Scroll compressor and refrigeration cycle device

Abstract

This scroll compressor comprises: a compression mechanism part which has a compression chamber that compresses a refrigerant and a plate that has formed therein a discharge port from which the refrigerant compressed by the compression chamber is discharged; a rotating shaft which is disposed such that the axial direction is the direction of gravity and which drives the compression mechanism part; a discharge valve mechanism which has a discharge valve that opens and closes the discharge port; and a valve seat which has an annular groove that is formed in the plate so as to surround a downstream opening of the discharge port, and on which the discharge valve is seated. The plate has an oil holding part which is formed so as to be recessed downward from an upper surface of the plate and which holds oil. The downstream opening of the discharge port is open in the oil holding part.

Description

Scroll compressor and refrigeration cycle device

[0001] The present disclosure relates to a scroll compressor and a refrigeration cycle apparatus including a discharge valve mechanism that opens and closes a discharge port that discharges a refrigerant.

[0002] The scroll compressor has a compression mechanism that compresses a refrigerant in a compression chamber formed by a fixed scroll and an orbiting scroll, and a rotating shaft that drives the compression mechanism. Each of the fixed scroll and the orbiting scroll has a configuration in which a scroll body is formed on a base plate. The compression mechanism has a compression chamber formed by combining the scroll bodies of the fixed scroll and the orbiting scroll. The scroll compressor causes the orbiting scroll to oscillate, moving the scroll from the outside to the center of the rotating shaft while reducing the volume of the compression chamber, and discharging the compressed refrigerant from the compression chamber to a discharge chamber.

[0003] In the scroll compressor, a fixed base plate, which is the base plate of the fixed scroll, is formed with a discharge port that discharges refrigerant compressed in the compression chamber to the discharge chamber. A downstream opening of the discharge port is open to the upper surface of the fixed base plate, and a discharge valve mechanism is disposed on the upper surface of the fixed base plate to cover the downstream opening of the discharge port. The discharge valve mechanism prevents refrigerant from leaking from the discharge chamber to the compression chamber and includes a discharge valve that opens and closes the discharge port and a valve guard that regulates the amount of deflection of the discharge valve. The discharge valve is seated on a valve seat formed on the fixed base plate so as to surround the downstream opening of the discharge port. The discharge valve mechanism airtightly separates the discharge chamber, which communicates with the downstream opening of the discharge port, from the compression chamber, which communicates with the upstream opening of the discharge port, by sealing the gap between the discharge valve and the valve seat with an oil film.

[0004] In scroll compressors equipped with this type of discharge valve mechanism, the oil discharged from the discharge port into the discharge chamber together with the refrigerant accumulates in the discharge chamber, causing the entire discharge valve mechanism located on the upper surface of the fixed base plate to become submerged in oil, making it difficult for the discharge valve to open.

[0005] Therefore, there is a conventional scroll compressor in which an oil reservoir, where the oil level is lower than the downstream opening of the discharge port, is formed on the outer periphery of the upper surface of the fixed base plate, and the oil is allowed to accumulate in the oil reservoir (see, for example, Patent Document 1). The scroll compressor of Patent Document 1 allows oil to accumulate in the oil reservoir, preventing the discharge valve mechanism from becoming immersed in oil, thereby suppressing a decrease in the responsiveness of the discharge valve opening operation.

[0006] Japanese Patent Application Laid-Open No. 2002-21729

[0007] While the technology of Patent Document 1 can suppress the deterioration of the responsiveness of the discharge valve due to oil, there is a concern that the oil may concentrate and accumulate in the oil reservoir, resulting in a shortage of oil between the discharge valve and the valve seat, and that this may result in an insufficient sealing force of the discharge port.In scroll compressors, if the sealing force of the discharge port is insufficient, refrigerant may leak from the discharge chamber to the compression chamber through the discharge port, resulting in a decrease in performance.

[0008] The present disclosure is intended to solve the above-mentioned problems, and aims to provide a scroll compressor and a refrigeration cycle device that can suppress a decrease in the responsiveness of the discharge valve due to oil and improve the sealing performance of the discharge port at the same time.

[0009] The scroll compressor of the present disclosure comprises a compression mechanism unit having a compression chamber that compresses a refrigerant and a plate formed with a discharge port through which the refrigerant compressed in the compression chamber is discharged; a rotating shaft arranged so that its axial direction is in the direction of gravity and that drives the compression mechanism unit; a discharge valve mechanism having a discharge valve that opens and closes the discharge port; and a valve seat on which the discharge valve is seated, the valve seat having an annular groove formed in the plate so as to surround the downstream opening of the discharge port on the inside, the plate being recessed downward from the upper surface of the plate and having an oil reservoir portion for collecting oil, the downstream opening of the discharge port opening into the oil reservoir portion.

[0010] A refrigeration cycle device according to the present disclosure includes the above scroll compressor, a condenser, a pressure reducer, and an evaporator.

[0011] The scroll compressor and refrigeration cycle apparatus according to the present disclosure have an oil reservoir on the upper surface of a plate on which a discharge port is formed, and the downstream opening of the discharge port is open in the oil reservoir. Because the downstream opening of the discharge port is open in the oil reservoir, the scroll compressor and refrigeration cycle apparatus can form a state in which oil is pooled around the downstream opening of the discharge port. Because the scroll compressor and refrigeration cycle apparatus can form a state in which oil is pooled around the downstream opening of the discharge port, a stable oil film can be formed between the discharge valve and the valve seat during operation, ensuring sealing. Furthermore, the scroll compressor and refrigeration cycle apparatus have a grooved valve seat. Because the valve seat of the scroll compressor and refrigeration cycle apparatus has a grooved valve seat, the contact area between the discharge valve and the valve seat is reduced compared to a configuration without a grooved valve, weakening the adhesive force of the oil film and suppressing a decrease in the responsiveness of the discharge valve due to oil. As a result, the scroll compressor and refrigeration cycle apparatus can simultaneously suppress a decrease in the responsiveness of the discharge valve due to oil and improve the sealing performance of the discharge port.

[0012] 13 is a schematic cross-sectional view showing an example of the configuration of a scroll compressor according to embodiment 1. FIG. 14 is a schematic plan view of a fixed scroll of the scroll compressor according to embodiment 1. FIG. 15 is a cross-sectional view taken along line A-A in FIG. 2. FIG. 16 is a cross-sectional view taken along line B-B in FIG. 2. FIG. 17 is a schematic enlarged cross-sectional view of a contact portion between a discharge valve and a valve seat of the scroll compressor according to embodiment 1. FIG. 18 is a plan view of a valve seat of the scroll compressor according to embodiment 1. FIG. 19 is a schematic plan view of a fixed scroll of the scroll compressor according to embodiment 2. FIG. 19 is a cross-sectional view taken along line C-C in FIG. 7. FIG. 20 is a cross-sectional view taken along line D-D in FIG. 7. FIG. 21 is an end view taken along line D-D in FIG. 7. FIG. 22 is a cross-sectional view taken along line E-E in FIG. 7. FIG. 23 is an end view taken along line E-E in FIG. 7. FIG. 24 is a schematic plan view of a fixed scroll of the scroll compressor according to embodiment 3. FIG. 25 is a cross-sectional view taken along line F-F in FIG. 13. FIG. 26 is a schematic cross-sectional view of a modified example of the fixed scroll of the scroll compressor according to embodiment 3. FIG. 27 is a schematic plan view of a fixed scroll of the scroll compressor according to embodiment 4. FIG. 28 is a cross-sectional view taken along line G-G in FIG. 16. FIG. 29 is an end view taken along line G-G in FIG. 16. FIG. 29 is an end view taken along line H-H in FIG. 29. FIG. 20 is a cross-sectional view taken along line I-I in FIG. 16. FIG. 29 is an end view taken along line I-I in FIG. Fig. 10 is a schematic plan view of a valve seat of a scroll compressor according to embodiment 5. Fig. 11 is a schematic vertical cross-sectional view of a discharge valve and a valve seat of a scroll compressor according to embodiment 5. Fig. 12 is a schematic vertical cross-sectional view of a modified example of a discharge valve and a valve seat of a scroll compressor according to embodiment 5. Fig. 13 is a schematic vertical cross-sectional view of a fixed base plate, a discharge valve mechanism, and a muffler of a scroll compressor according to embodiment 6. Fig. 14 is a plan view of a muffler of a scroll compressor according to embodiment 6. Fig. 15 is a schematic configuration diagram of a scroll compressor according to embodiment 7. Fig. 16 is a schematic configuration diagram of a refrigeration cycle device according to embodiment 8.

[0013] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In each drawing, components denoted by the same reference numerals are identical or equivalent, and this applies throughout the entire specification. Furthermore, the forms of components shown in the entire specification are merely examples and are not limited to these descriptions. Furthermore, the shape, size, arrangement, etc. of the configurations shown in each drawing may be changed as appropriate within the scope of the present disclosure. Furthermore, the size of each structure and the positional relationship between structures in each drawing may differ from the actual size. Furthermore, the size, etc. of identical parts in each drawing may not strictly correspond to each other.

[0014] Embodiment 1 [Configuration of Scroll Compressor 1] Fig. 1 is a schematic cross-sectional view showing an example of the configuration of a scroll compressor 1 according to embodiment 1. The configuration of the scroll compressor 1 of embodiment 1 will be described below.

[0015] Scroll compressor 1 has a compression mechanism 5, an electric motor 4, a rotating shaft 7, and other components. The compression mechanism 5, electric motor 4, rotating shaft 7, and other components are housed inside a container 2 that forms the outer shell of scroll compressor 1. Within container 2, compression mechanism 5 is disposed in the upper part of container 2, and electric motor 4 is disposed in the lower part of container 2. The interior of container 2 is divided by a frame 6 into a suction chamber 14 into which low-pressure refrigerant is drawn from the outside, and a discharge chamber 13 filled with high-pressure refrigerant discharged to the outside. In the following description, the direction in which rotating shaft 7 extends is referred to as the axial direction, the direction perpendicular to the axial direction is referred to as the radial direction, and the direction around the rotating shaft is referred to as the circumferential direction.

[0016] The container 2 includes, for example, a cylindrical central container 2a, an upper container 2b, and a lower container 2c. The upper container 2b is fitted into the opening of the central container 2a, and the lower container 2c is fitted into the opening at the bottom of the central container 2a, sealing the interior of the container 2. A suction pipe 11 for drawing in refrigerant is connected to the side of the central container 2a. The suction pipe 11 communicates with a suction chamber 14. The suction chamber 14 is located below the frame 6 within the container 2 and is filled with refrigerant flowing in from the suction pipe 11. A discharge pipe 12 for discharging refrigerant is connected to the upper container 2b. The discharge pipe 12 communicates with a discharge chamber 13. The discharge chamber 13 is located above the compression mechanism 5 within the container 2 and is filled with refrigerant discharged from the compression mechanism 5. A reservoir 3a for storing refrigeration oil (hereinafter simply referred to as oil) is formed at the bottom of the container 2. The reservoir 3a stores oil for lubricating the compression mechanism 5 and sliding parts including bearings, which will be described later.

[0017] The compression mechanism 5 and the electric motor 4 are connected via a rotary shaft 7. The rotational force generated by the electric motor 4 is transmitted to the compression mechanism 5 via the rotary shaft 7 to drive the compression mechanism 5. In the compression mechanism 5, the rotational force of the rotary shaft 7 compresses the refrigerant.

[0018] The scroll compressor 1 of the first embodiment is a so-called vertical scroll compressor arranged so that the axial direction of the rotary shaft 7 is the direction of gravity. The scroll compressor 1 of the first embodiment is also a low-pressure shell scroll compressor in which the container 2 is filled with refrigerant before being compressed by the compression mechanism 5. The refrigerant used in the scroll compressor 1 is, for example, carbon dioxide. The refrigerant is not limited to carbon dioxide, and other refrigerants may be used.

[0019] An oil pump 3 is fixed to the lower end of the rotating shaft 7. The oil pump 3 is a positive displacement pump such as a trochoid pump. As the rotating shaft 7 rotates, the oil pump 3 pumps oil stored in a reservoir 3a through an oil passage 71 provided inside the rotating shaft 7. The oil pumped up through the oil passage 71 is supplied to the sliding parts and the compression chamber 5a for the purposes of lubricating the sliding parts and sealing gaps in the compression chamber 5a, which will be described later.

[0020] The compression mechanism 5 is supported by a frame 6. The frame 6 is fixed to the inner peripheral surface of the vessel 2 by shrink fitting, welding, or the like. The frame 6 is disposed between the compression mechanism 5 and the electric motor 4 inside the vessel 2. A shaft hole is formed in the center of the frame 6, and a rotary shaft 7 passes through this shaft hole.

[0021] The frame 6 has an inner frame space 6d between it and the orbiting scroll 40 (described later), and the compression mechanism 5 is housed in the inner frame space 6d. The frame 6 is formed with a suction port 6a, and gaseous refrigerant that flows into a suction chamber 14 from a suction pipe 11 is drawn into a compression chamber 5a (described later) of the compression mechanism 5 through the suction port 6a.

[0022] An annular thrust bearing 6b is disposed on the frame 6 at a sliding surface between the frame 6 and an orbiting scroll 40 (described later) of the compression mechanism 5. Radial oil supply grooves 6c extending from the radially inner side to the radially outer side are formed on the upper surface of the thrust bearing 6b. Oil used to lubricate the sliding parts is collected in a frame space 6d. The oil collected in the frame space 6d flows through the oil supply groove 6c from the radially inner side to the radially outer side, into an Oldham ring space 15a formed between the orbiting scroll 40 and the frame 6, and lubricates an Oldham ring 15 (described later) accommodated in the Oldham ring space 15a.

[0023] An oil drain pipe 21 is connected to the frame 6. The upper end of the oil drain pipe 21 communicates with the Oldham ring space 15a, and the lower end extends toward the electric motor 4. Oil that accumulates in the Oldham ring space 15a is discharged below the frame 6 by the oil drain pipe 21.

[0024] The sub-frame 20 is provided below the electric motor 4 inside the vessel 2. The sub-frame 20 is fixed to the inner peripheral surface of the vessel 2 by shrink fitting, welding, or the like. A sub-bearing 8b that supports the rotating shaft 7 is provided in the center of the sub-frame 20. The sub-bearing 8b is made up of a ball bearing. However, the sub-bearing 8b may be made up of a bearing configuration other than a ball bearing.

[0025] A reservoir 3 a for storing oil is formed in the bottom of the container 2 , located below the sub-frame 20 .

[0026] The compression mechanism 5 has a fixed scroll 30 and an orbiting scroll 40 arranged below the fixed scroll 30. The fixed scroll 30 is fixedly arranged relative to the frame 6. The fixed scroll 30 is not limited to being fixedly arranged relative to the frame 6, and may be fixed to the inner circumferential surface of the vessel 2. The orbiting scroll 40 is arranged in the space between the fixed scroll 30 and the frame 6. An Oldham ring 15 is provided between the orbiting scroll 40 and the frame 6 to prevent the orbiting scroll 40 from rotating. The Oldham ring 15 is arranged in an Oldham ring space 15a. The Oldham ring space 15a is provided to accommodate the Oldham ring 15 and to stably supply oil to contact portions between mechanically contacting parts.

[0027] The fixed scroll 30 has a fixed base plate 30a and a fixed scroll 31 provided on one surface of the fixed base plate 30a. The orbiting scroll 40 has a swing base plate 40a and a swing scroll 41 provided on one surface of the swing base plate 40a. The fixed scroll 30 and the orbiting scroll 40, with the fixed scroll 31 and the swing scroll 41 combined, are disposed in the container 2. The compression mechanism 5 has a compression chamber 5a formed by combining the fixed scroll 31 and the swing scroll 41. As the rotating shaft 7 rotates, the compression chamber 5a moves from the radially outer side to the radially inner side while reducing in volume, compressing the refrigerant therein.

[0028] A discharge port 32 is formed in the fixed base plate 30a of the fixed scroll 30, and discharges the gas refrigerant compressed in the compression chamber 5a to a high pressure into the discharge chamber 13. The discharge port 32 is formed by vertically penetrating the fixed base plate 30a. The discharge port 32 is formed in the center of the fixed base plate 30a. The fixed base plate 30a is provided with a discharge valve mechanism 50 that opens and closes the discharge port 32. The discharge valve mechanism 50 is provided to prevent backflow of refrigerant from the high-pressure side to the low-pressure side, specifically from the discharge chamber 13 to the compression chamber 5a, through the discharge port 32. Hereinafter, backflow of refrigerant from the discharge chamber 13 to the compression chamber 5a, in other words, refrigerant leakage from the high-pressure side to the low-pressure side, may be referred to as "high- and low-pressure leakage."

[0029] The discharge valve mechanism 50 includes a discharge valve 51, a valve holder 52, and a fixing member 53. The details of the discharge valve mechanism 50 will be described later.

[0030] A cylindrical boss portion 42 is formed in the center of the surface of the oscillating base plate 40a of the oscillating scroll 40 opposite to the surface on which the oscillating spiral body 41 is formed. Hereinafter, the surface of the oscillating base plate 40a on which the cylindrical boss portion 42 is formed will be referred to as the back surface of the oscillating base plate 40a. A oscillating bearing 8c is fixed to the inside of the boss portion 42. The oscillating bearing 8c is made of a bearing material used for sliding bearings, such as a copper-lead alloy, and the bearing material is press-fitted into the inside of the boss portion 42 and fixed therein.

[0031] A slider 16 is rotatably disposed inside the swing bearing 8c. The slider 16 is fitted to an eccentric shaft portion 7a (described later) provided at the upper end of the rotary shaft 7 so as to be able to move relative to the eccentric shaft portion 7a, and automatically adjusts the swing radius of the swing scroll 40. The slider 16 is provided so that the fixed scroll 31 and the swing scroll 41 are always in contact with each other when the swing scroll 40 swings.

[0032] The orbiting scroll 40 is connected to the eccentric shaft portion 7a of the rotating shaft 7 via the slider 16, and with the above-mentioned configuration, the orbiting radius is automatically adjusted by the slider 16, and the orbiting scroll 40 oscillates in accordance with the rotation of the rotating shaft 7. A cylindrical intra-frame space 6d is formed between the back surface of the orbiting base plate 40a of the orbiting scroll 40 and the frame 6, and the orbiting bearing 8c rotates together with the slider 16 within the intra-frame space 6d during the orbiting motion of the orbiting scroll 40.

[0033] The electric motor 4 has a stator 4b and a rotor 4a. The stator 4b is connected by lead wires (not shown) to glass terminals (not shown) located between the frame 6 and the stator 4b to obtain electric power from an external source. The rotor 4a is fixed to the rotating shaft 7 by a fixing means such as shrink fitting.

[0034] The rotating shaft 7 is composed of an eccentric shaft portion 7a at the upper end of the rotating shaft 7, a main shaft portion 7b, and a counter shaft portion 7c at the lower end of the rotating shaft 7. The axes of the main shaft portion 7b and the counter shaft portion 7c are aligned with the axis of the rotating shaft 7, while the axis of the eccentric shaft portion 7a is eccentric with respect to the axis of the rotating shaft 7. The eccentric shaft portion 7a is connected to the boss portion 42 via a slider 16. The main shaft portion 7b is fitted into the main bearing 8a via a sleeve 17, which is a cylindrical member. The main shaft portion 7b slides against the main bearing 8a via an oil film. The main bearing 8a is fixed to the frame 6 by press-fitting a bearing material used for sliding bearings, such as a copper-lead alloy. The counter shaft portion 7c slides against the counter bearing 8b provided in the center of the subframe 20.

[0035] The rotating shaft 7 is provided with a first balancer 18 and a second balancer 19. The first balancer 18 offsets imbalance caused by the orbiting scroll 40 and the slider 16. The first balancer 18 is attached to the rotating shaft 7 in the suction chamber 14 and is arranged to rotate together with the rotating shaft 7. The first balancer 18 is housed inside a cylindrical balancer cover 18a. The balancer cover 18a houses the first balancer 18 inside, and is disposed in the suction chamber 14 and fixed to the frame 6 like the first balancer 18. The balancer cover 18a is made of, for example, metal.

[0036] The second balancer 19 offsets the imbalance caused by the orbiting scroll 40 and the slider 16. The second balancer 19 is disposed between the rotor 4a and the subframe 20, and is attached to the lower surface of the rotor 4a.

[0037] [Operation of Scroll Compressor 1] When power is supplied to the stator 4b of the electric motor 4, the rotor 4a generates torque, causing the rotating shaft 7, which is supported by the main bearing 8a and the sub-bearing 8b of the frame 6, to rotate. The rotation of the rotating shaft 7 is transmitted to the orbiting scroll 40 via the eccentric shaft portion 7a and the boss portion 42. The orbiting scroll 40 revolves while its rotation is restricted by the Oldham ring 15. That is, the orbiting scroll 40 is driven by the eccentric shaft portion 7a of the rotating shaft 7 to perform an orbiting motion while its rotation is restricted by the Oldham ring 15, which reciprocates in the direction of the Oldham groove of the frame 6. As a result, the volume of the compression chamber 5a, which is formed by the combination of the fixed scroll 30 and the orbiting scroll 41 of the orbiting scroll 40, changes due to the orbiting motion of the orbiting scroll 40.

[0038] As the orbiting scroll 40 swings, gaseous refrigerant is drawn into the container 2 through the suction pipe 11 and taken into the compression chamber 5a through the suction port 6a. The refrigerant taken into the compression chamber 5a gradually moves toward the center of the orbiting scroll 40 due to the swinging motion of the orbiting scroll 40, and is compressed as its volume decreases. The compressed refrigerant is then discharged from the discharge port 32 provided in the fixed scroll 30 by opening the discharge valve mechanism 50, and is then discharged from the scroll compressor 1 through the discharge pipe 12, i.e., into the refrigerant circuit.

[0039] The imbalance caused by the movements of the orbiting scroll 40 and the Oldham ring 15 is balanced by a first balancer 18 attached to the rotary shaft 7 and a second balancer 19 attached to the rotor 4a.

[0040] [Oil Flow in Scroll Compressor 1] Oil in the reservoir 3a at the bottom of the container 2 is pumped up by the oil pump 3, flows into a downstream opening of an oil passage 71 formed in the rotating shaft 7, and flows out from an upper opening of the oil passage 71. The oil flowing out from the upper opening of the oil passage 71 is supplied to sliding parts, such as the compression mechanism 5, the eccentric shaft 7a, and the main shaft 7b, to lubricate them. After lubrication, the oil returns to the reservoir 3a by gravity. Some of the oil supplied to the sliding parts flows into the compression chamber 5a together with the refrigerant and is then discharged from the compression chamber 5a through the discharge port 32 into the discharge chamber 13. The oil discharged into the discharge chamber 13 collides with the inner surface of the upper container 2b and then falls onto the upper surface 30a1 of the fixed base plate 30a of the fixed scroll 30. The oil that has fallen onto the upper surface 30a1 of the fixed base plate 30a is guided below the frame 6 via an oil passage (not shown) formed through the fixed base plate 30a and the frame 6, and returns to the reservoir 3a.

[0041] [Configuration of Discharge Valve Mechanism 50] Fig. 2 is a schematic plan view of the fixed scroll 30 of the scroll compressor 1 according to the first embodiment. Fig. 3 is a cross-sectional view taken along line A-A in Fig. 2. Fig. 4 is a cross-sectional view taken along line B-B in Fig. 2. Note that the fixed scroll 31 is not shown in Figs. 3 and 4. Fig. 5 is a schematic enlarged cross-sectional view of a contact portion between the discharge valve 51 and the valve seat 54 of the scroll compressor 1 according to the first embodiment. Fig. 6 is a plan view of the valve seat 54 of the scroll compressor 1 according to the first embodiment. Note that in Fig. 6, the discharge valve 51 is shown by a dotted line to clarify the positional relationship between the discharge valve 51 and the valve seat 54.

[0042] The discharge valve mechanism 50 includes a discharge valve 51 that opens and closes the discharge port 32, and a valve retainer 52 that is arranged on the opposite side of the discharge valve 51 from the discharge port 32 and that restricts the amount of deflection of the discharge valve 51. The discharge valve mechanism 50 includes a fixing member 53 that fixes the discharge valve 51 and the valve retainer 52 to the compression mechanism 5. The fixing member 53 is formed, for example, with a bolt or the like. The discharge valve mechanism 50 is formed in an elongated shape overall, with one end side being a fixed portion 50a that is fixed by the fixing member 53, and the other end side being an opening / closing portion 50b that opens and closes the discharge port 32.

[0043] The discharge valve 51 is a long, plate-shaped reed valve structure valve and is a flexible, thin, plate-shaped leaf spring. The thickness of the discharge valve 51 is constant throughout. One end of the discharge valve 51 in the longitudinal direction (left-right direction in FIG. 3 ) is fixed to the fixed base plate 30a by a fixing member 53. The discharge valve 51 has a valve base end 51a fixed to the fixed base plate 30a and a valve tip end 51b facing the discharge port 32 so as to cover the downstream opening 32a of the discharge port 32. In the illustrated example, the shape of the discharge valve 51 when viewed from above has a uniform width in the short direction (up-down direction in FIG. 6 ) along the longitudinal direction (left-right direction in FIG. 6 ). However, this shape is not limited to this. The shape of the discharge valve 51 may also be configured to have a linear portion whose width in the short direction (up-down direction in FIG. 6 ) is uniform along the longitudinal direction (left-right direction in FIG. 6 ) and a circular portion provided at the tip of the linear portion. In this configuration, the circular portion has a diameter greater than the width of the straight portion in the short direction, and functions as a valve tip portion 51 b that opens and closes the discharge port 32 .

[0044] The discharge valve 51 closes the discharge port 32 when the valve tip 51b is seated on a valve seat 54 (described later) and opens the discharge port 32 when it is separated from the valve seat 54. The discharge valve 51 prevents high and low pressure leakage when the valve tip 51b is seated on the valve seat 54 and closes the discharge port 32. When the refrigerant in the compression chamber 5a is compressed to a high pressure, the valve tip 51b of the discharge valve 51 is lifted against the elastic force and separated from the valve seat 54, thereby opening the discharge port 32.

[0045] When the valve tip 51b of the discharge valve 51 is seated on the valve seat 54, an oil film 55 is formed between the valve tip 51b of the discharge valve 51 and the valve seat 54, as shown in Figure 5. The oil film 55 seals the downstream opening 32a of the discharge port 32, maintaining the discharge valve 51 in a closed state and preventing high and low pressure leakage.

[0046] The valve guard 52 is provided on the discharge valve 51 to regulate the amount of deflection of the discharge valve 51. The valve guard 52 is formed in a long plate shape. The valve guard 52 has a valve guard base end 52a that is fixed to the fixed base plate 30a together with the discharge valve 51 by a fixing member 53, and a valve guard tip end 52b that is a free end and is curved in a direction away from the discharge valve 51 as it approaches the tip. The valve guard 52 comes into contact with the discharge valve 51 when the discharge valve 51 is deflected by the pressure of the refrigerant discharged from the discharge port 32, thereby regulating the amount of deflection of the discharge valve 51. Note that the valve guard 52 is not limited to a curved shape as shown in the figure, and may be linear and configured to be linearly separated from the discharge valve 51 from the valve guard base end 52a toward the valve guard tip end 52b.

[0047] The valve seat 54 is formed on the upper surface 30a1 of the fixed base plate 30a. The valve seat 54 is a portion on which the discharge valve 51 is seated. The valve seat 54 has a groove 54a recessed from the upper surface 30a1 of the fixed base plate 30a. As shown in FIG. 6 , the groove 54a is formed in an annular shape having an inner peripheral edge 54a1 and an outer peripheral edge 58. The groove 54a is formed in an annular shape so as to surround the downstream opening 32a of the discharge port 32. The groove 54a is configured so that the valve tip portion 51b of the discharge valve 51 does not entirely cover the groove 54a, but rather at least a portion of the groove 54a is exposed. The groove 54a is configured so that the outer peripheral edge of the tip side of the valve tip portion 51b of the discharge valve 51 is located between the inner peripheral edge 54a1 and the outer peripheral edge 58 of the groove 54a in a plan view. As shown in FIG. 6, the valve seat 54 is a portion on the upper surface 30a1 of the fixed base plate 30a between an inner peripheral edge 57, which is the inner periphery of the downstream opening 32a, and an outer peripheral edge 58, which is the outer periphery of the groove 54a.

[0048] If the valve seat 54 does not have the groove 54a, the discharge valve 51 will stick to the valve seat 54 due to the suction force of the oil film 55, increasing the oil film rupture resistance and making it difficult to open the valve. However, in the scroll compressor 1, the valve seat 54 has the groove 54a, which reduces the contact area between the valve tip 51b and the valve seat 54, reducing the oil film rupture resistance and making it easier to open the valve.

[0049] In the illustrated example, the discharge valve mechanism 50 configured as described above is fixed to the fixed base plate 30a of the compression mechanism 5. However, the member to which the discharge valve mechanism 50 is fixed is not limited to the fixed base plate 30a. For example, if the compression mechanism 5 is configured to have a chamber on the end face of the fixed scroll 30 opposite the orbiting scroll 40, the member to which the discharge valve mechanism 50 is fixed may be the chamber. The chamber is a plate-like member that is disposed so as to cover the downstream opening 32a of the discharge port 32 and reduces noise generated by the refrigerant blown out from the discharge port 32. In short, the discharge valve mechanism 50 is a member that constitutes the compression mechanism 5, and it is sufficient that it is fixed to the plate on which the discharge port 32 is formed. The following description will be given assuming that the discharge valve mechanism 50 is fixed to the fixed base plate 30a.

[0050] The scroll compressor 1 has the following structure for the fixed base plate 30a, on which the discharge valve mechanism 50 is installed, which makes it possible to suppress a decrease in the responsiveness of the discharge valve 51 due to oil and improve the sealing performance of the discharge port 32.

[0051] 2 to 4, the fixed base plate 30a has an oil reservoir 60 that collects oil discharged from the downstream opening 32a of the discharge port 32. In Figures 2 to 4, dots indicate oil collected in the oil reservoir 60. Also, in Figures 2 to 4, dotted arrows indicate the direction of oil flow on the upper surface 30a1 of the fixed base plate 30a.

[0052] The oil reservoir 60 is formed by recessing the upper surface 30a1 of the fixed base plate 30a downward, and includes a bottom wall 61 and a peripheral wall 62 extending upward from the outer edge of the bottom wall 61. The bottom wall 61 is a horizontal surface extending horizontally. The downstream opening 32a of the discharge port 32 is formed in the bottom wall 61. The valve seat 54 is also formed in the bottom wall 61. Note that, hereinafter, the entire upper surface of the fixed base plate 30a before the upper surface 30a1 is recessed downward is referred to as the back surface 63 to distinguish it from the upper surface 30a1 after the oil reservoir 60 is formed. The back surface 63 is a surface parallel to the surface of the fixed base plate 30a on which the fixed scroll 31 is provided.

[0053] The peripheral wall 62 has an inclined surface 62a that slopes downward from the radially outer side to the radially inner side. The peripheral wall 62 may have a shape in which multiple flat inclined surfaces are continuously formed around the entire circumference, or may have a funnel shape with a continuous curved surface around the entire circumference. The oil reservoir 60 may be shaped so that oil discharged from the downstream opening 32a of the discharge port 32, falls to the upper surface 30a1 of the fixed base plate 30a, and accumulates around the downstream opening 32a in the bottom wall 61. The shape of the peripheral wall 62 is not limited as long as the oil reservoir 60 is shaped so that oil accumulates around the downstream opening 32a. The shape of the peripheral wall 62 is not limited to a shape in which the entire circumference of the peripheral wall 62 has an inclined surface 62a. The peripheral wall 62 may have a vertical surface 62b in part, as shown by the dotted line in FIG. 3 . The peripheral wall 62 may have an inclined surface 62a that slopes downward from the radially outer side toward the radially inner side.

[0054] 2, the outer periphery 62a1 of the inclined surface 62a coincides with the outer periphery 30a11 of the upper surface 30a1 of the fixed base plate 30a, but the outer periphery 62a1 of the inclined surface 62a may be a portion that is a certain width inward from the outer periphery 30a11 of the upper surface 30a1 of the fixed base plate 30a. In other words, the fixed base plate 30a may have an annular flat portion on the outer periphery of the upper surface 30a1 of the fixed base plate 30a, and the portion inward from the flat portion may be the inclined surface 62a.

[0055] 3, the valve guard tip 52b of the valve guard 52 is positioned below the height position of the back surface 63 of the fixed base plate 30a, but the present invention is not limited to this. The scroll compressor 1 may be configured such that the valve guard tip 52b is positioned above the height position of the back surface 63 of the fixed base plate 30a.

[0056] [Operation and Function of Discharge Valve Mechanism 50] In the discharge valve mechanism 50 according to the first embodiment, the discharge valve 51 is pressed against the valve seat 54 by the pressure difference between the discharge chamber 13 and the compression chamber 5a, thereby closing the valve. As the refrigerant is compressed in the compression chamber 5a, the pressure in the compression chamber 5a increases. When the pressure in the compression chamber 5a reaches a set pressure, the discharge valve 51 bends and moves away from the valve seat 54, thereby opening the valve. The open discharge valve 51 is supported by the valve holder 52. When the discharge of the high-pressure refrigerant from the compression chamber 5a is completed, the discharge valve 51 returns to its original flat plate shape and enters a closed state.

[0057] The oil discharged from the discharge port 32 into the discharge chamber 13 falls onto the upper surface 30a1 of the fixed base plate 30a as described above. Here, since the oil reservoir 60 is formed on the upper surface 30a1 of the fixed base plate 30a, the oil on the upper surface 30a1 of the fixed base plate 30a flows into and accumulates in the oil reservoir 60 as indicated by the dotted arrows in Figures 2 to 4.

[0058] In the scroll compressor 1, oil is accumulated in the oil reservoir 60, so that the oil accumulates around the downstream opening 32a that opens into the oil reservoir 60. In the scroll compressor 1, the oil can be accumulated around the downstream opening 32a of the discharge port 32, so that a stable oil film 55 can be formed between the discharge valve 51 and the valve seat 54 during operation, ensuring sealing performance.

[0059] In the scroll compressor 1, an adhesive force due to the oil film 55 between the discharge valve 51 and the valve seat 54 acts on the discharge valve 51. As described above, the valve seat 54 of the scroll compressor 1 has the groove 54a. Therefore, in the scroll compressor 1, compared to a configuration in which the valve seat 54 does not have the groove 54a, the contact area between the valve tip 51b and the valve seat 54 is reduced, which weakens the adhesive force due to the oil film 55 and reduces the oil film rupture resistance. By reducing the oil film rupture resistance, the scroll compressor 1 can suppress a decrease in the responsiveness of the discharge valve 51 due to oil.

[0060] As described above, the scroll compressor 1 can suppress a decrease in the responsiveness of the discharge valve 51 due to oil and improve the sealing performance of the discharge port 32 when the valve is closed.

[0061] Furthermore, the scroll compressor 1 can stably form an oil film 55 between the discharge valve 51 and the valve seat 54, thereby absorbing the impact when the discharge valve 51 seats on the valve seat 54 and achieving the effect of suppressing the stress generated in the discharge valve 51.

[0062] Furthermore, in the scroll compressor 1, when the depth of the oil reservoir 60 is deeper than the plate thickness of the discharge valve 51, at least a portion of the underside of the valve retainer base end 52a of the valve retainer 52, which abuts against the upper surface of the valve base end 51a of the discharge valve 51, is immersed in the oil accumulated in the oil reservoir 60. By immersing at least a portion of the underside of the valve retainer 52 in oil, the scroll compressor 1 can cause the oil to act as an absorbing member that absorbs collisions of the discharge valve 51 with the valve retainer 52 when the valve is open. Therefore, the scroll compressor 1 can improve the strength reliability against collisions of the discharge valve 51 and the valve retainer 52.

[0063] Furthermore, in the scroll compressor 1, the oil reservoir 60 makes it easy for oil to accumulate around the downstream opening 32a of the discharge port 32, which is particularly effective in improving sealing performance during startup for the following reasons: When the compressor is operating, the discharge valve 51 opens and closes at high speed, and refrigerant is discharged from the discharge port 32. Therefore, when the compressor is operating, the impact of high and low pressure leakage is less than during startup. On the other hand, during startup, the discharge valve 51 is closed. Therefore, when the compressor is starting up, if the sealing performance of the discharge port 32 is poor, the impact of high and low pressure leakage becomes significant.

[0064] Effect of Scroll Compressor 1 of First Embodiment As described above, the scroll compressor 1 of the first embodiment includes a compression mechanism 5 having a fixed base plate 30a that is a plate formed with compression chambers 5a that compress refrigerant and discharge ports 32 through which the refrigerant compressed in the compression chambers 5a is discharged, and a rotating shaft 7 that is disposed so that its axial direction is the direction of gravity and drives the compression mechanism 5. The scroll compressor 1 also includes a discharge valve mechanism 50 having a discharge valve 51 that opens and closes the discharge port 32, and a valve seat 54 that has an annular groove 54a formed in the plate so as to surround the downstream opening 32a of the discharge port 32 and on which the discharge valve 51 is seated. The fixed base plate 30a is recessed downward from an upper surface 30a1 of the fixed base plate 30a and has an oil reservoir 60 that reservoirs oil, and the downstream opening 32a of the discharge port 32 opens into the oil reservoir 60.

[0065] In the scroll compressor 1, the downstream opening 32a of the discharge port 32 is open to the oil reservoir 60, allowing oil to accumulate around the downstream opening 32a of the discharge port 32. Because the scroll compressor 1 allows oil to accumulate around the downstream opening 32a of the discharge port 32, a stable oil film 55 can be formed between the discharge valve 51 and the valve seat 54 during operation, ensuring sealing performance. Furthermore, in the scroll compressor 1, the valve seat 54 has a groove 54a. Because the valve seat 54 has the groove 54a, the scroll compressor 1 reduces the contact area between the discharge valve 51 and the valve seat 54 compared to a configuration without the groove 54a, thereby weakening the suction force of the oil film 55 and suppressing a decrease in the responsiveness of the discharge valve 51 due to oil. As described above, the scroll compressor 1 can simultaneously suppress a decrease in the responsiveness of the discharge valve 51 due to oil and improve the sealing performance of the discharge port 32.

[0066] The oil reservoir 60 has a bottom wall 61 where the downstream opening 32a of the discharge port 32 is open, and a peripheral wall 62 extending upward from the outer edge of the bottom wall 61. The peripheral wall 62 has an inclined surface 62a that slopes downward as it approaches the radially inner side from the radially outer side perpendicular to the axial direction. The oil reservoir 60 may have an inclined surface over the entire circumference of the peripheral wall 62 that slopes downward as it approaches the downstream opening 32a of the discharge port 32 from the radially outer side perpendicular to the axial direction, or the peripheral wall 62 may be funnel-shaped.

[0067] In the scroll compressor 1, the peripheral wall 62 of the oil reservoir 60 is inclined, which makes it easier for oil to flow toward the bottom wall 61 and for oil to accumulate around the downstream opening 32a opened in the bottom wall 61.

[0068] Embodiment 2. FIG. 7 is a schematic plan view of the fixed scroll 30 of the scroll compressor 1 according to embodiment 2. FIG. 8 is a cross-sectional view taken along the line CC in FIG. 7. FIG. 9 is a cross-sectional view taken along the line DD in FIG. 7. FIG. 10 is an end view taken along the line DD in FIG. 7. FIG. 11 is a cross-sectional view taken along the line EE in FIG. 7. FIG. 12 is an end view taken along the line EE in FIG. 7. Note that the fixed scroll 31 is not shown in FIGS. 8 to 12. In embodiment 2, the shape of the upper surface 30a1 of the fixed base plate 30a, including the oil reservoir 60, differs from embodiment 1. The rest of the configuration is the same as or equivalent to embodiment 1. The following description will focus on the configurations of embodiment 2 that differ from embodiment 1, and configurations not described in embodiment 2 are the same as embodiment 1.

[0069] In the scroll compressor 1 of the second embodiment, the portion of the upper surface 30a1 of the fixed base plate 30a where the discharge valve mechanism 50 is installed forms a flat inclined surface 33 inclined with respect to the axial direction. The inclined surface 33 slopes downward from the radially outer side toward the downstream opening 32a of the discharge port 32. The inclined surface 33 extends radially on the upper surface 30a1. The portion of the upper surface 30a1 extending radially from the inclined surface 33 also forms a flat inclined surface 34. The inclined surfaces 33 and 34 are inclined in opposite directions. The surface of the upper surface 30a1 that connects the inclined surface 33 and the inclined surface 34 in the circumferential direction forms an arc-shaped curved surface 35.

[0070] In the scroll compressor 1 of the first embodiment, the installation portion of the discharge valve mechanism 50 is a horizontal surface extending in the horizontal direction. In contrast, in the scroll compressor 1 of the second embodiment, the installation portion of the discharge valve mechanism 50 is an inclined surface 33 that is inclined with respect to the axial direction.

[0071] In the scroll compressor 1 of the second embodiment, the oil reservoir 60 refers to a portion of the upper surface 30a1 of the fixed base plate 30a that includes the lowermost portion 36, which is the connecting portion between the inclined surface 33 and the inclined surface 34.

[0072] As shown in Figure 8, the discharge valve mechanism 50 is disposed on the inclined surface 33 such that the longitudinal direction of the discharge valve mechanism 50 follows the inclination of the inclined surface 33. The discharge valve mechanism 50 is disposed at an angle with respect to the axial direction such that the fixed portion 50a is at the top and the opening / closing portion 50b is at the bottom. The discharge port 32 is inclined with respect to the axial direction. In this way, in the scroll compressor 1, the installation portion of the discharge valve mechanism 50 is not limited to a horizontal surface, and may be an inclined surface.

[0073] In the scroll compressor 1 of the second embodiment, as shown by the dotted arrows in FIGS. 7 to 10, oil on the upper surface 30a1 of the fixed base plate 30a flows toward the bottom of the oil reservoir 60 and accumulates there.

[0074] [Effects of Scroll Compressor 1] The scroll compressor 1 of the second embodiment can achieve the same effects as those of the first embodiment.

[0075] Embodiment 3. Figure 13 is a schematic plan view of the fixed scroll 30 of the scroll compressor 1 according to embodiment 3. Figure 14 is a cross-sectional view taken along the line F-F of Figure 13. Note that the fixed scroll 31 is not shown in Figure 14. In embodiment 3, the shape of the upper surface 30a1 of the fixed base plate 30a including the oil reservoir 60 differs from embodiment 2. The other configurations are the same as or equivalent to those of embodiment 2. The following description will focus on the configurations of embodiment 3 that differ from embodiment 2, and the configurations not described in embodiment 3 are the same as those of embodiment 2.

[0076] In the scroll compressor 1 of the third embodiment, the upper surface 30a1 of the fixed base plate 30a has an oil level adjusting portion 64 that adjusts the position of the oil level in the oil reservoir 60. The oil level adjusting portion 64 regulates the amount of oil that accumulates in the oil reservoir 60 to improve the responsiveness of the opening operation of the discharge valve 51. The oil level adjusting portion 64 is configured with a height restricting surface 64a that regulates the oil level in the oil reservoir 60 to a position lower than the back surface 63 of the fixed base plate 30a, in other words, a position lower than the upper end position 30a3 of the fixed base plate 30a. As shown in FIG. 13 , the height restricting surface 64a has a shape in which both ends of a circular arc are connected by a straight line when viewed in plan. The shape of the height restricting surface 64a is not limited to this shape and may be any shape.

[0077] The height restriction surface 64a is formed on a part of the upper surface 30a1 of the fixed base plate 30a. As shown in FIG. 14 , the height restriction surface 64a is formed at a position lower than the upper end position 30a3 of the fixed base plate 30a, extending from the outer peripheral edge 60a of the oil reservoir 60 to the outer peripheral edge 30a2 of the fixed base plate 30a. In the illustrated example, the height restriction surface 64a is a horizontally flat surface, but the height restriction surface 64a is not limited to a horizontally flat surface. For example, the height restriction surface 64a may be an inclined surface that slopes downward from the outer peripheral edge 60a of the oil reservoir 60 toward the outer peripheral edge 30a2 of the fixed base plate 30a, as indicated by the dotted line 64c in FIG. 14 .

[0078] The vertical position of the height restriction surface 64a is set to a position lower than the upper end position 30a3 of the fixed base plate 30a and higher than the downstream opening 32a of the discharge port 32. When the discharge port 32 is inclined with respect to the axial direction as shown in Figure 14, the vertical position of the height restriction surface 64a is set to a position equal to or higher than the upper end 32a1 of the downstream opening 32a of the discharge port 32. In the scroll compressor 1, by allowing oil to accumulate at least up to the upper end 32a1 of the downstream opening 32a of the discharge port 32, the discharge port 32 can be sealed and high and low pressure leakage can be suppressed.

[0079] The scroll compressor 1 has the following advantages when the vertical position of the height restriction surface 64a is set to be the same as the height position of the upper end 32a1 of the downstream opening 32a of the discharge port 32. Compared to when the vertical position of the height restriction surface 64a is set above the upper end 32a1 of the downstream opening 32a of the discharge port 32, the scroll compressor 1 can reduce the area of ​​the valve tip 51b of the discharge valve 51 that is immersed in oil, thereby reducing the oil film rupture resistance and improving the responsiveness when the valve is opened.

[0080] 13 and 14 show an example in which the configuration of embodiment 2 is applied to embodiment 3, but a configuration in which embodiment 3 is applied to the configuration of embodiment 1 may also be used, as shown in the following FIG. 15.

[0081] Fig. 15 is a schematic cross-sectional view of a modified example of the fixed scroll 30 of the scroll compressor 1 according to the third embodiment. As shown in Fig. 15, the scroll compressor 1 is configured such that the oil reservoir 60 has a bottom wall 61 that is a horizontal surface, the discharge valve mechanism 50 is installed on the bottom wall 61, and the upper surface 30a1 of the fixed base plate 30a has a height restriction surface 64a. In this way, the scroll compressor 1 may have a configuration in which the third embodiment is applied to the configuration of the first embodiment.

[0082] [Effects of Scroll Compressor 1 of Embodiment 3] The scroll compressor 1 of Embodiment 3 has the same effects as those of Embodiment 1 or 2, as well as the following effect. In the scroll compressor 1, the upper surface 30a1 of the fixed base plate 30a has a height restriction surface 64a. Therefore, in the scroll compressor 1, the oil level in the oil reservoir 60 is restricted to the position of the height restriction surface 64a. The height restriction surface 64a is lower than the upper end position 30a3 of the fixed base plate 30a and higher than the downstream opening 32a of the discharge port 32. Therefore, in the scroll compressor 1, the oil level in the oil reservoir 60 can be reliably kept lower than the back surface 63 of the fixed base plate 30a. Therefore, in the scroll compressor 1, the area of ​​the valve tip 51b of the discharge valve 51 immersed in oil can be reduced, thereby reducing the oil film rupture resistance and improving the responsiveness when the valve is opened.

[0083] Furthermore, in a configuration in which the discharge port 32 is inclined with respect to the axial direction, the scroll compressor 1 has the following effects when the height restriction surface 64a is set at a height position equal to the upper end 32a1 of the downstream opening 32a of the discharge port 32. Compared to a case in which the height restriction surface 64a is set higher than the upper end 32a1 of the downstream opening 32a of the discharge port 32, the scroll compressor 1 can reduce the area of ​​the valve tip 51b of the discharge valve 51 that is immersed in oil, thereby reducing the oil film rupture resistance and improving the responsiveness when the valve is opened.

[0084] Fourth Embodiment. Figure 16 is a schematic plan view of the fixed scroll 30 of a scroll compressor 1 according to a fourth embodiment. Figure 17 is a cross-sectional view taken along line G-G in Figure 16. Figure 18 is an end view taken along line G-G in Figure 16. Figure 19 is an end view taken along line H-H in Figure 16. Figure 20 is a cross-sectional view taken along line I-I in Figure 16. Figure 21 is an end view taken along line I-I in Figure 16. Note that the fixed scroll 31 is not shown in Figures 17 to 21. In the fourth embodiment, the configuration of the oil level adjusting unit 64 differs from that of the third embodiment. The remaining configuration is the same as or equivalent to that of the third embodiment. The following description will focus on the configurations in the fourth embodiment that differ from those of the third embodiment, and the configurations not described in the fourth embodiment are the same as those of the third embodiment.

[0085] In the scroll compressor 1 of the third embodiment, the oil level adjustment section 64 is configured with a height restriction surface 64a. In the scroll compressor 1 of the fourth embodiment, the oil level adjustment section 64 is configured with a discharge groove 64b. The discharge groove 64b is formed at a position lower than the rear surface 63 of the fixed base plate 30a, in other words, at a position lower than the upper end position 30a3 of the fixed base plate 30a, and extends from the outer peripheral edge 60a of the oil reservoir 60 to the outer peripheral edge 30a2 of the fixed base plate 30a. In the illustrated example, as shown in FIGS. 20 and 21 , the bottom surface 64b1 of the discharge groove 64b slopes downward from the outer peripheral edge 60a of the oil reservoir 60 toward the outer peripheral edge 30a2 of the fixed base plate 30a. However, it may be a horizontal surface. In the illustrated example, the discharge groove 64b is configured with two grooves, a first groove 64ba and a second groove 64bb, as shown in FIG. 16 . However, it may be configured with only one of them. The scroll compressor 1 has the discharge groove 64b on the upper surface 30a1 of the fixed base plate 30a, so that the height position of the oil level in the oil reservoir 60 can be regulated to the upper end position of the bottom surface 64b1 of the discharge groove 64b.

[0086] [Effects of the Scroll Compressor 1 of the Fourth Embodiment] The scroll compressor 1 of the fourth embodiment can achieve the same effects as those of the third embodiment.

[0087] Fifth Embodiment. Figure 22 is a schematic plan view of the valve seat 54 of the scroll compressor 1 according to the fifth embodiment. Figure 23 is a schematic vertical cross-sectional view of the discharge valve 51 and the valve seat 54 of the scroll compressor 1 according to the fifth embodiment. Figure 24 is a schematic vertical cross-sectional view of a modified example of the discharge valve 51 and the valve seat 54 of the scroll compressor 1 according to the fifth embodiment. In the fifth embodiment, the shape of the valve seat 54 differs from that of the first to fourth embodiments. The other configurations are the same as or equivalent to those of the first to fourth embodiments. The following description will focus on the configurations in which the fifth embodiment differs from the first to fourth embodiments, and the configurations not described in the fifth embodiment are the same as those of the first to fourth embodiments.

[0088] The scroll compressor 1 of the fifth embodiment has a configuration in which a notch 56 is formed in the valve seat 54. The notch 56 is intended to reduce the contact area of ​​the discharge valve 51 with the valve seat 54, in other words, the oil film formation area, thereby reducing the adhesive force of the oil film 55 and reducing the oil film rupture resistance. As shown in FIG. 23 , the notch 56 is formed in the inner peripheral edge of the valve seat 54, in other words, the inner peripheral edge 57 of the downstream opening 32 a. As shown in FIG. 22 , the notch 56 is located on the valve seat 54 toward the valve tip 51 b in the longitudinal direction of the discharge valve 51 (the left-right direction in FIG. 22 ) in a plan view. The notch 56 may also be formed in the inner peripheral edge 54 a 1 of the groove 54 a of the valve seat 54, as shown in a modified example in FIG. 24 .

[0089] Three notches 56 are provided. The shape of the notches 56 is an arc. The number of notches 56 is not limited to three, but may be one or two, or may be four or more. The shape of the notches 56 is not limited to an arc, but may be an ellipse, a strip, a fan, or the like.

[0090] [Effects of Scroll Compressor 1 of Embodiment 5] The scroll compressor 1 of Embodiment 5 can achieve the same effects as those of Embodiments 1 to 4, as well as the following effect. In the scroll compressor 1, the valve seat 54 has the notch 56, which reduces the contact area between the discharge valve 51 and the valve seat 54 and makes the oil film formation area smaller than in a configuration without the notch 56. In the scroll compressor 1, the oil film formation area can be reduced, which reduces the adsorption force of the oil film 55 and makes it easier to open the discharge valve 51. As a result, the scroll compressor 1 can reduce the increase in oil film rupture resistance caused by oil accumulation around the discharge port 32, and can improve the responsiveness of the opening operation of the discharge valve 51.

[0091] Sixth Embodiment Figure 25 is a schematic vertical cross-sectional view of the fixed base plate 30a, discharge valve mechanism 50, and muffler 90 of a scroll compressor 1 according to a sixth embodiment. Figure 26 is a plan view of the muffler 90 of the scroll compressor 1 according to the sixth embodiment. The sixth embodiment has a configuration including the muffler 90, and other configurations are the same as or equivalent to those of the first to fifth embodiments. The following description will focus on configurations in which the sixth embodiment differs from the first to fifth embodiments, and configurations not described in the sixth embodiment are the same as those of the first to fifth embodiments.

[0092] The scroll compressor 1 of the sixth embodiment is provided with a muffler 90 for silencing noise. The muffler 90 is intended to reduce refrigerant discharge noise. The muffler 90 is fixed to the fixed base plate 30a above the fixed base plate 30a so as to cover the discharge valve mechanism 50. The muffler 90 has a cylindrical portion 91 with a closed upper surface and a flange portion 92 extending outward from the lower end edge of the cylindrical portion 91. The flange portion 92 of the muffler 90 is fixed to the fixed base plate 30a by fixing members 93 such as bolts.

[0093] The cylindrical portion 91 has a muffler discharge port 94 that penetrates in the vertical direction. The muffler discharge port 94 is formed in a position that does not overlap the discharge port 32 in a plan view. The cylindrical portion 91 has a discharge port peripheral wall 91a that slopes downward toward the muffler discharge port 94. The entire circumference of the discharge port peripheral wall 91a is an inclined surface that is inclined with respect to the axial direction, which is the direction of gravity. The discharge port peripheral wall 91a may be funnel-shaped, or may have a shape in which multiple inclined surfaces are connected in the circumferential direction.

[0094] A space 95 is formed between the muffler 90 and the fixed base plate 30a, into which the refrigerant discharged from the discharge port 32 flows. The refrigerant that flows into the space 95 from the discharge port 32 is discharged into the discharge chamber 13 through a muffler discharge port 94.

[0095] [Effects of Scroll Compressor 1 of Sixth Embodiment] The scroll compressor 1 of the sixth embodiment provides the same effects as those of the first to fifth embodiments, as well as the following effect. In the scroll compressor 1, the cylindrical portion 91 of the muffler 90 has a discharge port peripheral wall 91a that slopes downward toward the muffler discharge port 94. Therefore, in the scroll compressor 1, oil contained in the refrigerant discharged from the muffler discharge port 94 into the discharge chamber 13 falls onto the upper surface of the muffler 90, flows along the discharge port peripheral wall 91a, and easily falls from the muffler discharge port 94 onto the upper surface 30a1 of the fixed base plate 30a. Therefore, the scroll compressor 1 more easily collects oil in the oil reservoir 60 than a configuration that does not have the discharge port peripheral wall 91a and in which the periphery of the muffler discharge port 94 is a flat surface extending horizontally. In the scroll compressor 1, the oil more easily collects oil in the oil reservoir 60, thereby improving the sealing performance of the discharge port 32.

[0096] If the scroll compressor has the muffler discharge port 94 positioned so as to overlap the discharge port 32 in a plan view, the oil contained in the refrigerant discharged from the discharge port 32 will be discharged directly from the muffler discharge port 94. In this case, the amount of oil flowing into the discharge chamber 13 from the muffler discharge port 94 increases, which may in turn increase the amount of oil discharged outside the container 2. This would result in a decrease in the amount of oil stored in the oil reservoir 60 of the scroll compressor.

[0097] In contrast, in the scroll compressor 1, the muffler discharge port 94 is formed at a position that does not overlap the discharge port 32 in a plan view. Therefore, the scroll compressor 1 can prevent the refrigerant containing oil discharged from the discharge port 32 from being discharged directly from the muffler discharge port 94. This makes it possible for the scroll compressor 1 to prevent a decrease in the amount of oil accumulated in the oil reservoir 60, and as a result, the sealing performance of the discharge port 32 can be improved.

[0098] Seventh Embodiment Fig. 27 is a schematic diagram of a scroll compressor 1 according to a seventh embodiment. The scroll compressor 1 of the seventh embodiment includes a control device 110 that controls the operation of the compression mechanism 5. The other configurations are the same as or equivalent to those of the first to sixth embodiments. The following description will focus on the configurations in the seventh embodiment that differ from the first to sixth embodiments, and the configurations not described in the seventh embodiment are the same as those of the first to sixth embodiments.

[0099] The control device 110 controls the power supply to control the rotation speed of the electric motor 4 and thereby controls the operation of the compression mechanism 5. The control device 110 performs control to make it easier for oil to accumulate in the oil reservoir 60 after operation is stopped.

[0100] The control device 110 is configured with dedicated hardware or a CPU (Central Processing Unit) that executes programs stored in memory. The CPU is also called a central processing unit, processing unit, arithmetic unit, microprocessor, microcomputer, or processor.

[0101] When the control device 110 is dedicated hardware, the control device 110 may be, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination thereof. Each functional unit realized by the control device 110 may be realized by a separate piece of hardware, or each functional unit may be realized by a single piece of hardware.

[0102] When the control device 110 is a CPU, each function executed by the control device 110 is realized by software, firmware, or a combination of software and firmware. The software and firmware are written as programs and stored in memory. The CPU realizes each function of the control device 110 by reading and executing the programs stored in memory. Here, the memory is, for example, a non-volatile or volatile semiconductor memory such as RAM, ROM, flash memory, EPROM, or EEPROM.

[0103] A part of the functions of the control device 110 may be realized by dedicated hardware, and a part may be realized by software or firmware.

[0104] The control device 110 performs the following control to facilitate oil accumulation in the oil reservoir 60 after operation is stopped. Before operation is stopped, the control device 110 performs control to temporarily increase the rotation speed of the electric motor 4 to operate it at high speed.

[0105] [Effects of Scroll Compressor 1 of Embodiment 7] The scroll compressor 1 of Embodiment 7 can achieve the same effects as those of Embodiments 1 to 6, as well as the following effect. By the above-described control by the control device 110, the scroll compressor 1 can make it easier for oil pumped from the reservoir 3 a by the oil pump 3 to reach the discharge chamber 13, and can actively create a state in which oil is more likely to accumulate in the oil reservoir 60 after operation is stopped. As a result, the scroll compressor 1 can ensure the sealing of the discharge port 32 at startup, suppress high and low pressure leakage, and achieve improved performance.

[0106] Eighth Embodiment An eighth embodiment relates to a refrigeration cycle apparatus such as an air conditioner that includes the scroll compressor 1 according to any one of the first to seventh embodiments.

[0107] 28 is a schematic configuration diagram of a refrigeration cycle apparatus 200 according to embodiment 8. The refrigeration cycle apparatus 200 includes a refrigerant circuit in which a scroll compressor 100, a suction muffler 101, a four-way switching valve 102, an outdoor heat exchanger 103, a pressure reducer 104, and an indoor heat exchanger 105 are connected by piping. Refrigerant circulates in the refrigerant circuit together with oil.

[0108] The outdoor heat exchanger 103 and the indoor heat exchanger 105 function as a condenser or an evaporator depending on the switching of the four-way selector valve 102. The four-way selector valve 102 can be omitted from the refrigeration cycle apparatus 200. Therefore, the refrigeration cycle apparatus 200 may be configured to include the scroll compressor 100, a condenser, a pressure reducer 104, and an evaporator. In the air conditioner, the indoor heat exchanger 105 is installed in the indoor device, and the remaining scroll compressor 100, four-way selector valve 102, outdoor heat exchanger 103, and pressure reducer 104 are installed in the outdoor device.

[0109] The scroll compressor 100 is the scroll compressor 1 according to any one of the first to seventh embodiments. The four-way switching valve 102 is connected to the discharge side of the scroll compressor 100 and switches the flow of refrigerant from the scroll compressor 100. The outdoor heat exchanger 103 is, for example, a fin-tube heat exchanger including a pipe through which the refrigerant flows and fins into which the pipe is inserted. The pressure reducer 104 expands the refrigerant. The pressure reducer 104 is, for example, an electronic expansion valve or a thermostatic expansion valve whose opening is adjustable, but may also be a capillary tube whose opening is not adjustable. The indoor heat exchanger 105 is, for example, a fin-tube heat exchanger including a pipe through which the refrigerant flows and fins into which the pipe is inserted.

[0110] In heating operation when the refrigeration cycle apparatus 200 is applied to an air conditioner, the four-way switching valve 102 is connected to the solid line side in FIG. 28 . The high-temperature, high-pressure refrigerant compressed by the scroll compressor 100 flows to the indoor heat exchanger 105, where it condenses and liquefies. The liquefied refrigerant is decompressed by the pressure reducer 104, becomes a two-phase refrigerant with low temperature and low pressure, flows to the outdoor heat exchanger 103, evaporates, gasifies, and returns to the scroll compressor 100 through the four-way switching valve 102. That is, the refrigerant circulates as shown by the solid arrows in FIG. 28 . Through this circulation, the refrigerant exchanges heat with outside air in the outdoor heat exchanger 103, which serves as an evaporator, and absorbs heat. The refrigerant that has absorbed heat is sent to the indoor heat exchanger 105, which serves as a condenser, where it exchanges heat with indoor air and warms the indoor air.

[0111] In cooling operation, the four-way switching valve 102 is connected to the dashed line side in Figure 28. When switching from heating operation to cooling operation, the indoor heat exchanger 105 changes from a condenser to an evaporator, and the outdoor heat exchanger 103 changes from an evaporator to a condenser. High-temperature, high-pressure refrigerant compressed by the scroll compressor 100 flows to the outdoor heat exchanger 103, where it condenses and liquefies. The liquefied refrigerant is decompressed by the pressure reducer 104 and becomes a low-temperature, low-pressure two-phase refrigerant. The low-temperature, low-pressure two-phase refrigerant flows to the indoor heat exchanger 105, evaporates, and gasifies, passing through the four-way switching valve 102 and returning to the scroll compressor 100. In other words, the refrigerant circulates as shown by the dashed arrows in Figure 28. Through this circulation, the refrigerant exchanges heat with the indoor air in the indoor heat exchanger 105, which serves as an evaporator, absorbing heat and cooling the indoor air. The refrigerant that has absorbed heat is sent to the outdoor heat exchanger 103, which is a condenser, and exchanges heat with the outside air, releasing the heat to the outside air.

[0112] The refrigerant used here is a fluorine-based refrigerant or a hydrocarbon-based refrigerant with a low global warming potential (GWP). Other refrigerants that can be used include, for example, a single refrigerant selected from R1234yf, R1234ze, R32, and R290, a mixture of two or more of these refrigerants, or a mixture of any of these refrigerants with other refrigerants. The refrigerant may also be a mixture containing R1132(E) or a mixture containing R1123. The refrigerant may also be a mixture of R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, and R459A.

[0113] [Effects of the refrigeration cycle apparatus 200 according to embodiment 8] The refrigeration cycle apparatus 200 includes the scroll compressor 100 according to any one of embodiments 1 to 7. Therefore, the refrigeration cycle apparatus 200 can obtain the same effects as those of the scroll compressor 100 according to any one of embodiments 1 to 7.

[0114] The refrigeration cycle device 200 can be applied to refrigerators, freezers, vending machines, refrigeration systems, water heaters, and the like in addition to air conditioners.

[0115] 1 Scroll compressor, 2 Container, 2a Central container, 2b Upper container, 2c Lower container, 3 Oil pump, 3a Storage section, 4 Electric motor, 4a Rotor, 4b Stator, 5 Compression mechanism section, 5a Compression chamber, 6 Frame, 6a Intake port, 6b Thrust bearing, 6c Oil supply groove, 6d Frame space, 7 Rotating shaft, 7a Eccentric shaft section, 7b Main shaft section, 7c Sub-shaft section, 8a Main bearing, 8b Sub-bearing, 8c Swing bearing, 11 Intake pipe, 12 Discharge pipe, 13 Discharge chamber, 14 Intake chamber, 15 Oldham ring, 15a Oldham ring space, 16 Slider, 17 Sleeve, 18 First balancer, 18a Balancer cover, 19 Second balancer, 20 Sub-frame, 21 Oil drain pipe, 30 Fixed scroll, 30a Fixed base plate, 30a1 upper surface, 30a11 outer periphery, 30a2 outer periphery, 30a3 upper end position, 31 fixed scroll, 32 discharge port, 32a downstream opening, 32a1 upper end, 33 inclined surface, 34 inclined surface, 35 curved surface, 36 lowermost portion, 40 swinging scroll, 40a swinging base plate, 41 swinging scroll, 42 boss portion, 50 discharge valve mechanism, 50a fixed portion, 50b opening / closing portion, 51 discharge valve, 51a valve base end portion, 51b valve tip portion, 52 valve guard, 52a valve guard base end portion, 52b valve guard tip portion, 53 fixed member, 54 valve seat, 54a groove portion, 54a1 inner peripheral edge portion, 55 oil film, 56 notch, 57 inner peripheral edge portion, 58 Outer peripheral edge portion, 60 oil reservoir portion, 60a outer peripheral edge, 61 bottom wall, 62 peripheral wall, 62a inclined surface, 62a1 outer periphery, 62b vertical surface, 63 back surface, 64 oil level adjustment portion, 64a height control surface, 64b discharge groove, 64b1 bottom surface, 64ba first groove, 64bb second groove, 64c dotted line, 71 oil passage, 90 muffler, 91 cylindrical portion, 91a discharge port peripheral wall, 92 flange portion, 93 fixing member, 94 muffler discharge port, 95 space, 100 scroll compressor, 101 suction muffler, 102 four-way switching valve, 103 outdoor heat exchanger, 104 pressure reducer, 105 indoor heat exchanger, 110 control device, 200 refrigeration cycle device.

Claims

1. A scroll compressor comprising: a compression mechanism having a compression chamber that compresses a refrigerant, and a plate formed with a discharge port through which the refrigerant compressed in the compression chamber is discharged; a rotating shaft arranged so that its axial direction is the direction of gravity and driving the compression mechanism; a discharge valve mechanism having a discharge valve that opens and closes the discharge port; and a valve seat on which the discharge valve is seated, the valve seat having an annular groove formed in the plate so as to surround the downstream opening of the discharge port from the inside, the plate being recessed downward from the upper surface of the plate and having an oil reservoir for storing oil, the downstream opening of the discharge port opening into the oil reservoir.

2. A scroll compressor as described in claim 1, wherein the oil reservoir has a bottom wall in which the downstream opening of the discharge port is open, and a peripheral wall extending upward from the outer edge of the bottom wall, and the peripheral wall has an inclined surface that slopes downward as it approaches the radial inside from the radial outside perpendicular to the axial direction.

3. A scroll compressor as claimed in claim 2, wherein the oil reservoir has a peripheral wall that is formed as an inclined surface that slopes downward from the radial outside perpendicular to the axial direction toward the downstream opening of the discharge port along the entire circumference.

4. A scroll compressor according to claim 2 or 3, wherein the peripheral wall of said oil reservoir is funnel-shaped.

5. A scroll compressor as described in claim 1, wherein the upper surface of the plate has an inclined surface that inclines downward as it approaches the downstream opening of the discharge port from the radial outside perpendicular to the axial direction, the oil reservoir portion is composed of a portion that includes the lowermost part of the inclined surface, and the elongated discharge valve mechanism has a fixed portion fixed to the plate and an opening / closing portion that faces the downstream opening of the discharge port and opens and closes the discharge port, and is arranged on the inclined surface so that the fixed portion is at the top and the opening / closing portion is at the bottom.

6. A scroll compressor according to any one of claims 1 to 5, wherein the upper surface of the plate has an oil level adjustment section for adjusting the position of the oil level in the oil reservoir.

7. A scroll compressor as claimed in claim 6, wherein said oil level adjusting portion is a height regulating surface formed at a position lower than the upper end position of said plate and extending from the outer periphery of said oil reservoir portion to the outer periphery of said plate.

8. A scroll compressor according to claim 6, wherein said oil level adjusting portion is a discharge groove formed at a position lower than the upper end position of said plate and extending from the outer periphery of said oil reservoir portion to the outer periphery of said plate.

9. A scroll compressor according to any one of claims 1 to 8, wherein the valve seat is formed with one or more notches.

10. A scroll compressor according to claim 9, wherein said notch is formed on the inner peripheral edge of said valve seat.

11. A scroll compressor according to claim 9, wherein said notch is formed on the inner peripheral edge of said groove.

12. A scroll compressor as claimed in any one of claims 1 to 11, further comprising a muffler arranged to cover the discharge valve mechanism and perform soundproofing, the muffler having a muffler discharge port penetrating in the vertical direction, and the muffler having a discharge port peripheral wall that slopes downward towards the muffler discharge port.

13. The scroll compressor according to claim 12, wherein the discharge port and the muffler discharge port are formed at positions that do not overlap when viewed in a plan view.

14. A scroll compressor as described in any one of claims 1 to 13, wherein the compression mechanism comprises a fixed scroll having a fixed base plate in which the discharge port is formed and a fixed spiral body formed on the fixed base plate, and an oscillating scroll having a oscillating base plate and an oscillating spiral body formed on the oscillating base plate, the fixed spiral body and the oscillating spiral body being combined to form the compression chamber, and the plate is the fixed base plate.

15. A scroll compressor as claimed in any one of claims 1 to 14, further comprising a control device for controlling operation of the compression mechanism, the control device temporarily increasing the rotation speed of the rotating shaft before operation is stopped.

16. A refrigeration cycle device comprising the scroll compressor according to any one of claims 1 to 15, a condenser, a pressure reducer, and an evaporator.

Images