionally, as a compressor equipped with a discharge valve mechanism that can open and close the discharge port from the discharge chamber side, various types of compressors such as a vane compressor, a rotary compressor, and a reciprocating compressor are used in addition to the scroll compressor. It has been known. The compressor 200 may be a compressor other than the scroll compressor, such as a vane compressor, a rotary compressor, and a reciprocating compressor. At this time, the valve seat 35 described above may be provided on the peripheral edge of the end of the discharge port of the compression mechanism on the discharge chamber side. Then, the above-mentioned discharge valve mechanism 100 may be provided in the discharge chamber of the closed container. As a result, the compressor 200 can obtain the effects shown in the first and second embodiments even if the compressor is a compressor other than the scroll compressor.

1 closed container, 2 center shell, 3 upper shell, 4 lower shell, 5 power supply terminal, 6 suction pipe, 7 discharge pipe, 8 inflow chamber, 9 discharge chamber, 10 compression mechanism, 11 fixed scroll, 12 base plate, 13 swirl Teeth, 14 seal members, 15 communication ports, 21 rocking scrolls, 22 base plates, 22a lower surface, 23 spiral teeth, 24 bosses, 25 thrust plates, 26 keyways, 27 seal members, 30 compression chambers, 31 discharge chambers, 32 discharge port, 32a peripheral part, 33 through hole, 33a peripheral part, 34 tapered part, 35 valve seat, 35a outer peripheral part, 40 motor, 41 stator, 42 rotor, 50 drive shaft, 51 spindle part, 52 eccentric shaft Part, 53 pump, 54 oil supply hole, 55 1st balance weight, 56 2nd balance weight, 60 frame, 61 keyway, 62 main bearing, 65 subframe, 66 auxiliary bearing, 70 oldam ring, 71 ring part, 72 Key, 73 key, 100 discharge valve mechanism, 101 fixture, 110 lead valve, 111 end, 112 end, 113 through hole, 114 first plate thickness, 114a surface, 114b outer circumference, 115 second plate thickness Part, 115a surface part, 116 lead valve recess, 116a peripheral part, 117 second lead valve recess, 120 valve retainer, 120a surface portion, 121 end, 122 end, 123 through hole, 124 valve retainer recess, 200 compressor , T1 thickness, T2 thickness, T3 thickness.

Claims

A compression mechanism unit in which a discharge port is formed and internally compressed refrigerant is discharged from the discharge port.
A closed container in which the compression mechanism unit is housed and a discharge chamber into which the refrigerant discharged from the discharge port flows is formed.
A discharge valve mechanism that is housed in the closed container and covers the discharge port from the discharge chamber side so as to be openable and closable.
With
The compression mechanism portion includes a valve seat on the peripheral edge of the end portion of the discharge port on the discharge chamber side.
The discharge valve mechanism includes a reed valve that extends from a fixed portion with the compression mechanism portion to the discharge port and contacts the valve seat.
The reed valve is elastically deformed by the pressure of the refrigerant discharged from the discharge port with the fixed portion as a fixed end, and the inside of the compression mechanism portion and the discharge chamber communicate with each other.
The reed valve is
The first plate thick part including the part that comes into contact with the valve seat,
A second plate thickness portion extending from the first plate thickness portion toward the fixing portion, and a second plate thickness portion.
With
A compressor in which the maximum thickness of the first plate thickness portion is thicker than the thickness of the second plate thickness portion.
The discharge valve mechanism includes a valve retainer that comes into contact with the reed valve when the reed valve is elastically deformed by the pressure of the refrigerant discharged from the discharge port.
The surface portion of the first plate thickness portion facing the valve retainer protrudes toward the valve retainer side from the surface portion of the second plate thickness portion facing the valve retainer.
When the reed valve comes into contact with the valve retainer on the surface portion of the valve retainer facing the reed valve at a portion facing the first plate thickness portion when the reed valve comes into contact with the valve retainer. The compressor according to claim 1, wherein a valve holding recess in which the thick portion of the first plate is inserted is formed.
When the first plate thickness portion and the valve seat are observed in the direction opposite to the first plate thickness portion and the valve seat, when the first plate thickness portion and the valve seat are observed.
The compressor according to claim 1 or 2, wherein the outer peripheral portion of the first plate thick portion is arranged outside the outer peripheral portion of the valve seat.
The first plate thick portion has a lead valve recess formed in a portion facing the discharge port so as to be recessed in the direction facing the first plate thick portion and the valve seat. The compressor according to any one item.
The compressor according to claim 4, wherein the thickness of the first plate thickness portion at the portion where the reed valve recess is formed is thinner than the thickness of the second plate thickness portion.
The compressor according to claim 4, wherein the thickness of the second plate thickness portion is thinner than the thickness of the first plate thickness portion at the portion where the reed valve recess is formed.
When the reed valve recess and the discharge port are observed in the direction opposite to the first plate thick portion and the valve seat, the reed valve recess is formed at a position inside the peripheral edge portion of the discharge port. The compressor according to any one of claims 4 to 6.
The discharge port is formed of a through hole that communicates the inside and the outside of the compression mechanism portion and a tapered portion formed on the peripheral edge of the end portion of the through hole on the discharge chamber side.
When observing the reed valve recess and the discharge port in the direction opposite to the first plate thick portion and the valve seat,
The compressor according to claim 7, wherein the peripheral edge portion of the reed valve recess is located inside the peripheral edge portion on the outer peripheral side of the tapered portion and outside the peripheral edge portion of the through hole.
Claims 4 to 8 are formed in the first plate thick portion so that a second lead valve recess recessed in the direction opposite to the first plate thickness portion and the valve seat is formed inside the lead valve recess. The compressor according to any one of the above.
The thickness of the first plate thick portion of the portion where the reed valve recess is formed is continuously reduced from the peripheral edge of the reed valve recess toward the center of the reed valve recess. The compressor according to any one of claims 9.
The compression mechanism unit is a scroll type compression mechanism unit.
The compression mechanism unit
A fixed scroll with a communication port that communicates the inside and outside of the compression chamber,
A discharge chamber in which the communication port is covered on the outer side of the compression chamber and the discharge port is formed,
With
The compressor according to any one of claims 1 to 10, wherein the discharge valve mechanism is attached to the discharge chamber.
The compression mechanism unit is a scroll type compression mechanism unit.
The compression mechanism unit includes a fixed scroll on which the discharge port is formed.
The compressor according to any one of claims 1 to 10, wherein the discharge valve mechanism is attached to the fixed scroll.