JP4449909B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor used for refrigeration air conditioning and the like.

Conventional scroll compressors for refrigeration and air conditioning are described in Japanese Patent Laid-Open Nos. 8-21068 and 8-284852, and such scroll compressors are shown in FIGS. 14 and 15, for example.
In FIG. 14, inside the shell 8, a scroll type compression mechanism C is disposed at the upper part, and an electric motor M is disposed at the lower part. The scroll-type compression mechanism C includes a fixed scroll 1, an orbiting scroll 2, an Oldham ring 3 that is a member for preventing rotation of the orbiting scroll 2, a crankshaft 5 that transmits the driving force of the electric motor M, and a tip portion of the crankshaft 5. The slider 25, which is engaged with the crank pin 53, and serves as a driven crank mechanism for enabling the orbiting scroll 2 to move in the radial direction, the frame 6 to which the fixed scroll 1 and the electric motor M are fastened, and the crankshaft 5 are provided. It comprises an upper bearing 71 and a lower bearing 72 that support it, a rocking bearing 73 that supports the rocking scroll 2, a thrust bearing 74, and the like.

The fixed scroll 1 includes an end plate 11 and a spiral wrap 12 erected on the inner surface thereof. The end plate 11 is provided with a discharge port 13 and a discharge valve mechanism for opening and closing the discharge port 13.
The discharge valve mechanism is opposed to the valve seat surface 13a provided with the discharge port 13, the valve guide surface 118a formed on the valve seat surface 13a as a cylinder surface, the upper portion of the valve guide surface 118a, that is, the valve seat surface 113a. A plurality of discharge passages 118c that open to the valve pressing surface 118b, the valve guide surface 118a and communicate with the discharge space, a valve drop hole 118d provided in the center of the valve pressing surface 118b, a valve seat surface 113a, and a valve pressing surface 118b. The disc-shaped valve element 117 is provided so as to be freely inserted without being constrained by a spring or the like, and to freely open and close the discharge port 13.

The orbiting scroll 2 includes an end plate 21 and a spiral wrap 22 standing on the inner surface thereof, and a slider 25 is interposed in a boss portion 23 standing on the outer surface of the end plate 21 via an orbiting bearing 73. The slider 25 is rotatably fitted, and a key-shaped crank pin 53 protruding from the upper end of the crankshaft 5 is fitted in a key groove provided on the inner surface, and is slidably engaged in the centrifugal direction. Yes.
By driving the electric motor M, the orbiting scroll 2 is driven via the crankshaft 5, the crankpin 53, the slider 25, and the boss portion 23, and the orbiting scroll 2 is rotated by an Oldham ring 3 that is an anti-rotation mechanism. Revolves on a circular orbit of revolution radius while being blocked.
Then, the refrigerant gas enters the shell 8 through the suction pipe 82, cools the electric motor M, passes through the passage 85 formed in the frame 6, and enters the suction chamber 16 from the suction passage 15 provided in the fixed scroll 1. Then, it is inhaled into the innermost chamber 24.
The refrigerant gas reaches the center while being compressed as the volume of the innermost chamber 24 decreases due to the revolving motion of the orbiting scroll 2, pushes the valve body 117 open from the discharge port 13, and the valve body 117. Is pressed against the valve pressing surface 118 b, enters the discharge space 14 through a plurality of discharge passages 118 c communicating with the valve chamber 118, and is further discharged to the outside through the discharge pipe 83.

In the case of a scroll compressor, the built-in compression ratio νth determined by the spiral geometry (ie, Vst: stroke volume, V *: compression chamber volume immediately before communication, n: polytropic index, νth = (Vst / V *) ⁿ ), and if the operating pressure ratio ν (= discharge pressure / suction pressure) is smaller than the built-in compression ratio νth, it is communicated with the discharge port 13 in an over-compressed state in the compression chamber, and the operating pressure ratio ν Is larger than the built-in compression ratio νth, it communicates with the discharge port 13 in an over / under compression state.
In the over-compressed state (νth> ν), the pressure in the compression chamber immediately before the vortex communicates is greater than the discharge pressure, so that no back flow of the refrigerant occurs even if the vortex communicates. The valve body 117 flows toward the discharge space 14 through the discharge passage 118c communicating with the chamber 118, and the valve body 117 remains pressed against the valve pressing surface 118b and does not sit on the valve seat surface 13a.
Further, in the over / under compression state (νth <ν), since the pressure in the compression chamber immediately before the vortex communicates is smaller than the discharge pressure, when the vortex communicates, the refrigerant is discharged from the discharge space 14 to the discharge passage 118c and the valve. It flows toward the discharge port 13 through the hole 118d. That is, the refrigerant flows backward. The back-flowing refrigerant directed to the discharge port 13 through the valve drop hole 118d collides with the valve body 117 and gives a force to move the valve body 117 in the direction of the valve seat surface 13a. When this action is large, the valve body 117 collides with the valve seat surface 13a.

Depending on the area of the discharge passage 118c and the valve drop hole 118d, even in an over / undercompressed state (νth <ν), when the operating pressure ratio ν is relatively small, the spring force as in a discharge valve mechanism using a reed valve or the like. Therefore, even if the valve body 117 is separated from the valve pressing surface 118b, the valve body 117 is not seated. In an over and under compression state where the operating pressure ratio is about 7 to 8 or more, the amount of backflow refrigerant passing through the valve drop hole 118d is large, and the action of moving the valve body 117 in the direction of the valve seat surface 13a is large. Sit on the surface 13a. Even when the compressor is stopped, the refrigerant on the high-pressure side moves to the low-pressure side, so that a reverse flow of the refrigerant occurs and the valve body 117 is seated on the valve seat surface 13a.
Further, in the discharge valve mechanism, as in the compressor using the reed valve in the discharge valve mechanism, the above-described refrigerant backflow occurs during the over / under compression operation, but the discharge valve is in a closed state compared to the reed valve. Therefore, a single chamber of only the compression chamber is not formed, pulsation as a noise generation factor does not occur in the compression chamber, and a pressure wave propagates to the discharge port 13 and the entire discharge space 14, that is, a wide space, As a result, pulsation is reduced. Further, since the valve body 117 itself does not collide with the valve seat surface 13a, the impact sound is small, and such a free valve type discharge valve mechanism has been used as a low noise discharge valve mechanism.

Japanese Patent Laid-Open No. 8-21068

Such a conventional scroll compressor has the following problems to be solved.
That is, in a scroll compressor having a conventional discharge valve mechanism, the valve lift is usually larger than that of the reed valve, and the spring force does not act on the valve. A closing delay occurs. Then, the orbiting scroll revolves in the direction opposite to that during operation, and the orbiting scroll continues to reverse due to the inertia of the rotating system for a short time even when the valve is closed.

For this reason, the pressure in the outermost chamber of the compression chamber is lower than the suction pressure, and the gas force in the centrifugal direction is acting in the centrifugal force direction during operation. Acting in the direction of the rotation center, the centrifugal force acting on the orbiting scroll 2 is overcome, and the orbiting scroll 2 is slid in the direction of the rotation center. This relationship is shown in FIG. 15. At this time, the slider 25 is accelerated by the gas force, and the inner surface of the slider 25 and the crank pin 53 collide with each other at a very high speed to generate a relatively loud metal sound. At this time, a gap is formed in the centrifugal direction of the spiral wrap of the orbiting scroll 2 and the fixed scroll 1, so that the refrigerant gas flows backward from the center side of the spiral, that is, from the high pressure side to the end of the spiral, that is, the low pressure side. The gas force in the centrifugal direction decreases, and the swinging scroll is again pressed against the side surface of the spiral wrap of the fixed scroll by the centrifugal force. Also at this time, since the slider 25 and the orbiting scroll 2 are accelerated, the collision speed is high and a relatively loud metal sound is generated again. This phenomenon occurs several times and the reverse rotation of the orbiting scroll stops. Since this metal sound is considerably louder than the compressor operation sound, it is highly likely that the user will accept it as an abnormal sound.

In addition, in the above-described free valve type discharge valve mechanism, there is no member that directly supports the valve, and since no spring force acts on the valve, the posture of the valve seated on the valve seat surface becomes unstable. In many cases, the valve tilts and collides with the valve seat surface, and the valve slides against the valve guide surface. This has been a cause of wear of the valve seat and valve guide and cracking of the valve.
Further, in the above-described free valve type discharge valve mechanism, the diameter of the valve drop hole is made relatively small with respect to the diameter of the discharge port so that the discharge valve is not seated as much as possible during excessive or insufficient compression within the compressor operating pressure range. Then, an abnormal noise due to the valve closing delay at the time of the stop is generated, and in order to prevent this abnormal noise, the diameter of the valve drop hole is set to the diameter of the discharge port so that the valve is quickly closed when the compressor is stopped. When trying to make it relatively large, this time, there was a dilemma that the noise during compressor operation during excessive and insufficient compression increased.
Then, an object of this invention is to provide the scroll compressor which can solve the said subject.

  A scroll compressor according to a first invention includes a valve seat surface provided with a discharge port communicating with an innermost chamber formed by a fixed scroll having a spiral wrap and an orbiting scroll having a spiral wrap, and the valve In a scroll compressor comprising: a valve chamber configured to partially include a seat surface; and a valve body that is loosely inserted into the valve chamber and can be seated on the valve seat surface to open and close the discharge port. Even when the inclination of the valve element becomes maximum in the valve chamber, the edge part of the valve element is provided around the discharge port so that the edge part of the valve element does not contact the valve seat surface and the vicinity thereof. It is characterized by forming a groove to escape.

  ADVANTAGE OF THE INVENTION According to this invention, the highly reliable compressor which does not generate | occur | produce abrasion of a valve seat surface and the other wall surface which comprises a valve chamber, and the generation | occurrence | production of a valve body crack can be provided.

Embodiment 1 of the Invention
1-4 is a figure which shows Embodiment 1 of the scroll compressor based on this invention, The same code | symbol is attached | subjected to the structure similar to the conventional scroll compressor shown in FIG. Omitted. The cross section of the discharge valve mechanism shown in FIG. 1 is the AA cross section of FIG.
1 and 2, the scroll compressor includes a valve member 18 having various surfaces and the like. Specifically, the valve pressing surface 18b facing the valve seat surface 13a, the valve seat surface 13a, and the valve pressing member are provided. A valve guide surface 18a that forms a side surface of the valve chamber 18e between the surfaces 18b, a valve chamber 18e composed of the valve seat surface 13a, the valve guide surface 18a, and the valve pressing surface 18b, and loosely inserted into the valve chamber 18e A disc-shaped valve body 17 that can be seated on the valve seat surface 13a and opens and closes the discharge port 13, and a plurality of discharge passages 18c that guide the compressed refrigerant from the discharge port to the discharge space 14 through the valve chamber, And a valve drop hole 18d provided at the center of the valve pressing surface 18b.

The valve body 17 is freely inserted into the valve chamber 18e as described above, that is, without being urged by a spring or the like, or supported by any member, and guided inside the valve chamber 18e by the valve guide surface 18a. It can be moved.
The slider 25 engages with the orbiting scroll 2, and the crankshaft 5 has a crank pin 25 serving as a crank portion that engages with the slider 25, and drives the orbiting scroll 2 through the slider 25. The slide amount that the slider 25 can move backward in the direction in which the centrifugal gap between the spiral wrap 22 of the orbiting scroll 2 and the spiral wrap 12 of the fixed scroll 1 increases is set to 0.5 mm or less.
That is, as shown in FIG. 3, the center position of the slider 25 in a state where the side surface of the spiral wrap 22 of the orbiting scroll 2 hits the side surface of the spiral wrap 12 of the fixed scroll 1, and the slider 25 on the center side of the crankshaft 5. The linear distance from the center position of the slider 25 in a state where it is slid to the crankpin 53 is defined as a slider retraction amount. The slider retraction amount is set to 0.5 mm or less.

Next, the effect of the above configuration will be described. Since the basic operation of the scroll compressor itself is substantially the same as that of the conventional scroll compressor shown in FIG. 14, the description thereof will be omitted, and the following will focus on the features of the present invention. explain.
Similar to the conventional compressor, in the discharge valve mechanism of the present invention, the valve lift determined by the distance between the valve seat surface 13a and the valve pressing surface 18b is usually larger than that of the reed valve. Since the spring force does not act, the noise is extremely low during the compressor operation, but immediately after the compressor stops, the valve body 17 is delayed and the orbiting scroll 2 revolves in the opposite direction to that during operation. Although the valve is closed, the swing scroll 2 continues to reverse due to the inertia of the rotating system. With the valve body 17 closed, the orbiting scroll 2 rotates reversely to become an expander.

  For this reason, the pressure in the outermost chamber of the compression chamber is lower than the suction pressure, and the gas force in the centrifugal direction is acting in the centrifugal force direction during operation. Acting in the direction of the rotation center, the centrifugal force acting on the orbiting scroll 2 is overcome, and the orbiting scroll 2 is slid in the direction of the rotation center. However, since the slider retraction amount is set to 0.5 mm or less, the distance to which the slider 25 is accelerated is very small, and the collision speed when the inner surface of the slider 25 collides with the crankpin 53 is reduced, and the compression is performed. The sound is almost unrecognizable from the outside.

At this time, since a slight gap is formed in the centrifugal direction of the spiral wrap of the orbiting scroll 2 and the fixed scroll 1, the refrigerant gas flows backward from the center side of the spiral, that is, from the high pressure side to the end of the spiral, that is, the low pressure side. The gas force in the centrifugal direction is reduced, and the orbiting scroll 2 is again pressed against the spiral wrap side surface of the fixed scroll 1 by the centrifugal force. Also at this time, since the slider retraction amount is set to 0.5 mm or less, the distance by which the orbiting scroll 2 is accelerated is short and the collision speed is small, so the collision sound is still at a level that cannot be recognized outside the compressor. .
Further, since the kinetic energy at the time of the collision of the slider 25 with the crankpin 53 is proportional to the slider retraction amount, the reverse noise when the compressor is stopped is also proportional to the slider retraction amount, and the slider retraction amount is 0.5 mm or less. Of course, it is better that the slider retract amount is small. However, since the slider retraction amount includes an accumulation tolerance of machining tolerances of many parts such as the crank pin 53, the slider 25, the swinging scroll 2, the fixed scroll 1, the frame 6, and the like, there is a limit to setting it small.

Therefore, an experiment was conducted to measure the maximum amplitude at the time of stopping (that is, the impact at the time of collision of the slider 25 with the crank pin 53) for the compressor having the discharge valve mechanism as a parameter. The range of the slider retraction amount that was smaller than the compressor equipped with the valve was determined.
As a result, as shown in FIG. 4, it was found that the slider retraction amount is 0.5 mm or less and is smaller than the amplitude when the compressor provided with the reed valve is stopped. In other words, it has been found that the abnormal noise when the compressor is stopped can be reduced to a level that cannot be recognized in terms of hearing.
Therefore, an abnormal noise is not generated when the compressor is stopped, and an extremely low noise compressor can be provided during operation and when the compressor is stopped.

In the first embodiment, the mechanism for preventing abnormal noise during reverse rotation is applied to the free valve type discharge valve mechanism. However, even if the discharge valve mechanism is the valve rotation support type discharge valve mechanism shown in FIG. it can.
In FIG. 5, the discharge valve mechanism 40 supports the valve body by a rotation support mechanism without applying a spring force to the valve body as in the case of the discharge valve mechanism of FIGS. 1 and 2, and opens and closes according to the gas flow. It tries to reduce the noise during driving.
The valve body 41 of the discharge valve mechanism 40 is rotatably fixed via a pin portion 42 that is integrated with the valve body 41. The pin portion 42 is provided in the hinge groove 43 in the support 44. The valve element 41 takes an open position indicated by a solid line in FIG. 5 and a closed position indicated by a broken line, and has a movement range of 90 ° to 120 ° as shown in FIG. It is set to be in a stable state. The other configuration is the same as that of the compressor shown in FIG.

  When the compressor is activated, the refrigerant gas reaches the center while being compressed as the volume of the innermost chamber 24 decreases due to the revolving motion of the orbiting scroll 2, and the valve body 41 is indicated by a dotted line from the discharge port 13. The valve element 41 is locked to the valve pressing surface 45 by lifting from the closed position to the open position indicated by the solid line. Since the refrigerant gas discharged from the discharge port 13 does not directly collide with the valve body 41, the valve body 41 has little fluttering and noise during operation can be reduced to some extent. When the compressor is stopped, the high-pressure refrigerant gas flows backward through the discharge pipe 83, and the refrigerant gas that has flowed back through the discharge pipe 83 collides with the valve body 41 in the open position, thereby closing the valve body 41. The closed position prevents reverse rotation of the orbiting scroll.

Further, FIG. 1 shows a case where the rocking bearing 73 is a female type, that is, a case where the crank portion of the crankshaft is a male type. However, as shown in FIG. It can be applied even when the crank part of the crankshaft is a female type.
Furthermore, FIG. 1 shows the angle formed by the sliding direction of the slider 25 with respect to the centrifugal force direction, that is, the case where the slider angle is 0 °, but the case where the slider angle is other than 0 ° as shown in FIG. But it can be applied.

Embodiment 2 of the Invention
FIG. 8 is a diagram showing a second embodiment of the scroll compressor according to the present invention.
In FIG. 8, reference numeral 25 denotes a slider, and 53 denotes a crank pin that forms a crank portion. An elastic member 25 a such as a resin is attached to the surface of the slider 25 in the two gaps in the centrifugal direction between the slider 25 and the crank pin 53. A crank mechanism is configured. However, the elastic force of the elastic member 25a attached to the rotation center side is set smaller than the resultant force of the centrifugal force of the orbiting scroll 2 and the centrifugal gas force acting on the orbiting scroll 2 when gas is compressed. That is, the elastic force of the elastic member 25a is set so that the spiral wrap 22 of the orbiting scroll and the spiral wrap 12 of the fixed scroll are not separated from each other. Other configurations are the same as those of the first embodiment, and the description thereof is omitted.

Next, the effect of the above configuration will be described.
As in the first embodiment, when the compressor is stopped, the inner surface of the slider 25 collides with the crankpin 53 by the same action, but the elastic member is attached to the gap far from the rotation center of the slider 25. Since 25a acts as a buffer material, the impact at the time of collision can be reduced. For this reason, the collision sound becomes a sound of a level that is hardly recognizable from the outside of the compressor. Further, again, when the swinging scroll is pressed against the spiral wrap side surface of the fixed scroll by centrifugal force, the collision sound is reduced by the elastic member 25a on the rotation center side, and becomes a level that cannot be recognized outside the compressor.
Therefore, an abnormal noise is not generated when the compressor is stopped, and an extremely low noise compressor can be provided during operation and when the compressor is stopped.

Further, the noise prevention mechanism during reverse rotation of the present embodiment is applied not only to the free valve type discharge valve mechanism but also to the valve rotation support type discharge valve mechanism shown in FIG. can do.
Further, FIG. 8 shows a case where the rocking bearing 73 is a female type, that is, a case where the crank portion of the crankshaft is a male type. However, as shown in FIG. It can be applied even when the crank part of the crankshaft is a female type.
Further, FIG. 8 shows the angle formed by the slider sliding direction with respect to the centrifugal force direction, that is, the slider angle is 0 °, but the present invention is applicable even when the slider angle is other than 0 ° as shown in FIG. it can.
Furthermore, the elastic member may be interposed between the crank portion of the crankshaft 5 and the slider 25 at at least one position on both ends of the slider 25 in the sliding direction. That is, in addition to the example shown in FIG. 8, the elastic member 25a may be attached to the crankpin side, or may be simply inserted loosely between the slider and the crankpin. In some cases, the elastic member may be provided only on one side without providing both ends of the slider.

Embodiment 3 of the Invention
FIG. 9 is a diagram showing a third embodiment of the scroll compressor according to the present invention.
In FIG. 9, reference numeral 25 denotes a slider, and 53 denotes a crank pin that forms a crank portion. Of the two gaps in the centrifugal direction between the slider 25 and the crank pin 53, the centrifugal force is always applied to the slider in the gap far from the rotation center. A leaf spring 25b is attached so that a spring force acts in the direction to constitute a driven crank mechanism. Further, the spring force of the leaf spring 25b is set to be larger than the centrifugal gas force for moving the slider acting at the time of reverse rotation described above. Other configurations are the same as those of the first embodiment, and the description thereof is omitted.

Next, the effect of the above configuration will be described.
As in the first embodiment, when the compressor is stopped, a gas force acts in the direction in which the slider 25 surface collides with the crankpin 53 by the same action, but the spring force of the leaf spring 25b attached to the slider 25 is Since the gas force is greater than this, the slider 25 does not collide with the crankpin 53.
Therefore, an abnormal noise is not generated when the compressor is stopped, and an extremely low noise compressor can be provided during operation and when the compressor is stopped.

Further, the noise prevention mechanism during reverse rotation of the present embodiment is applied not only to the free valve type discharge valve mechanism but also to the valve rotation support type discharge valve mechanism shown in FIG. can do.
Further, FIG. 9 shows a case where the rocking bearing 73 is a female type, that is, a case where the crank portion of the crankshaft is a male type. However, as shown in FIG. It can be applied even when the crank part of the crankshaft is a female type.
Further, FIG. 9 shows the angle formed by the sliding direction of the slider with respect to the centrifugal force direction, that is, the case where the slider angle is 0 °. However, the present invention can be applied even when the slider angle is not 0 ° as shown in FIG. it can.
The spring 25b described above may be a spring member having another shape, and for example, a coil spring may be used.

Embodiment 4 of the Invention
FIG. 10 is a diagram showing a fourth embodiment of the scroll compressor according to the present invention.
In FIG. 10, 13b is a relief groove formed on the valve seat surface 13a, whose inner diameter is slightly smaller than the diameter of the valve body 17 and whose outer diameter is slightly larger than the diameter of the valve guide surface 18a. Even when the inclination of the valve body 17 is maximized between the valve lifts of the valve body 17 determined by the distance between the valve seat surface 13a and the valve pressing surface 18b, the edge portion 17a of the valve body 17 remains in the relief groove 13b. The inner diameter of the relief groove 13b is configured in a dimensional relationship that does not hit the edge portion on the inner diameter side. Other configurations are the same as those of the first embodiment, and the description thereof is omitted.

Next, the effect of the above configuration will be described.
FIG. 10 shows a state where the valve body 17 is inclined and seated on the valve seat surface 13a. Conventionally, when such a seating is performed, the edge portion 17a of the valve body 17 hits the valve seat surface 13a. Therefore, the impact force when the valve body 17 is seated concentrates on that portion of the valve seat surface 13a. It was causing wear. As this progresses, the outer peripheral side of the valve seat surface 13a wears, the inner diameter of the relief groove 13b decreases, and the overhang of the valve body 17 with respect to the valve seat surface 13a (the length that the valve body 17 protrudes from the inner diameter of the escape groove 13b) increases. As a result, the valve element 17 was cracked.
However, as in the fourth embodiment, even when the inclination of the valve body 17 is maximized, that is, even when the edge portion 17a of the valve body 17 collides with the innermost diameter side of the valve seat surface 13a, Since the edge portion 17a of the valve body 17 constitutes the inner diameter of the escape groove 13b in such a dimensional relationship that the edge portion 17a of the valve body 17 does not hit the edge portion on the inner diameter side of the escape groove 13b, the edge portion 17a of the valve body 17 is formed of the valve seat surface 13a. The valve seat surface 13a is not worn.
Therefore, it is possible to provide a highly reliable compressor that does not cause wear of the valve seat surface 13a and cracking of the valve body 17.

  Further, such a dimensional relationship may be applied to the relief groove 18f on the valve pressing surface 18b side as shown in FIG. That is, a relief groove is provided on the outer peripheral side of the valve pressing surface 18b, and the inner diameter of the relief groove 18f of the valve pressing surface can be determined so that the edge portion of the valve does not hit the valve pressing surface even when the inclination of the valve body 17 becomes maximum. It ’s fine.

Embodiment 5 of the Invention
FIG. 11 is a diagram showing a fifth embodiment of the scroll compressor according to the present invention.
In FIG. 11, the scroll compressor includes a valve seat plate 19 provided with a valve seat surface 19a that forms a periphery of a discharge port 13 communicating with an innermost chamber formed by a fixed scroll 1 and an orbiting scroll 2, and a valve And a valve guide member 18 that forms the chamber 18e in cooperation with the valve seat surface 19a. The valve seat plate 19 and the valve guide member 18 are subjected to a hardening process such as a quenching process, and the hardness is set larger than the raw materials of the respective parts. In other words, the entire wall surface constituting the valve chamber 18e is subjected to a hardening process that increases the hardness compared to the raw material. Other configurations are the same as those of the first embodiment, and the description thereof is omitted.

Next, the effect of the above configuration will be described.
FIG. 11 shows a state in which the valve body 17 is sliding while being in contact with the valve guide surface 18a. In this way, when the valve body 17 slides on one side, the valve guide surface 18a is locally worn near the valve pressing surface 18b where the valve body 17 slides quickly and near the valve seat surface 19a. . As this progressed, local wear further deepened, and the valve element 17 was caught by the worn portion, hindering operation and causing valve cracking.

Further, as described in the fourth embodiment, when the valve body 17 is inclined and seated on the valve seat surface 19a, the outer peripheral side of the valve seat surface 19a is worn, and in the worst case, the overhang of the discharge valve with respect to the valve seat surface 19a is caused. Enlarging and causing cracking of the valve body 17.
However, as in the fifth embodiment, the wall surface of the valve chamber 18e composed of the valve seat surface 19a, the valve guide surface 18a, and the valve pressing surface 18b is composed of a high hardness member subjected to a hardening process such as a quenching process. If so, the wear on these parts will be minor.
Therefore, it is possible to provide a highly reliable compressor in which the valve seat surface, the valve guide surface, and the valve pressing surface are not worn and the valve body is not cracked.

In the present embodiment, hardening treatment such as hardening treatment is applied to all three surfaces of the valve seat surface, the valve guide surface, and the valve pressing surface, but the hardening treatment is applied to at least one of these surfaces. A curing process such as a process may be performed.
Furthermore, in the present embodiment, the hardness by the curing process such as the quenching process is set to be larger than that of the raw material before curing, but a material equal to or larger than the hardness of the valve body is directly used. You may do it.

Embodiment 6 of the Invention
12 and 13 are diagrams showing Embodiment 6 of the scroll compressor according to the present invention.
In the sixth embodiment, as shown in FIG. 12, a plurality of discharge passages 18c extend in the left-right direction instead of the up-down direction and open in the horizontal direction. However, each member is dimensioned and arranged so that the opening area of the valve drop hole 18d is 5 to 20% of the total opening area of the plurality of discharge passages 18c. Other configurations are the same as those of the first embodiment, and the description thereof is omitted.

Next, the effect of the above configuration will be described.
In the case of the free valve type discharge valve mechanism shown in FIG. 12, the collision speed of the valve element 17 to the valve seat surface 13a and the valve pressing surface 18b and the operating pressure conditions for starting the collision to the valve seat surface 13a are plural. The ratio of the total opening area of the discharge passage 18c and the opening area of the valve drop hole 18d, and the refrigerant reverse flow rate at the time of spiral communication are substantially determined. Among these, what can be controlled at the time of designing is the ratio of the opening areas of the plurality of discharge passages 18c and the valve drop holes 18d. In the case of an air conditioner, normally, the compressor operating range is about the operating pressure ratio ν8 or less, and the discharge valve mechanism does not cause the valve element 17 to collide with the valve seat surface 13a during excessive or insufficient compression in this range. Further, in consideration of wear around the valve, it is required that the valve body 17 has little fluttering in the vicinity of the valve pressing surface 18b, and that the valve body 17 is promptly closed when stopped.

FIG. 13 shows the valve closing performance at the stop and the operation (operating pressure ratio ν12) when the discharge valve structure of FIG. 12 is shaken with (valve opening area) / (total discharge passage area) as a parameter. The result of having experimentally measured the relationship between the collision speed of the valve body on the valve pressing surface (proportional to approximately the 1/2 power of the valve fluttering amount) is shown. The operating pressure ratio is usually up to about 8. However, it is necessary to ensure the same strength as the reed valve even in the abnormal operation mode such as fan block operation, so it is almost the maximum operating pressure ratio that can occur in the air conditioner unit. 12 was measured.

About the valve closing property at the time of a stop, it becomes so bad that the said area ratio: (valve drop opening area) / (discharge passage total opening area) is small. Further, the collision speed of the valve element 17 to the valve pressing surface during operation increases as the area ratio: (valve drop opening area) / (discharge passage total opening area) increases.
Usually, the lower limit of the operating pressure ratio is about 2 in the compressor operating range of the air conditioner. For this reason, it is necessary to close the valve at the operating pressure ratio of 2 or less. At this time, the area ratio is 5%. Further, if the collision speed of the valve body to the valve pressing surface is the same as that of a reed valve having a small valve lift, the possibility of wear of each part around the valve and valve cracking becomes extremely small. For this reason, it is necessary to suppress the collision speed to be equal to or lower than that of the reed valve. This condition is satisfied when the area ratio is 20% or less.

Therefore, if the ratio of (valve drop opening area) / (discharge passage total opening area) is set to 5 to 20%, the operating pressure ratio including the abnormal operation state of the fan block or the like is 12 during operation of the compressor. The valve body 17 does not collide with the valve seat surface 13a to a certain extent and the noise is extremely low. At this time, the collision speed of the valve with the valve pressing surface is less than the reed valve, wear of each part around the valve is small, Since the possibility is very small, the reliability is high, and when the compressor is stopped, the discharge valve is quickly closed, so that the reverse rotation sound at the time of stopping can be reduced.
Therefore, it is possible to provide a highly reliable compressor that has extremely low noise during operation of the compressor and low noise when stopped.

The discharge valve mechanism of the sixth embodiment may be applied to any one of the first to third embodiments. As for the effects, the noise during operation is extremely low because the valve element 17 does not collide with the valve seat surface 13a within the compressor operation range, as in the sixth embodiment. Regarding the noise at the time of stoppage, the sound that the slider 25 collides with the crankpin 53 and the sound that the spiral wrap 22 of the orbiting scroll collides with the spiral wrap 12 of the fixed scroll are the same as in the first to third embodiments. This is an unrecognizable level, and the noise is even lower than in the sixth embodiment.
Therefore, it is possible to provide a compressor with extremely low noise both during operation and when the compressor is stopped.

1 is an overall cross-sectional view showing a first embodiment of a scroll compressor according to the present invention. It is a figure which shows the discharge valve mechanism of the scroll compressor shown in FIG. 1, (a) is a top view of a guide member, (b) is AA sectional drawing in (a). The figure explaining the slider retraction amount of the scroll compressor shown in FIG. The graph which shows the relationship between slider retraction amount and the maximum amplitude at the time of a compressor stop. The figure which shows the example of the other discharge valve mechanism which can apply Embodiment 1. FIG. The figure which shows the example of the other crank mechanism part which can apply Embodiment 1. The figure which shows the example different from FIG. 6 of the other crank mechanism part which can apply Embodiment 1. FIG. The figure which shows Embodiment 2 of the scroll compressor which concerns on this invention. The figure which shows Embodiment 3 of the scroll compressor which concerns on this invention. The figure which shows Embodiment 4 of the scroll compressor which concerns on this invention. The figure which shows Embodiment 5 of the scroll compressor which concerns on this invention. The figure which shows Embodiment 6 of the scroll compressor which concerns on this invention. FIG. 13 is a graph showing the relationship between (valve drop hole opening area) / (discharge passage total opening area), stop valve closing performance, and collision speed of the valve body on the valve pressing surface during operation in the discharge valve structure shown in FIG. 12. The whole sectional view showing the conventional scroll compressor. The figure explaining the problem of the conventional scroll compressor.

5 Crankshaft, 13 Discharge port, 13a Valve seat surface,
13b Relief groove, 17 valve body, 18 valve guide member,
18a valve guide surface, 18b valve pressing surface, 18c discharge passage,
18d valve drop hole, 18e valve chamber, 19 valve seat plate,
25 slider, 25a elastic member, 25b leaf spring,
53 Crankpin (Crank part)

Claims (1)

A valve seat surface forming a periphery of a discharge port communicating with the innermost chamber formed by a fixed scroll having a spiral wrap and a swing scroll having a spiral wrap, and partially including the valve seat surface A scroll compressor comprising: a valve chamber, and a valve body that is loosely inserted into the valve chamber and can be seated on the valve seat surface to open and close the discharge port.
Even when the inclination of the valve body becomes maximum in the valve chamber, the edge portion of the valve body is arranged around the discharge port so that the edge portion of the valve body does not contact the valve seat surface and its vicinity surface. A scroll compressor characterized in that a groove for escaping is formed.

Images