JP2012102612A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To overcome a problem that, in order to provide an appropriate supply amount of a lubricating oil in compressing the oil down to a supercritical pressure using a carbon dioxide refrigerant, an oil outlet needs to be arranged at a position where the oil outlet covers less than 50% of the total area in its maxim area opening from an annular seal member to a back pressure chamber side, however the tip of a slanted cut part of the annular seal member is caught with the oil outlet to be broken when the oil outlet crosses the annular seal member during the operation of a compressor.SOLUTION: The oil inlet of an oil supply passage is disposed at a position where the oil inlet opens in a high pressure space, and the oil outlet of the oil supply passage is disposed at a position where the oil outlet reciprocates across the annular seal member through a turning operation of a turning spiral member to open alternately in a high pressure space and an intermediate pressure space and to cover less than 50% of the total area in the maximum area opening in the intermediate space, wherein the direction of the outer circumferential end of the slanted cut part of the annular seal member is aligned with the turning direction when the oil outlet crosses the annual seal member.

Description

  The present invention relates to a technology for supplying an appropriate amount of lubricating oil for a scroll compressor used in a refrigeration cycle apparatus or the like to a compression space, and uses a refrigerant having a high discharge pressure, for example, carbon dioxide (hereinafter, carbon dioxide) as a refrigerant. The present invention relates to a scroll compressor.

  Scroll compressors are popular because they have low vibration and low noise characteristics, and the flow of compressed fluid is unidirectional, so the fluid resistance during high-speed operation is small and the compression efficiency is high. As a conventional scroll compressor, the one configured in FIG. 4 is known. That is, the scroll compressor 55 is configured to include the hermetic container 1, the compression mechanism portion 2 and the electric motor 3 disposed therein, and the electric motor 3 includes the stator 4 and the rotor 5. is doing.

  The compression mechanism unit 2 meshes the fixed spiral member 10 and the swirl spiral member 11 to form a plurality of compression spaces 31, and the swirl spiral member 11 that is swung by the crankshaft 9 at the tip of the drive shaft 6 is compressed. By moving the space 31 toward the center of the spiral and gradually reducing its volume, the refrigerant gas for air conditioning is sucked and compressed.

  On the opposite side of the swirl spiral member 11 from the swirl spiral blade surface, the bearing member 7 constituting a part of the compression mechanism 2, the swivel bearing 13 fixed to the bearing member 7, and the bearing 8 are lubricated and cooled. An upper lubricating oil reservoir 21 and a lubricating oil reservoir 22 are provided. On the other hand, a back pressure chamber 28 in which a rotation restraint component 12 for preventing the rotation of the swirling spiral member 11 is provided, and the back pressure chamber 28 is an annular seal member 25 having an oblique cut portion 25a, and an upper lubricating oil reservoir 21. And communicated with the upper lubricating oil reservoir 21 through an oil supply passage 37.

  The oil inlet portion 37a of the oil supply passage 37 is disposed at a position that opens to the upper lubricating oil reservoir 21, and the oil outlet portion 38a of the oil supply passage 37 is reciprocated across the annular seal member 25 by the revolving motion of the swirl spiral member 11. The upper lubricating oil reservoir 21 and the back pressure chamber 28 are alternately opened.

  The lubricating oil in the upper lubricating oil reservoir 21 is configured such that the hole size of the oil outlet portion 38a of the oil supply passage 37 is 1.0 to 2.0 mm and intermittently straddles the annular sealing member 25 over the annular sealing member 25. 21 and the back pressure chamber 28 are alternately opened, an appropriate amount of lubricating oil is supplied from the upper lubricating oil reservoir 21 as the high pressure space to the back pressure chamber 28 as the intermediate pressure space to lubricate the rotation restraint component 12. ing.

  Further, the lubricating oil is supplied from the back pressure chamber 28 to the suction space 32 and the compression space 31 as the low pressure space via the pressure adjusting mechanism 33, and prevents the leakage of refrigerant gas and the like during compression, and the fixed spiral member 10 The sliding surface of the swirl spiral member 11 is lubricated (see, for example, Patent Document 1).

JP 2004-19499 A

However, in the conventional scroll compressor oiling configuration, the oil outlet is located on the side of the back pressure chamber from the annular seal member in order to supply an appropriate amount of lubricating oil when compressed to supercritical pressure using a carbon dioxide refrigerant. However, when the oil outlet crosses the annular seal member during operation of the compressor, the tip of the oblique cut portion of the annular seal member is There was a problem that the oil outlet part was caught and damaged. An object of the present invention is to provide a highly reliable scroll compressor because an oblique cut portion of an annular seal portion is not caught by an oil outlet portion.

  In order to solve the above-described problems, a scroll compressor according to the present invention includes a swirl swirl member that sucks refrigerant gas into a compression space formed by meshing with a fixed swirl member and compresses the refrigerant gas to a discharge pressure by swirling motion, and the swirl swirl member A bearing member provided on the side opposite to the blade surface, a high-pressure space in which the lubricating oil is accumulated in the center of the bearing member, an intermediate pressure space located inside the outer periphery of the bearing member, and a high-pressure space and an intermediate pressure space are partitioned And a scroll compressor that supplies lubricating oil using an oil supply passage provided in the swirl spiral member. The oil inlet portion of the oil supply passage is alternately opened to a high-pressure space and an intermediate-pressure space, and also to an intermediate-pressure space. The maximum opening area is arranged at a position that is 50% or less of the total area, and the direction of the outer peripheral end of the oblique cut portion of the annular seal member is the direction of the turning motion when the oil outlet portion straddles the annular seal member. One in which was Itasa.

  As described above, in the scroll compressor of the present invention, the oil inlet portion of the oil supply passage is disposed at a position that opens to the high-pressure space, and the oil outlet portion of the oil supply passage is moved by the swirling motion of the swirl spiral member. It reciprocates across and opens alternately to the high-pressure space and the intermediate-pressure space, and is arranged at a position where the maximum area opened to the intermediate-pressure space is 50% or less of the total area, and the outer peripheral end of the oblique cut portion of the annular seal member Since the outer peripheral end of the oblique cut portion of the annular seal member is not caught by the oil outlet portion by making the direction of the oil flow coincide with the turning motion direction when the oil outlet portion straddles the annular seal member, a highly reliable scroll compressor Is obtained.

Sectional drawing which shows the scroll compressor in Embodiment 1 of this invention The figure which shows the positional relationship accompanying the turning motion of the turning spiral member of the oil supply channel | path and the annular seal member in Embodiment 1 of this invention. The figure which shows the positional relationship of the diagonal cut part of the cyclic | annular seal member by this invention, and the turning locus | trajectory of the oil outlet part center. Sectional view showing a conventional scroll compressor

  According to a first aspect of the present invention, a refrigerant gas is introduced into a compression space formed by meshing a swirl spiral blade and a fixed spiral blade having a fixed spiral member having a fixed spiral blade and a fixed mirror plate, a swirl spiral blade and a swirl mirror plate. A swirling spiral member that sucks and compresses to the discharge pressure by a swirling motion, a bearing member provided on the anti-blade surface side of the swirling spiral member, and a high-pressure space that is located inside the center of the bearing member and accumulates lubricating oil under the discharge pressure An intermediate pressure space located inside the outer periphery of the bearing member, an annular seal member that partitions the high pressure space and the intermediate pressure space, and an oil supply passage provided in the swirl spiral member, and using the oil supply passage, The present invention relates to a scroll compressor that supplies lubricating oil by a pressure difference between a space and an intermediate pressure space.

  And this invention arrange | positions the oil inlet part of the said oil supply path in the position opened to the said high voltage | pressure space, and reciprocates the oil outlet part of an oil supply path across the annular seal member by the revolving motion of the swirl spiral member. The space is opened alternately in the space and the intermediate pressure space, and the maximum area opened in the intermediate pressure space is arranged at a position that is 50% or less of the total area, and the direction of the outer peripheral end of the oblique cut portion of the annular seal member is the oil outlet portion. Is made to coincide with the turning motion direction when straddling the annular seal member.

  According to this embodiment, when the oil outlet portion straddles the annular seal member during operation of the compressor, the tip of the oblique cut portion of the annular seal member is not caught by the oil outlet portion, so that the scroll compression is highly reliable. Machine can be provided.

  The second invention is a scroll compressor according to the first invention, wherein carbon dioxide is used as a refrigerant gas and the compressor is compressed to a supercritical pressure. When carbon dioxide is used as the refrigerant gas, the pressing load on the seal surface of the annular seal portion increases, but since the oblique cut portion does not catch on the oil outlet portion, a highly reliable scroll compressor can be provided.

(Embodiment 1)
FIG. 1 is a cross-sectional view showing a scroll compressor according to an embodiment of the present invention. In the illustrated scroll compressor 50, a compression mechanism section 2 and an electric motor 3 are disposed inside the sealed container 1. The compression mechanism unit 2 is provided on the opposite side of the swirl swirl blade surface of the swirl swirl member 11, the swirl swirl member 11 having the swirl swirl blade and the swirl end plate, and the fixed swirl member 10 having the fixed swirl blade and the fixed end plate. It is comprised from the bearing member 7 graded.

  The electric motor 3 includes a stator 4 fixed inside the hermetic container 1 and a rotor 5 rotatably supported inside the stator 4, and a drive shaft 6 is coupled to the rotor 5 in a through state. ing. One end of the drive shaft 6 is rotatably supported by a bearing 8 of a bearing member 7 constituting a part of the compression mechanism portion 2. A crankshaft 9 that performs an eccentric motion with respect to the drive shaft 6 is provided at the tip of the drive shaft 6 supported by the bearing 8.

  On the other hand, the plurality of compression spaces 31 are formed by meshing the fixed spiral blades of the fixed spiral member 10 and the swirl spiral blades of the swirl spiral member 11.

  The rotation spiral member 11 is prevented from rotating by the rotation restraint component 12, and the rotation spiral member 11 only performs the rotation motion via the rotation bearing 13 by the crankshaft 9. The swirling spiral member 11 moves in the compression space 31 while gradually decreasing the volume toward the center of the spiral, and sucks, for example, carbon dioxide gas as a refrigerant gas from the suction pipe 45 through the suction port 14 and compresses it toward the center. .

  The carbon dioxide gas raised to the discharge pressure is discharged from the discharge pipe 46 through the discharge port 15 and the container internal space 16.

  Further, the other end side of the drive shaft 6 is supported by a bottom bearing 17, and a positive displacement pump 18 is provided at the tip thereof. Lubricating oil collected in a bottom lubricating oil reservoir 19 provided at the lower part of the sealed container 1 passes through an oil supply path 20 provided at the center of the drive shaft 6 by a positive displacement pump 18 and is supplied to the upper part of the crankshaft 9. It is supplied to the upper lubricating oil reservoir 21. The lubricating oil lubricates and cools the slewing bearing 13, and then accumulates in a lubricating oil reservoir 22 provided at a position inside the center of the bearing member 7, lubricates the bearing 8 through the lubricating oil reservoir 22, and collects the bottom lubricating oil reservoir. Return to 19.

  The lower surface of the swivel end plate 23 constituting a part of the swirl spiral member 11 is separated from the inner upper surface 24 of the bearing member 7 with a predetermined gap, and is provided in the inner upper surface 24 (groove) of the bearing member 7. Sealed by an annular seal member 25. That is, the bearing member 7 includes the swirl spiral member 11 in a separated state having a gap that enables a swivel motion.

The bearing member 7 is provided with a recess 26, and the rotation restraint component 12 is disposed. Further, a back pressure chamber 28 formed by the fixed end plate 27 of the fixed spiral member 10, the swivel end plate 23, and the bearing member 7 is provided at a position inside the outer periphery of the bearing member 7. The lubricating oil reservoir 22 and the back pressure chamber 28 are configured to be able to communicate with each other by an oil supply passage (the vertical hole 38 and the horizontal hole 37) provided inside the swirl spiral member 11 (the swivel end plate 23).

  The high pressure space communicating with the lubricating oil reservoir 22 having the predetermined gap and the intermediate pressure space communicating with the back pressure chamber 28 are partitioned by an annular seal member 25. The annular seal member 25 is provided with an oblique cut portion 25a to cope with thermal expansion during the operation of the compressor, and the oil outlet portion 38a at the open end of the vertical hole 38 straddles the annular seal member in the direction of the outer peripheral end of the oblique cut portion. It is made to correspond to the turning motion direction.

  Further, the container internal space 16 and the lubricating oil reservoir 22 and the upper lubricating oil reservoir 21 communicate with each other via the bearing 8 and the swivel bearing 13, and the lubricating oil reservoir 22 and the upper lubricating oil reservoir 21 are substantially the same as the discharge pressure. A high-pressure space under pressure is formed, and the recess 26 and the back pressure chamber 28 form an intermediate pressure space.

  That is, a part of the lubricating oil supplied to the lubricating oil reservoir 22 is supplied to the recess 26 and the back pressure chamber 28 while being reduced to an intermediate pressure via an oil supply passage (vertical hole 38 and horizontal hole 37) having a throttling effect. Thus, the rotation restraint component 12 and the like disposed in the recess 26 are lubricated.

  In other words, in the scroll compressor of the present embodiment, the lubricating oil is supplied through the oil supply passage by using the first differential pressure between the discharge pressure and the intermediate pressure, that is, by the pressure difference between the high pressure space and the intermediate pressure space. ing.

  As the lubricating oil supplied to the back pressure chamber 28 accumulates, the pressure in the back pressure chamber 28 increases. In order to keep the pressure in the back pressure chamber 28 constant, a pressure adjustment mechanism 33 is provided between the back pressure chamber 28 that forms the intermediate pressure space and the suction space 32 that forms the low pressure space of the compression space 31. . When the pressure in the back pressure chamber 28 becomes higher than the set pressure, the pressure adjusting mechanism 33 is activated, and the lubricating oil in the back pressure chamber 28 is supplied to the suction space 32, and the pressure in the back pressure chamber 28 is substantially constant. To be kept.

  That is, the lubricating oil supplied to the back pressure chamber 28 as the intermediate pressure space is supplied to the suction space 32 as the low pressure space through the second oil supply passage including the pressure adjusting mechanism 33. In other words, the lubricating oil in the intermediate pressure space is pumped to the low pressure space through the second oil supply passage by the second differential pressure between the intermediate pressure and the suction pressure.

  The lubricating oil supplied to the suction space 32 is guided to the compression space 31 to prevent leakage of refrigerant gas and the like during compression and to seal, and the fixed swirl member 10, the swirl swirl member 11, the bearing member 7 and the like. It plays the role of lubricating the sliding surface.

  The discharge pressure of the compressor and lubricating oil reservoir 22, the intermediate pressure of the back pressure chamber 28, and the suction pressure of the suction space 32 are set as appropriate. In particular, the pressure in the back pressure chamber 28 causes the swirling spiral member 11 to be fixed to the fixed spiral member 10. In order to press, the pressure is set higher than the pressure in the suction space 32 by a predetermined pressure.

  In order to obtain a predetermined pressure, the pressure adjusting mechanism 33 adjusts the dimensions of the vertical hole 38 and the horizontal hole 37 that have a throttle effect that allows the lubricating oil reservoir 22 and the back pressure chamber 28 to communicate with each other.

  By the way, the back pressure for pressing the swirl spiral member 11 against the fixed spiral member 10 is the above-mentioned second differential pressure, but if this back pressure increases, it will lead to abnormal wear of the sliding portion and increase in friction loss. It is not preferable to increase the second differential pressure. That is, the back pressure is set to an appropriate value and is always kept constant.

  On the other hand, when the discharge pressure increases, the overall differential pressure (difference between the discharge pressure and the suction pressure) increases. Therefore, if the second differential pressure is a constant value, the first differential pressure increases. Therefore, in the case of a carbon dioxide refrigerant in which the first differential pressure is excessive, refueling is particularly excessive. Intermittent oil supply by the oil supply passage of the present invention effectively acts on this excessive oil supply, and this will be described below.

  FIG. 2 is a plan view showing a change in the positional relationship of the vertical hole 38 and the annular seal member 25 with one swivel movement of the swirl spiral member, and shows a state where the swivel end plate 23 of the swirl swirl member 11 is viewed from the lower surface side. ing.

  In the figure, the outermost circle represents the outer circumferential line 35 of the bearing member 7 as an outer wall surrounding the back pressure chamber 28, the central circle represents the oil supply path 20 provided in the drive shaft 6, and The annular seal member 25 is indicated by two alternate long and short dash lines between the circle and the circle at the center.

  Furthermore, an oil inlet portion 37a and an oil outlet portion 38a serving as an oil supply passage provided in the rotating end plate 23 and provided in the turning end plate 23 and provided in the rotating end plate 23 and communicating with the lubricating oil reservoir 22 and the back pressure chamber 28 are provided. The flange 36 of the swirl spiral member 11 holding the swivel bearing 13 is shown.

  The figure shows the relative positional relationship between the oil outlet 38 a serving as the open end of the vertical hole 38 and the annular seal member 25 provided on the bearing member 7 with respect to the swiveling motion of the swirling spiral member 11.

  That is, as shown by the arrows in the order of “a” to “d” in FIG. 2, the swirl spiral member 11 swirls in a state of being eccentric with respect to the outer circumferential line 35 of the back pressure chamber 28. At this time, the inner peripheral portion of the annular seal member 25 forms a high pressure space, and the outer peripheral portion forms an intermediate pressure space.

  Therefore, only when the oil outlet portion 38 a of the vertical hole 38 is positioned on the outer peripheral portion of the annular seal member 25, the lubricating oil reservoir 22 in the high pressure space and the back pressure chamber 28 that is the intermediate pressure space are communicated, and the lubricating oil reservoir 22 is lubricated. Oil is supplied to the back pressure chamber 28 from the oil outlet 38a.

  Therefore, the lubricating oil can be supplied only when the oil outlet portion 38a in the state of FIG. 2b opens to the intermediate pressure space. In other words, the oil outlet portion 38a reciprocates across the annular seal member 25 during the turning motion, and is disposed at a position where 50% or less of the area of the oil outlet portion 38a is opened in the intermediate pressure space.

  Further, the direction of the outer peripheral end of the oblique cut portion 25 a of the annular seal member 25 is made to coincide with the swivel movement direction of the swirl spiral member 11. Therefore, a highly reliable scroll compressor can be provided without the outer peripheral end of the oblique cut portion 25a of the annular seal member 25 being caught by the oil outlet portion 38a during the compressor operation.

  As described above, the scroll compressor according to the present invention can obtain a highly reliable scroll compressor because the outer peripheral end of the oblique cut portion of the annular seal member is not caught by the oil outlet portion. The present invention can also be applied to equipment using a heat pump such as an air conditioner, a dehumidifier, or a water heater.

7 Bearing member 10 Fixed spiral member 11 Swirl spiral member 20 Oil supply path 25 Annular seal member 25a Diagonal cut portion 38a Oil outlet portion 31 Compression space

Claims (2)

A fixed spiral member in which fixed spiral blades are erected on a fixed spiral end plate;
A swirl swirl member in which a swirl swirl blade that is engaged with the fixed swirl blade to form a compression chamber is erected on a swirl end plate;
A bearing member that is disposed on the side of the swirl spiral member opposite to the compression chamber and supports the swirl spiral member;
An annular seal member that is disposed in a space formed by the swirl spiral member and the bearing member, and divides the space into an inner peripheral high-pressure space and an outer peripheral intermediate pressure space;
Provided inside the swivel end plate, the oil inlet portion opens into the high pressure space, the oil outlet portion opens alternately to the high pressure space and the intermediate pressure space across the annular seal member by the swirling motion of the swirl spiral member, and An oil supply passage having a maximum area opening to the intermediate pressure space of 50% or less,
The annular seal member has an oblique cut portion at one place in the circumferential direction, and a scroll compressor in which the direction of the outer peripheral end of the oblique cut portion is made to coincide with the turning motion direction when the oil outlet portion straddles the annular seal member. . The scroll compressor according to claim 1, wherein carbon dioxide is used as a refrigerant gas compressed in the compression chamber, and the compressor is compressed to a supercritical pressure.