JP2005264738A - Compressor - Google Patents

Abstract

A highly reliable compressor provided with an oil pump 130 in which a decrease in conveyance amount is small even during low-speed operation.
An oil pump includes a shaft having a lower end extending vertically into oil and rotating, and an oil pump formed at the lower end of the shaft. The oil pump is a cylinder formed at the lower end of the shaft. A hollow portion and a shaft 117 are coaxially supported and rotatably disposed in the cylindrical cavity portion, and the shaft 117 is coaxially supported and an oil lifting means 132 which rotates coaxially with the shaft 117, and the cylindrical hollow portion and the sleeve By providing the oil seal means between them, the leakage from the oil passage can be reduced, the amount of oil transported to the compression element 110 can be secured, and a highly reliable compressor can be provided. .
[Selection] Figure 1

Description

  The present invention relates to an improvement of an oil pump that supplies oil to a sliding portion of a compressor.

  In recent years, due to demands for the global environment, household refrigerator-freezers and air conditioners have been increasingly moved toward energy saving. Under such circumstances, the compressor has been converted into an inverter, and the operation speed has been reduced at a low speed. With conventional centrifugal pumps, it has become difficult to supply sufficient oil to the sliding parts constituting the compressor.

  Conventionally, as this type of compressor, there is a compressor provided with a viscous pump that can easily obtain a stable pumping capacity even at a low speed, instead of a centrifugal pump (see, for example, Patent Document 1).

  The conventional compressor will be described below with reference to the drawings. In the following description, the upper and lower relationships are based on a state where the compressor is installed in a normal posture.

  FIG. 7 is a cross-sectional view of a conventional compressor described in Patent Document 1. FIG. 8 is an enlarged view of a main part of a conventional compressor.

  7 and 8, oil 1 is stored at the bottom of a sealed container (not shown). The electric element 5 includes a stator 6 and a rotor 7.

  A rotor 7 is fitted to a shaft 10 provided in a compression element (not shown), and at least a lower end is immersed in the oil 1 and a cylindrical extension 15 that rotates coaxially with the shaft 10 is fixed. ing.

  A spiral groove 16 is formed in the cylindrical extension 15 so that the oil 1 rises as the shaft 10 rotates, and a sleeve 21 is disposed in the cylindrical cavity 20 formed at the lower end of the shaft 10. ing. The sleeve 21 has a slight gap in the axial direction of the shaft 10 between the cylindrical cavities 20, includes a spiral groove 16 of the cylindrical extension 15, and is constrained in the rotational direction by an arm 22 fixed to the stator 6. Has been.

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

When the electric element 5 is energized, the rotor 7 rotates, and the shaft 10 rotates accordingly, and the compression element (not shown) performs a predetermined operation. The oil 1 is viscously dragged by the spiral groove 16 in the oil passage 23 formed between the spiral groove 16 formed in the cylindrical extension 15 and the sleeve 21 as the cylindrical extension 15 rotates. Is rotated up and pumped up to the upper part of the shaft 10. Since the oil 1 does not depend only on the centrifugal force whose force decreases at low speed rotation, but rises by the force dragged viscously, the oil 1 is pumped up even at low speed rotation.
WO 93/22557 pamphlet

  However, in the above-described conventional configuration, the oil that has risen through the oil passage 23 formed between the cylindrical extension 15 and the sleeve 21 leaks from the gap between the cylindrical cavity 20 and the sleeve 21 at the lower end of the shaft 10, and is conveyed. The amount is reduced. In particular, it has been difficult to supply sufficient oil 1 to the sliding portion constituting the compressor at a low speed rotation, and the sliding portion is worn and the compression element is locked.

  Further, in order to reduce the leak amount of the oil 1 from the cylindrical cavity 20 and the sleeve 21 at the lower end of the shaft 10, in order to reduce the gap between the cylindrical cavity 20 and the sleeve 21, processing with high accuracy or high There was a problem that it was necessary to assemble with accuracy and the cost of the compressor would be high.

  SUMMARY OF THE INVENTION The present invention solves the above-described conventional problems, and an object of the present invention is to provide a highly reliable compressor including an oil pump that can prevent a decrease in the amount of oil conveyed due to leakage even at low speed rotation.

  In order to solve the above-described conventional problems, a compressor according to the present invention includes an oil pump having a cylindrical cavity, a sleeve, and an oil head at the lower end of the shaft, and an oil seal means between the cylindrical cavity and the sleeve. Therefore, the oil seal means prevents oil leakage from between the cylindrical cavity and the sleeve, ensures a sufficient amount of oil transport even at low speed rotation, and supplies oil to the sliding parts constituting the compressor. It has the effect of becoming possible.

  The compressor of the present invention can provide a highly reliable compressor that prevents a decrease in the amount of oil transport, secures oil supply to the sliding parts that constitute the compressor even at low speed rotation.

  According to the first aspect of the present invention, oil is stored in a sealed container and a compression element driven by an electric element composed of a stator and a rotor is accommodated, and the lower end of the compression element extends vertically into the oil. A rotating shaft, and an oil pump formed at the lower end of the shaft. The oil pump is supported at the lower end of the shaft and is coaxially supported by the shaft and rotates to the cylindrical cavity. A sleeve provided freely, and an oil lifting means included in the sleeve and rotating together with the shaft, and an oil seal means is provided between the cylindrical cavity and the sleeve. Since oil leakage from the oil passage can be reduced, the amount of oil transported to the compression element is secured and a highly reliable compressor is secured. An effect that can be provided is obtained.

  According to a second aspect of the present invention, in the first aspect of the present invention, the oil seal means is a spiral passage formed between the shaft and the sleeve so that the oil rises as the shaft rotates. Therefore, in the gap between the cylindrical cavity and the sleeve, the oil rises due to the rotation of the shaft against the oil trying to leak due to its own weight. The oil leakage between the cylindrical cavity and the sleeve can be prevented more reliably, and an effect that a highly reliable compressor can be provided can be obtained.

  According to a third aspect of the present invention, in the invention of the first or second aspect, the oil lift means is formed in the cylindrical cavity, and the wing is formed in a direction in which the oil rises as the shaft rotates. In addition to the effect of the invention according to claim 1, in addition to the effect of the invention according to claim 1, a large amount of oil can be supplied to the compression element in a short time. The effect that a highly reliable compressor can be provided is obtained.

  According to a fourth aspect of the present invention, in the first or second aspect of the invention, the oil lift means includes a cylindrical extension projecting below the shaft, and the cylinder extension between the cylindrical extension and the sleeve. A helical passage formed in a direction in which the oil ascends as the shaft rotates. In addition to the effect of the invention according to claim 1 or 2, the compression element can be reliably compressed even at a low rotational speed by forming a viscous pump. The effect that the oil can be supplied to and a highly reliable compressor can be provided is obtained.

  The invention according to claim 5 is the invention according to claim 4, wherein the guide blades in the vertical direction are formed on the upper part of the oil lift means of the sleeve, and the relative rotation difference between the screw and the oil is reduced. In addition to the effect of the invention according to claim 4, the amount of oil transported to the compression element portion can be increased, and an effect that a highly reliable compressor can be provided is obtained. .

  The invention according to claim 6 is driven at an operation frequency including at least an operation frequency of 600 to 1200 r / min in the invention according to claims 1 to 5, and according to claims 1 to 5. In addition to the effect of the present invention, the compressor input can be kept small, and coupled with the stable oil supply, low power consumption can be obtained, and a highly reliable compressor can be provided.

  According to a seventh aspect of the present invention, in the first to sixth aspects of the invention, the arm is fixed to the stator and restrains and supports the sleeve in the rotational direction, and the sleeve rotates during the operation of the compression element. In addition to the effects of the invention according to claims 1 to 6, in addition to the effects of the invention according to claims 1 to 6, the sleeve does not rotate, thereby reducing the oil conveyance amount that raises the spiral passage between the sleeve and the shaft. Therefore, a highly reliable compressor can be provided.

  The invention according to claim 8 is the invention according to claims 1 to 7, wherein the compression element is elastically supported in the hermetic container, and the components are integrated with the compression element. Since it is not necessary to attach components to the sealed container, in addition to the effects of the inventions according to claims 1 to 7, the effect that a compressor with good assemblability can be provided is obtained.

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

(Embodiment 1)
FIG. 1 is a cross-sectional view of a compressor according to Embodiment 1 of the present invention. 2 and 3 are enlarged views of the main part in the same embodiment.

  Hereinafter, the present embodiment will be described with reference to FIGS. 1, 2, and 3.

  1, 2, and 3, the sealed container 100 stores oil 101 and is filled with a refrigerant gas 102.

  The compression element 110 includes a block 112 that forms a cylinder 111, a piston 113 that is reciprocally fitted in the cylinder 111, and a shaft that includes a main shaft portion 115 and an eccentric portion 116 that are pivotally supported by a bearing portion 114 of the block 112. 117, a connecting rod 118 that connects the eccentric portion 116 and the piston 113, and forms a reciprocating compression mechanism.

  The electric element 120 includes a stator 121 fixed below the block 112 and connected to an inverter drive circuit (not shown), and a rotor 122 containing a permanent magnet (not shown) and fixed to the main shaft 115. The inverter drive circuit is driven at a plurality of operation frequencies including an operation frequency lower than 1200 r / min, for example.

  An oil pump 130 immersed in the oil 101 is formed at the lower end of the main shaft portion 115 of the shaft 117.

  The spring 125 elastically supports the compression element 110 in which the oil pump 101 is integrated with the hermetic container 100 via the stator 126.

  Next, the configuration of the oil pump 130 will be described in detail.

  The main shaft portion 115 is provided with a cylindrical cavity portion 131 below it, and is disposed so as to include a screw 133 as an oil lifting means 132 at the tip of an extension projecting downward. The wing part 134 of the screw 133 is disposed so as to push the 101 upward.

  Further, a plurality of guide vanes 142 are provided in the longitudinal direction above the screw 133 inside the sleeve 141. The inner diameter of the cylindrical cavity 131 of the main shaft 115 and the outer diameter of the spiral groove 140 formed in the sleeve 141 provide a clearance of about 0.1 mm to 1 mm in diameter.

  An oil hole 136 communicating with the sliding portion 135 formed by the main shaft portion 115 and the bearing portion 114 is provided inside the main shaft portion 115 along the axial center direction, and is communicated with the cylindrical cavity portion 131.

  In addition, by inserting a sleeve 141 in which a spiral groove 140 is formed on the outer periphery in a direction in which the oil 101 is raised by the rotation of the main shaft portion 115 in the cylindrical cavity 131 below the main shaft portion 115, a spiral passage as the oil seal means 147 is formed. 148 is formed.

  The arms 143 whose both ends are fixed to the stator 121 are engaged with a notch 144 provided below the sleeve 141 at the center portion, and function as rotation suppression means by supporting the sleeve 141 in a non-rotatable manner.

  About the compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  When the stator 121 is energized by an inverter drive circuit (not shown), the rotor 122 rotates together with the shaft 117. Accordingly, the eccentric motion of the eccentric portion 116 causes the piston 113 to reciprocate in the cylinder 111 via the connecting rod 118 to perform a predetermined compression operation for compressing the suction gas.

  As the shaft 117 rotates, the main shaft 115 rotates, and the screw 133 rotates in the sleeve 141 that is non-rotatably supported by the arm 143. As the screw 133 rotates, the oil 101 is given a thrust in a direction perpendicular to the rotation surface, and rises in the sleeve 141, passes through the oil hole 136, and moves to the sliding portion 135 formed by the bearing portion 114 and the main shaft portion 115. Reach and lubricate.

  At this time, the oil 101 also rotates in the rotational direction about the axis by the rotation of the screw 133, but the oil 101 is centered by the plurality of guide blades 142 provided on the sleeve 141 provided above the screw 133. The rotation of the is suppressed. As a result, the relative speed between the oil 101 and the screw 133 is generated, and the shearing force between the wing part 134 of the screw 133 and the oil 101 is increased, so that the thrust applied to the oil 101 is increased, and in a shorter time. A large amount of oil 101 can be supplied to the sliding portion 135 formed by the bearing portion 114 and the main shaft portion 115.

  Furthermore, a spiral passage 148 that is a spiral oil passage formed in a direction in which the oil 101 rises as the shaft 117 rotates is formed between the cylindrical cavity 131 below the main shaft 115 and the sleeve 141. Therefore, the oil 101 rises along the spiral spiral passage 148 when the oil 101 is viscously dragged with the rotation of the cylindrical cavity 131.

  Therefore, the oil does not leak downward due to its own weight from the gap between the cylindrical cavity 131 and the sleeve 141, and leakage can be prevented, and the oil 101 to the sliding portion 135 can be prevented even at low speed rotation where the amount of oil 101 transported is reduced. The effect that the supply amount of can be secured is obtained.

  Further, since the compression element 110 is elastically supported and the sleeve 141 is engaged with the central portion of the arm 143 and is not floating in the cylindrical cavity 131 but is floating, the rotation of the shaft 117 causes the rotation. The oil pressure generated by the oil 101 interposed between the cylindrical cavity 131 and the sleeve 141 works over the entire circumference, so that the sleeve 141 constantly tries to maintain the same axis as the cylindrical cavity 131.

  For this reason, the sleeve 141 always has a slight gap between the cylindrical cavities 131, and hardly causes twisting. Therefore, the sliding wear between the cylindrical cavities 131 and the sleeve 141 is extremely small.

  As a result, wear powder is not generated and circulates through the sliding portion 135 together with the oil 101, and the compression element 110 is not locked by being bitten by the sliding portion 135, and the compressor has high reliability. Could be realized.

(Embodiment 2)
FIG. 4 is a cross-sectional view of the compressor according to the second embodiment of the present invention, and FIGS. 5 and 6 are enlarged views of main parts according to the same embodiment.

  Hereinafter, the present embodiment will be described with reference to FIGS. 4, 5, and 6.

  4, 5, and 6, the airtight container 200 stores oil 201 and is filled with a refrigerant gas 203.

  The compression element 205 includes a block 211 that forms a cylinder 210, a piston 212 that is reciprocally fitted in the cylinder 210, and a shaft that includes a main shaft portion 216 and an eccentric portion 217 that are pivotally supported by a bearing portion 215 of the block 211. 218, an eccentric portion 217, and a connecting rod 219 for connecting the piston 212, and a reciprocating compression mechanism is formed.

  The electric element 225 includes a stator 226 fixed below the block 211 and connected to an inverter drive circuit (not shown), and a rotor 227 containing a permanent magnet (not shown) and fixed to the main shaft portion 216. An electric element for driving the inverter is formed and driven by the inverter driving circuit at a plurality of operating frequencies including an operating frequency lower than 1200 r / min, for example.

  An oil pump 240 immersed in the oil 201 is formed at the lower end of the main shaft portion 216 of the shaft 218.

  The spring 230 elastically supports the compression element 205 in which the oil pump 240 is integrated with the hermetic container 200 via the stator 231.

  Hereinafter, the configuration of the oil pump 240 will be described in detail.

  5 and 6, the oil lift means 260 includes a cylindrical cavity 241 and a spiral groove 243 engraved in a cylindrical extension 242 projecting downward below the main shaft portion 216 of the shaft 218. The hollow portion 241 and the spiral groove 243 form a spiral passage 253 that is an oil passage.

  Then, a sleeve 246 in which a spiral groove 244 is formed in the direction in which the oil 201 ascends due to the rotation of the main shaft portion 216 on the outer periphery is inserted so as to include the cylindrical extension portion 242 of the main shaft portion 216 in the cylindrical cavity portion 241. Yes.

  The gap between the cylindrical extension 242 and the sleeve 246 forms a spiral passage 247 and the gap between the main shaft 216 and the sleeve 246 forms a spiral passage 253 that is an oil seal means 252.

  The outer diameter of the spiral groove 243 engraved in the cylindrical extension 242 and the inner diameter of the sleeve 246, and the outer diameter of the spiral groove 244 of the sleeve 246 and the inner diameter of the cylindrical cavity 241 are 0.1 mm to 1 mm in diameter. Is provided.

  Further, the arm 250 supports the sleeve 246 in a non-rotatable manner by engaging with a notch 251 provided below the sleeve 246 at the center.

  About the compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  When the electric element 225 is energized by the inverter drive circuit (not shown), the rotor 227 rotates with the shaft 218.

  As the shaft 218 rotates, the cylindrical extension 242 rotates in the sleeve 246, and the oil 201 passes through the spiral passage 247 formed between the cylindrical extension 242 and the sleeve 246 to rotate the cylindrical extension 242. Along with this, it is rotationally lifted by being dragged in a viscous manner, passes through an oil hole 255 communicating with the cylindrical cavity 241, reaches the sliding portion 256 formed by the main shaft portion 216 and the bearing portion 215, and lubricates.

  In the present invention, the oil 201 is viscously dragged with the rotation of the cylindrical cavity portion 241 by the helical spiral passage 247 provided between the cylindrical cavity portion 241 and the sleeve 246 below the main shaft portion. Since the oil 201 ascends the spiral passage 247, the oil 201 can be prevented from leaking from the gap between the cylindrical cavity 241 and the sleeve 246 due to its own weight.

  Therefore, no oil leaks even at a low rotational speed, and the oil 201 can be stably supplied to the sliding portion 256.

  Further, the compression element 205 is elastically supported and the sleeve 246 engages the central portion of the arm 250 and floats without rotating between the cylindrical cavity 241 and the cylindrical extension 242. Therefore, the hydraulic pressure generated by the oil 201 interposed between the cylindrical extension 242 and the sleeve 246 works over the entire circumference, so that the sleeve 246 constantly tries to maintain the same axis as the cylindrical extension 242.

  For this reason, a slight gap is secured between the cylindrical extension 242 and the sleeve 246, and almost no twisting occurs. Very few occurrences.

  As a result, wear powder is generated and circulates along with the oil 201 to the sliding portion 256 and is not caught by the sliding portion 256 to lock the compression element 205, so that the compression element 205 can be reliably ensured even at a low rotational speed. The oil 201 can be supplied to the compressor, and a highly reliable compressor can be realized.

  As described above, the compressor according to the present invention is a highly reliable compressor including an oil pump that can sufficiently convey oil even at a low speed. Therefore, a dehumidifier, a showcase, and a vending machine including a household refrigerator are used. It can also be applied to applications using a refrigeration cycle.

Sectional drawing of the compressor in Embodiment 1 of this invention The principal part enlarged view of the compressor in the embodiment The principal part enlarged view of the compressor in the embodiment Sectional drawing of the compressor in Embodiment 2 of this invention The principal part enlarged view of the compressor in the embodiment The principal part enlarged view of the compressor in the embodiment Cross section of a conventional compressor Enlarged view of the main parts of a conventional compressor

Explanation of symbols

100, 200 Airtight container 101, 201 Oil 110, 205 Compression element 117, 218 Shaft 120, 225 Electric element 121, 226 Stator 122, 227 Rotor 130, 240 Oil pump 131, 241 Cylindrical cavity 132, 260 Oil lifting means 133 Screw 134 Wings 141,246 Sleeve 142 Guide vanes 143,250 Arms 147,252 Oil seal means 148,247,253,261 Spiral passage 242 Cylindrical extension

Claims (8)

An oil is stored in a sealed container, and a compression element driven by an electric element composed of a stator and a rotor is accommodated. The compression element has a lower end extending vertically into the oil, and a rotating shaft. An oil pump formed at the lower end, the oil pump being supported by the cylindrical cavity formed at the lower end of the shaft, a sleeve coaxially supported by the shaft, and rotatably disposed in the cylindrical cavity. An oil lift means supported on the same axis and rotating together with the shaft, and an oil seal means provided between the cylindrical cavity and the sleeve. The compressor according to claim 1, wherein the oil seal means is a spiral passage formed between the shaft and the sleeve so that the oil rises as the shaft rotates. 3. The compressor according to claim 1, wherein the oil lift means is formed in the cylindrical cavity portion, and includes a screw having a blade portion formed in a direction in which the oil rises as the shaft rotates. The oil lift means includes a cylindrical extension projecting downward in the cylindrical cavity, and a spiral passage formed in a direction in which oil rises as the shaft rotates between the cylindrical extension and the sleeve. The compressor according to claim 1 or 2. 4. The compressor according to claim 3, wherein a longitudinal guide vane is formed on an upper part of the oil head means of the sleeve. The compressor according to any one of claims 1 to 5, which is driven at an operating frequency including an operating frequency of at least between 600 and 1200 r / min. The compressor according to any one of claims 1 to 6, further comprising an arm fixed to the stator and restraining and supporting the sleeve in the rotational direction. The compressor according to any one of claims 1 to 7, wherein the compression element is elastically supported in the sealed container.

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