JP2018141427A - Hermetic scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve assemblability while suppressing enlarging of a cutout part provided in a stator outer peripheral surface of an electric motor section for passage of an oil drain pipe, and also improve performance.SOLUTION: A hermetic scroll compressor comprises a compression mechanism section having a fixed scroll, an orbiting scroll and a frame, an electric motor section having a stator and a rotor, a closed vessel housing the compression mechanism section and the electric motor section and having an oil sump at a bottom, a driving shaft fixed to the rotor of the electric motor section for driving the orbiting scroll, a main bearing provided on the frame for supporting the driving shaft, and an oil drain pipe for guiding oil lubricating the main bearing to the oil sump. The oil drain pipe has an insertion part inserted into the frame, an oil guide part disposed in a cutout part formed in a stator outer periphery of the electric motor section, and a leading end part having an open end opened at an oil sump side. A leading end width of the leading end part of the oil drain pipe is formed to be smaller than a width of the oil guide part.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a hermetic scroll compressor, and is particularly suitable as a refrigerant compressor used in a refrigeration cycle for refrigeration or air conditioning.

  An example of a hermetic scroll compressor used in a refrigeration cycle for refrigeration or air conditioning is described in Japanese Patent Application Laid-Open No. 2006-97517 (Patent Document 1).

  In this Patent Document 1, the lubricating oil stored in the bottom of the sealed container is sucked up to the refrigerant compression part through the oil guide hole in the drive shaft, and the bearing part that supports the drive shaft and the slide of the refrigerant compression part. After the moving part is lubricated, the compressor is configured to return the lubricating oil to the bottom of the hermetic container via an oil discharge passage provided in the frame of the refrigerant compressor and an oil discharge pipe connected to the oil discharge passage. Is described.

  In addition, a plurality of communication grooves (notch portions having a concave groove shape) communicating the upper space and the lower space of the motor are provided on the outer peripheral surface of the stator (stator) of the motor, and one of these communication grooves is provided. Describes that the pipe support groove for supporting the oil draining pipe is larger than the other communication grooves. Further, it is also described that pipe support portions for supporting a part of the oil drainage pipe are provided at both ends of the stator of the electric motor.

JP 2006-97517 A

  The thing of the said patent document 1 describes making the said pipe support groove (notch part) for letting the said oil drain pipe provided in the stator outer peripheral surface of an electric motor larger than another communicating groove. However, if the notch having a concave groove shape through which the oil drainage pipe is passed is increased, the rigidity of the stator is lowered. That is, the stator is fixed in the closed container by shrink fitting or the like, so that the compressive stress around the notch increases as the notch increases. The stator is composed of an electromagnetic steel plate. However, when compressive stress is applied to the electromagnetic steel plate, the magnetic permeability is lowered and the magnetic resistance is increased, so that the magnetic flux hardly flows. For this reason, there exists a subject that the performance of a scroll compressor falls.

  In particular, when a compressor having the same capacity is miniaturized, the amount of oil supplied to the sliding portion is about the same as before the miniaturization, and therefore the diameter of the oil drain pipe cannot be changed because the flow resistance is not increased. For this reason, the size of the notch through which the oil drainage pipe passes is relatively large with respect to the stator, and the performance degradation of the compressor becomes remarkable.

  Further, in the case where the pipe support portion is provided in the electric motor, the pipe insertion hole formed in the pipe support portion is formed to have a diameter substantially the same as or slightly larger than the outer diameter of the oil discharge pipe. The tolerance for is small. For this reason, when the drainage pipes are inserted into the pipe insertion holes, if the coaxiality thereof is not sufficient, it becomes difficult for the drainage pipes to come into contact with the electric motor, and the compressor cannot be assembled. is there.

  An object of the present invention is to provide a hermetic scroll compression that can improve assembly performance and improve performance while suppressing an increase in a notch for passing an oil drain pipe provided on an outer peripheral surface of a stator of an electric motor section. There is to get a chance.

  In order to solve the above-described problems, the present invention includes a fixed scroll, a turning scroll, and a frame. The compression scroll is formed by combining the fixed scroll and the turning scroll, and the working fluid is moved by turning the turning scroll. A compression mechanism section for compressing, an electric motor section provided with a stator and a rotor for driving the compression mechanism section, a sealed container containing the compression mechanism section and the electric motor section and having an oil sump at the bottom, and an electric motor section A drive shaft fixed to the rotor and rotating and driving the orbiting scroll; a main bearing provided on the frame for supporting the drive shaft; and an oil drain for guiding oil lubricated to the main bearing to the oil sump A hermetic scroll compressor comprising: a pipe; and the oil drain pipe includes an insertion portion that is inserted into the frame, and a plug of the motor portion. A leading end portion having an opening end opened on the oil reservoir side, and a leading end width of the leading end portion of the oil drainage pipe. Is formed smaller than the width of the oil guide portion.

  According to the present invention, hermetic scroll compression that can improve assembly performance and improve performance while suppressing an increase in a notch for passing an oil drain pipe provided on an outer peripheral surface of a stator of an electric motor section. There is an effect that can get a machine.

It is a longitudinal cross-sectional view which shows Example 1 of the hermetic scroll compressor of this invention. FIG. 2 is a horizontal cross-sectional view of the stator portion shown in FIG. 1, showing only the stator and the sealed container, and omitting other configurations. It is principal part sectional drawing of the front-end | tip part vicinity of the oil draining pipe shown in FIG. It is the sectional view on the aa line of FIG. 3A. It is a bottom view of FIG. 3A. FIG. 2 is a view for explaining a state in which an oil drain pipe is inserted into a cutout portion of a stator outer peripheral surface in the assembly of the hermetic scroll compressor shown in FIG. 1. It is principal part sectional drawing of the front-end | tip part vicinity of the drainage pipe in Example 2 of the hermetic scroll compressor of this invention. It is the bb sectional view taken on the line of FIG. 5A. FIG. 5B is a cross-sectional view taken along the line cc of FIG. 5A. It is principal part sectional drawing of the front-end | tip part vicinity of the oil discharge pipe in Example 3 of the hermetic scroll compressor of this invention. It is the dd sectional view taken on the line of FIG. 6A. It is the ee sectional view taken on the line of FIG. 6A. It is principal part sectional drawing of the front-end | tip part vicinity of the oil drainage pipe in Example 4 of the hermetic scroll compressor of this invention. It is the ff sectional view taken on the line of FIG. 7A. It is the g1-g1 sectional view taken on the line of FIG. 7A. It is the g2-g2 sectional view taken on the line of FIG. 7A.

  Hereinafter, specific examples of the hermetic scroll compressor of the present invention will be described with reference to the drawings. In each figure, the part which attached | subjected the same code | symbol has shown the part which is the same or it corresponds.

Example 1 of the hermetic scroll compressor of the present invention will be described with reference to FIGS. 1, 2, 3 </ b> A to 3 </ b> C, and FIG. 4.
FIG. 1 is a longitudinal sectional view showing Embodiment 1 of a hermetic scroll compressor according to the present invention, FIG. 2 is a horizontal sectional view of a stator portion shown in FIG. 1, showing only a stator and a hermetically sealed container, FIG. First, the overall configuration of the hermetic scroll compressor according to the first embodiment will be described with reference to FIGS. 1 and 2.

  A hermetic scroll compressor 1 according to the first embodiment is a refrigerant compressor used in a refrigeration cycle such as a refrigeration apparatus or an air conditioner, and compresses a working fluid such as a refrigerant flowing in the refrigeration cycle, An electric motor unit 3 that drives the compression mechanism unit 2, a closed container 4 that houses the compression mechanism unit 2, the electric motor unit 3, and the like are included. Further, the hermetic scroll compressor 1 of this embodiment is a vertical scroll compressor in which the compression mechanism portion 2 and the electric motor portion 3 are arranged vertically, and an oil sump 12 is formed at the bottom. Has been.

  The compression mechanism unit 2 includes a fixed scroll 5, a turning scroll 6 meshing with the fixed scroll 5, and a frame 7 to which the fixed scroll 5 is fixed. The outer periphery of the frame 7 is fixed to the sealed container 4 by welding.

  The fixed scroll 5 includes an end plate 5a, a spiral wrap 5b erected on the end plate 5a, a suction port 5c provided on the outer peripheral side of the wrap, and a center (end of the end plate) side of the wrap 5b. 5d, and the outer peripheral side of the end plate 5a is fixed to the frame 7 with bolts 10. A suction pipe 14 penetrating the sealed container 4 is connected to the suction port 5 c of the fixed scroll 5.

The orbiting scroll 6 includes an end plate 6a, a spiral wrap 6b erected on the end plate 6a, a boss 6c provided at the center of the rear surface (on the opposite side) of the end plate 6a, and the like. The orbiting scroll 6 is sandwiched between the fixed scroll 5 and the frame 7, and the wrap 5 b of the fixed scroll 5 and the wrap 6 b of the orbiting scroll 6 are combined (engaged) with each other, whereby the compression chamber 11 is formed. Is formed.
The orbiting scroll 6 is configured such that its rotation is prevented by an Oldham ring (spinning prevention mechanism) 9 so as to orbit.

  The Oldham ring 9 is disposed between the rear side of the end plate 6 a of the orbiting scroll 6 and the frame 7, and a key provided on the Oldham ring 9 is a keyway provided on the orbiting scroll 5 and the frame 7. A revolving mechanism for revolving the orbiting scroll 6 is configured.

The electric motor unit 3 constitutes a rotational drive unit that drives the compression mechanism unit 2 via a drive shaft 8, and includes a stator 3a and a rotor 3b.
The stator 3a is attached to the sealed container 4 by means such as shrink fitting, and includes a winding 3aa, laminated steel plates (iron cores) 3ab, and an insulator 23. The outer peripheral surface of the steel plate 3ab is fixed in intimate contact with the inner surface of the sealed container 4. On the outer peripheral surface of the steel plate 3ab, as shown in FIG. Are formed at a plurality of locations. A gap (passage) 26a is formed between the cutout portion 3ac and the sealed container 4, and the refrigerant gas discharged from the discharge port 5d of the fixed scroll 5 passes through the gap 26a. The electric motor unit 3 is configured to be cooled.

  Further, in FIG. 2, 3ad is a groove-shaped notch for arranging the oil guide portion 28b of the oil draining pipe 28 so as to penetrate through the notch 3ad as shown in FIG. Thus, a gap (passage) 26b is formed between the closed container 4 and the airtight container 4. The notch 3ad is formed larger than the notch 3ac through which the above-described refrigerant gas passes. The width of the notch 3ad is the same as that of the other notch 3ac, but the inner circumference is formed in an arc shape in accordance with the shape of the oil drain pipe 28. The width of the arc-shaped portion is formed to be larger than the width of the other notch 3ac.

Note that 3ae shown in FIG. 2 is a tooth around which the winding 3aa is wound, and 3af is a slot in which the winding 3aa is disposed.
Further, the insulator 23 shown in FIG. 1 is made of resin and is attached to the upper end and the lower end of the steel plate 3ab, and the insulator 23 is provided so as not to contact the sealed container 4.

  As shown in FIG. 1, the main shaft portion of the drive shaft 8 is fixed to the rotor 3b by shrink fitting or press fitting at the center thereof, and the rotor 3b and the drive shaft 8 rotate integrally. A crank portion 8 a that performs an eccentric motion is provided at the upper end portion of the drive shaft 8. A revolving bearing 13 is provided on the inner surface of the boss portion 6 c on the back of the orbiting scroll 6, and a crank portion 8 a of the drive shaft 8 is inserted into the orbiting bearing 13. Thereby, the crank part 8a and the orbiting scroll 6 are connected, and the driving shaft 8 rotates to drive the orbiting scroll 6 through the crank part 8a.

  The frame 7 is provided with a main bearing 15 formed of a roller bearing for supporting the drive shaft 8 at the center thereof. A frame seal 16 is detachably attached to the frame 7 so as to hold down the main bearing 15 from below. Thus, the main bearing 15 is covered with the frame seal 16.

  Reference numeral 17 denotes a secondary bearing that supports a portion of the drive shaft 8 below the rotor 3b. The secondary bearing 17 is attached to a lower frame 18 fixed to the inner surface of the hermetic container 4 via a secondary bearing housing 19. Yes. Thus, the drive shaft 8 is supported on both sides of the electric motor unit 3 by the main bearing 15 and the auxiliary bearing 17, and the orbiting scroll 6 is driven via the orbiting bearing 13 by the crank portion 8 a at the upper end. To do.

  The hermetic container 4 includes a body portion 4a, a lid cap 4b fixed over the outer upper portion of the body portion 4a, and a bottom cap 4c fixed over the outer lower portion of the body portion 4a. The frame 7 and the lower frame 18 are fixed to the body 4a by welding. Further, a discharge pipe 22 is provided in the body portion 4 a of the sealed container 4 so as to communicate with a space between the frame 7 and the electric motor unit 3 (an upper space of the electric motor unit).

  The above-described oil reservoir 12 is formed at the bottom of the hermetic container 4 in order to store the oil, and the oil in the oil reservoir 12 passes through the oil supply hole 8b formed in the drive shaft 8 and the slewing bearing. 13 to be guided to 13. A part of the oil guided to the oil supply hole 8b is also supplied to the auxiliary bearing 17 through the lateral oil supply hole 8c. Therefore, an oil supply pump 24 is provided at the lower end portion of the drive shaft 8, and the oil in the oil reservoir 12 is supplied to the oil supply hole 8b by the oil supply pump 24.

The oil supply pump 24 is provided concentrically with the shaft center of the drive shaft 8, and the oil supply hole formed in the axial direction of the drive shaft 8 is used for lubricating oil stored in the oil reservoir 12. It is configured to be supplied to the slewing bearing 13, the main bearing 15, the auxiliary bearing 17 and the like through 8b.
Reference numeral 25 denotes a magnet that is attached to the bottom cap 4c of the sealed container 4 and removes metal powder or the like mixed in the oil in the oil reservoir 12 from the oil.

  When the drive shaft 8 is rotated by the electric motor unit 3, the orbiting scroll 6 performs an orbiting motion with respect to the fixed scroll 5 without rotating due to the action of the Oldham ring 9. A balance weight 20 is attached to the drive shaft 8 between the rotor 3b and the orbiting scroll 6 and a rotor balance weight 21 is also attached to the lower part of the rotor 3b in order to cancel out the unbalanced force generated by the turning motion. It has been.

  In the compression chamber 11 formed by the fixed scroll 5 and the orbiting scroll 6, the volume is reduced by the orbiting motion of the orbiting scroll 6 and the compression operation is performed. Further, as the orbiting scroll 6 orbits, the working fluid (refrigerant gas) flowing through the refrigeration cycle flows into the intake port 5c through the intake pipe 14 and is sucked into the compression chamber 11 from here. After passing through the compression stroke, it is discharged from the discharge port 5d of the fixed scroll 5 to the discharge chamber (discharge space) 30 in the sealed container 4.

  The compressed refrigerant gas discharged into the discharge chamber 30 passes through a passage (not shown) formed between the inner peripheral surface of the sealed container 4 and the outer peripheral surfaces of the fixed scroll 5 and the frame 7. It flows into the upper space 31 of the electric motor unit 3 in the sealed container 4 and is then discharged from the discharge pipe 22 to the refrigeration cycle outside the compressor 1. Thus, the space in the sealed container 4 is configured as a so-called high pressure chamber type in which the discharge pressure is maintained.

  Part of the oil supplied to the swivel bearing 13 through the oil supply hole 8b flows into the back pressure chamber 32, lubricates the sliding portion of the Oldham ring 9, and further in the back pressure chamber 32. In order to adjust the pressure, the pressure is supplied to the compression chamber 11 and the like via a back pressure control valve (not shown) provided in the fixed scroll 5. Thereby, the sliding part of the fixed scroll 5 and the turning scroll 6 is also lubricated.

  Most of the oil supplied to the slewing bearing 13 through the oil supply hole 8b is lubricated to the sealed bearing through the through hole 7a formed in the frame 7 and the oil drain pipe 28 after lubricating the main bearing 15. It is configured to be returned to the oil sump 12 at the bottom of the four.

  In the scroll compressor 2 shown in FIG. 1, the oil drain pipe 28 is an L-shaped pipe, and the insertion portion 28 a on the upper end side is inserted into the through hole 7 a formed on the side surface of the frame 7. It is fixed with.

  However, in the case of a compressor having a structure in which the lower outer peripheral portion of the frame 7 is adjacent to the inner wall of the sealed container 4, the through-hole 7a is formed downward in the outer peripheral portion of the lower end of the frame 7, The oil drain pipe 28 is formed in a straight line, and the upper end of the oil drain pipe 28 is inserted into the through hole 7a as an insertion part, and the oil is stored in the oil reservoir 12 at the bottom of the closed container 4 through the straight oil drain pipe 28. You may make it guide to the side.

  The oil drain pipe 28 is formed of a cylindrical pipe made of metal such as iron, for example, and includes an insertion portion 28a for fixing to the frame 7, and extends downward from the insertion portion 28a. An oil guide portion 28b that passes through the notch 3ad (gap 26b) provided on the outer peripheral surface of the steel plate 3ab 3a and guides oil downward from the motor portion 3, and extends from the oil guide portion 28b to the lower end. A tip portion 28c having an open end that opens on the side of the reservoir 12 is provided.

  In this example, the oil drain pipe 28 is configured to penetrate only the notch 3ad formed on the outer peripheral surface of the steel plate 3ab of the stator 3a, but is attached to the upper and lower ends of the steel plate 3ab. It is good also as a structure which provides the support part which fixes the said oil drain pipe 28 in the outer peripheral surface of the insulator 23, and also penetrates this insulator 23 and supports the said oil drain pipe.

  Also in the conventional scroll compressor, the oil drain pipe is inserted and passed through the notched part of the recessed groove shape formed on the outer peripheral surface of the stator, but the compressor is required to be downsized. The width dimension of the notch is approximately the same as or slightly larger than the outer diameter of the oil drain pipe 28, and the tolerance becomes small, so that a sufficient tolerance cannot be secured.

  More specifically, the stator 3a is made of a steel plate having excellent magnetic properties, and when compressive stress is applied, the magnetic properties (permeability) tend to decrease. For this reason, when a large compressive stress acts on the notch, the magnetic field generated by the motor during the operation of the compressor is greatly reduced, so that the performance of the scroll compressor is greatly reduced.

  In order to suppress this deterioration in performance, it is necessary to make it difficult for stress to be applied to the steel plate of the stator. For this reason, it is necessary to make the notch as small as possible. That is, it is necessary to make the width dimension of the notch close to the outer diameter of the oil drain pipe.

  For this reason, when assembling the scroll compressor, the work of inserting the oil drain pipe into the notch is required to be highly accurate. However, if the assembly accuracy decreases due to deterioration of the assembly device for assembling the scroll compressor, the oil drain pipe is tilted and contacts the stator of the motor part when performing the assembly operation of inserting the oil drain pipe into the notch. As a result, the oil drain pipe cannot be inserted, which makes it difficult to assemble the scroll compressor.

  Therefore, in the present embodiment, as shown in FIG. 1, the tip end portion 28c of the oil drain pipe 28 is tapered to the lower side, and the tip width of the tip end portion 28 is set to the tube portion of the oil guide portion 28b. It is configured to be smaller than the width of. By comprising in this way, the operation | work which inserts the said oil drain pipe 28 in the said notch part 3ad becomes easy, and an assembly property can be improved significantly.

  Next, with reference to FIGS. 3A to 3C, the shape of the vicinity of the tip of the oil drain pipe 28 in the first embodiment will be described in detail. 3A is a cross-sectional view of the main part in the vicinity of the tip of the oil draining pipe shown in FIG. 1, FIG. 3B is a cross-sectional view taken along the line aa in FIG. 3A, and FIG.

  As shown in FIG. 3A, the oil drain pipe 28 in the first embodiment is formed of a cylindrical pipe, and the oil guide portion 28 b disposed in the notch portion 3 ad on the outer periphery of the stator 3 a in the motor portion 3. And a leading end portion 28c extending from the oil guide portion 28b to the lower end and opening on the oil reservoir 12 side. Further, the width of the distal end portion 28c of the oil drainage pipe 28, for example, the distal end width L2 of the lower end portion of the distal end portion 28c is formed in a tapered shape so as to be smaller than the width L1 of the oil guiding portion 28b. ing.

  That is, as shown in FIG. 3C, the flow path cross-sectional area of the lower end portion 28c of the oil drain pipe 28 is smaller than the flow path cross-sectional area of the oil guide portion 28b shown in FIG. The outer peripheral length in the tip portion 28c is also smaller than the outer peripheral length in the oil guide portion 28b. Further, the tip portion 28c of the oil drain pipe 28 is formed in a tapered shape in which the outer diameter and the flow passage cross-sectional area gradually decrease toward the oil reservoir 12 side.

  With this configuration, the width dimension of the distal end portion 28c of the oil drain pipe 28 can be made smaller than the width dimension of the notch 3ad on the outer periphery of the stator 3a into which the oil drain pipe 28 is inserted. The margin of the tip 28c with respect to the notch 3ad can be increased. Accordingly, when the scroll compressor is assembled, the oil drain pipe 28 can be easily inserted into the notch 3ad on the outer periphery of the stator 3a.

  FIG. 4 is a diagram for explaining how the oil drain pipe 28 is inserted into the notch 3ad on the outer peripheral surface of the stator 3a in the assembly of the hermetic scroll compressor shown in FIG. With reference to this figure, the process of inserting the oil drain pipe 28 into the notch 3ad in the assembly of the scroll compressor will be described.

  First, the stator 3a of the electric motor unit 3 is attached to a predetermined location in the body 4a of the sealed container 4 by shrink fitting or the like, and the body 4a of the sealed container 4 incorporating the stator 3a is installed on the surface plate of the assembly apparatus. Is done. On the other hand, the insertion portion 28 a of the oil drain pipe 28 is inserted and fixed in the through hole 7 a of the frame 7 in the frame 7 of the compression mechanism portion 2. When inserting this compression mechanism part 2 in the trunk | drum 4a of the said airtight container 4, the compression mechanism part 2 is inserted in the said trunk | drum 4a from the top in the state in which the oil draining pipe 28 is attached. In this insertion process, first, the lower end portion (tip portion 28c) of the oil drain pipe 28 reaches the upper end of the stator 3a, and then the oil drain pipe 28 is formed on the outer periphery of the stator 3a while lowering the compression mechanism portion 2. It is inserted into the notch 3ad for inserting an oil drain pipe.

  At this time, as shown in FIG. 3A, the oil drain pipe 28 has a tip 28c having a tapered shape in which the tip width L2 is smaller than the width L1 of the oil guide portion 28b. Therefore, the width of the lower end portion of the oil drainage pipe 28 can be sufficiently reduced with respect to the width (size) of the notch portion 3ad. That is, since the margin of the tip 28c relative to the notch 3ad can be increased, the oil drain pipe 28 can be easily inserted into the notch 3ad on the outer periphery of the stator 3a when the scroll compressor is assembled. Is possible.

  Thus, according to the present embodiment, the insertability of the tip 28c when the oil drainage pipe 28 is inserted into the notch 3ad on the outer periphery of the stator 3a is improved. If the distal end portion 28c can be inserted into the notch portion 3ad, the oil guiding portion 28b thereafter can be inserted along the notch portion 3ad. Therefore, with the configuration of this embodiment, the oil drain pipe 28 can be easily inserted, so that the assembly of the scroll compressor can be improved.

  Furthermore, according to the present embodiment, since the margin of the notch 3ad formed on the outer periphery of the stator 3a can be reduced with respect to the outer diameter of the oil guide portion 28b of the oil drain pipe 28, the notch 3ad is The oil discharge pipe 28 can be formed in a size close to the diameter of the oil guide portion 28b. Therefore, the swing width of the oil guide portion 28b of the oil drain pipe 28 during operation of the compressor can be reduced, thereby reducing the vibration of the oil drain pipe 28. Moreover, since it can suppress that the notch part 3ad becomes large, when the stator 3a is fixed, the compressive stress which acts on a notch part can be reduced. As a result, the magnetic characteristics of the stator 3a can be improved, so that the performance of the compressor can be improved.

  As described above, according to the present embodiment, it is possible to suppress an increase in the size of the concave groove-shaped notch through which the oil drain pipe provided on the outer peripheral surface of the stator of the motor is passed, while discharging to the notch. The oil pipe can be easily inserted. Therefore, it is possible to obtain a hermetic scroll compressor that can improve the assemblability and improve the performance of the compressor.

  Next, a second embodiment of the hermetic scroll compressor of the present invention will be described with reference to FIGS. 5A to 5C. 5A is a cross-sectional view of the main part near the tip of the oil draining pipe in the second embodiment, FIG. 5B is a cross-sectional view taken along the line bb of FIG. 5A, and FIG. 5C is a cross-sectional view taken along the line cc of FIG. Note that the overall configuration of the hermetic scroll compressor of the second embodiment is the same as that of the first embodiment described above, and the description will focus on the differences from the first embodiment. In FIGS. 5A to 5C, the same reference numerals as those in FIGS. 1 to 4 denote the same or corresponding parts.

  Also in the second embodiment, as in the first embodiment, the oil drain pipe 28 is formed of a cylindrical L-shaped pipe, and the upper end portion of the insertion portion 28a and the stator 3a constituting the electric motor portion 3 are also provided. A central oil guide portion 28b penetrating the outer peripheral side of the oil reservoir and a tip portion 28c on the oil reservoir 12 side (lower end side). The insertion portion 28a of the oil drain pipe 28 is inserted into and fixed to a through hole 7a formed on the side surface of the frame 7 and communicating with the main bearing 15 (see FIG. 1).

  The difference between the second embodiment and the first embodiment is that, as shown in FIG. 5A, the oil drain pipe 28 has a distal end portion 28 c that gradually decreases in outer diameter toward the oil reservoir 12. In other words, the thickness is reduced, and the outer diameter is gradually reduced. Thereby, the tip width L2 (or outer diameter) of the tip portion 28c of the oil drain pipe 28 is formed smaller than the width L1 (or outer diameter) of the oil guide portion 28b.

  Further, as shown in FIG. 5B showing the bb cross section (horizontal cross section) of the oil guide portion 28b and FIG. 5C showing the cc cross section (horizontal cross section) of the tip portion 28c, the oil drainage The thickness of the tip portion 28c of the pipe 28 is thinner than the thickness of the oil guiding portion 28b.

  Further, in the second embodiment, unlike the first embodiment, the inner diameter of the oil drain pipe 28 is the same from the oil guide portion 28b to the tip portion 28c. Accordingly, the flow passage cross-sectional area of the tip portion 28c of the oil drain pipe 28 is equal to the flow passage cross-sectional area of other portions such as the oil guide portion 28a of the oil drain pipe 28, and the lower end (oil sump side) of the tip portion 28c. Therefore, the flow passage resistance of the oil drain pipe 28 can be reduced, and the input of the scroll compressor can be reduced from that of the first embodiment.

  Also in the second embodiment, as in the first embodiment, the notch 3ad for passing the oil drain pipe provided on the outer peripheral surface of the stator 3a of the electric motor unit 3 is prevented from becoming large, and this notch The oil drain pipe can be easily inserted into the section. Therefore, it is possible to improve the assemblability and improve the performance of the compressor.

  A third embodiment of the hermetic scroll compressor of the present invention will be described with reference to FIGS. 6A to 6C. 6A is a cross-sectional view of the main part in the vicinity of the distal end portion of the oil draining pipe according to the third embodiment, FIG. 6B is a cross-sectional view taken along the line dd in FIG. 6A, and FIG. Note that the overall configuration of the hermetic scroll compressor of the third embodiment is the same as that of the first embodiment described above, and the description will focus on the differences from the first embodiment. Moreover, in FIGS. 6A to 6C, the portions denoted by the same reference numerals as those in FIGS. 1 to 4 are the same or corresponding portions.

  Also in the third embodiment, as in the first and second embodiments, the oil drain pipe 28 is formed of a cylindrical L-shaped pipe, and includes an insertion portion 28a on the upper end side, and a central oil guide portion. 28b and a tip portion 28c on the oil reservoir 12 side (lower end side). Further, as shown in FIG. 1, the insertion portion 28 a of the oil drain pipe 28 is also inserted and fixed in the through hole 7 a formed on the side surface of the frame 7 and communicating with the main bearing 15.

  The difference of the third embodiment from the first and second embodiments is that, as shown in FIG. 6A, the oil drain pipe 28 has a distal end portion 28c at the outer peripheral corner of the oil reservoir 12 side. 28c1 is chamfered, and the end outer peripheral corner portion 28c1 is formed in a tapered shape.

  As a result, the outer diameter of the pipe (oil drain pipe) is narrowed as in the first embodiment, and the distal end portion 28c of the oil drain pipe 28 is gradually reduced toward the oil reservoir 12 as in the second embodiment. The taper shape can be easily manufactured without processing to reduce the thickness, and the flow passage cross-sectional area is also made constant up to the lower end of the drainage pipe as in the second embodiment. Can do.

  6C showing a dd cross section (horizontal cross section) of the oil guide portion 28b, and FIG. 6C showing an ee cross section (horizontal cross section) of the end peripheral corner portion 28c1 chamfered at the tip end portion 28c. As can be seen from the above, the thickness of the outer peripheral corner portion 28c1 is thinner than the thickness of the oil guide portion 28b. Therefore, the distal end width L2 (or outer diameter) of the distal end portion 28c of the oil drain pipe 28 can be formed smaller than the width L1 (or outer diameter) of the oil guiding portion 28b.

  Further, the oil discharge pipe 28 can have the same inner diameter from the oil guide portion 28b to the tip portion 28c, and as a result, the flow passage cross-sectional area of the tip portion 28c of the oil drain pipe 28 has a lower end (an end portion on the oil reservoir side). ), The flow path resistance can be reduced.

  Further, in the third embodiment, as in the first and second embodiments, the notch portion 3ad for passing the oil drain pipe provided on the outer peripheral surface of the stator 3a of the electric motor portion 3 is suppressed from increasing. The oil drain pipe can be easily inserted into the notch. Therefore, it is possible to improve the assemblability and improve the performance of the compressor.

  Next, Embodiment 4 of the hermetic scroll compressor of the present invention will be described with reference to FIGS. 7A to 7D. 7A is a cross-sectional view of the main part near the tip of the drainage pipe in the fourth embodiment, FIG. 7B is a cross-sectional view taken along line ff of FIG. 7A, FIG. 7C is a cross-sectional view taken along line g1-g1 of FIG. It is the g2-g2 sectional view taken on the line of FIG. 7A. The overall configuration of the hermetic scroll compressor according to the fourth embodiment is also the same as that of the first embodiment described above, and the description will focus on the differences from the first embodiment. Moreover, in FIGS. 7A to 7D, the portions denoted by the same reference numerals as those in FIGS. 1 to 4 are the same or corresponding portions.

  Also in the fourth embodiment, as in the first to third embodiments, the oil drain pipe 28 is configured by a cylindrical L-shaped pipe, and includes an insertion portion 28a on the upper end side, a central oil guide portion 28b, And a tip 28c on the oil reservoir 12 side. Further, the insertion portion 28a of the oil drain pipe 28 is also inserted and fixed in the through hole 7a formed on the side surface of the frame 7 (see FIG. 1).

  The difference of the fourth embodiment from the first to third embodiments is that, as shown in FIG. 7A, the distal end portion 28c of the oil drainage pipe 28 is cut off obliquely. As a result, the width of the tip portion 28c of the oil drain pipe 28 can be gradually reduced downward (in the direction of the oil sump 12), and the tip width L2 that is the lower end of the oil drain pipe 28 can be made substantially zero. .

  That is, the front end width L2 of the front end portion 28c can be made smaller than the width L1 of the oil guide portion 28b, and the cutout portion 3ad through which the oil drainage pipe formed on the outer peripheral surface of the stator 3a of the electric motor unit 3 passes is not enlarged. Since the oil drain pipe 28 can be easily inserted into the notch 3ad, the assembly of the scroll compressor can be improved.

  Moreover, since it can suppress that the said notch part 3ad becomes large similarly to the said Examples 1-3, the compressive stress which acts on a notch part can be reduced and the magnetic characteristic of the stator 3a can be improved. Therefore, the performance of the scroll compressor can be improved.

  Further, according to the fourth embodiment, since the tip end portion 28c of the oil drain pipe 28 is cut off obliquely, the channel area on the outlet side of the oil drain pipe 28 is reduced to the channel cut-off of the oil guide portion 28b. It can be larger than the area. As a result, the flow resistance when draining oil from the tip 28c can be reduced as compared with those of the first to third embodiments, and the input of the scroll compressor can also be reduced.

In addition, this invention is not limited to the Example mentioned above, Various modifications are included. For example, in the above-described embodiment, the case of a hermetic scroll compressor that compresses refrigerant gas as a working fluid has been described. However, the present invention is not limited to one that compresses refrigerant gas, but hermetically compresses air or other gas. The same applies to the type scroll compressor.
It is also possible to add the configuration of another embodiment to the configuration of one embodiment. Further, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.

1: Hermetic scroll compressor, 2: Compression mechanism,
3: Electric motor part, 3a: Stator, 3aa: Winding, 3ab: Steel plate (iron core),
3ac, 3ad: notch, 3ae: teeth, 3af: slot, 3b: rotor,
4: Sealed container, 4a: trunk, 4b: lid cap, 4c: bottom cap,
5: fixed scroll, 5a: end plate, 5b: wrap, 5c: suction port, 5d: discharge port,
6: Orbiting scroll, 6a: End plate, 6b: Wrap, 6c: Boss
7: Frame, 7a: Through hole,
8: Drive shaft, 8a: Crank part, 8b: Oiling hole, 8c: Lateral oiling hole,
9: Oldham ring (rotation prevention mechanism), 10: Bolt,
11: compression chamber, 12: oil sump, 13: slewing bearing, 14: suction pipe,
15: main bearing, 16: frame seal, 17: auxiliary bearing,
18: Lower frame, 19: Secondary bearing housing,
20: balance weight, 21: rotor balance weight,
22: Discharge pipe, 23: Insulator, 24: Oil supply pump,
25: Magnet, 26a, 26b: Air gap,
28: Oil drain pipe, 28a: Insertion part, 28b: Oil guide part, 28c: Tip part,
28c1: end outer peripheral corner,
30: Discharge chamber, 31: Upper space, 32: Back pressure chamber.

Claims (8)

A fixed scroll, a turning scroll, and a frame; a compression chamber formed by combining the fixed scroll and the turning scroll; and a compression mechanism that compresses the working fluid by turning the turning scroll; and a stator and a rotor An electric motor unit for driving the compression mechanism unit, a sealed container containing the compression mechanism unit and the electric motor unit and having an oil sump at the bottom, and a rotating scroll fixed to the rotor of the electric motor unit and rotating the orbiting scroll In a hermetic scroll compressor comprising: a drive shaft that drives; a main bearing that is provided on the frame and supports the drive shaft; and an oil drain pipe that guides oil that has lubricated the main bearing to the oil reservoir.
The oil drainage pipe has an insertion part inserted into the frame, an oil guide part disposed in a notch part formed on the outer periphery of the stator of the electric motor part, and an opening end opened on the oil reservoir side. A tip having
The hermetic scroll compressor, wherein a tip width of the tip portion of the oil drainage pipe is smaller than a width of the oil guide portion. The hermetic scroll compressor according to claim 1,
The oil discharge pipe has a cylindrical shape, and a tip end portion of the oil discharge pipe is formed in a tapered shape in which an outer diameter and a flow passage cross-sectional area gradually decrease toward the oil reservoir. Compressor. The hermetic scroll compressor according to claim 1,
The oil discharge pipe has a cylindrical shape, and a tip end portion of the oil discharge pipe is formed in a tapered shape that is gradually thinned toward the oil reservoir and gradually decreases in outer diameter. Compressor. The hermetic scroll compressor according to claim 1,
The oil drainage pipe has a cylindrical shape, and a tip portion of the oil drainage pipe is chamfered at an end outer peripheral corner portion on the oil reservoir side, and the end outer peripheral corner portion is formed in a tapered shape. Hermetic scroll compressor. The hermetic scroll compressor according to claim 3 or 4,
The hermetic scroll compressor characterized in that the flow passage cross-sectional area at the tip portion of the oil drain pipe is the same from the upstream side to the downstream end of the tip portion. The hermetic scroll compressor according to claim 1,
A sealed mold characterized in that the tip width of the tip of the oil drain pipe is formed smaller than the width of the oil guide section by forming the tip of the oil drain pipe obliquely cut off. Scroll compressor. In the hermetic scroll compressor according to any one of claims 1 to 6,
The oil drainage pipe is formed of an L-shaped pipe, and an insertion portion on the upper end side thereof is inserted and fixed into a through hole formed on the side surface of the frame and communicating with the main bearing. Type scroll compressor. In the hermetic scroll compressor according to any one of claims 1 to 6,
The lower outer peripheral portion of the frame is configured to be adjacent to the inner wall of the sealed container, a through hole communicating with the main bearing is formed downward in the outer peripheral portion of the lower end of the frame, and the oil drain pipe is formed in a straight line shape The hermetic scroll compressor is characterized in that the insertion portion on the upper end side is inserted into the through hole and fixed.

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