JPH06249164A - Scroll compressor - Google Patents

Abstract

PURPOSE:To bypass high and low pressures securely even if large-pressure pulses are generated due to liquid compression at flooded start of the day of a scroll compressor to prevent oil inside the compressor from being diluted. CONSTITUTION:A compression element comprising a fixed scroll 1 and an oscillating scroll 3 is arranged in a closed container, an electric motor element to drive the compression element is installed in a suction pressure atmosphere 15 inside the closed container, a delivery muffler chamber 14 which stores high- pressure gas sucked and compressed by the compressed element and separates it from sucked gas is provided. Then, in a scroll compressor in which a connecting hole 33 which passes through the delivery muffler chamber 14 and suction pressure atmosphere and a valve mechanism which closes the connecting hole 33 are installed, the valve mechanism is structured with a valve holder 30 and a combination valve 31 of a temperature-sensitive valve 31a and a highly rigid material valve 31b, and the highly rigid material valve 31b is located on the connecting hole side, and the temperature sensitive valve 31a is located on the valve holding side.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used for an air conditioner or a refrigerator.

[0002]

2. Description of the Related Art FIG. 17 is a sectional view showing a conventional scroll compressor disclosed in Japanese Patent Laid-Open No. 3-237286. In the figure, 1 is a fixed scroll having a spiral portion, 2 is a discharge hole formed substantially in the center of the fixed scroll 1, 3 is an orbiting scroll having a spiral portion, and 4 is an orbit for preventing the orbiting scroll 3 from rotating. An Oldham ring 5 that gives motion, 5 a thrust bearing that receives the thrust load of the orbiting scroll 3, 6 a crankshaft that transmits the driving force of the electric motor, 7 a centrifugal pump hole formed eccentrically to the crankshaft 6, and 8 Oldham A main frame that supports the ring 4 and the thrust bearing 5, 9 is a sub-frame, and 10 is a balance weight. Reference numeral 1 above
The components designated by 10 are the compression elements of the scroll compressor. Reference numeral 11 represents a stator, and 12 represents a rotor, and these constituent parts are electric motor elements. The fixed scroll 1, the main frame 8 and the sub-frame 9 in the compression element are airtightly joined to the inner wall of the closed container 13 by shrink fitting or the like, and the discharge muffler 14 and the suction pressure chamber, that is, the suction pressure atmosphere portion 15 are divided in the vertical direction. There is. Further, 16 is a discharge pipe for discharging a discharge gas, 17 is a suction pipe for introducing a suction gas, and 18 is a lubricating oil for lubricating a sliding portion such as a compressor bearing.

Next, the operation of the above-mentioned conventional scroll compressor will be described. The power generated by the electric motor element is transmitted to the orbiting scroll 3 by the crankshaft 6, and the Ordham ring 4 makes an orbital movement, thereby forming a pair of spirals of the orbiting scroll 3 and the fixed scroll 1 combined with each other. The volume of the compression chamber 19 is changed so that the refrigerant gas sucked from the suction pipe 17 toward the inner circumference from the outer peripheral portion of the spiral is sucked through the suction passage 20 and compressed, and is discharged from the discharge hole 2 as high-temperature high-pressure discharge gas. It is discharged into the discharge muffler 14 and then discharged from the compressor through the discharge pipe 16. At that time, the lubricating oil 18 at the bottom of the closed container 13 is given an oil supply head by the centrifugal force by the eccentric hole 7 of the crankshaft 6 and ascends in the eccentric hole 7 to lubricate sliding parts such as bearings, and then the suction pressure. It is discharged into the atmosphere part 15 and returns to the bottom part of the closed container.

Since the conventional scroll compressor is constructed as described above, when the compressor is stopped, especially when the compressor is in a stopped state for a long time and the temperature of the compressor is low, the scroll compressor or the air-conditioning system can be operated. The refrigerant may be liquefied and flow into the compressor in a large amount, and a large amount of saturated liquid in which the lubricating oil in the compressor is dissolved may be retained (sleeping state). When the compressor is started in such a state, the space in which the saturated liquid stays is the suction pressure space, so the pressure of the starting pressure is suddenly reduced from the balanced state, and the saturated liquid refrigerant vaporizes rapidly. Due to the viscosity of the lubricating oil, a foaming state occurs, and the bubbles formed by the refrigerant and the lubricating oil are sucked into the compression chamber through the suction passage 20, compressed, and discharged to the discharge muffler 14,
It is discharged to the circuit of the refrigeration or air conditioner through the discharge pipe 16. This causes a large amount of lubricating oil to be discharged to the outside of the compressor, reducing the amount of lubricating oil inside the compressor, causing abnormal wear and seizure of the sliding part due to poor supply of lubricating oil to the sliding part of the compressor. Was becoming. Further, when lying down, a large amount of liquid refrigerant may accumulate not only in the compressor but also in the accumulator (not shown) attached to the suction side of the compressor. If the compressor is started in such a state, as described above, the lubricating oil in the compressor is taken out of the compressor and the large amount of liquid refrigerant accumulated in the accumulator when the compressor residual oil becomes small And the lubricating oil in the compressor was diluted, and abnormal wear and seizure occurred on the sliding parts of the compressor due to the decrease in oil concentration.

FIG. 18 is a cross-sectional view of a conventional scroll compressor provided with a high / low pressure bypass valve mechanism for the purpose of preventing lubricating oil from being taken out of the compressor at the time of starting to sleep. In the scroll compressor shown in FIG. 18, the fixed scroll 1, the main frame 8 and the sub frame 9 that are hermetically fitted in the closed container 13 are provided.
A communication hole 33 is formed in the vicinity of the peripheral edge portion of the above so as to penetrate the discharge muffler 14 and the suction pressure atmosphere portion 15. On the upper surface of the fixed scroll 1 in which the opening of the communication hole 33 on the discharge muffler 14 side is formed, a valve device 34 for opening and closing the opening is provided. This valve device 34 is
For example, a valve 35, which is made of bimetal or shape memory alloy and which opens the opening of the communication hole 33 when the temperature is low and closes the opening of the communication hole 33 when the temperature rises, is fixed to the upper surface of the fixed scroll 1 by the bolt 32. .

According to the scroll compressor configured as described above, when the compressor is stopped for a long time and the refrigerant is condensed inside the compressor, the temperature of the compressor is almost equal to the outside atmosphere. At this time, the valve 35 is in a state where the communication hole 33 is opened. When the compressor is activated, the suction pressure atmosphere portion 15 is depressurized by sucking the refrigerant gas into the compression chamber, but since the communication hole 33 is opened to the discharge muffler 14, the discharge gas bypasses to the suction side. The depressurization rate (ratio of pressure decrease to elapsed time) decreases. Therefore, the degree of foaming of the mixed liquid of the refrigerant and the lubricating oil can be suppressed, and the amount of the mixed bubbles of the refrigerant and the lubricating oil flowing into the compression chamber through the suction passage 20 can be suppressed. Further, since the lubricating oil flowing into the compression chamber and discharged to the discharge muffler 14 is returned to the suction pressure atmosphere portion 15 through the communication hole 33, the amount of lubricating oil taken out of the compressor can be reduced. If the discharge muffler 14 is provided with a concave portion or the like serving as an oil reservoir and the communication hole 33 is provided in that portion, oil return can be effectively performed. After a lapse of a certain time after the compressor is started, the valve 35 in the high-temperature discharge gas atmosphere is
Deforms so that the temperature rises and the communication hole 33 is closed.
This puts the compressor in a normal operating state, but the communication hole 3
By setting the cross-sectional area of No. 3 and the opening / closing temperature of the valve 35 to the optimum values, the degree and duration of the bubbling state can be controlled and the amount of lubricating oil in the compressor can be maintained at an appropriate value.

[0007]

The conventional scroll compressor having a high / low pressure bypass mechanism is constructed as described above, but it is a bypass valve using a temperature sensitive valve such as bimetal or shape memory alloy. In the mechanism, since the rigidity of these valves is lower than that of general steel such as Swedish steel, when the valve is closed and the collision speed against the fixed scroll base plate is high, the valve cracks at the tip of the valve and the valve The root may be damaged. Therefore, in order to reduce the collision speed, the valve lift amount must be reduced.However, if the valve lift amount is reduced, the valve will close due to a slight difference in pressure between high and low pressure. There is a problem that the valve may be closed before the bubbling of the liquid refrigerant is stopped, and the necessary bypass time and the bypass effect cannot be obtained. Further, in the case of starting with a large amount of liquid refrigerant lying down, the refrigerant may be sucked into the compression chamber in a liquid state, and a large pressure pulse may be generated as discharge pressure due to liquid compression. In this case, the dynamic pressure due to the pressure pulse acts on the back pressure of the valve to close the valve, and the valve closes within a few seconds immediately after startup, and the bypass effect cannot be obtained at all. Further, when the valve is closed by the pressure pulse, the collision speed against the fixed scroll base plate is considerably high, which causes problems such as valve cracking and valve root damage.

The present invention has been made in order to solve the above-mentioned problems, and a large-pressure pulse due to liquid compression is required only for the bypass required time until the foaming of the liquid refrigerant in the compressor and the accumulator at start-up is stopped. Even if occurs, the high and low pressures are reliably bypassed, the sudden pressure drop on the suction pressure atmosphere side at startup is mitigated, and the generation of the mixed liquid of the refrigerant and lubricating oil retained in the compressor is suppressed, By preventing the oil from being taken out of the machine and mitigating the sudden liquid back phenomenon from the accumulator, it is possible to prevent the oil from diluting inside the compressor and ensure the required oil concentration, as well as valve cracking, valve root damage, etc. An object of the present invention is to provide a scroll compressor provided with a highly reliable high and low pressure bypass mechanism that does not occur.

[0009]

SUMMARY OF THE INVENTION A scroll compressor according to the present invention includes a compression element which is disposed in a closed container and includes a fixed scroll section and an orbiting scroll section which is driven by a drive element, and the compression element described above. A high pressure portion disposed on the side opposite to the orbiting scroll portion side of the fixed scroll portion for discharging high pressure refrigerant gas compressed by a compression element, and a suction pressure atmosphere portion provided inside the closed container and partitioned from the high pressure portion. And a communication hole provided in the fixed scroll portion that communicates the suction pressure atmosphere portion and the high pressure portion, a valve retainer provided in the high pressure portion so as to cover the communication hole, and when releasing the communication hole, A valve that is a combination of a temperature-sensitive valve and a high-rigidity material valve is provided near the communication hole that is in close contact with the valve retainer and closes the communication hole when closing the communication hole when closing the communication hole. .

Further, in the scroll compressor according to the present invention, the high pressure portion is arranged in the vicinity of the discharge portion of the fixed scroll,
A chamber for introducing a part of the high pressure refrigerant gas from the high pressure portion is provided on the side opposite to the orbiting scroll portion side of the fixed scroll portion, and the communication hole communicates the high pressure refrigerant gas and the suction pressure atmosphere portion inside the chamber. .

Further, in the scroll compressor according to the present invention, the valve retainer is arranged in the chamber.

Further, in the scroll compressor according to the present invention, when the valve comes into close contact with the valve retainer, a cover for covering the side surface of the valve is provided in the valve retainer.

Further, in the scroll compressor according to the present invention, the radius of curvature of the surface of the valve on the valve pressing side is smaller than the radius of curvature of the surface of the valve pressing on the valve side.

Further, in the scroll compressor according to the present invention, the surface of the valve retainer that is in close contact with the valve is equal to or slightly larger than the width of the valve, and the width of the surface opposite to the surface in close contact with the valve is the valve. The width of the closely contacting surface is made larger and the valve retainer is tapered.

Further, in the scroll compressor according to the present invention, the oil-immersive elastic body is fixed to one of the surface of the valve retainer which is in close contact with the valve and the face of the valve retainer which is in close contact with the valve retainer.

Further, in the scroll compressor according to the present invention, a recess for accommodating the temperature sensitive valve is provided on the surface of the scroll compressor which is in close contact with the valve combined with the valve retainer, and when the valve combined with the communication hole is opened. In addition, the temperature-sensitive valve is in close contact with the bottom of the concave portion, and the high-rigidity material valve is in close contact with the temperature-sensitive valve with a predetermined gap on the convex portion of the surface that is in close contact with the valve with the combined valve retainer. .

[0017]

In the scroll compressor according to the present invention, a communication hole provided in the fixed scroll section for communicating the suction pressure atmosphere section and the high pressure section, and a valve retainer arranged in the high pressure section so as to cover the communication hole. When the communication hole is opened, it is in close contact with the valve retainer, and when closing the communication hole, it is in close contact with the communication hole of the fixed scroll and closes the communication hole. Since a valve with a combination of valves is provided, even if the valve is in close contact with the valve retainer and a large pressure pulse is generated at room temperature before starting or at a low temperature immediately after starting, the dynamic pressure due to that pulse Does not act as back pressure on the valve and does not close. On the other hand, when the temperature is high during normal operation, the temperature sensitive valve is deformed by the temperature of the refrigerant gas in the high pressure section, moves away from the valve retainer in close contact with the high rigidity material valve, and closes the communication hole due to the differential pressure. Bypass the high pressure part and the low pressure suction pressure atmosphere part for the required time.

Further, in the scroll compressor according to the present invention, the high pressure portion is arranged in the vicinity of the discharge portion of the fixed scroll,
A chamber for introducing a part of the high-pressure refrigerant gas from the high-pressure portion is provided on the opposite side of the fixed scroll portion to the orbiting scroll portion side, and the communication hole communicates the high-pressure refrigerant gas inside the chamber with the suction pressure atmosphere portion. Therefore, in the low temperature state immediately after startup, the valve is in close contact with the valve retainer and the communication hole is opened, and during high temperature during normal operation, the temperature sensitive valve is deformed by the temperature of the refrigerant gas in the high pressure section. By separating from the valve retainer in close contact with the high-rigidity material valve and closing the communication hole by the differential pressure, the high pressure portion and the low pressure suction pressure atmosphere portion are bypassed for a required time.

Further, in the scroll compressor according to the present invention, the temperature rise of the chamber due to the heat mass of the chamber is delayed with respect to the temperature rise of the high pressure portion, and
Since the valve retainer is installed in the chamber, the temperature of the valve retainer and the temperature-sensitive valve that is in close contact with the valve retainer also have a time delay, which is necessary for the heat mass adjustment of the chamber due to the time delay with respect to the valve closing set temperature. The high pressure part and the low pressure suction pressure atmosphere part are bypassed for a certain period of time.

Further, in the scroll compressor according to the present invention, when the valve comes into close contact with the valve retainer, the cover for covering the side surface of the valve is provided in the valve retainer, so that the valve comes into close contact with the valve retainer at the time of starting. Then, even if a large pressure pulse is generated by storing it in the cover and deforming the valve during normal operation and causing it to go out of the cover, the pressure pulse is The valve will not close due to interference pressure reduction.

Further, in the scroll compressor according to the present invention, the radius of curvature of the valve-holding side surface of the valve is made smaller than the radius of curvature of the valve-holding side of the valve retainer. Even if a large pressure pulse occurs, the gap does not close well, and the dynamic pressure does not wrap around the valve back surface, and the valve does not close.

Further, in the scroll compressor according to the present invention, the surface of the valve retainer that is in close contact with the valve is made equal to or slightly larger than the width of the valve, and the width of the surface opposite to the surface in close contact with the valve is equal to that of the valve. Since the valve retainer is tapered by making it wider than the close contact surface, even if a large pressure pulse occurs, the fluid flow from the valve retainer to the communication hole becomes smooth and the dynamic pressure decreases, and The valve does not close because the pressure that acts around as a back pressure decreases.

Further, in the scroll compressor according to the present invention, since the oil-immersive elastic body is fixed to either the surface of the valve retainer which is in close contact with the valve or the surface of the valve retainer which is in close contact with the valve retainer,
Before starting, the valve and valve retainer are in close contact with each other, and even if a large pressure pulse is generated, the dynamic pressure does not wrap around the valve back face and the valve does not close.

Further, in the scroll compressor according to the present invention, a concave portion for accommodating the temperature sensitive valve is provided on the surface of the valve retainer which is in close contact with the valve, and when the communication hole is opened, the temperature of the bottom surface of the concave portion is increased. The high-rigidity material valve has a certain clearance on the convex part of the surface where the sensitive valve is in close contact with the valve retainer valve. When the temperature is relatively low, only the temperature-sensitive valve deforms, but it does not make contact with the high-rigidity material valve, and the high-rigidity material valve and the valve retainer are in close contact, so even if a large pressure pulse acts, the valve will not Do not close The temperature rises when approaching the normal operating condition with the passage of time, and when the temperature reaches a certain set temperature, the temperature-sensitive valve and the high-rigidity material valve come into contact with each other. It deforms and separates from the valve retainer, and the valve closes due to the differential pressure.

[0025]

【Example】

Example 1. Example 1 will be described with reference to FIG. FIG. 1 is a vertical cross-sectional view of a main part of the scroll compressor, and FIG. 2 is a vertical cross-sectional view of a valve portion showing the operation of the valve. FIG. 3 is an explanatory diagram showing changes over time in the discharge muffler temperature and the difference between the discharge pressure and the suction pressure. In FIG. 1, the same reference numerals as those in FIGS. 17 and 18 denote the same or corresponding parts, and detailed description thereof will be omitted. In the figure, 30 is a valve retainer of a high / low pressure bypass valve mechanism at the time of bed start, 31a is a temperature sensitive reed valve, 31b is a highly rigid material reed valve, 3
2 is a bolt for integrally fixing the valve retainer 30, the temperature-sensitive reed valve 31a, and the high-rigidity material reed valve 31b to the fixed scroll base plate 1 so as to be in close contact with each other at room temperature, and 31 is the temperature-sensitive reed valve 31a and the high-rigidity material. A valve in which a reed valve 31b is combined, and 33 is a discharge muffler 14 and a suction pressure atmosphere portion 15
It is a communication hole that communicates with.

Next, the operation will be described. As shown in FIG. 2A, the valve retainer 30, the temperature-sensitive reed valve 31a, and the high-rigidity material reed valve 31b are integrally fixed to the back surface of the fixed scroll at room temperature so that they come into close contact with each other. Therefore, even if a large pressure pulse due to liquid compression is generated by starting up in this state, the valve retainer 3
Since the valve 31 combined with 0 is in close contact, back pressure does not wrap around between the valve 31 combined with the valve retainer, and therefore the valve 31 combined does not close. As shown in FIG. 3, the temperature of the discharge muffler 14 rises as it approaches the normal operation as time elapses after the start-up. Since the temperature of the combined valve 31 and valve retainer 30 follows the temperature of the discharge muffler 14, the non-fixed end side of the temperature sensitive reed valve 31a is deformed as shown in FIG. The valve 31b also deforms. Due to the deformation, a gap 34 is formed between the valve retainer 30 and the valve 31 combined with each other, and a high and low pressure differential pressure acts on the gap 34. Therefore, as shown in FIG.
1 is closed and normal operation is performed. Further, by using a valve made of a high-rigidity material for the reed valve on the side of the communication hole 33, the strength of the high-rigidity material valve 31b is large, and the stress due to the collision at the time of valve closing and the root stress are ensured while ensuring a sufficient lift amount. It can be set below the allowable value.

As described above, the temperature sensitive reed valve 31a
By using both the high rigidity material reed valve 31b and the high rigidity material reed valve 31b, and by closely contacting the valve 31 and the valve retainer 30 that have been combined at low temperature before and immediately after startup, even if a large pressure pulse due to liquid compression occurs The combined valve 31 does not close until the temperature is reached. Therefore, the discharge muffler 14 and the suction pressure atmosphere portion 15 communicate with each other at the time of start-up, thereby bypassing the suction pressure atmosphere portion 15 side at the time of start-up so that the sudden pressure drop on the side of the suction pressure atmosphere portion 15 is alleviated and the refrigerant accumulated in the compressor is absorbed. Preventing oil dilution in the compressor by suppressing foaming of the mixed liquid of lubricating oil, preventing oil from being taken out of the compressor, and mitigating a sudden liquid back from the accumulator (not shown). You can Further, since a valve made of a high-rigidity material is used on the side of the communication hole 33, the valve stress due to a collision when the valve is closed and the valve root stress can be set below the allowable value of the valve while ensuring a sufficient lift amount. Therefore, it is possible to prevent the valve from being damaged by the impact when the valve is closed, and it is possible to obtain a highly reliable compressor. In this embodiment, the temperature-sensitive reed valve 31a,
Although the case where the high-rigidity material reed valve 31b is provided one by one, the same effect can be obtained even if each of the high-rigidity material reed valves 31b has a plurality of sheets due to the deformation amount, the valve material, and the like.

Example 2. In Example 1, the combined valve 3
1. A small gap may be formed between the valve retainer 30 due to dimensional variation, fixing method variation, etc., and a large pressure pulse due to liquid compression wraps around the gap and acts on the valve as a back pressure. May close. This embodiment is designed to prevent the valve from closing and will be described with reference to FIGS. FIG. 4 is a perspective view of a main part of the high / low pressure bypass valve mechanism showing the present embodiment, FIG. 5 is an explanatory view showing an operating state of the present embodiment, and FIG. 6 is a large pressure pulse during liquid compression and a time from starting. It is explanatory drawing which shows the relationship of. Figure 4
In the figure, 31 is a temperature sensitive valve 31a and a high rigidity material valve 3
A valve in which 1b is combined in the same manner as in Example 1, 30 is a valve retainer,
Reference numeral 35 is a cover integrally formed with the valve retainer 30 via a side surface of the valve 31 and a minute gap 37, and reference numeral 36 is a cover integrally formed with the valve retainer 30 via a front surface of the valve 31 and a minute gap. Figure 4
As shown in FIG. 6, the combined valve 31 is fixed so as to be in close contact with the valve retainer 30 in a low temperature state before and immediately after the activation. At this time, a slight gap may be formed between the combined valve 31 and valve retainer 30.

Next, the operation will be described. As shown in FIG. 5, in the low temperature state before and immediately after the startup, the combined valve 31
Is in a space formed by the valve retainer 30 and the covers 35 and 36. During normal operation, when the temperature of the combined valve 31 exceeds the set temperature, the combined valve 31 is deformed and goes out of the valve side cover 35 and the valve front cover 36, and the communication hole 33 is opened by the high and low pressure differential pressure. close. As shown in FIG. 6, when a large pressure pulse is generated due to liquid compression due to a bed full liquid start and the like, a slight gap is created between the valve 31 and the valve retainer 30 that are combined due to dimensional variations and fixing methods. Even if there is, if the valve temperature is below the set temperature and is inside the cover, the combined valve 3
1, the side cover 35 and the valve front cover 36 interfere with each other,
It is possible to prevent variations in the combined valves 31 due to a reduced pressure and a large pressure pulse, and to prevent valve closure due to back pressure action. Therefore, even if a large pressure pulse is generated due to the generation of liquid compression immediately after startup, the valve will not close unless the valve temperature reaches the set temperature.

As described above, even if there is a gap between the valve and the valve retainer due to variations in the dimensions of the valve and the valve retainer and variations in the fixing method, if the valve is inside the cover, a large pressure pulse due to liquid compression Since the cover reduces interference pressure, the valve rises to a set valve closing temperature and deforms, and does not close until it goes out of the cover, so that high pressure and low pressure can be reliably bypassed for a required time at startup.

Example 3. Example 3 will be described with reference to FIG. In the figure, 30 is a valve retainer, 31 is a radius of curvature R ₁ (R ₁ <R ₂ ) smaller than the radius of curvature R ₂ of the valve retainer 30, and the temperature sensitive valve 31 a and the high rigidity material valve 31 b are the same as those of the first embodiment. The same combination. By fixing the combined valve 31 and the valve retainer 30 to the rear surface of the fixed scroll 1, the combined valve 31 is fixed to the valve retainer 30 in a preloaded state. Therefore, even if there are variations in dimensions and variations in the fixing method, fixing with [Valve radius of curvature R ₁ ] <[Valve radius of curvature R ₂ ] will cause a difference in the rigidity of valve 31 combined with valve retainer 30. The combined valve 31 is deformed and fixed so as to conform to the valve retainer 30 in the preloaded state, so that the combined valve 31 and the valve retainer 30 are surely brought into close contact with each other. In the state where the combined valve 31 is in close contact with the valve retainer 30, the combined valve 31 does not close even if a large pressure pulse due to liquid compression occurs because the dynamic pressure does not wrap around the rear surface of the combined valve 31. It is possible to reliably bypass the high pressure and the low pressure for the required time.

Example 4. Example 4 will be described with reference to FIGS. FIG. 8 is a perspective view showing the fourth embodiment, and FIG. 9 shows an operating state. In FIG. 8, 30 is a valve retainer in which the end face opposite to the valve side is wider than the end face on the valve side.
It is integrally fixed to the valve 31 (not shown). The valve 31 includes a temperature sensitive valve 31a and a high rigidity material valve 31b.
In the same manner as in Example 1. Regarding the operation, as shown in FIG. 9, by making the valve retainer 30 in a tapered shape, the flow of the fluid flowing from the periphery of the valve retainer into the communication hole is smoothed by reducing the loss due to bending or the like.
Therefore, the dynamic pressure generated in the vicinity of the valve 31 combined with the valve retainer 30 is relieved, so that the valve 31 combined with the valve retainer 30 is combined.
Even if it wraps around as back pressure between them, it is difficult to close because the dynamic pressure itself is small. Therefore, even if there is a gap between the valve 31 and the valve retainer 30 that are combined due to variations in dimensions and variations in fixing method, the dynamic pressure generated in the gap due to back pressure due to the large pressure pulse due to liquid compression is reduced. The combined valve 31 does not close. Therefore, the high pressure and the low pressure can be reliably bypassed for a required time at the time of startup.

Example 5. Example 5 will be described with reference to FIG. FIG. 10 is a perspective view showing a main part of the high / low pressure bypass valve according to the fifth embodiment. In the figure, 30 has a valve retainer, 31 has a radius of curvature equal to or smaller than the radius of curvature R of the valve retainer,
The temperature-sensitive valve 31a and the high-rigidity material valve 31b are combined in the same manner as in the first embodiment. Reference numeral 38 is an oil-immersive elastic body fixed to the valve retainer 30. This valve 31 and oil-immersive elastic body 38
By fixing the valve retainer 30 fixed to the fixed scroll 1 to the back surface of the fixed scroll 1, the combined valve 31 comes into close contact with the oil-impregnated elastic body 38 fixed to the valve retainer 30. Therefore, even if there are variations in dimensions and variations in the fixing method, the valve 31 comes into close contact with the oil-permeable elastic body 38, and even if a large pressure pulse is generated due to liquid compression, the differential pressure wraps around the back surface of the valve 31. First, since the combined valve 31 is not closed, the high pressure and the low pressure can be reliably bypassed for a required time at the time of startup.

Example 6. Example 6 will be described with reference to FIGS. 11, 12 and 13. FIG. 11 is a perspective view showing the main part of the high / low pressure bypass valve mechanism, FIG. 12 is a vertical sectional view showing the operating state of this embodiment, and FIG. 13 shows the effect of this embodiment. It is explanatory drawing which shows the relationship between the time from starting, and. In FIG. 11, 30 is a valve retainer, 31a
Is a temperature sensitive reed valve, 31b is a highly rigid material reed valve,
Reference numeral 35 denotes a side cover integrally formed with the valve retainer 30 via a side surface of the high rigidity material reed valve 31b, and 36 denotes a front surface integrally formed with the front surface of the high rigidity material reed valve 31b and a valve retainer 30 via a minute clearance. The cover 39 is a closed space composed of a recess provided on the valve-side surface of the valve retainer 30 and a high-rigidity material reed valve 31b. The temperature-sensitive reed valve 31a is housed in the closed space 39 and the valve retainer is retained. 30 and a high-rigidity material reed valve 31b are fixed. Also, before booting,
At a low temperature immediately after startup, the temperature-sensitive reed valve 31a is in contact with the bottom surface of the recess of the valve retainer 30 with the high-rigidity material reed valve 31b, and the temperature-sensitive reed valve 31a and the high-rigidity material valve 31b are in predetermined positions. It is fixed with a gap of.

Next, the operation will be described with reference to FIGS. As shown in FIG. 12A, in a low temperature state before and immediately after startup, the temperature-sensitive reed valve 31a and the high-rigidity material reed valve 31b are inside the space formed by the valve retainer 30, the side cover 35, and the front cover 36. It is in. If a large pressure pulse is generated due to liquid compression due to a full liquid start-up, etc., even if there is a slight gap between the highly rigid material reed valve 31b and the valve retainer 30 due to dimensional variation, fixing method variation, etc., inside the cover In the case of (1), the side cover 35 and the front cover 36 interfere with each other and reduce the pressure, and it is possible to prevent the valve from being closed due to the back pressure effect due to the large pressure pulse. Therefore, even if a large pressure pulse is generated due to liquid compression immediately after startup, if the high-rigidity material reed valve 31b is provided in the side cover 35 and the front cover 36, the valve will not close. After startup, as the temperature of the discharge muffler 14 rises, the temperature of the temperature-sensitive reed valve 31a in the closed space 39 also rises and deforms. As shown in FIG. 12B, as the valve temperature increases, the high-rigidity material reed valve 31b comes into contact with the high-rigidity material reed valve 31b.
1b is pressed and deformed together, and as shown in FIG. 12 (c), it comes out from the side cover 35 and the front cover 36. By going out from the side cover 35 and the front cover 36, high and low pressure differential pressures wrap around to the back surface of the combined valve 31, the combined valve 31 is closed, and the communication hole 33 is closed. Further, since the temperature-sensitive reed valve 31a is housed in the closed space 39 constituted by the valve retainer 30 and the high-rigidity material reed valve 31b, the discharge gas does not directly hit the temperature-sensitive reed valve 31a, so the discharge muffler 14 There is a time delay in the rise in valve temperature with respect to the rise in temperature. As shown in FIG. 13, when the valve closed set temperature T _sh is set, the temperature of the discharge muffler 14 becomes T _sh.
Since the time to reach t ₁ is the time t ₂ at which the temperature in the closed space 39 reaches T _sh , a time delay of t ₂ −t ₁ is possible. By adjusting the volume of the valve retainer 30 and the gap between the temperature sensitive reed valve 31a and the high-rigidity material reed valve 31b, the time to reach the valve closing set temperature T _sh can be arbitrarily adjusted.

As described above, by adjusting the volume of the valve retainer 30 and the gap between the temperature-sensitive reed valve 31a and the high-rigidity material reed valve 31b, the time required for the valve to reach the valve closing set temperature can be freely adjusted. Therefore, the high pressure and the low pressure can be surely bypassed for the required time at the time of startup.

Example 7. Example 7 will be described with reference to FIG. In this embodiment, as shown in FIG. 14, the discharge muffler 14 is not built in the closed container 13, and the high pressure and low pressure bypasses provided in the scroll compressor in which the compression element is provided in the suction pressure atmosphere portion 15. It is a mechanism. In the figure, 4
0 is a chamber fixed to the back of the fixed scroll 1, 3
1 is fixed in the chamber 40 and has a temperature sensitive valve 31a.
And a high-rigidity material valve 31b are combined in the same manner as in the first embodiment. Reference numeral 41 denotes a discharge chamber through which the discharge gas passes, reference numeral 42 denotes a chamber inner space surrounded by the chamber 40 and the back surface of the fixed scroll 1, and the suction pressure atmosphere portion 15 outside the chamber 40 is sealed by packing or the like. 43 communicates the discharge chamber 41 and the chamber inner space 42,
This is an introduction hole for introducing a part of the discharge gas passing through the chamber into the chamber internal space 42. Reference numeral 33 is a communication hole that communicates the chamber inner space 42 and the suction pressure atmosphere portion 15, and the combined valve 31 controls the opening and closing of the communication. In the scroll compressor of the present embodiment configured in this way, the chamber internal space 42 sealed with the suction pressure atmosphere portion 15 has the same atmosphere as the discharge muffler 14 shown in the first to sixth embodiments. A high / low pressure bypass mechanism similar to that of No. 6 is provided.

Next, the operation will be described. When the compressor is stopped for a long time and the refrigerant is condensed inside the compressor,
The temperature of the compressor is almost equal to the external atmosphere, and at this time, the reed valve 31 is in a state where the communication hole 33 is opened.
When the compressor is activated, the suction pressure atmosphere portion 15 is depressurized by sucking the refrigerant gas into the compression chamber 45.
Since 3 is opened to the discharge chamber 41 through the chamber inner space 42 and the introduction hole 43, the discharge gas bypasses to the suction side, and the depressurization rate (ratio of decrease in pressure with respect to elapsed time) decreases. Therefore, the degree of foaming of the mixed liquid of the refrigerant and the lubricating oil can be suppressed, and the amount of the mixed bubbles of the refrigerant and the lubricating oil flowing into the compression chamber can be suppressed. After a lapse of a certain time after the compressor is started, the temperature of the reed valve 31 in the high temperature discharge gas atmosphere of the chamber inner space 42 rises and deforms so as to close the communication hole 33. This puts the compressor in a normal operating state, but the cross-sectional area of the communication hole 33, the combined valve 31
The degree of foaming and the duration of foaming can be controlled by optimally setting the opening / closing temperature of, and the amount of lubricating oil in the compressor can be maintained at an appropriate value.

As described above, a part of the discharge gas from the discharge chamber 41 is introduced into the chamber inner space 42, and the communication hole 3 for communicating the chamber inner space 42 and the suction pressure atmosphere portion 15 with each other.
3, the communication hole 33 is opened when the compressor is started, and the valve mechanism that closes the communication hole 33 at the time of steady operation is provided. Therefore, the discharge gas temperature can be used even if the discharge muffler is not built in the closed container. Therefore, the high pressure and the low pressure can be surely bypassed at the time of start-up, etc., so that the sudden pressure drop on the suction pressure atmosphere portion 15 side is alleviated and the mixed liquid of the refrigerant and the lubricating oil retained in the compressor is absorbed. It is possible to prevent the oil dilution in the compressor by suppressing the foaming, preventing the oil from being taken out of the compressor, and mitigating the sudden liquid back from the accumulator.

Example 8. Example 8 will be described with reference to FIGS. This embodiment is a scroll compressor of the same type as that of Embodiment 7, FIG. 15 is a cross-sectional view of the essential parts of the scroll compressor, and FIG. 16 is an explanatory diagram showing the operating time for valve closing. Figure 1
5, the same reference numerals as those in FIG. 14 indicate the same or corresponding portions, and detailed description thereof will be omitted. In the figure, 40 is a chamber fixed to the back surface of the fixed scroll 1, 42 is a space inside the chamber surrounded by the chamber 40 and the back surface of the fixed scroll 1, and a high / low pressure bypass valve mechanism is arranged in the chamber internal space 42. Has been done. This valve mechanism is composed of a valve 31 in combination with a valve retainer 30. Reference numeral 31 is a valve in which a temperature sensitive reed valve 31a and a highly rigid material reed valve 31b are combined as in the first embodiment, and the valve retainer 30 is the above-mentioned one. It is formed integrally with the chamber 40. Therefore, the valve 31 combined with the bolt 40 for fixing the chamber 40 to the fixed scroll 1 is also fixed together with the chamber 40. At this time, the combined valve 31 and valve retainer 30
Are fixed so that they come into close contact with each other.

Next, the operation will be described. The combined valve 31 is in close contact with the valve retainer 30 (chamber 40) at a low temperature immediately before startup and immediately after startup, and is in close contact with the valve retainer 30 (chamber 40) until the valve temperature reaches the valve closing set temperature.
When the temperature approaches the normal operating state and reaches a temperature equal to or higher than the set temperature, a gap is created between the combined valve 31 and the valve retainer 30, and the high and low pressure differential pressure wraps around there to close the combined valve 31. FIG. 16 shows the temperature of the chamber inner space 42 and the combined valve 31.
3 shows the changes in the temperature of 1 and the temperature of the chamber 40, that is, the temperature of the valve retainer 30 from the start. Since the chamber 40 is exposed to the suction pressure atmosphere portion 15, a time delay occurs until the valve closing set temperature is reached, as compared with the temperature increase in the chamber internal space 42. Combined valve 31
Is in contact with the valve retainer 30, that is, the chamber 40, the temperature of the combined valve 31 follows the temperature of the chamber 40, and the temperature rise of the combined valve also has a time delay with respect to the temperature of the chamber internal space 42. Occurs. Therefore, the time required for the temperature of the combined valve 31 to reach the valve closing set temperature is delayed from the temperature of the chamber internal space 42. The temperature of the chamber 40 is greatly affected by the heat mass of the chamber 40, and the time for the temperature of the combined valve 31 to reach the valve closing set temperature can be arbitrarily adjusted by changing the heat mass of the chamber 40.

As described above, even if the discharge muffler is not built in the closed container, the discharge gas temperature can be used, and the heat mass of the chamber can be adjusted to freely set the time for the valve to reach the valve closing set temperature. Since it can be adjusted, the high pressure and the low pressure can be surely bypassed for the required time at the time of startup. Although the valve retainer 30 is integrally formed with the chamber 40 in this embodiment, the valve retainer 3
0 may be attached to the chamber 40 in a state of good heat conduction.

Example 9. The valve retainer 30 integrally formed with the chamber 40 shown in FIG. 15 of the eighth embodiment is provided with the side cover 35 and the front cover 36 of FIG. Even if there is a gap between the valve 31 and the valve retainer 30 that are combined due to variations in dimensions and variations in the fixing method, the combined valve 31
If is inside the side cover 35 and the front cover 36, the large pressure pulse due to the liquid compression interferes with and is depressurized by the side cover 35 and the front cover 36, so that the valve 31 rises to the set valve closing temperature and is deformed. It does not close until it comes out of the side cover 35 and the front cover 36, and even if the discharge muffler is not built in the closed container, the discharge gas temperature can be used and the heat mass of the chamber can be adjusted.
Since the valve can freely adjust the time to reach the valve closing set temperature, the high pressure and the low pressure can be surely bypassed for the required time at the time of startup.

Example 10. The valve presser 30 integrally formed with the chamber 40 shown in FIG. 15 of the eighth embodiment has a radius of curvature larger than that of the valve 31 combined as shown in FIG. 7 of the third embodiment, and the combined valve 31. If it is deformed so that it fits in the valve retainer 30 with the preload applied and fixed, the combined valve 31 and the valve retainer 30 will have a variation in the size of the combined valve 31 and the retainer 30 and a variation in the fixing method. Firmly adheres to each other, and the dynamic pressure does not wrap around the back surface of the combined valve 31. Therefore, even if a large pressure pulse due to liquid compression occurs, the combined valve 31 does not close until the set valve closing temperature rises. Even if the discharge muffler is not built in the closed container, the discharge gas temperature can be used, and by adjusting the heat mass of the chamber, the time for the valve to reach the valve closed set temperature can be freely adjusted. Since, it is possible to bypass time, only the high and low pressure ensures time required activation.

Example 11. If the valve retainer 30 integrally formed with the chamber 40 shown in FIG. 15 of the eighth embodiment is formed into a tapered shape as shown in FIG.
The loss of the fluid flowing from the periphery into the communication hole 33 due to bending is reduced, so that the dynamic pressure generated in the vicinity of the smoothed and combined valve 31 and the valve retainer 30 is relieved. Therefore, the combined valve 31 and the valve retainer 30 have different sizes and different fixing methods.
Even if a gap is generated between the valve retainer 30 and the valve retainer 30, the dynamic pressure of the pressure pulse due to liquid compression is reduced. Therefore, even if a large pressure pulse occurs, the combined valve 31 is closed until the set valve closing temperature is reached. In addition, the discharge gas temperature can be used even if the discharge muffler is not built in the closed container, and the time for the valve to reach the valve closed set temperature can be freely adjusted by adjusting the heat mass of the chamber. Therefore, the high pressure and the low pressure can be surely bypassed for the required time at the time of startup.

Example 12. The valve retainer 30 integrally formed with the chamber 40 shown in FIG. 15 of the eighth embodiment is fixed with the oil-impregnated elastic body 38 as shown in FIG. 10 of the fifth embodiment, and the combined valve is used before starting the compressor. If the 31 and the oil-immersed elastic body 38 are brought into close contact with each other, the combined valve 31 can be surely brought into close contact with the oil-immersed elastic body even if there are variations in the dimensions of the valve 31 and the valve retainer 30 and variations in the fixing method. Combined valve 31
Since the dynamic pressure does not wrap around to the back of the, even if a large pressure pulse due to liquid compression occurs, the combined valve 31 does not close until the set valve closing temperature, and the discharge muffler is not built in the closed container. However, the discharge gas temperature can be used,
By adjusting the heat mass of the chamber, the valve
Since the time to reach the valve closing set temperature can be freely adjusted, the high pressure and the low pressure can be surely bypassed for the required time at the time of startup.

Example 13 If the valve 31 combined with the valve retainer 30 for bypassing the high and low pressure shown in the eighth embodiment is configured as shown in FIG. 11 of the sixth embodiment, variations in the dimensions of the valve 31 and the valve retainer 30 combined and fixed. Even if a gap occurs between the combined valve 31 and the valve retainer 30 due to the variation in the method, if the combined valve 31 is inside the cover, the large pressure pulse due to liquid compression interferes and is reduced in pressure by the cover. The combined valve 31 does not close until the set valve closing temperature rises and the combined valve 31 is deformed and comes out of the cover. Furthermore, by adjusting the valve holding volume and the heat mass of the chamber 40, it is possible to freely adjust the time for the combined valve 31 to reach the valve closing set temperature.
Even if the discharge muffler is not built in the closed container, the discharge gas temperature can be used, and by adjusting the heat mass of the chamber, the valve can freely adjust the time to reach the valve closing set temperature, At startup, the high and low pressure can be reliably bypassed for the required time.

[0048]

The scroll compressor according to the present invention is
A communication hole provided in the fixed scroll part that communicates the suction pressure atmosphere part with the high pressure part, a valve retainer arranged in the high pressure part so as to cover this communication hole, and a valve retainer when opening the communication hole. However, when closing the communication hole, a temperature sensitive valve and a valve combining a high-rigidity material valve are provided in the vicinity of the communication hole that is in close contact with the communication hole of the fixed scroll and closes the communication hole.
At room temperature, such as before startup, or at low temperature immediately after startup, even if a valve comes into close contact with the valve retainer and a large pressure pulse is generated, the dynamic pressure due to that pulse does not act as the back pressure of the valve, so the valve does not close. Along with the high temperature during normal operation, the temperature-sensitive valve is deformed by the temperature of the refrigerant gas in the high pressure section, and is separated from the valve retainer in close contact with the high rigidity material valve, and the communication hole is closed by the differential pressure. The high-pressure part and low-pressure suction pressure atmosphere part can be bypassed for the required time, and the sudden pressure drop on the suction pressure atmosphere part side at the time of start-up can be alleviated, and the mixture liquid of refrigerant and lubricating oil that has accumulated in the compressor It is possible to prevent the oil from being diluted inside the compressor by suppressing the foaming and preventing the oil from being taken out to the outside of the compressor and mitigating the sudden liquid back from the accumulator. Furthermore, since the high-rigidity material valve is combined with the temperature-sensitive valve, the valve can be prevented from being damaged due to the impact when the valve is closed, and a highly reliable scroll compressor can be obtained.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of essential parts of a scroll compressor showing an embodiment of the present invention.

FIG. 2 is a cross-sectional view of essential parts showing an operating state of a high / low pressure bypass valve of a scroll compressor according to an embodiment of the present invention.

FIG. 3 is an explanatory diagram showing a relationship between a discharge muffler temperature of a scroll compressor and a difference between a discharge pressure and a suction pressure.

FIG. 4 is a perspective view showing a high / low pressure bypass valve of a scroll compressor according to another embodiment of the present invention.

FIG. 5 is a cross-sectional view of essential parts showing an operating state of a high / low pressure bypass valve of a scroll compressor according to another embodiment of the present invention.

FIG. 6 is an explanatory diagram showing a state of a large pressure pulse during liquid compression of the scroll compressor.

FIG. 7 is a cross-sectional view of essential parts showing a high-low pressure bypass valve of a scroll compressor according to another embodiment of the present invention.

FIG. 8 is a perspective view of a main part of a scroll compressor showing another embodiment of the present invention.

FIG. 9 is an explanatory diagram showing the effect of the scroll compressor according to another embodiment of the present invention.

FIG. 10 is a perspective view of a main part of a scroll compressor showing another embodiment of the present invention.

FIG. 11 is a perspective view of a main part of a high / low pressure bypass valve of a scroll compressor according to another embodiment of the present invention.

FIG. 12 is an explanatory diagram showing an effect of a scroll compressor showing another embodiment of the present invention.

FIG. 13 is a cross-sectional view of essential parts showing an operating state of a high / low pressure bypass valve of a scroll compressor according to another embodiment of the present invention.

FIG. 14 is a cross-sectional view of essential parts of a scroll compressor showing another embodiment of the present invention.

FIG. 15 is a cross-sectional view of essential parts of a scroll compressor showing another embodiment of the present invention.

FIG. 16 is an explanatory view showing the effect of the scroll compressor showing another embodiment of the present invention.

FIG. 17 is a cross-sectional view of a conventional scroll compressor.

FIG. 18 is a cross-sectional view of a conventional scroll compressor.

[Explanation of symbols]

 1 Scroll compressor 2 Oscillating scroll 14 Discharge muffler 15 Suction pressure atmosphere part 30 Valve retainer 31 Combined valve 31a Temperature sensitive valve 31b High rigidity material valve 33 Communication hole

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁵ Identification number Reference number within the agency FI Technical indication location F04C 29/10 321 A 6907-3H (72) Inventor Hiroshi Ogawa 2-2 Marunouchi, Chiyoda-ku, Tokyo No. 3 Sanryo Electric Co., Ltd.

Claims (8)

[Claims] 1. A compression element comprising a fixed scroll portion and an orbiting scroll portion driven by a drive element, which is disposed in a closed container, and a side of the compression element opposite to the orbiting scroll portion side of the fixed scroll portion. And a high pressure portion for discharging high pressure refrigerant gas compressed by the compression element, a suction pressure atmosphere portion provided inside the closed container and partitioned from the high pressure portion, the suction pressure atmosphere portion and the high pressure portion. A communication hole provided in the fixed scroll part that communicates the parts,
A valve retainer arranged in the high-pressure portion so as to cover the communication hole, and close to the valve retainer when the communication hole is opened, and close to the communication hole of the fixed scroll when the communication hole is closed. A scroll compressor, comprising: a temperature sensitive valve disposed in the vicinity of the communication hole to close the communication hole; and a valve formed by combining a highly rigid material valve. 2. A chamber in which the high-pressure portion is disposed in the vicinity of the discharge portion of the fixed scroll, and a portion of the high-pressure refrigerant gas is introduced from the high-pressure portion to a side of the fixed scroll portion opposite to the orbiting scroll portion side. 2. The scroll compressor according to claim 1, wherein a high pressure refrigerant gas inside the chamber is communicated with the suction pressure atmosphere portion through the communication hole. 3. The scroll compressor according to claim 2, wherein the valve retainer is provided in the chamber. 4. The scroll compressor according to claim 1, wherein a cover for covering a side surface of the valve when the valve comes into close contact with the valve retainer is provided in the valve retainer. 5. The scroll compressor according to claim 1, wherein a radius of curvature of a surface of the valve on the valve retainer side is smaller than a radius of curvature of a surface of the valve retainer on the valve side. 6. The surface of the valve retainer that is in close contact with the valve is equal to or slightly larger than the width of the valve, and the width of the surface on the side opposite to the surface in close contact with the valve is The scroll compressor according to claim 1, wherein the scroll is made larger than the width and the valve retainer is tapered. 7. An oil-immersive elastic body is fixed to one of a surface of the valve retainer that is in close contact with the valve and a surface of the valve that is in close contact with the valve retainer. Scroll compressor. 8. A recess for accommodating a temperature-sensitive valve is provided on a surface of the valve retainer that is in close contact with the combined valve, and the recess bottom surface is provided when the communication hole is opened by the combined valve. The temperature-sensitive valve is in close contact with the temperature-sensitive valve, and the high-rigidity material valve is in close contact with the temperature-sensitive valve with a predetermined gap on the convex portion of the surface of the valve retainer that is in close contact with the combined valve. The scroll compressor according to claim 1, wherein: