JP2010242590A - Hermetic compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To limit the maximum rotation rock quantity without increasing vibration during normal operation even if brake torque of an electric compression element during stopping is high. <P>SOLUTION: An outer circumference part 127 of a compressor side snubber 117 is formed by a prescribed curved surface in which outer diameter from a bottom part 140 over a head part 137 become small in at least a part, and is formed so as to keep ratio of outer diameter of the head part 137 to an outer diameter of the bottom part 140 in a range of 90-97%. Spring force of a coil spring 118 is quickly increased in response to rotation direction displacement by the curved surface of an outer circumference part of the compressor side snubber 117 and eventually reduces the maximum rotation rock quantity even if compression load right before stop is heavy and brake torque is high. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a hermetic compressor used in a refrigeration refrigerator / cooler.

  Conventionally, as this type of hermetic compressor, there is one in which an elastic support device that reduces vibration and noise is provided in a hermetic container (see, for example, Patent Document 1).

  Hereinafter, the conventional hermetic compressor will be described with reference to the drawings.

  6 is a longitudinal sectional view of a conventional hermetic compressor, FIG. 7 is a top view of the conventional hermetic compressor, FIG. 8 is an enlarged cross-sectional view of a main part of the conventional hermetic compressor, and FIG. 9 is a conventional hermetic type. It is operation | movement explanatory drawing of a compressor.

  6 to 9, the sealed container 1 elastically supports and accommodates an electric compression element 4 including an electric element 2 and a compression element 3 by a plurality of elastic support devices 5. The electric element 2 includes a stator 6 and a rotor 7 and drives the compression element 3.

  Next, the main configuration of the compression element 3 will be described.

  The cylinder block 8 includes a bearing portion 9. The shaft 10 includes a main shaft portion 11 and an eccentric portion 12. The main shaft portion 11 is pivotally supported by the bearing portion 9 of the cylinder block 8 and the rotor 7 is press-fitted and fixed. The eccentric portion 12 is connected to the piston 14 by the coupling mechanism 13. It is connected.

  Next, the configuration of the elastic support device 5 will be described.

  The elastic support device 5 includes a shell-side snubber 15, a compressor-side snubber 17, and a coil spring 18. The shell side snubber 15 is fixed to the bottom of the sealed container 1. The compressor side snubber bar 17 is fixed to the electric compression element 4.

  The coil spring 18 is sandwiched between the shell-side snubber 15 and the compressor-side snubber 17 at both ends.

  The electric compression element 4 is provided with a discharge pipe 30 that guides the refrigerant (not shown) compressed by the compression element 3 to the outside of the sealed container 1, and is connected to the sealed container 1.

  The operation of the hermetic compressor configured as described above will be described below.

  During operation, when electricity is supplied to the electric element 2, the rotor 7 rotates, the shaft 10 is rotationally driven, and the rotational movement of the shaft 10 is transmitted to the piston 14 by the coupling mechanism 13 to perform a compression operation.

  At this time, the electric element 2 generates rotational torque according to the compression load generated by the piston 14 and continues the compression operation.

  At this time, although the electric compression element 4 vibrates with the compression operation, the elastic support device 5 attenuates the transmission to the sealed container 1 and reduces the vibration of the whole hermetic compressor.

Further, when the electric supply to the electric element 2 is stopped at the time of stopping, the rotational torque generated by the electric element 2 is lost, so that the compression load generated by the piston 14 is applied to the shaft 10 and the rotor 7 by the coupling mechanism 13. Brake torque is applied and rotational motion stops. At this time, the electric compression element 4 rotates in the rotation direction of the rotor 7 about the main shaft portion 11 of the shaft 10 according to the brake torque, but the elastic support device 5 absorbs the energy and rotates in the rotation direction. By repeating the rotational oscillating motion in the counter-rotating direction, the transmission to the hermetic container 1 is attenuated, and the oscillation of the whole hermetic compressor when stopped is also reduced.
JP 2000-097153 A

  However, in the conventional configuration described above, since the compression load is large when the discharge pressure immediately before the stop or the suction pressure is high, the brake torque acting on the rotor 7 or the shaft 10 that has been rotating at the time of the stop increases. Also, the amount of rotational swing about the main shaft portion 11 of the electric compression element 4 is increased.

  At this time, as shown in FIG. 8, a large force is generated in the restraint portion such as the internal pipe immediately before stopping, and it is necessary to increase the rigidity in designing the discharge pipe 30 and the like. For this reason, there is a problem that vibration transmitted from the electric compression element 4 through the discharge pipe 30 during operation increases and vibration of the whole hermetic compressor increases.

  On the other hand, there is a method of increasing the spring force of the coil spring 18 of the elastic support device 5 in order to suppress the rotational swing amount when the electric compression element 4 is stopped. However, when the spring force is increased, the damping force of vibration during operation decreases. Therefore, the vibration transmitted through the coil spring 18 is increased, and the vibration of the whole hermetic compressor is increased.

  SUMMARY OF THE INVENTION The present invention solves the above-described conventional problems, and an object of the present invention is to provide a hermetic compressor that reduces the amount of rotational oscillation of the electric compression element when stopped and has low vibration and high reliability.

  In order to solve the above-described conventional problems, in the hermetic compressor according to the present invention, the outer peripheral portion of the compressor-side snubber is formed with a predetermined curved surface whose outer diameter decreases at least partially from the bottom to the head. The ratio of the outer diameter of the head to the outer diameter of the bottom portion is formed to be in the range of 90 to 97%. Even when the compression load immediately before the stop is large and the brake torque is large, the compressor side Due to the curved surface of the outer peripheral portion of the snubber, the spring force of the coil spring increases rapidly according to the displacement in the rotational direction, and as a result, the maximum amount of rotational swing is reduced.

  The hermetic compressor of the present invention can reduce the amount of rotational oscillation of the electric compression element even when the brake torque of the electric compression element exceeds a predetermined value. A high hermetic compressor can be provided.

According to the first aspect of the present invention, there is provided an airtight container, an electric compression element that includes a piston that is housed in the airtight container and reciprocates in a compression chamber, and a tightly wound portion at both ends that elastically support the electric compression element. The coil spring is inserted at both ends into a shell side snubber that is a protrusion provided on the sealed container side and a compressor side snubber provided on the electric compression element side, and the compressor side snubber is provided. The outer peripheral portion of the head is formed with a predetermined curved surface whose outer diameter decreases from the bottom to the head, and the ratio of the outer diameter of the head to the outer diameter of the bottom is within a range of 90 to 97%. Even when the compression load just before the stop is large and the brake torque is large, the portion where the curved surface of the outer periphery of the compressor-side snubber is in contact with the inner surface of the coil spring is fast. In addition, the spring force in the rotational direction is increased by reducing the effective winding portion of the coil spring with a slight displacement. As a result, the maximum amount of rotational oscillation is reduced, vibration is small, and a highly reliable hermetic compressor Can be provided.

  The invention according to claim 2 is characterized in that, in the invention according to claim 1, the outer peripheral portion of the compressor side snubber is a curved surface having an R shape in a longitudinal section, and is in contact with a coil spring. Since the surface is continuous, the spring constant can be continuously changed without generating a specific force in the coil spring. Therefore, in addition to the effect of the invention according to claim 1, a more reliable hermetic compression Machine can be provided.

  The invention according to claim 3 is the invention according to claim 1 or 2, wherein the coil spring has a spring characteristic that restrains rotation of the electric compression element in a state where the electric compression element is elastically supported. The spring constant of the spring characteristic with respect to the displacement in the rotational direction of the electric compression element is in the range of 2 to 5 N / mm, and the coil spring spring is used to reduce the vibration of the whole hermetic compressor. Even when the force is reduced, the maximum amount of rotational swing immediately before stopping can be reduced, so that the vibration can be further reduced in addition to the effect of the invention described in claim 1 or 2.

  The invention according to claim 4 is the invention according to any one of claims 1 to 3, wherein the electric element is operated at a plurality of rotation speeds including a rotation speed less than a commercial power supply frequency. Thus, since the coil spring having a low spring constant can be used by reducing the maximum amount of rocking rotation at the time of stopping, in addition to the effect of the invention according to any one of claims 1 to 3, further lower rotation Since it can drive | operate with, it can reduce the power consumption as a refrigerator.

  The invention according to claim 5 is characterized in that, in the invention according to any one of claims 1 to 4, the compression chamber has a volume exceeding 10 cc, and the compression load increases as the volume increases. Although the brake torque generated at the time of stoppage increases and increases, the maximum amount of rotational swing can be reduced. Therefore, in addition to the effect of the invention according to any one of claims 1 to 4, the reliability is further high. A hermetic compressor can be provided.

  The invention according to claim 6 is the fastening according to any one of claims 1 to 5, wherein the head of the compressor-side snubber is fastened to fasten the compression element and the electric element constituting the electric compression element. Since the bolt has the same shape as the head of the bolt and the number of parts can be reduced, in addition to the effect of the invention according to any one of claims 1 to 5, a more inexpensive hermetic compressor is provided. Can do.

  The invention according to claim 7 is the invention according to any one of claims 1 to 6, wherein the connecting portion between the head portion and the outer peripheral portion of the compressor-side snubber has a shape in a longitudinal section of the wire diameter of the coil spring. It has a round shape of 1/2 or more, and the snubber head damages the coil spring when rotating and swinging at a stop by increasing the radius of the connecting part between the snubber head and the outer periphery than the wire diameter of the coil spring. In addition to the effects of the invention according to any one of claims 1 to 6, it is possible to provide a highly reliable hermetic compressor.

  Hereinafter, embodiments of a hermetic compressor according to the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.

(Embodiment 1)
1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention, FIG. 2 is a top view of the hermetic compressor according to the same embodiment, and FIG. 3 is a schematic diagram of the hermetic compressor according to the same embodiment. FIG. 4 is an operation explanatory view of the hermetic compressor in the same embodiment, and FIG. 5 is a spring characteristic diagram of a coil spring of the hermetic compressor in the same embodiment.

  Here, the spring characteristic diagram of the coil spring in FIG. 5 is a spring characteristic diagram with respect to the displacement of the electric compression element, and the element stored in the coil spring when the electric compression element rotates and the coil spring is displaced in the rotation direction. The force (spring force) that tries to return to is shown.

  In FIGS. 1 to 5, the sealed container 101 elastically supports and accommodates an electric compression element 104 including an electric element 102 and a compression element 103 by a plurality of elastic support devices 105. The electric element 102 includes a stator 106 and a rotor 107 and drives the compression element 103.

  At this time, the electric element 102 operates at a plurality of rotation speeds including a rotation speed less than the commercial power supply frequency.

  Next, the main configuration of the compression element 103 will be described.

  The cylinder block 108 includes a bearing portion 109. The shaft 110 includes a main shaft portion 111 and an eccentric portion 112. The main shaft portion 111 is pivotally supported by the bearing portion 109 of the cylinder block 108 and the rotor 107 is press-fitted and fixed. The eccentric portion 112 is connected to the piston 114 by the coupling mechanism 113. It is connected.

  The capacity of the compression chamber 148 formed by the cylinder block 108 and the piston 114 is set to be 10 cc.

  Next, the configuration of the elastic support device 105 will be described.

  The elastic support device 105 includes a shell-side snubber 115, a compressor-side snubber 117, and a coil spring 118. The shell side snubber 115 is fixed to the bottom of the sealed container 101. The compressor side snubber bar 117 is fixed to the electric compression element 104.

  The compressor-side snubber 117 is formed integrally with the head of a fastening bolt 157 that fastens the compression element 103 and the electric element 102.

  In addition, the outer peripheral portion 127 of the compressor-side snubber 117 is formed with an R-shaped curved surface such that at least a part of the longitudinal cross section decreases from the bottom portion 140 to the head portion 137, and with respect to the outer diameter of the bottom portion 140. The ratio of the outer diameter of the head 137 is formed to be in the range of 90 to 97%.

  Further, the head portion 137 of the compressor-side snubber 117 and the connecting portion 147 of the outer peripheral portion 127 have an R shape that is ½ or more of the wire diameter of the coil spring 118.

  A protrusion 115 having an outer diameter smaller than that of the head 137 is provided on the shell-side snubber 115 side of the head 137 of the compressor-side snubber 117.

  The spring constant of the spring characteristic with respect to the displacement in the rotational direction of the coil spring 118 is set in the range of 2 to 5 N / mm, and both ends are sandwiched between the shell side snubber 115 and the compressor side snubber 117.

  The electric compression element 104 is provided with a discharge pipe 130 that guides the refrigerant (not shown) compressed by the compression element 103 to the outside of the shell, and is connected to the sealed container 101.

  The operation of the hermetic compressor configured as described above will be described below.

  During operation, when electricity is supplied to the electric element 102, the rotor 107 rotates, the shaft 110 is driven to rotate, and the rotational motion of the shaft 110 is transmitted to the piston 114 by the coupling mechanism 113 to perform a compression operation.

  At this time, the electric element 102 generates rotational torque according to the compression load generated by the piston 114 and continues the compression operation.

  At this time, although the electric compression element 104 vibrates in accordance with the compression operation, the elastic support device 105 attenuates the transmission to the sealed container 101 and reduces the vibration of the whole hermetic compressor.

  Further, when the electric supply to the electric element 102 is stopped at the time of stopping, the rotational torque generated by the electric element 102 is lost, so that the compression load generated by the piston 114 is applied to the shaft 110 and the rotor 107 by the coupling mechanism 113. Brake torque is applied and rotational motion stops. At this time, the electric compression element 104 rotates in the rotation direction of the rotor 107 about the main shaft portion 111 of the shaft 110 according to the brake torque, but the elastic support device 105 absorbs the energy and rotates in the rotation direction. By repeating the rotational oscillating motion in the counter-rotating direction, the transmission to the hermetic container 101 is attenuated, and the oscillation of the whole hermetic compressor when stopped is also reduced.

  Here, when the discharge pressure immediately before the stop or the suction pressure is high, since the compression load is large, the brake torque acting on the rotor 107 and the shaft 110 that have been rotating at the time of the stop also increases, and the electric compression element The rotational swing around the main shaft portion 111 of 104 is also increased.

  At this time, the rotational swing amount increases, and the force acting on the restraint portion such as the discharge pipe 130 increases, but the outer peripheral portion 127 of the compressor-side snubber 117 in the present embodiment has a vertical cross section from the bottom portion 140 to the head portion. It has an R shape that decreases toward 137, and the ratio of the outer diameter of the head 137 to the outer diameter of the bottom 140 is in the range of 90 to 97%.

  Therefore, as shown in FIG. 5, the inner surface of the coil spring 118 is more in contact with the axial direction of the curved surface of the outer peripheral portion 127 of the compressor-side snubber 117 with respect to the rotational displacement of the electric compression element 104. Since the effective winding portion of the coil spring 118 decreases and the spring force in the rotational direction increases with a slight displacement in 104 in the rotational direction, the vibration transmitted to the sealed container 101 is reduced during normal operation, and when the operation is stopped. The maximum amount of rotational swing of the electric compression element 104 can be reduced. As a result, the force acting on the restraint portion such as the discharge pipe 130 is also reduced.

  Therefore, it is possible to provide a hermetic compressor with low vibration and high reliability.

  In particular, since the outer peripheral portion 127 of the compressor-side snubber 117 is formed in an R shape such that the longitudinal cross section becomes smaller from the bottom portion 140 to the head portion 137, when the electric compression element 104 stops, the electric compression element 104 Even if the coil spring 118 is deformed along with the rotation, the coil spring 118 is linearly deformed along the R shape of the outer peripheral portion of the compressor-side snubber 117, and the spring force suppresses the rotational oscillation of the electric compression element 104. Acts as follows.

  Therefore, since the coil spring 118 is linearly deformed and stress is not concentrated locally, the rotational swing of the compression element 104 can be smoothly suppressed, and the reliability of the coil spring 118 is improved and the compressor side is increased. Sliding between the snubber 117 and the coil spring 118 is suppressed, and noise accompanying the sliding can be reduced.

Furthermore, the ratio of the outer diameter of the head 137 to the outer diameter of the bottom 140 is in the range of 90 to 97%. If this ratio is less than 90% and the head has a fairly tapered shape, electric compression is performed. When the element 104 is stopped, if the coil spring 118 is not greatly deformed along with the rotation of the electric compression element 104, the spring force in the rotation direction of the electric compression element 104 cannot be obtained. The effect of suppressing is reduced.

  For this reason, the electric compression element 104 rotates and swings greatly, and the force acting on the restraint portion such as the discharge pipe 130 is large, which causes a reduction in reliability such as breakage of the discharge pipe 130.

  When the spring force of the coil spring 118 is increased in order to compensate for a reduction in the effect of suppressing the rotational swing of the electric compression element 104, the vibration damping force by the coil spring 118 is reduced, so that the vibration transmitted through the coil spring 118 is large. As a result, the vibration of the whole hermetic compressor is increased.

  On the other hand, when the ratio of the outer diameter of the head portion 137 to the outer diameter of the bottom portion 140 exceeds 97%, the compressor-side snubber 117 becomes substantially cylindrical in the axial direction, and the outer peripheral portion of the compressor-side snubber 117 is also in normal operation. Since 127 and the inner peripheral part of the coil spring 118 slide in the axial direction for a long time, noise accompanying the sliding is generated, and the effect of reducing the vibration transmitted to the sealed container 101 by the coil spring 118 is greatly impaired.

  As described above, when the ratio of the outer diameter of the head 137 to the outer diameter of the bottom 140 is in the range of 90 to 97%, when the electric compression element 104 is stopped, the electric compression element 104 An effect of suppressing rotational swing and reducing a force acting on a restraint portion such as the discharge pipe 130, an effect of suppressing noise caused by sliding between the outer peripheral portion 127 of the compressor-side snubber 117 and the inner peripheral portion of the coil spring 118; The effect of reducing vibration transmitted to the sealed container 101 by the coil spring 118 during normal operation can be obtained in a well-balanced manner.

  In addition, the ratio of the outer diameter of the head 137 to the outer diameter of the bottom 140 of the outer peripheral portion 127 of the compressor-side snubber 117 is in the range of 90 to 97%. The effects described above can be obtained with the best balance.

  The protrusion 115 of the compressor-side snubber 117 is formed so as not to come into contact with or slide with the coil spring 118, and when a vertical impact is applied to the hermetic compressor. Is formed so as to abut against the shell-side snubber 115, and the electric compression element 104 or the like is damaged by this vertical impact, or the coil spring 118 is displaced from the shell-side snubber 115 or the compressor-side snubber 117. Can be prevented.

  In the first embodiment of the present invention, the ratio of the outer diameter of the head 137 to the outer diameter of the bottom 140 of the outer peripheral portion 127 of the compressor-side snubber 117 is the above design, and the The axial height dimension (H) to the portion 137 is set to be in the range of 50 to 70% of the outer diameter dimension of the bottom portion 140, and specifically, the axial height dimension (H) is designed in the range of 11 to 13 mm. The axial height of the protrusion 150 is designed to be about 60% of the axial height dimension (H) from the bottom 140 to the head 137.

  With the above design, the elastic support device 105 is not increased in size in the axial direction, the effect of suppressing the rotational swing of the electric compression element 104, the effect of suppressing the noise associated with the sliding of the compressor side snubber 117 and the coil spring 118, and The effect of reducing vibration by the coil spring 118 during operation can be obtained with sufficient balance.

The spring constant of the spring characteristic with respect to the displacement in the rotational direction of the coil spring 118 is 2 to 5N.
Since the spring constant is set within the range of / mm, the spring constant during normal operation is relatively soft, but the spring constant can be hardened at the time of stop so that the maximum amount of rotation swing can be reduced. As a result, the hermetic compressor can be operated at a lower speed.

  Therefore, since the hermetic compressor can be operated at a lower rotation, the power consumption as the refrigerator can be reduced.

  In addition, since the compression chamber 148 has a large volume exceeding 10 cc, the compression load immediately before the stop is large, so the brake torque also increases. However, the spring constant of the coil spring 118 at the stop increases, so the maximum rotational swing amount decreases. To do.

  Therefore, a highly reliable hermetic compressor with low vibration can be provided.

  Moreover, the number of parts can be reduced by forming the compressor side snubber 117 with the head of the fastening bolt 157 which fastens the compression element 103 and the electric element 102.

  Therefore, an inexpensive hermetic compressor can be provided.

  Further, since the shape in the longitudinal section of the head portion 137 of the compressor-side snubber 117 and the connecting portion 147 of the outer peripheral portion 127 is an R shape that is ½ or more of the wire diameter of the coil spring 118, the compressor is more effective than the wire diameter of the coil spring 118. R of the connecting portion 147 of the head portion 137 of the side snubber 117 and the outer peripheral portion 127 is increased, and the head portion 137 of the compressor side snubber 117 can be prevented from being damaged by the rotation and oscillation at the time of stopping.

  Therefore, a highly reliable hermetic compressor can be provided.

  As described above, the hermetic compressor according to the present invention provides a hermetic compressor in which the force generated in the internal piping is reduced even when the load is high, and the amount of rotational oscillation during the stop is reduced. Therefore, it can also be applied to high-load business use and air-conditioning applications.

1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. Top view of hermetic compressor in the same embodiment The principal part expanded sectional view of the hermetic compressor in the embodiment Operation explanatory diagram of hermetic compressor in the same embodiment Spring characteristic diagram of coil spring of hermetic compressor in the same embodiment Vertical section of a conventional hermetic compressor Top view of a conventional hermetic compressor Main section enlarged sectional view of a conventional hermetic compressor Operation explanatory diagram of a conventional hermetic compressor

DESCRIPTION OF SYMBOLS 101 Airtight container 102 Electric element 103 Compression element 104 Electric compression element 114 Piston 115 Shell side snubber 117 Compressor side snubber 118 Coil spring 127 Outer periphery 137 Head 140 Bottom part 148 Compression chamber 157 Fastening bolt

Claims (7)

An electric compression element including a hermetic container, a piston that is housed in the hermetic container and reciprocates in a compression chamber, and a coil spring having tightly wound portions at both ends that elastically support the electric compression element; Are inserted at both ends into a shell-side snubber that is a protrusion provided on the closed container side and a compressor-side snubber provided on the electric compression element side, and the outer peripheral portion of the compressor-side snubber is at least partially Is formed with a predetermined curved surface whose outer diameter decreases from the bottom to the head, and the ratio of the outer diameter of the head to the outer diameter of the bottom is in the range of 90 to 97%. Mold compressor. The hermetic compressor according to claim 1, wherein the outer peripheral portion of the compressor-side snubber is a curved surface having an R shape in a longitudinal section. The coil spring has a spring characteristic that restrains the rotation of the electric compression element in a state where the electric compression element is elastically supported, and the spring constant of the spring characteristic with respect to the displacement in the rotation direction of the electric compression element is 2 to 5N. 3. The hermetic compressor according to claim 1, wherein the hermetic compressor is within a range of / mm. The hermetic compressor according to any one of claims 1 to 3, wherein the electric compression element is operated at a plurality of rotation speeds including a rotation speed less than a commercial power supply frequency. The hermetic compressor according to any one of claims 1 to 4, wherein the compression chamber has a volume exceeding 10 cc. The hermetic compression according to any one of claims 1 to 5, wherein the compressor-side snubber head has the same shape as a head of a fastening bolt that fastens the compression element and the electric element constituting the electric compression element. Machine. The hermetic compression according to any one of claims 1 to 6, wherein a connecting portion between the head portion and the outer peripheral portion of the compressor-side snubber has an R shape in which a shape in a longitudinal section is ½ or more of a wire diameter of a coil spring. Machine.

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