JP4644495B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor, and is particularly suitable for a scroll compressor including a release valve device that discharges a working fluid from a working chamber during overcompression or liquid compression.

  A scroll compressor used in a room air conditioner or the like is used under a wide range of operating conditions, and therefore cannot be avoided from being over-compressed with gas or compressed with refrigerant or refrigerant oil. Accordingly, there is a need for a scroll compressor that can withstand this.

  As a scroll compressor having an overcompression and liquid compression prevention structure, there is one disclosed in Japanese Patent Application Laid-Open No. 2002-221171 (Patent Document 1). This scroll compressor is shown in FIGS. 11 to 13 and its structure will be described.

  As shown in FIG. 11, a discharge pressure chamber 21c is formed in a sealed container 21 having a suction port 21a and a discharge port 21b. An electric motor 22 and a compression mechanism portion 23 are accommodated in the discharge pressure chamber 21c. The compression mechanism section 23 is formed by meshing a fixed scroll 24 having a spiral gas passage and a revolving scroll 25 having a spiral wrap 25a that is disposed so as to be opposed to the fixed scroll 24 and has a spiral wrap 25a. 28. The orbiting scroll 25 is connected to an Oldham ring 26 that revolves while preventing the rotation of the orbiting scroll 25, and is also connected to an eccentric portion 27 a of a crankshaft 27 that is rotationally driven by the electric motor 22.

  By driving the electric motor 22, the revolving scroll 25 is swung while the refrigerant is sucked from the suction port 21 a, led to the compression chamber 28 composed of the fixed scroll 24 and the revolving scroll 25 and sequentially compressed, and the compressed refrigerant is fixed to the fixed scroll. The discharge outlet 24a is discharged into the discharge pressure chamber 21c. And the refrigerant | coolant discharged | emitted by the discharge pressure chamber 21c is discharged | emitted from the discharge port 21b of the airtight container 21. FIG. In this scroll compressor, a release valve device 29 that connects the compression chamber 28 and the discharge pressure chamber 21 c is provided on a base plate 24 b above the fixed scroll 24.

  As shown in FIGS. 12 and 13, the release valve device 29 has a release hole 29a, a valve seat portion 29b, a release valve chamber 29c, and a bush press-fit portion 29d formed continuously, and their center lines are concentric. It is formed to become. Further, the release valve device 29 abuts the release valve 29e on the valve seat portion 29b, a spring 29f latched on the spring latching portion 29h of the bush 29g, abuts on the upper surface of the release valve 29e, and the bush 29g on the bush press-fit portion. 29d is press-fitted. Thus, the release valve 29e is constantly pressed against the valve seat portion 29b. The bush 29g is provided with a pressure relief hole 29i for discharging the overcompressed gas or liquid.

  The release valve device 29 is used during overcompression when the pressure in the compression chamber 28 becomes equal to or higher than the discharge pressure in the middle of the compression stroke, or during liquid compression in which liquid refrigerant is sucked from the suction port depending on temperature conditions during operation, etc. Further, as shown in FIG. 13, the spring 29f is compressed and the release valve 29e is opened. The release valve 29e is opened when it is overcompressed to a set pressure (discharge pressure + weight of the release valve 29e + elastic pressing force of the spring 29f) or more. When the release valve 29e is opened, the gas or liquid refrigerant that has risen above the set pressure of the discharge pressure chamber 21c is discharged from the compression chamber 28 to the discharge pressure chamber 21c, as indicated by the white frame arrow. As a result, it is possible to reduce the overcompression loss between the fixed scroll 24 and the orbiting scroll 25 and to prevent the lap from being damaged.

  With the rotation of the orbiting scroll, the compression chamber 28 having a pressure equal to or lower than the discharge pressure is then communicated with the release hole 29a, and the spring 29f is extended and the release valve 29e is closed as shown in FIG. As described above, the states shown in FIGS. 12 and 13 are repeated at the time of overcompression or liquid compression.

Japanese Patent Laid-Open No. 2002-221171

  However, in the release valve device 29 of the scroll compressor of Patent Document 1, a relatively large elastic pressing force of the spring 29f is applied to the discharge set pressure, and the compression force of the spring 29f is always pressed against the release valve 29e. As loaded. For this reason, the release valve 29e is not opened unless the pressure is higher than this, and the overcompressed gas or liquid refrigerant cannot be discharged. As a result, the opening delay of the release valve 29e has occurred.

  Further, when discharging the over-compressed gas or liquid refrigerant, the release hole 29a, the valve seat passage 29k between the valve seat 29b and the release valve 29e generated when the release valve 29e is opened, the release valve periphery 29m, the pressure relief The channel resistance was generated by the channel area ratio of the holes 29i. As a result, the operating load of the electric motor 22 is increased by the increase in the pressure in the compression chamber 28, and the compressor performance is deteriorated.

  Further, the pressing force of the spring 29f changes due to variations in depth accuracy when the bush press-fitting portion 29d is manufactured, variations in position accuracy when the bush 29g is pressed, and variations in the spring constant when the spring 29f is manufactured. Therefore, a large variation occurs in the pressure at which the release valve 29e is opened, and it is difficult to obtain a stable release valve function in mass production.

  Since the bush 29g is press-fitted into the bush press-fitting portion 29d, high processing accuracy is required for the bush 29g. If the pressure relief hole 29i is provided by machining, it takes a long time to process the bush 29g, which makes the part relatively expensive.

  In addition, the assembly force of the spring 29f locked to the spring locking portion 29h of the bush 29g in the prior art is not considered at all, so it is weak and is likely to come off when discharging the overcompressed gas or liquid refrigerant during operation. Had drawbacks.

  The release valve 29e has a relationship between the valve seat portion 29b and the release valve chamber 29c depending on the size of the spring 29f, the dimensions of the valve seat portion 29b, the release valve chamber 29c, the release valve 29e, and the natural length and diameter of the spring 29f. It had the disadvantage that it could get caught in between.

  An object of the present invention is to provide a scroll compressor that can prevent delay in opening of a release valve and reduce flow path resistance, improve performance, and have a reliable and reliable release valve function.

The purpose is
A compression mechanism that meshes the orbiting scroll and the fixed scroll to form a compression chamber, and compresses the working fluid sucked into the compression chamber;
A closed container that houses the compression mechanism and has a discharge pressure chamber into which the working fluid compressed in the compression chamber is discharged;
The fixed scroll includes a release valve device that opens the communication between the compression chamber and the discharge pressure chamber when the pressure in the compression chamber rises above a set pressure.
The release valve device includes a release passage provided in the fixed scroll so as to communicate the compression chamber and the discharge pressure chamber, a release valve provided to open and close the release passage, and the release A valve pressing body that applies an elastic pressing force to the valve when the valve closes the release flow path, and a retainer that limits a movement range of the valve pressing body,
The valve pressing body is disposed between the release valve and the retainer, the release valve is free when the release channel is closed, and the release valve is compressed when the release channel is opened. Having an elastic part,
The release flow path includes a release hole communicated with the compression chamber, and a release valve chamber communicated with the release hole and the discharge pressure chamber and having a larger diameter than the release hole, and the valve pressing body. Is provided in the release valve chamber, and includes a guide portion that guides movement in the release valve chamber, and an elastic portion that generates elastic pressing force,
The guide portion is a guide member having an outer diameter slightly smaller than the inner diameter of the release valve chamber, and the elastic portion is a coil spring mounted on the guide member.
Scroll compressor characterized by that
Is achieved.

The purpose is
A compression mechanism that meshes the orbiting scroll and the fixed scroll to form a compression chamber, and compresses the working fluid sucked into the compression chamber;
A closed container that houses the compression mechanism and has a discharge pressure chamber into which the working fluid compressed in the compression chamber is discharged;
The fixed scroll includes a release valve device that opens the communication between the compression chamber and the discharge pressure chamber when the pressure in the compression chamber rises above a set pressure.
The release valve device includes a release passage provided in the fixed scroll so as to communicate the compression chamber and the discharge pressure chamber, a release valve provided to open and close the release passage, and the release A valve pressing body that applies an elastic pressing force to the valve when the valve closes the release flow path, and a retainer that limits a movement range of the valve pressing body,
The valve pressing body is disposed between the release valve and the retainer, the release valve is free when the release channel is closed, and the release valve is compressed when the release channel is opened. Having an elastic part,
The release flow path includes a release hole communicated with the compression chamber, and a release valve chamber communicated with the release hole and the discharge pressure chamber and having a larger diameter than the release hole, and the valve pressing body. Is provided in the release valve chamber, and includes a guide portion that guides movement in the release valve chamber, and an elastic portion that generates elastic pressing force,
A scroll compressor characterized in that the guide member is formed of sintered or resin.
Is achieved.

  According to the scroll compressor of the present invention, the delay in opening the release valve can be prevented, the operation load can be reduced, and the compressor performance can be improved.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.

  First, a scroll compressor according to a first embodiment of the present invention will be described with reference to FIGS.

  First, the overall configuration of the scroll compressor 1 of the present embodiment will be described with reference to FIGS. 1 and 2. FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention, and FIG. 2 is a transverse sectional view of a compression mechanism portion of FIG.

  The scroll compressor 1 is composed of a high-pressure chamber type hermetic scroll compressor, is used as a part of a refrigeration cycle such as a room air conditioner, and is used under a wide range of operating conditions. The scroll compressor 1 includes a compression mechanism unit 3 having a orbiting scroll 6 and a fixed scroll 5 provided with spiral wraps 6a and 5c, an electric motor 4 for driving the compression mechanism unit 3, a compression mechanism unit 3 and an electric motor. 4 and a cylindrical vertically long sealed container 2 in which 4 is accommodated. A compression mechanism unit 3 is disposed in the upper part of the sealed container 2, and an electric motor 4 is disposed in the lower part. The orbiting scroll 6 and the fixed scroll 5 are meshed vertically. A lubricating oil 13 is stored at the bottom of the sealed container 2.

  The sealed container 2 is configured by welding a lid chamber 2b and a bottom chamber 2c up and down to a cylindrical case 2a. The lid chamber 2b is provided with a suction port 2d, and the inside of the sealed container 2 provided with a discharge port 2e on the side surface of the case 2a is a discharge pressure chamber 2f. A compression mechanism 3 and an electric motor 4 are accommodated in the discharge pressure chamber 2f.

  The compression mechanism unit 3 is integrated with the fixed scroll 5 having the spiral wrap 5c on the base plate 5d, the orbiting scroll 6 having the spiral wrap 6a on the base plate 5d, and the fixed scroll 5 with a fastening member or the like. And a frame 9 that supports the orbiting scroll 6.

  That is, as shown in FIG. 2, the fixed scroll 5 is provided with a gas passage 5b communicating with the suction port 5a and the discharge pressure chamber 2f. The gas passage 5b is spirally formed by a spiral wrap 5c. An orbiting scroll 6 formed in a substantially disk shape is opposed to the fixed scroll 5 and is arranged to be orbitable. As shown in FIG. 2, a spiral wrap 6a meshing with the wrap 5c of the fixed scroll 5 is provided on the upper surface of the orbiting scroll 6, and the suction chamber 10 and the compression chamber 11 are interposed between the wrap 5c and the wrap 6a. Is formed.

  The fixed scroll 5 is fixed to the frame 9 by bolts 8, and the outer peripheral side of the frame 9 is fixed to the inner wall surface of the sealed container 2 by welding. The fixed scroll 5 is provided with a release valve device 15. The frame 9 includes a main bearing 9a that rotatably supports the crankshaft 7. An eccentric portion 7 b of the crankshaft 7 is connected to the lower surface side of the orbiting scroll 6.

  An Oldham ring 12 is arranged between the lower surface side of the orbiting scroll 6 and the frame 9, and the Oldham ring 12 is attached to a groove formed on the lower surface side of the orbiting scroll 6 and a groove formed on the frame 9. The Oldham ring 12 functions to cause the orbiting scroll 6 to revolve without rotating due to the eccentric rotation of the eccentric portion 7 b of the crankshaft 7.

  The electric motor 4 includes a stator 4a and a rotor 4b. The stator 4a is fastened to the sealed container 2 by press fitting or the like. The rotor 4b is rotatably arranged in the stator 4a. The electric motor 4 is configured to orbit the orbiting scroll 6 via a crankshaft 7 fixed to the rotor 4b.

  The crankshaft 7 includes a main shaft 7 a and an eccentric portion 7 b and is supported by a main bearing 9 a and a lower bearing 17 provided on the frame 9. The eccentric portion 7 b is formed integrally with the main shaft portion 7 a of the crankshaft 7 so as to be eccentric, and is fitted to a orbiting bearing provided on the back surface of the orbiting scroll 6. The crankshaft 7 is driven by the drive of the electric motor 4, and the eccentric portion 7 b is eccentrically rotated with respect to the main shaft portion 7 a of the crankshaft 7 to drive the orbiting scroll 6. The crankshaft 7 has an oil supply passage 7c for guiding the lubricant 13 to the main bearing 9a, the lower bearing 17 and the slewing bearing. The oil supply passage 7c sucks the lubricant 13 into the shaft end on the motor unit side. An oil supply pipe 7d leading to is attached.

  An intermediate pressure chamber 14 is formed between the back side of the orbiting scroll 6 and the frame 9 and serves as an intermediate pressure between the pressure of the suction port 2d and the pressure of the discharge pressure chamber 2f. Lubricating oil 13 sealed at the bottom of the hermetic container 2 is supplied to the main bearing 9a and the like through an oil supply passage 7c formed at the center of the crankshaft 7 due to the pressure difference between the intermediate pressure chamber 14 and the discharge pressure chamber 2f. The intermediate pressure chamber 14 is formed in a path for supplying the lubricating oil 13 in the sealed container 2 to the sliding portion of the compression mechanism portion 3.

  When the compression mechanism section 3 is swung through the crankshaft 7 driven by the electric motor 4, the volume decreases as the compression chamber 11 formed by the orbiting scroll 6 and the fixed scroll 5 moves toward the center of the scroll. Then, the sucked refrigerant gas is compressed. The compressed refrigerant gas is discharged from the discharge port 5e provided at the approximate center of the base plate 5d of the fixed scroll 5 to the discharge pressure chamber in the sealed container 2.

  The suction port 2d is for guiding the refrigerant gas to the suction side of the compression mechanism unit 3 through the sealed container 2 from its upper surface. The discharge port 2e is connected to the side surface so as to communicate with the discharge pressure chamber 2f in the sealed container 2.

  In the scroll compressor 1, when the orbiting scroll 6 is swung through the crankshaft 7 by rotating the rotor 4 b of the electric motor 4, the refrigerant gas sucked from the gas suction port 2 d is mixed with the fixed scroll 5 and the orbiting scroll. 6 is discharged from the discharge port 5e provided in the center of the fixed scroll 5 to the discharge pressure chamber 2f of the sealed container 2. The discharged refrigerant gas is guided downward through a passage provided on the outer periphery of the frame 9, and after cooling the electric motor 4, the refrigerant gas is guided into the refrigeration cycle outside the sealed container 2 from the discharge port 2 e.

  Next, the release valve device 15 will be described with reference to FIGS. 3 is an enlarged sectional view of the release valve device 15 of FIG. 1 in a closed state, FIG. 4 is an enlarged sectional view of the release valve device portion 15 of FIG. 3, and FIG. 5 is a plan view of the fixed scroll of FIG. 6 is an enlarged view of a main part of FIG.

  The release valve device 15 is for discharging from the compression chamber 11 to the discharge pressure chamber 2f when the pressure in the compression chamber 11 becomes equal to or higher than the discharge pressure, and a plurality of compression chambers formed in the compression mechanism section. Are installed at a plurality of locations of the fixed scroll 5 (see FIG. 5).

  This release valve device 15 is normally closed, and depending on the operating conditions such as gas refrigerant or room air conditioner, liquid refrigerant or mainly mist-like lubricating oil 13 is drawn into the compression chamber 11 from the suction port 2d as a working fluid. The In the process in which these working fluids are compressed by the orbiting movement of the orbiting scroll 6, when the pressure in the compression chamber 11 becomes equal to or higher than the discharge pressure, the release valve device 15 opens and the compression chamber 11 and the discharge pressure chamber are opened. 2f is communicated.

  As shown in FIGS. 3 and 4, the release valve device 15 includes a release flow path 15 i, a release valve 15 d, a valve pressing body 15 h, and a retainer 16. The release channel 15i is composed of a release hole 15a and a release valve chamber 15c, and is formed on the base plate 5d of the fixed scroll 5 so as to communicate the compression chamber 11 and the discharge pressure chamber 2f. The release valve 15d is for opening and closing the release flow path 15i.

  The valve pressing body 15h is for applying an elastic pressing force to the release valve 15d when the release valve 15d is closed. The valve pressing body 15h is installed in the release valve chamber 15c and is disposed between the release valve 15d and the retainer 16. . A guide portion that guides the movement in the release valve chamber 15c and an elastic portion that generates elastic pressing force are provided. The retainer 16 is for limiting the movement range of the valve pressing body 15h and holding the valve pressing body 15h in the release valve chamber 15c at a predetermined position during overcompression.

  A release hole 15a communicating with the compression chamber 11, an annular valve seat 15b, and a release valve chamber 15c communicating with the discharge pressure chamber 2f are formed continuously from the fixed scroll 5, and the compression chamber 11 and the discharge pressure chamber 2f are formed. The release flow path 15i that connects The release hole 15a has a small diameter and the release valve chamber 15c has a large diameter, and a valve seat 15b is formed at a step portion of the release valve chamber 15c.

  That is, the release hole 15a, the valve seat 15b, and the release valve chamber 15c are formed in a region in the thickness direction of the base plate 5d of the fixed scroll 5. In particular, the release hole 15a is formed so as to reduce its volume, which is the dead volume of the compression chamber 11, by minimizing its inner diameter and length. Further, the release valve chamber 15c has a larger diameter than the release hole 15a so that the size of the valve pressing body 15h that can sufficiently secure the function can be obtained.

  The release valve chamber 15c is provided with a release valve 15d that opens when the pressure in the compression chamber 11 exceeds the set pressure of the discharge pressure chamber 2f and releases the gas or fluid in the compression chamber 11 to the discharge pressure chamber 2f. It is installed. The annular valve seat 15b provided on the boundary surface between the release hole 15a and the release valve chamber 15c on the release valve chamber 15c side of the release hole 15a has a release valve formed of a disc-shaped spring steel plate or the like. It arrange | positions so that 15d may contact | abut.

  A valve pressing body 15h including a guide member 15f constituting a guide portion and an elastic member 15e constituting an elastic portion is mounted on the release valve 15d. The valve pressing body 15h is formed of a thin steel plate or the like, and is configured by integrally combining one end of the elastic member 15e with a part of the guide member 15f by press-fitting or the like.

  The release channel 15i is formed to extend vertically, and the release valve 15d is configured to receive the load of the valve pressing body 15h. The release valve 15d is opened when it is overcompressed to a set pressure (discharge pressure + weight of the release valve 15d + weight of the elastic member 15e + weight of the guide member 15f) or more. Note that the pressing force by “the weight of the release valve 15d + the weight of the elastic member 15e + the weight of the guide member 15f” is extremely small.

  The guide member 15f has an outer diameter slightly smaller than the inner diameter of the release valve chamber 15c, and can move within the release valve chamber 15c. The elastic member 15e is a coil spring, is attached to the guide member 15f, and is moved together with the guide member 15f. The elastic member 15e is configured to be free when the release valve 15d closes the release flow path 15i, and to be compressed while the release valve 15d opens the release flow path 15i. The free state of the elastic member 15e in this case is a state where the valve pressing body 15h is not in contact with the retainer 16. This is a state where the reaction force from the retainer 16 is not applied to the elastic member 15e.

  The retainer 16 has a gas or liquid escape hole 16a, and is attached above the base plate 5d of the fixed scroll 5 with a bolt 18 or the like with a gap from the upper surface of the base plate 5d. The retainers 16 of the release valve devices 15 provided at a plurality of locations are formed of a single member.

  In the above configuration, when the electric motor 4 is driven to rotate and the orbiting scroll 6 performs an orbiting motion, the refrigerant gas is guided from the suction port 2d to the suction chamber 10 and the compression chamber 11, and the compressed gas is discharged from the discharge port 5e of the fixed scroll 5. It is discharged to the discharge pressure chamber 2f and further discharged from the discharge port 2e of the sealed container 2 to the piping of a refrigeration cycle such as a room air conditioner.

  During the normal operation in which the pressure in the compression chamber 11 is equal to or lower than the set pressure “discharge pressure + weight of the release valve 15d + weight of the valve pressing body 15h” in the process of compressing the refrigerant gas, the discharge pressure chamber is more than the pressure in the compression chamber 11 Since the pressure of 2f is higher, the release valve 15d is brought into contact with the valve seat 15b due to the pressure difference, and the release hole 15a is closed (see FIG. 3). Since the differential pressure is constantly applied to the upper surface of the release valve 15d during this closing, this closing is continued. Thus, during normal operation, the working fluid is not discharged from the release valve device 15 into the discharge pressure chamber 2f. At this time, the volume of the release hole 15a becomes a part of the volume of the compression chamber 11 and becomes a dead volume accompanied by re-expansion loss of the gas remaining in the compression stroke. Therefore, as described above, it is desirable to make the volume as small as possible. .

  On the other hand, when the pressure in the compression chamber 11 exceeds the set pressure in the process of compressing the refrigerant gas or liquid refrigerant or lubricating oil in the operating condition of the room air conditioner or the like (during operation due to overcompression), The pressure in the compression chamber 11 becomes higher than the pressure in the discharge pressure chamber 2f, and the release valve 15d is separated from the valve seat 15b by the pressure difference, and the release hole 15a is opened (see FIG. 4). Along with the movement of the release valve 15d, the valve pressing body 15h is moved while being guided by the guide member 15f. When the guide member 15f is further moved, the guide member 15f comes into contact with the retainer 16 to restrict its movement, and the elastic member 15e is pressed and compressed by the release valve 15d.

  During this time, the working fluid in the compression chamber 11 passing through the release hole 15a passes through the valve seat passage 15n between the valve seat 15b and the release valve 15d as shown by the white frame arrow in FIG. It passes through the release valve periphery 15j between the inner wall of the chamber 15c and reaches the discharge pressure chamber 2f side of the release valve 15d. Thereafter, the over-compressed working fluid is discharged into the discharge pressure chamber 2f through the escape hole 15g provided in the central portion of the guide member 15f and the escape hole 16a of the retainer 16. This can prevent over-compression loss and scroll wrap damage.

  In this overcompression operation state, with the rotation of the orbiting scroll, the compression chamber 11 having a pressure equal to or lower than the discharge pressure communicates with the release hole 15a next, and the pressure in the compression chamber 11 is the pressure in the discharge pressure chamber 2f. The release valve 29e is instantaneously closed by the elastic pressing force of the elastic member 15e together with the differential pressure. As described above, the states shown in FIGS. 4 and 3 are repeated during the overcompression operation.

  In the scroll compressor 1 in the present embodiment, as the set pressure for opening the release valve 15d, it is possible to eliminate the compression force of the elastic member that is always loaded on the release valve by press-fitting the bush in a conventionally known compressor, Instead, only the dead weight of the valve pressing body 15h (the elastic member 15e and the guide member 15f) is loaded, so that the set pressure for opening the release valve 15d can be remarkably lowered, and due to the delay in opening the release valve 15d. The electric motor load corresponding to the pressure rise in the compression chamber 11 is reduced, and the compressor performance can be improved. In addition, it is possible to eliminate variations in compressor performance caused by fluctuations in the pressure at which the release valve opens due to variations in manufacturing accuracy, such as conventional bush press-fitting holes and spring constants of elastic members. It is only necessary to manage the weight of the guide member 15f and the elastic member 15e to be controlled, the set pressure at which the release valve 15d is opened can be stabilized, and the scroll compressor 1 having stable performance can be supplied. .

  It is as follows when the effect based on this embodiment demonstrated above is described collectively with a structure.

  According to the present embodiment, the valve pressing body 15h is disposed between the release valve 15d and the retainer 16, becomes free when the release valve 15d closes the release flow path, and the release valve 15d opens the release flow path. Since it is configured to have an elastic portion that is compressed in an open state, the release valve 15d can be prevented from delaying the opening, and the pressure increase in the compression chamber 11 can be suppressed accordingly, thereby reducing the operating load. It is possible to improve the compressor performance by reducing it, and it is possible to stably obtain the start of opening of the release valve 15d, and thereby to obtain a stable function as the release valve device 15 in mass production.

  Further, according to the present embodiment, the release flow path 15i includes the release hole 15a communicated with the compression chamber 11, the release valve communicated with the release hole 15a and the discharge pressure chamber, and has a larger diameter than the release hole 15a. Since the valve pressing body 15h includes a guide portion that is disposed in the release valve chamber 15c and is guided to move in the release valve chamber 15c, and an elastic portion that generates an elastic pressing force. The valve pressing body 15h can be reliably moved in the large-diameter release valve chamber 15c while reducing the re-expansion loss of the working fluid by the release hole 15a by reducing the volume of the release hole 15a. High performance and high reliability can be obtained.

  Further, according to the present embodiment, the guide portion is formed by the guide member 15f having an outer diameter slightly smaller than the inner diameter of the release valve chamber 15c, and the elastic portion is formed by the coil spring 15e attached to the guide member 15f. Therefore, it is possible to obtain a guide member 15f having an appropriate guide function while obtaining an elastic pressing force with an inexpensive and highly reliable coil spring 15e.

  Furthermore, according to the present embodiment, the guide member 15f has an outer diameter of a gap that can move through the release valve chamber 15c, and a passage through which gas or liquid pressurized above the set pressure of the discharge pressure chamber 2f is released. Since it is an opening, a reliable guide function and a reliable gas or liquid discharge function can be combined.

  Furthermore, according to the present embodiment, the release valve device 15 is provided at a plurality of locations corresponding to the plurality of compression chambers 11 formed in the compression mechanism unit 3, and the retainers 16 of these release valve devices 15 are the same member. Therefore, it is possible to reliably prevent over-compression with an inexpensive structure.

  Further, according to the present embodiment, the orbiting scroll 6 and the fixed scroll 5 are meshed vertically, the release flow path 15i is formed to extend vertically, and the release valve 15d receives the load of the guide member 15f and the coil spring 15e. Thus, the load of the guide member 15f and the coil spring 15e can be applied to the release valve 15d while the release valve 15d is closed. The circuit closing performance can be ensured.

  Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 7 is a sectional view of the release valve device 15 of the scroll compressor according to the second embodiment of the present invention in a closed state, and FIG. 8 is a sectional view of the release valve device 15 in FIG. The second embodiment is different from the first embodiment in the following points, and is basically the same as the first embodiment in other points.

  In this second embodiment, the valve pressing body 15h is formed by a single coil spring 15h having a tightly wound portion 15k constituting a guide portion and an extendable / contractible portion 15e constituting an elastic portion. That is, FIG. 7 shows a state in which the release valve 15d is closed, but the tightly wound portion 15k in which there is almost no gap between adjacent wire members on the upper portion of the valve pressing body 15h smoothly moves inside the release valve chamber 15c. The outer expandable portion 15e is formed in a coil shape with an outer diameter size, and the lower expandable portion 15e has a cushioning action against the pressure when the gas or fluid is released from the release hole 15a, and the release valve 15d is instantaneously released after the gas or fluid is released. It is intended to play a role for closing back. The expandable portion 15e has a smaller outer diameter than the tightly wound portion 15k, so that it does not come into contact with the inner wall of the release valve chamber 15c even when the expandable portion 15e is contracted to increase its diameter. Has been. FIG. 8 shows that the release valve 15d and the valve pressing body 15h are used to release gas or fluid as indicated by the white frame arrow because the pressure in the compression chamber 11 is overcompressed from the discharge pressure chamber 2f and the release valve 15d opens. The state which is contacting the retainer 16 of the retaining ring at the time of raising is shown.

  According to the second embodiment, the valve pressing body 15h is formed by a single coil spring having a tightly wound portion constituting the guide portion and an extendable portion constituting the elastic portion, so that an extremely inexpensive valve It can be set as a pressing body.

  Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 9 is a sectional view of the release valve device portion 15 of the scroll compressor according to the third embodiment of the present invention in a closed state, and FIG. 10 is a sectional view of the release valve device portion 15 in FIG. The third embodiment is different from the first embodiment in the following points, and is basically the same as the first embodiment in other points.

  In the scroll compressor according to the third embodiment, the guide member 15f is formed of a cylindrical body, a relief hole 15g is formed at the center of the cylindrical body, and a plurality of relief holes 15L are formed around the relief hole 15g. Since this guide member 15f has a similar structure to a conventional bush, it is possible to use production equipment and to ensure the performance of releasing the working fluid from the guide member 15f as in the conventional case.

  Moreover, the close_contact | adherence winding part was provided in the both ends of the coil spring which comprises the elastic member 15e. By using both ends as close winding portions, the assembly direction of the coil spring is not limited to one direction at the time of assembly with the guide member 15f, so that the assemblability is good. Further, the tightly wound portion makes it difficult for the guide member 15f to come off, so that the assemblability can be improved with an inexpensive structure and the coil spring can be prevented from coming off.

  According to the present embodiment, the ratio of the natural length and the diameter of the elastic member 15e is 1: 0.8 to 4.0, and the elastic member 15e can be expanded and contracted, the diameter of the annular valve seat 15b, and the release. The ratio of the inner diameter of the valve chamber 15c and the outer diameter of the release valve 15d was 1: 3 or less: 5 or less: 3 or more. By having such a relationship, when the release valve 15d is separated from the valve seat 15b and the release flow path i is opened, the release valve 15d is prevented from being caught in the release flow path 15i by being out of posture. Can do.

  Moreover, according to the present embodiment, the flow area ratio of the release hole 15a, the valve seat passage 15n, the release valve periphery 15j, and the escape passage 15m is 1: 1 to 10: 1 to 15: 1 to 20, The flow path resistance of the release valve device 15 can be reduced.

  The guide member 15f shown in FIGS. 9 and 10 can be manufactured at a low cost even in a fine shape by being obtained by molding a sintered metal or resin.

  Further, as representatively shown in the third embodiment (even in other embodiments), the retainer 16 is not necessarily required to have a gap with the base plate 5d of the fixed scroll 5. Similarly, as representatively shown in the third embodiment, the release valve chamber 15c is formed in a two-stage shape, and the guide portion or the guide member is structured to restrict the approach to the release hole side more than necessary. It is possible to prevent the part or the guide member from vibrating greatly in the release valve chamber and generating an impact sound with the retainer 16.

  As described above, according to the scroll compressor to which the embodiment of the present invention is applied, it is possible to prevent the delay in opening the release valve and reduce the flow resistance when discharging the overcompressed gas or the liquid refrigerant with a small dead volume. It is possible to reduce the operating load and improve the compressor performance. Further, the release valve can be prevented from being caught, and a reliable and stable release valve function can be obtained in a mass production and at a low cost.

It is a longitudinal cross-sectional view of the scroll compressor of 1st Example of this invention. It is a cross-sectional view of the compression mechanism part of FIG. It is an expanded sectional view of the closed state of the release valve apparatus of FIG. It is an expanded sectional view of the open circuit state of the release valve apparatus part of FIG. It is a top view of the fixed scroll of FIG. It is a principal part enlarged view of FIG. It is sectional drawing of the closed state of the release valve apparatus of the scroll compressor of 2nd Example of this invention. It is sectional drawing of the open circuit state of the release valve apparatus of FIG. It is sectional drawing of the closed state of the release valve apparatus part of the scroll compressor of 3rd Example of this invention. It is sectional drawing of the open circuit state of the release valve apparatus part of FIG. The longitudinal cross-sectional view of the conventional scroll compressor. It is an expanded sectional view of the closed state of the release valve apparatus of FIG. It is an expanded sectional view of the open circuit state of the release valve apparatus of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Scroll compressor, 2 ... Sealed container, 2a ... Case, 2b ... Lid chamber, 2c ... Bottom chamber, 2d ... Intake port, 2e ... Discharge port, 2f ... Discharge pressure chamber, 3 ... Compression mechanism part, 4 ... Electric motor 4a ... Stator, 4b ... Rotor, 5 ... Fixed scroll, 5a ... Suction port, 5b ... Gas passage, 5c ... Wrap, 5d ... Base plate, 5e ... Discharge port, 6 ... Revolving scroll, 6a ... Wrap, 7 ... crankshaft, 7a ... main shaft, 7b ... eccentric part, 7c ... oil supply passage, 8 ... bolt, 9 ... frame, 9a ... main bearing, 10 ... suction chamber, 11 ... compression chamber, 12 ... Oldham ring, 13 ... lubricating oil 14 ... Intermediate pressure chamber, 15 ... Release valve device, 15a ... Release hole, 15b ... Valve seat, 15c ... Release valve chamber, 15d ... Release valve, 15e ... Elastic member, 15f ... Guide member, 15g ... Relief hole, 15h ... Valve pressing body, 5i ... release passage, 15j ... release valve around, 15n ... valve seat passage, 15L ... relief holes, 15 m ... relief passage 16 ... retainer, 16a ... relief holes.

Claims (7)

A compression mechanism that meshes the orbiting scroll and the fixed scroll to form a compression chamber, and compresses the working fluid sucked into the compression chamber;
A closed container that houses the compression mechanism and has a discharge pressure chamber into which the working fluid compressed in the compression chamber is discharged;
The fixed scroll includes a release valve device that opens the communication between the compression chamber and the discharge pressure chamber when the pressure in the compression chamber rises above a set pressure.
The release valve device includes a release passage provided in the fixed scroll so as to communicate the compression chamber and the discharge pressure chamber, a release valve provided to open and close the release passage, and the release A valve pressing body that applies an elastic pressing force to the valve when the valve closes the release flow path, and a retainer that limits a movement range of the valve pressing body,
The valve pressing body is disposed between the release valve and the retainer, the release valve is free when the release channel is closed, and the release valve is compressed when the release channel is opened. It has a resilient portion to be,
The release flow path includes a release hole communicated with the compression chamber, and a release valve chamber communicated with the release hole and the discharge pressure chamber and having a larger diameter than the release hole, and the valve pressing body. Is provided in the release valve chamber, and includes a guide portion that guides movement in the release valve chamber, and an elastic portion that generates elastic pressing force,
The guide part is a guide member having an outer diameter slightly smaller than the inner diameter of the release valve chamber, and the elastic part is a coil spring attached to the guide member.
A scroll compressor characterized by that. 2. The scroll compressor according to claim 1 , wherein the guide member has an outer diameter of a gap slidable with the release valve chamber, and is a gas or liquid pressurized to a pressure higher than a set pressure of the discharge pressure chamber. A scroll compressor characterized in that a passage for releasing air is opened. The scroll compressor according to claim 1 ,
The scroll compressor, wherein the orbiting scroll and the fixed scroll are meshed vertically, the release flow path is provided extending vertically, and the release valve receives a load of the valve pressing body. The scroll compressor according to claim 1 ,
A scroll compressor characterized by having tight windings at both ends of a coil spring constituting the elastic portion. In the scroll compressor according to claim 2 ,
The release hole, a valve seat passage formed between the valve seat and the release valve that is generated when the release valve is opened, a space around the release valve that is a space between the release valve and the wall surface of the release flow path, and A scroll compressor characterized in that a flow passage area ratio of an escape passage provided in or around the guide portion is 1: 1 to 10: 1 to 15: 1 to 20. The scroll compressor according to claim 1 ,
The ratio of the natural length and the diameter of the coil spring constituting the elastic part is 1: 0.8 to 4.0, and the elastic part can be expanded / contracted, the valve seat diameter, the release valve chamber diameter, and the release valve diameter ratio. Is defined as 1: 3 or less: 5 or less: 3 or more. A compression mechanism that meshes the orbiting scroll and the fixed scroll to form a compression chamber, and compresses the working fluid sucked into the compression chamber;
A closed container that houses the compression mechanism and has a discharge pressure chamber into which the working fluid compressed in the compression chamber is discharged;
The fixed scroll includes a release valve device that opens to communicate the compression chamber and the discharge pressure chamber when the pressure in the compression chamber rises above a set pressure,
The release valve device includes a release passage provided in the fixed scroll so as to communicate the compression chamber and the discharge pressure chamber, a release valve provided to open and close the release passage, and the release A valve pressing body that applies an elastic pressing force to the valve when the valve closes the release flow path, and a retainer that limits a movement range of the valve pressing body,
The valve pressing body is disposed between the release valve and the retainer, the release valve is free when the release channel is closed, and the release valve is compressed when the release channel is opened. It has a resilient portion to be,
The release flow path includes a release hole communicated with the compression chamber, and a release valve chamber communicated with the release hole and the discharge pressure chamber and having a larger diameter than the release hole, and the valve pressing body. Is provided in the release valve chamber, and includes a guide portion that guides movement in the release valve chamber, and an elastic portion that generates elastic pressing force,
A scroll compressor characterized in that the guide member is formed of sintered or resin.

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