JP5183773B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor, and more particularly to attachment of a vane spring constituting the rotary compressor.

  Conventionally, as a method for attaching a vane spring in a rotary compressor, a method in which a vane spring is press-fitted into a vane spring attachment hole formed in a back portion of the vane and the vane spring is held by the lateral pressure is generally used. However, when the vane spring is not attached correctly or when an excessive force is applied to the vane spring, the vane spring cannot be held only by the side pressure, and the vane spring may be ejected.

  The following various countermeasures are disclosed with respect to such problems of the prior art. For example, “Installation for attaching a blade (corresponding to a vane) to a cylinder having a cylinder chamber with a roller (corresponding to a rolling piston) as if it is elastically contacted with the roller via a blade spring (corresponding to a vane spring) A rotary portion having a structure that receives the back end portion of the blade spring and stops the outward movement of the spring opening near the opening portion of the spring chamber that opens to the outer surface of the cylinder. A blade mounting structure in a compressor is disclosed (see Patent Document 1). The blade attachment structure in this rotary compressor has a blade spring end corresponding to a vane spring having a large diameter, and a part of a hole for attaching the blade spring is enlarged in diameter to serve as a locking portion. Are to be locked.

  Further, “a cylinder formed inside a compression chamber concentric with the drive shaft, a rolling piston that is driven to rotate integrally with the eccentric shaft portion of the drive shaft and rolls along the inner peripheral surface of the cylinder, In a rotary compressor comprising a vane pressed against an outer peripheral surface of a rolling piston by a spring (corresponding to a vane spring) mounted on the surface, in a diaphragm 8 insertion support hole formed on an inner peripheral surface of the cylinder A rotary compressor is disclosed in which a groove that engages and supports the spring end on the vane side is provided on the peripheral surface (see Patent Document 2). In this rotary compressor, the end of the spring is enlarged, and a groove is provided in a part of the spring insertion support hole (corresponding to the vane spring mounting hole), and the end of the spring is engaged and supported by the groove. It is supposed to be.

  Further, “a crankshaft driven by a drive source, a roller (which corresponds to a rolling piston) that is rotatably fitted to the crankshaft and rotates in the cylinder, and reciprocates in contact with the outer periphery of the roller. A vane that divides the inside of the cylinder into a high-pressure chamber and a low-pressure chamber, a coiled spring that constantly presses the vane against the roller (corresponding to a vane spring), and a guide hole that guides the spring (corresponding to a vane spring mounting hole) In the rotary compressor provided with the above-mentioned rotary compressor, a screwed portion into which the outer diameter of the spring is screwed is formed on the inner wall of the guide hole on the opposite vane side (see Patent Document 3). ). In this rotary compressor, a spiral groove is formed in a part of a guide hole to which a spring is attached to form a screwed portion, and the spring is supported by the screwed portion.

  In addition to this, “the vane spring stopper is provided with two substantially cylindrical blade portions that serve as guides for fitting into the insertion holes formed in the cylinder, and these two blade portions are provided with a sufficient maximum load of the vane spring. The rotary compressor is disclosed that is formed integrally with the bottom portion of the vane spring stopper with a width that can be held in the width, and the width between the tip portions of the two blade portions is larger than the inner diameter of the insertion hole ”(patent Reference 4). This rotary compressor is provided with a vane spring stopper to prevent the vane spring from coming off.

  Furthermore, “a cylinder constituting the compression chamber, a roller rolling in the compression chamber (corresponding to a rolling piston), and a vane pressed by the elastic force of a coil spring (corresponding to a vane spring) on the outer periphery of the roller. The coil spring has a small diameter part that can be moved and a large diameter part that is fixed, and the large diameter part of the coil spring is inserted into the inner diameter of the spring hole that is formed in the cylinder in the direction of the central axis. Has been fixed by passing a locking pin through a pin hole drilled in the axial direction of the cylinder ”(see Patent Document 5). In this rotary compressor, the vane spring is prevented from coming off by using a locking pin.

Japanese Utility Model Publication No. 60-49283 (first page, FIG. 2) Japanese Utility Model Publication No. 60-90583 (first page, FIG. 3) Japanese Utility Model Publication No. 60-98781 (first page, FIG. 4) JP 2002-61588 A (3rd page, FIG. 4) Japanese Patent Laid-Open No. 10-61576 (page 3, FIG. 1)

  Conventionally, a method of press-fitting a vane spring into a vane spring mounting hole formed on the back of the vane and holding the vane spring with the lateral pressure thereof, as in a vane spring mounting method in a rotary compressor that has been implemented as a general technique. In this case, the vane spring may not be held only by the side pressure and may jump out when there is an improper attachment of the vane spring or when an impact force is applied to the compressor during transportation. That's right.

  Even in such a situation, in many models, the cylinder is fixed directly to the sealed container, and the inner wall of the sealed container is located near the end of the vane spring mounting hole. Even so, the inner wall of the sealed container would function as a stopper, and there was no immediate effect. However, from a long-term viewpoint, since the operation is performed in a state where the vane spring is locked but not fixed, a problem such as an increase in noise or a part of the vane spring is worn out. It often led to problems such as breakage.

  The techniques described in Patent Document 1 and Patent Document 2 increase the diameter of the end portion of the vane spring, expand a part of the vane spring mounting hole, and engage the end portion of the vane spring with the end surface of the expanded diameter portion. It stopped. However, the vane springs are merely “locked”, and the vane springs are not “fixed”. Therefore, by driving the rotary compressor, there is a possibility that a part of the vane spring is worn and eventually broken.

  In addition, the techniques described in Patent Document 1 and Patent Document 2 illustrate that the vane spring has a shape in which about 1 to 1.5 times the wire diameter has entered the step in the enlarged diameter portion. ing. In other words, in order to install the vane spring, it is necessary to reduce the diameter of the vane spring to more than twice the diameter of the vane spring and put it to the enlarged diameter part, which makes it very difficult and troublesome to install the vane spring. The problem that remained.

  The technique described in Patent Document 3 uses a spiral groove formed in a part of a guide hole to which a spring is attached as a screwing portion, and the spring is fixed by the screwing portion. There was a problem that it was expensive. In addition, the attachment of the spring to the screwing portion has to be performed while rotating the spring, and there is a problem that it takes time and labor to attach the spring.

  The techniques described in Patent Literature 4 and Patent Literature 5 have to add parts in order to prevent the vane spring from coming off. That is, functional parts such as a vane spring stopper and a locking pin are added to prevent the vane spring from coming off. Therefore, there is a problem that the addition of the functional parts further increases the cost. In addition, with the addition of functional parts, there is also a problem that it takes a lot of time and labor for processing work.

  As described above, the conventional technique merely locks the vane spring and does not securely fix the vane spring to the vane spring mounting hole, and attaches the vane spring to the vane spring mounting hole. There are three problems that are complicated and that it is necessary to add a new functional component to fix the vane spring in the vane spring mounting hole, and these cannot be solved satisfactorily.

  The present invention has been made to solve the above-described problems. The vane spring can be securely fixed to the vane spring mounting hole, and the vane spring can be easily mounted to the vane spring mounting hole. The present invention provides a rotary compressor that does not require the addition of new functional parts in order to fix a vane spring in a mounting hole.

  A rotary compressor according to the present invention includes a cylinder that constitutes a compression chamber that is attached to form a gap with an inner wall of a sealed container to be stored, a rolling piston that rolls within the cylinder, and an outer periphery of the rolling piston. A rotary compressor comprising: a vane to be pressed; a vane spring that presses the vane against the rolling piston; and a vane spring mounting hole for mounting the vane spring formed on a back portion of the vane. The spring mounting hole is formed with an enlarged diameter portion having a diameter larger than that of the vane spring mounting hole, and a non-diameter enlarged portion having a diameter smaller than the enlarged diameter portion is formed so as to sandwich the enlarged diameter portion. The vane spring includes a small-diameter spring portion movable with the non-diameter-enlarged portion, and the vane spring includes the vane spring. The vane spring mounting hole has a center diameter smaller than the outer diameter of the jig to be pushed into the mounting hole, and a plurality of wound and closely wound large-diameter spring portions that are locked to the expanded diameter portion. And a step generated in the vane spring mounting hole due to a difference between the diameter of the enlarged diameter portion and the enlarged diameter portion, the large diameter spring portion is not plastically deformed even when the vane spring is pushed by the jig. In order to prevent the large diameter spring portion locked to the spring from coming off, the range is 10% to 50% with respect to the spring diameter of the vane spring.

  According to the rotary compressor according to the present invention, the vane spring can be securely fixed, and it is possible to prevent wear and breakage of the vane spring due to minute vibration of the vane spring holding position during operation of the rotary compressor. it can.

It is a cross-sectional view which shows the structure of the rotary compressor which concerns on embodiment. It is detailed sectional drawing which shows a vane spring and a vane spring attachment hole. It is sectional drawing which shows the state in which the vane spring was attached to the vane spring attachment hole. It is explanatory drawing which shows the relationship between the ratio of a level | step difference and the spring diameter of a vane spring, and the removal load of a large diameter spring part. It is detail sectional drawing which shows the positioning method of a vane spring. It is detailed sectional drawing which shows the state inside a vane spring attachment hole when an impact force generate | occur | produces.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional view showing a configuration of a rotary compressor 100 according to an embodiment of the present invention. The rotary compressor 100 is used for a refrigerator, a freezer, a vending machine, an air conditioner, a water heater, and the like. The rotary compressor 100 compresses a refrigerant circulating through a refrigeration cycle (heat pump cycle), for example, and sends it out as a high-temperature and high-pressure refrigerant. Here, the case where the refrigerant used for the rotary compressor 100 is carbon dioxide (carbon dioxide) is shown as an example.

  The rotary compressor 100 is roughly composed of a compression element 20 and an electric element 30. The compression element 20 and the electric element 30 are accommodated in the sealed container 10. In addition, the compression element 20 shall be accommodated in the lower side of the airtight container 10, and the electric element 30 shall be accommodated in the upper side of the airtight container 10, respectively. The electric element 30 includes a rotor 31 attached to the crankshaft 40 and a stator 31 attached to the sealed container 10.

  The compression element 20 includes a cylinder 21 constituting a compression chamber, a rolling piston 24 that rotates in the cylinder 21 by an eccentric portion of the crankshaft 40, and the cylinder 21 that is in contact with the rolling piston 24 is divided into a high pressure side and a low pressure side. A vane 25 to be defined, and an upper bearing 22 and a lower bearing 23 that seal the opening of the cylinder 21 are configured. The vane 25 is reciprocated by being pressed against the outer periphery of the rolling piston 24 by the elastic force of the vane spring 50. The vane spring 50 is attached by being fitted into a vane spring attachment hole 80 formed on the back of the vane of the cylinder 21.

  The sealed container 10 is formed using a thick shell. This is because the compression element 20 which is a precision part is mounted in the sealed container 10. That is, it is for making it difficult to transmit the distortion | strain of the airtight container 10 which generate | occur | produces to the compression element 20 by arc spot welding etc. FIG. The compression element 20 is configured to be screwed to a mechanical holder 60 attached in the sealed container 10. That is, the compression element 20 is attached to the sealed container 10 via the mechanical holder 60. For this reason, the outer diameter of the cylinder 21 constituting the compression element 20 forms a gap so as not to contact the inner wall of the sealed container 10.

  In the rotary compressor 100 configured as described above, the refrigerant that has flowed into the cylinder 21 is compressed by the cooperation of the rolling piston 24 and the vane 25 that configure the compression element 20, and air (not shown) of the electric element 30 is not illustrated. It is sent out to the upper part of the electric element 30 through the gap, and is discharged to the outside of the hermetic container 10 from the discharge pipe 72 rotated by the rotation of the rotor 31.

  On the other hand, if the configuration is such that the cylinder 21 is directly attached to the sealed container 10, the sealed container 10 will serve as a lid even if the vane spring 50 is removed from the vane spring mounting hole 80. The function of the vane spring 50 is not lost immediately. However, in the rotary compressor 100 according to this embodiment, the cylinder 21 is attached to the sealed container 10 via the mechanical holder 60, and a gap is formed so that the outer diameter of the cylinder 21 does not contact the inner wall of the sealed container 10. Has been.

  Therefore, when the vane spring 50 is removed from the vane spring mounting hole 80, the removed vane spring 50 enters the gap formed between the sealed container 10 and the cylinder 21 and presses the vane 25. Will be lost. That is, the function of the rotary compressor 100 is immediately reduced. Therefore, the vane spring 50 is required to be configured so as not to be detached from the vane spring mounting hole 80.

  FIG. 2 is a detailed sectional view showing the vane spring 50 and the vane spring mounting hole 80. Based on FIG. 2, the structure and function of the vane spring 50 and the vane spring mounting hole 80 will be described. The vane spring 50 is formed in a coil shape, has a small-diameter spring portion 51 that is movable on the side that presses the vane 25, and has a large-diameter spring portion 52 that is closely wound on the opposite side. The vane spring 50 is shown as an example in which the vane spring 50 has a tapered shape in which the diameter gradually increases from the small diameter spring portion 51 toward the large diameter spring portion 52.

  The vane spring mounting hole 80 is provided with a diameter-expanded portion 81 for fixing and holding the large-diameter spring portion 52 of the vane spring 50, a non-diameter-expanded portion 82 having a smaller diameter than the diameter-expanded portion 81, and the vane spring 50. An opening 83 for insertion / extraction is formed. A step 85 is formed in the vane spring mounting hole 80 due to the difference in diameter between the enlarged diameter portion 81 and the non-expanded diameter portion 82. The step 85 is 10% to 50% of the spring diameter of the vane spring 50 (the reason for this will be described in detail in FIG. 4).

  FIG. 3 is a cross-sectional view showing a state in which the vane spring 50 is attached to the vane spring attachment hole 80. The vane spring 50 attached to the vane spring attachment hole 80 is configured such that the large-diameter spring portion 52 is fitted into an enlarged diameter portion 81 formed in the vane spring attachment hole 80. The vane spring 50 is fixed and held in the vane spring mounting hole 80 by the lateral pressure of the large-diameter spring portion 52 of the vane spring 50.

  FIG. 4 is an explanatory diagram showing the relationship between the ratio between the step 85 and the spring diameter of the vane spring 50 and the removal load of the large-diameter spring portion 52. Based on FIG. 4, it will be described how the vane spring 50 is prevented from coming off from the relationship between the step 85 and the spring diameter of the vane spring 50. In FIG. 4, the vertical axis represents the slipping load of the large-diameter spring portion 52, and the horizontal axis represents the ratio (%) calculated by dividing the step 85 by the spring diameter of the vane spring 50. The removal load is a force necessary to extract the vane spring 50 from the vane spring mounting hole 80. That is, it is difficult to come off when the removal load is large, and it is easy to come off when the removal load is small.

  A solid line A represents the maximum load applied to the vane spring 50 during normal use of the rotary compressor 100. A solid line B represents a load applied to the vane spring 50 when an impact force applied to the rotary compressor 100 is taken into consideration. A solid line C represents an actual measurement value of the removal load of the vane spring 50 and the ratio between the step 85 and the spring diameter of the vane spring 50. As shown in FIG. 4, the larger the removal load of the large-diameter spring portion 52, the greater the ratio between the step 85 and the spring diameter of the vane spring 50. In other words, when it is desired to increase the removal load of the large-diameter spring portion 52, the step 85 with respect to the spring diameter of the vane spring 50 may be increased. Note that an increase in the load of the large diameter spring portion 52 means that the fixing strength of the vane spring 50 is also increased.

  Therefore, the step diameter 85 and the spring diameter of the vane spring 50 may be determined from the relationship with the magnitude of the unloading load of the large diameter spring portion 52, and in addition, each of the compression elements 20 constituting the compression compressor 20 housed in the rotary compressor 100. It is desirable to determine in consideration of the size of the part. In this case, if the lower limit of the step 85 is ensured by 10% or more with respect to the spring diameter of the vane spring 50, it is possible to secure a sufficient removal load considering the impact force.

  In other words, since a sufficient removal load is ensured even when an excessive impact load is applied, such as when the rotary compressor 100 is transported or compressed, the vane spring 50 can be prevented from coming off. Can do. However, if the step 85 is increased more than necessary, the removal load of the vane spring 50 is increased, but the installation of the vane spring 50 becomes complicated. It is desirable to make it 50% or less with respect to the spring diameter.

  FIG. 5 is a detailed cross-sectional view showing a method for positioning the vane spring 50. Based on FIG. 5, the position determination of the vane spring 50 mounted in the vane spring mounting hole 80 will be described. The vane spring 50 is inserted into the vane spring mounting hole 80 from the opening 83 of the vane spring mounting hole 80 by a pushing jig 150 or the like. Then, the end position of the vane spring 50 is determined.

  As described above, the step 85 in the vane spring mounting hole 80 is 50% or less of the maximum spring diameter of the vane spring 50. Therefore, even if the large-diameter spring portion 52 of the vane spring 50 is fixed in the enlarged-diameter portion 81, the entire large-diameter spring portion 52 is not hidden. That is, when the vane spring 50 is attached to the vane spring attachment hole 80, even if the large-diameter spring portion 52 of the vane spring 50 is fitted to the enlarged-diameter portion 81, the large-diameter spring portion 52 is not connected to the vane spring attachment hole 80. It can be visually recognized from the opening 83.

  Usually, the outer diameter of the pushing jig 150 is larger than the center diameter (Z) of the large-diameter spring portion 52 of the vane spring 50. This is because the vane spring 50 is surely inserted into the vane spring mounting hole 80. Accordingly, the vane spring 50 can be reliably inserted, and the attachment position can be reliably determined by visually recognizing the large diameter spring portion 52. If the outer diameter of the pushing jig 150 is smaller than the center diameter (Z) of the large-diameter spring portion 52 of the vane spring 50, the pushing jig 150 gets stuck in the large-diameter spring portion 52. .

  Further, since the step 85 in the vane spring mounting hole 80 is 50% or less of the maximum spring diameter of the vane spring 50, when the vane spring 50 is mounted, the large-diameter spring portion 52 of the vane spring 50 is not expanded. The large diameter spring portion 52 does not have to be greatly reduced in diameter when passing through the shaft. That is, when the vane spring 50 is inserted into the vane spring mounting hole 80, the large-diameter spring portion 52 must be reduced in diameter to the size of the non-diameter-expanded portion 82, but the ratio between the step 85 and the spring diameter of the vane spring 50. If it is 50% or more, the large-diameter spring portion 52 must be greatly reduced in diameter, and extra labor is required. Accordingly, since the step 85 is 50% or less of the maximum spring diameter of the vane spring 50, the vane spring 50 can be easily attached.

  The vane spring 50 attached as described above is fixed by the lateral pressure of the large-diameter spring portion 52 fitted in the enlarged-diameter portion 81 of the vane spring attachment hole 80 when the rotary compressor 100 is in a normal operation state. Since it is held, friction due to minute vibration between the large diameter spring portion 52 of the vane spring 50 and the vane spring mounting hole 80 does not occur. That is, when the rotary compressor 100 is operating normally, the vane spring 50 is not worn. However, when an impact force is generated in the rotary compressor 100 during transportation or liquid compression, excessive force is applied to the large-diameter spring portion 52 of the vane spring 50, and the large-diameter spring portion 52 moves inside the enlarged-diameter portion 81. May move.

  FIG. 6 is a detailed cross-sectional view showing a state inside the vane spring mounting hole 80 when an impact force is generated. As described above, when an impact force is generated in the rotary compressor 100, the large-diameter spring portion 52 may move in the enlarged-diameter portion 81. However, since there is a step between the enlarged diameter portion 81 and the non-expanded diameter portion 82 inside the vane spring mounting hole 80, the large diameter spring portion 52 does not come off from the enlarged diameter portion 81. That is, the vane spring 50 does not jump out of the vane spring mounting hole 80.

  Further, even if the large-diameter spring portion 52 of the vane spring 50 moves in the enlarged diameter portion 81, the state in which the side pressure is applied in the enlarged diameter portion 81 is maintained, so that the operation state of the rotary compressor 100 is normal. When returning to operation, the large-diameter spring portion 52 of the vane spring 50 is quickly fixed and held in the enlarged-diameter portion 81 of the vane spring mounting hole 80. Therefore, friction due to minute vibration between the large-diameter spring portion 52 of the vane spring 50 and the vane spring mounting hole 80 does not occur.

  As described above, the rotary compressor 100 uses the side pressure of the vane spring 50 (large-diameter spring portion 52) to securely fix the vane spring mounting hole 80, and the vane spring 50 can be easily operated. It solves the three problems that it can be attached to the attachment hole 80 and that no new functional parts need to be added to fix the vane spring 50 to the vane spring attachment hole 80. Therefore, wear of the vane spring 50 can be reduced while preventing the vane spring 50 from coming off. In addition, since it can be easily attached, it is possible to provide a rotary compressor 100 with high stability and reliability in which the compression performance is not lowered while the labor required for the machining process is saved.

  DESCRIPTION OF SYMBOLS 10 Airtight container, 20 Compression element, 21 Cylinder, 22 Upper bearing, 23 Lower bearing, 24 Rolling piston, 25 Vane, 30 Electric element, 31 Rotor, 32 Stator, 40 Crankshaft, 50 Vane spring, 51 Small diameter spring part , 52 Large diameter spring part, 60 Mechanical holder, 72 Discharge pipe, 80 Vane spring mounting hole, 81 Large diameter part, 82 Non-diameter part, 83 Opening part, 85 Step, 100 Rotary compressor, 150 Pushing jig.

Claims (6)

A cylinder constituting a compression chamber attached to form a gap with the inner wall of the sealed container to be stored;
A rolling piston that rolls in the cylinder;
A vane pressed against the outer periphery of the rolling piston;
A vane spring that presses the vane against the rolling piston;
A rotary compressor provided with a vane spring mounting hole for mounting the vane spring formed on the back of the vane;
In the vane spring mounting hole,
A diameter-expanded portion having a diameter larger than the diameter of the vane spring mounting hole is formed, and a non-diameter-expanded portion having a diameter smaller than the diameter-expanded portion is formed so as to sandwich the diameter-expanded portion,
The vane spring is
A small-diameter spring portion movable at the non-diameter-enlarged portion;
A center diameter smaller than an outer diameter of a jig for pushing the vane spring into the vane spring mounting hole, and a plurality of closely wound large-diameter spring portions that are locked to the enlarged diameter portion, and
A step generated in the vane spring mounting hole due to the difference between the diameter of the vane spring mounting hole and the diameter of the enlarged diameter portion,
Even when the vane spring is pushed by the jig, the large-diameter spring portion is not plastically deformed and the large-diameter spring portion locked to the enlarged-diameter portion does not come out. A rotary compressor characterized by having a range of 10% to 50% with respect to the diameter. The center diameter of the large diameter spring part is
2. The rotary compressor according to claim 1, wherein the length is determined to be visible from an opening end of the vane spring mounting hole in a state where the vane spring is mounted in the vane spring mounting hole. The vane spring is
The rotary compressor according to claim 1 or 2, wherein the rotary compressor is attached by being fitted into the vane spring attachment hole. The vane spring is
The large-diameter spring portion is fitted into the enlarged-diameter portion of the vane spring mounting hole, and the vane spring is fixed to the vane spring mounting hole by a lateral pressure of the large-diameter spring portion. The rotary compressor according to any one of 3. The rotary compressor is
The rotary compressor according to any one of claims 1 to 4, wherein the rotary compressor is for high-pressure refrigerant. The rotary compressor according to any one of claims 1 to 5, wherein carbon dioxide is used as a refrigerant of the rotary compressor.

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