WO2016021590A1

WO2016021590A1 - Open-type compressor

Info

Publication number: WO2016021590A1
Application number: PCT/JP2015/072069
Authority: WO
Inventors: 善彰宮本; 央幸木全; 後藤　利行; 創佐藤
Original assignee: 三菱重工業株式会社
Priority date: 2014-08-08
Filing date: 2015-08-04
Publication date: 2016-02-11
Also published as: CN106662093A; KR102096139B1; JP2016037922A; EP3150855B1; AU2015300143A1; KR20180112091A; AU2015300143B2; EP3150855A1; EP3150855A4; JP6462265B2; KR20170010406A

Abstract

Provided is an open-type compressor with which it is possible to prevent a reduction in oil supply amount caused by an increase in flow-path pressure loss particularly in a high rotational speed range, and to improve reliability in lubrication performance. Disclosed is an open-type compressor (1) comprising: a drive shaft (9) having one end protruding outside a housing (2); an oil supply pump (37) provided in an outer circumferential section of the drive shaft (9); a pump chamber (39) that is formed around the drive shaft (9), and into which oil pumped up by the oil supply pump (37) is discharged; an axial-direction oil supply passage (41) that is pierced inside the drive shaft (9) along the direction of the axis L thereof, and that supplies the oil from the pump chamber (39) to a sliding part; and a radial-direction oil supply passage (40) that guides the oil in the pump chamber (39) to the axial-direction oil supply passage (41). The axial-direction oil supply passage (41) is provided in a position that is decentered by a predetermined dimension Δh with respect to the axis L of the drive shaft (9). The radial-direction oil supply passage (40) is provided on a side toward which the axial-direction oil supply passage (41) is decentered.

Description

Open type compressor

The present invention enables oil supply to a sliding part through an oil supply passage which is provided on the outer periphery of the drive shaft and pumped up by an oil supply pump driven by the drive shaft along the axial direction in the drive shaft. It relates to an open type compressor.

In a horizontal type open type compressor, one end of the drive shaft that is rotatably supported inside the housing via a bearing protrudes outside the housing and is driven by power from the outside. In the case of adopting a forced oiling system in which the lubricating oil is pumped up by an oil supply pump and then lubricated to a sliding part such as a bearing, the drive shaft is driven by the drive shaft as shown in Patent Document 1. The oil pump is provided, and the oil pumped up by the oil pump is supplied to the sliding portion through an oil passage formed in the drive shaft along the axial direction.

In the case of a hermetic compressor, it is not limited to a vertical type or a horizontal type. Generally, a centrifugal or positive displacement oil pump is provided at the shaft end of the drive shaft, and the lubricating oil filled in the sealed container is supplied to the oil pump. A configuration is adopted in which the oil is pumped by the oil and the oil is supplied to the sliding portion through an oil supply passage which is perforated in the drive shaft along the axial direction. In such a forced oil supply system, an oil supply passage formed in the drive shaft along the axial direction is provided with a predetermined dimension offset with respect to the axis, and oil supply is performed using centrifugal force. Japanese Patent Application Laid-Open No. H10-228707 discloses a device that improves performance.

JP 2005-282446 A Japanese Patent Laid-Open No. 8-219063

As described above, in the case of a hermetic compressor that employs a forced oiling system, it is not necessary to obtain external power, and since one end of the drive shaft can be opened and an oiling passage can be drilled in the axial direction, It is difficult to be affected, and the rotational speed and centrifugal force of the oil supply pump can be increased in proportion to the rotational speed of the drive shaft. As a result, the amount of oil supply can be increased and the oil supply performance can be improved, so there is no particular problem. However, in the case of an open type compressor, it is necessary to obtain external power, and it is difficult to make one end of the drive shaft an open end. Therefore, the oil pumped up by the oil pump is once discharged into the pump chamber formed around the drive shaft, and the oil passage is provided in the axial direction by the oil passage provided in the radial direction from the pump chamber to the drive shaft. It is necessary to supply oil.

Therefore, pressure loss due to centrifugal force is unavoidable at the inlet portion of the oil supply passage that is structurally drilled in the radial direction. Since this flow path pressure loss tends to increase as the rotational speed of the drive shaft increases, particularly when the axial oil supply passage is provided on the axis (no eccentricity) of the drive shaft, As shown in FIG. 3, there was a characteristic that the amount of oil supply decreased.

The present invention has been made in view of such circumstances, and is particularly capable of suppressing a decrease in the amount of oil supply due to an increase in flow path pressure loss in a high rotation speed range and improving the reliability with respect to the lubrication performance. An object is to provide a mold compressor.

According to a first aspect of the present invention, there is provided a drive shaft that is rotatably supported in a housing, one end of which protrudes outside the housing, and an outer peripheral portion of the drive shaft. An oil pump to be driven, a pump chamber formed around the drive shaft and from which oil pumped up by the oil pump is discharged, and drilled along the axial direction in the drive shaft, from the pump chamber An open type compressor comprising: an axial oil supply passage for supplying oil to a sliding portion; and a radial oil supply passage provided in the drive shaft and guiding the oil in the pump chamber to the axial oil supply passage. The axial oil supply passage is provided at a position that is decentered by a predetermined dimension with respect to the axis of the drive shaft, and the radial oil supply passage is an open type compressor provided on the eccentric direction side of the axial oil supply passage. .

According to the first aspect of the present invention, the axial oil supply passage formed in the drive shaft is provided at a position deviated by a predetermined dimension with respect to the axis of the drive shaft, and the pump pumped up by the oil pump Since the radial oil supply passage that guides the chamber oil to the axial oil supply passage is provided in the eccentric direction of the axial oil supply passage, the axial oil supply passage is eccentric, and the radial oil supply passage is provided on the eccentric direction side. Accordingly, the passage length of the radial direction oil supply passage can be shortened, and the flow path pressure loss due to the centrifugal force generated at the inlet portion of the radial direction oil supply passage can be reduced. In other words, in the case where the axial oil supply passage is not decentered, the length of the radial oil supply passage is the drive shaft radius, but when the radial oil supply passage is provided on the eccentric side of the axial oil supply passage, The passage length can be made shorter than the radius, and the flow path pressure loss can be reduced accordingly. Further, by decentering the axial oil supply passage by a predetermined dimension, it is possible to improve the oil supply performance for the sliding portion by utilizing the centrifugal pump effect that acts on the oil in the axial oil supply passage. Therefore, the synergistic effect of the reduction effect of the flow pressure pressure loss in the radial direction oil supply passage and the improvement effect of the oil supply performance by the axial direction oil supply passage suppresses the decrease in the oil supply amount especially in the high rotation speed range, and the reliability for the lubrication performance. Can increase the sex.

In the open type compressor of the first aspect of the present invention, the radial direction oil supply passage may be provided at a position where the passage length is the shortest length on the axis line in the eccentric direction.

According to the first aspect of the present invention, since the radial direction oil supply passage is provided at a position where the passage length is the shortest length on the axis line in the eccentric direction, the length of the radial direction oil supply passage is set to the axial direction oil supply passage. It is possible to minimize the flow path pressure loss due to the centrifugal force generated at the inlet portion of the radial direction oil supply passage by shortening the length by the amount corresponding to the eccentric dimension. Thereby, the amount of oil supply in the high rotation speed region can be improved, and the oil supply performance can be further improved.

In any one of the above-described open type compressors according to the first aspect of the present invention, a passage diameter of the axial oil supply passage may be larger than a passage diameter of the radial oil supply passage.

According to the first aspect of the present invention, since the passage diameter of the axial oil supply passage is larger than the passage diameter of the radial oil supply passage, it is easy to obtain the centrifugal pump effect due to eccentricity, and the flow passage in the passage Pressure loss can be reduced. In addition, the connecting portion between the radial direction oil supply passage and the axial direction oil supply passage is processed so as not to cause steps or burrs, and flow pressure loss occurs at the connection portion between the radial direction oil supply passage and the axial direction oil supply passage. The oil supply performance can be improved by suppressing the decrease in the oil supply amount in the high rotation speed range.

According to the present invention, the axial oil supply passage is decentered, the length of the radial oil supply passage is shortened by the amount of the radial oil supply passage provided on the eccentric direction side, and is generated at the inlet portion of the radial oil supply passage. The flow pressure loss due to the centrifugal force can be reduced, and the axial oil supply passage is decentered by a predetermined size, so that the centrifugal pump effect that acts on the oil in the axial oil supply passage is used to supply oil to the sliding portion. Since the performance can be improved, the oil supply amount can be reduced, especially in the high engine speed range due to the synergistic effect of reducing the flow pressure pressure loss in the radial direction oil supply passage and the effect of improving the oil supply performance by the axial direction oil supply passage. It can suppress and can improve the reliability with respect to lubrication performance.

It is a longitudinal section of an open type compressor concerning an embodiment of the present invention. It is sectional drawing (A) of the drive shaft in the said open type compressor, and its right view (B). FIG. 3 is a cross-sectional view corresponding to aa in FIG. It is sectional drawing equivalent to FIG. 3 of the modification of the radial direction oil supply path provided in the said drive shaft. It is a graph which shows the oil supply characteristic in the said open type compressor.

Embodiments according to the present invention will be described below with reference to FIGS. 1 to 5.
FIG. 1 is a longitudinal sectional view of an open type compressor according to an embodiment of the present invention. FIG. 2 is a sectional view (A) of a drive shaft and a right side view (B) thereof, and FIGS. FIG. 2A is a cross-sectional view corresponding to the line aa in FIG.
The open-type compressor 1 includes a cylindrical housing 2 in which a front housing 3 and a rear housing 4 having a bottomed shape are integrally coupled via bolts 5.

A bearing member 6 is fixedly installed via a bolt 7 on the opening end side of the front housing 3 in the housing 2, and a radial bearing portion 6 </ b> A of the bearing member 6 and a rolling bearing 8 installed in the front housing 3. Thus, the drive shaft 9 is rotatably supported. One end of the drive shaft 9 protrudes outside through the front housing 3, and power from an external drive source such as an engine is input to the protruding portion via the pulley 10 and the electromagnetic clutch 11. ing.

The pulley 10 is rotatably supported on the outer periphery of a flange member 13 fixedly installed on the front end surface of the front housing 3 via a bolt 12 via a rolling bearing 14, and a coil assembly 15 of the electromagnetic clutch 11 is incorporated therein. Is. Further, the armature assembly 16 of the electromagnetic clutch 11 is assembled to the external projecting end of the drive shaft 9 with a bolt 17 through the boss portion so as to face the pulley 10. Further, a mechanical seal 18 for sealing and sealing the penetrating portion of the drive shaft 9 is installed on the inner periphery of the flange member 13.

A compression mechanism 19 is incorporated inside the housing 2 on the rear housing 4 side. Here, the compression mechanism 19 is a scroll compression mechanism 19 including a pair of fixed scrolls 20 and a turning scroll 21. The scroll compression mechanism 19 is configured such that a pair of fixed scroll 20 and orbiting scroll 21 are engaged with each other by shifting the phase by 180 °, and a plurality of compression chambers 22 are formed between the

scrolls

20, 21. 19 itself is well known.

The fixed scroll 20 is fastened and fixed to the bearing member 6 via bolts 23, and a discharge cavity 26 is formed between the rear surface of the end plate and the inner surface of the rear housing 4. A discharge port 24 that discharges compressed gas into the discharge cavity 26 and a discharge valve 25 that opens and closes the discharge port 24 are provided on the end plate of the fixed scroll 20. Further, the rear housing 4 is provided with a discharge port 27 for discharging the compressed gas discharged into the discharge cavity 26 to the outside so that a discharge pipe constituting a refrigeration cycle can be connected.

The orbiting scroll 21 has a boss portion 28 on the back surface of the end plate, and a crank pin 9A provided on the inner end side of the drive shaft 9 with respect to the boss portion 28 via a drive bush 29 and an orbiting bearing 30. It is configured to be coupled and driven to rotate through the crankpin 9A by the rotation of the drive shaft 9. Further, the orbiting scroll 21 is supported by a thrust bearing 31 provided on the end plate back surface on the bearing member 6, and an Oldham link or pin ring interposed between the end plate back surface and the bearing member 6. The rotation is prevented by a well-known rotation prevention mechanism 32 composed of the above, and the revolving turning drive is performed with respect to the fixed scroll 20.

A suction port 33 for connecting a suction pipe on the refrigeration cycle side is provided on the outer periphery on the front end side of the rear housing 4, and the low pressure gas sucked into the suction cavity 34 from the suction port 33 is compressed in the compression chamber 22 of the scroll compression mechanism 19. It is configured to be sucked into and compressed. In the present embodiment, the compression mechanism 19 is provided with a step portion for changing the wrap height in the spiral direction of the fixed scroll 20 and the orbiting scroll 21, and the outer wrap height is made higher than the inner wrap height. The so-called stepped scroll compression mechanism 19 capable of three-dimensional compression capable of compressing the gas not only in the circumferential direction but also in the axial direction is not limited to this.

On the other hand, a required amount of lubricating oil is filled in the front housing 3, and the lower space in the front housing 3 is used as an oil reservoir 35 so that the oil is collected in the oil reservoir 35. The oil in the oil sump 35 is sucked into the oil supply pump 37 through the suction passage 36.

The oil supply pump 37 forms an eccentric portion 9B (see FIG. 2) in the outer peripheral portion of the drive shaft 9 penetrating the front end surface of the front housing 3, and the front end surface of the front housing 3 is opposed to the eccentric portion 9B. A known rotary positive displacement pump having a configuration in which a rotor 38 that rotates eccentrically in a cylinder formed between the end faces of the flange member 13 is fitted.

Oil pumped from the oil reservoir 35 by the oil supply pump 37 is discharged into a pump chamber 39 formed between the eccentric portion 9B around the drive shaft 9 and the mechanical seal 18. The oil pumped into the pump chamber 39 slides through the radial bearing portion 6A, the drive bush 29, the swivel bearing 30, the thrust bearing 31 and the like through the radial oil supply passage 40 and the axial oil supply passage 41 provided in the drive shaft 9. It is supplied to a part or a sliding part of the mechanical seal 18.

As shown in FIGS. 2 and 3, the axial oil supply passage 41 provided along the axis L in the drive shaft 9 has a predetermined dimension (eccentric dimension) Δh with respect to the axis L of the drive shaft 9. It is provided at an eccentric position. A radial oil supply passage 40 that guides oil in the pump chamber 39 to the axial oil supply passage 41 is provided in the eccentric direction of the axial oil supply passage 41. In this embodiment, the radial direction oil supply passage 40 is provided at a position where the passage length h1 is the shortest length on the axis line in the eccentric direction. Accordingly, the passage length h1 of the radial direction oil supply passage 40 is shorter by Δh (Δh = h−h1) than the passage length h of the axial direction oil supply passage 41 provided on the axis L of the drive shaft 9. can do.

However, as described above, the present invention is not limited to the case where the radial direction oil supply passage 40 is provided on the eccentric axis, and the passage length h1 is the shortest length. As shown in FIG. Alternatively, the radial oil supply passage 40A may be provided in a direction having a certain angle with respect to the first oil supply passage. Even with such a configuration, the passage length h2 of the radial oil supply passage 40A can be made shorter than the passage length h of the axial oil supply passage 41 provided on the axis L of the drive shaft 9. The passage length h2 is h1 <h2 <h. In other words, the radial oil supply passage that guides the oil in the pump chamber 39 to the axial oil supply passage 41 is not limited to the eccentric axial line, and is provided on the eccentric direction side of the axial oil supply passage 41 to drive the length of the passage. The axial oil supply passage 41 can be shortened as compared with the case where the axial oil supply passage 41 is provided on the axis L of the shaft 9.

Further, as described above, when the axial direction oil supply passage 41 and the radial direction

oil supply passages

40, 40A are provided, the axial direction oil supply passage 41 is formed as a blind hole formed along the axis L from one end of the crankpin 9A. On the other hand, the radial

oil supply passages

40, 40A are holes provided perpendicular to the radial direction in the vicinity of the end of the blind hole, and at the intersection (connecting portion), steps and burrs that cause flow path pressure loss are formed. It is necessary to prevent this from occurring. Therefore, by making the passage diameter d1 of the axial direction oil supply passage 41 larger than the passage diameter d2 of the radial direction

oil supply passages

40, 40A (d1> d2), the axial oil supply passage 41 has a centrifugal pump effect due to eccentricity. It is easy to obtain, and it is configured to be able to reduce the flow path pressure loss in the passage and to perform communication processing so that a step, a burr, or the like does not occur at the connecting portion between both

passages

40, 40A and 41.

With the configuration described above, according to the present embodiment, the following operational effects can be obtained.
In the open compressor 1, when the electromagnetic clutch 11 is turned on, the power input from the external drive source via the pulley 10 is transmitted to the drive shaft 9, and the drive shaft 9 is rotationally driven. As a result, the orbiting scroll 21 of the scroll compression mechanism 19 is driven to revolve around the fixed scroll 20, and the low pressure gas sucked into the suction cavity 34 from the suction port 33 is sucked into the compression chamber 22, compressed to a high pressure and discharged. The liquid is discharged from the port 24 into the discharge cavity 26 and discharged from the discharge port 27 to the refrigeration cycle.

During this time, the oil supply pump 37 driven by the rotation of the drive shaft 9 sucks the lubricating oil in the oil sump 35 through the suction passage 36 and pumps it into the pump chamber 39. The oil pumped into the pump chamber 39 lubricates the sliding portion of the mechanical seal 18 and is guided to the axial oil supply passage 41 via the radial

oil supply passages

40, 40 </ b> A. Supplied to the sliding portions such as the bearing portion 6A, the drive bush 29, the slewing bearing 30, the thrust bearing 31 and the like, and lubricates each sliding portion. The oil that has lubricated the sliding parts is collected in an oil sump 35 at the bottom of the housing 2 and recirculated.

Here, in the present embodiment, the axial oil supply passage 41 is provided at a position eccentric by a predetermined dimension Δh with respect to the axis L of the drive shaft 9, and the oil in the pump chamber 39 is supplied to the axial oil supply passage 41. Radial direction

oil supply passages

40, 40 </ b> A for guiding are provided on the eccentric direction side of the axial direction oil supply passage 41. Accordingly, the passage lengths h1 and h2 can be made shorter (h1 <h2 <h) than that in which the axial oil supply passage 41 is provided on the axis L of the drive shaft 9.

For this reason, the passage lengths h1 and h2 of the radial

oil supply passages

40 and 40A are shortened corresponding to the dimension Δh in which the axial oil supply passage 41 is decentered, and this occurs at the inlet portion of the radial

oil supply passages

40 and 40A. Flow path pressure loss due to centrifugal force can be reduced. Further, by decentering the axial oil supply passage 41 by the predetermined dimension Δh, the oil supply performance for the sliding portion can be enhanced by utilizing the centrifugal pump effect that acts on the oil in the axial oil supply passage 41.

FIG. 5 is a graph showing the oil supply characteristics when the forced oil supply method is employed, with the horizontal axis representing the rotational speed (rpm) of the drive shaft 9 and the vertical axis representing the oil supply amount (cm ³ / min). In contrast to the theoretical value indicated by the solid line, in the case where the axial direction oil supply passage 41 is provided on the axis L, the length h of the radial direction oil supply passage becomes longer. Refueling amount will decrease. In the case where the axial oil supply passage 41 is provided eccentrically with respect to the axis L and the radial

oil supply passages

40, 40A are provided on the eccentric direction side and the passage lengths h1, h2 are shortened as in this embodiment, plot ▲ As shown by, the amount of oil supply in the high rotation speed region can be improved and brought close to the theoretical value.

Therefore, according to the present embodiment, the synergistic effect of the effect of reducing the flow pressure pressure loss in the radial direction

oil supply passages

40 and 40A and the effect of improving the oil supply performance by the axial direction oil supply passage 41, the oil supply amount in the high rotation speed region is reduced. It is possible to suppress the decrease and increase the reliability with respect to the lubricating performance.

Particularly, the radial direction oil supply passage 40 is provided at a position where the passage length h1 is the shortest length on the axis line in the eccentric direction. Therefore, the passage length h1 of the radial direction oil supply passage 40 is shortened by an amount corresponding to the eccentric dimension Δh of the axial direction oil supply passage 41, and the length h1 is set as the shortest length at the inlet portion of the radial direction oil supply passage 40. The flow path pressure loss due to the generated centrifugal force can be minimized. Thereby, the amount of oil supply in the high rotation speed region can be improved, and the oil supply performance can be further improved.

Further, in the radial direction

oil supply passages

40, 40A and the axial direction oil supply passage 41, the passage diameter d1 of the axial direction oil supply passage 41 is larger than the passage diameter d2 of the radial direction

oil supply passages

40, 40A (d1> d2). The centrifugal pump effect due to the eccentricity of the axial oil supply passage 41 can be easily obtained, and the flow pressure loss in the passage can be reduced. In addition, the connecting portion between the radial direction

oil supply passages

40 and 40A and the axial direction oil supply passage 41 is processed so as not to generate a step or a burr, and the flow path pressure loss at the connecting portion between both the

passages

40, 40A and 41 is processed. Therefore, the synergistic effect can suppress the decrease in the amount of oil supply in the high engine speed range and improve the oil supply performance.

Particularly, the open type compressor 1 according to the present embodiment can improve the lubrication performance when applied to the open type scroll compressor 1 adopting a forced oiling system that operates at a high speed of 3600 rpm or more.

In addition, this invention is not limited to the invention concerning the said embodiment, A deformation | transformation is possible suitably. For example, in the above embodiment, an example in which the present invention is applied to a scroll type compressor has been described as an example of the open type compressor 1. However, other types of open type compressors such as a rotary type, a swash plate type, and a reciprocating type are also described. Of course, the same applies.

Further, in the above embodiment, the oil pump 37 has been described with respect to an example in which a rotary positive displacement pump is applied. However, the present invention is not limited to this, and other types of oil pumps such as a screw pump may be used. Good.

DESCRIPTION OF SYMBOLS 1 Open type compressor 2 Housing 9 Drive shaft 37 Oil supply pump 39

Pump chamber

40, 40A Radial direction oil supply passage 41 Axial oil supply passage L Drive shaft axis line Δh Eccentric dimension h1, h2 Radial direction oil supply passage length d1 Axial direction Oil supply passage diameter d2 Radial direction oil supply passage diameter

Claims

A drive shaft that is rotatably supported in the housing and has one end projecting to the outside of the housing;
An oil supply pump provided on an outer peripheral portion of the drive shaft and driven by rotation of the drive shaft;
A pump chamber formed around the drive shaft and from which oil pumped by the oil pump is discharged;
An axial oil supply passage which is perforated along the axial direction in the drive shaft and supplies oil from the pump chamber to a sliding portion;
In an open type compressor provided with the radial direction oil supply passage provided in the drive shaft, and guiding the oil of the pump chamber to the axial direction oil supply passage,
The axial oil supply passage is provided at a position decentered by a predetermined dimension with respect to the axis of the drive shaft,
The radial oil supply passage is an open-type compressor provided on an eccentric side of the axial oil supply passage.
2. The open type compressor according to claim 1, wherein the radial direction oil supply passage is provided at a position where the passage length is the shortest on the axis in the eccentric direction.
The open type compressor according to claim 1 or 2, wherein a passage diameter of the axial oil supply passage is larger than a diameter of the radial oil supply passage.