WO2018047904A1

WO2018047904A1 - Open-type compressor

Info

Publication number: WO2018047904A1
Application number: PCT/JP2017/032261
Authority: WO
Inventors: 創佐藤; 善彰宮本; 尚夫水野; 章浩野口; 後藤　孝; 敏幸鹿内; 秀作後藤
Original assignee: 三菱重工サーマルシステムズ株式会社
Priority date: 2016-09-07
Filing date: 2017-09-07
Publication date: 2018-03-15
Also published as: JP2018040293A; JP6756551B2; EP3447295A4; EP3447295A1

Abstract

An open-type compressor (1A) equipped with: a drive shaft (5) rotationally driven around a central axis (X); a crank pin (51) eccentric thereto; a drive bearing (67) into which the crank pin (51) is inserted; an orbiting scroll (62) that has an orbiting end plate (62a) having a drive bearing accommodation part (66) in which the drive bearing (67) is accommodated, and orbiting laps (62b); and a housing (2) having an oil guiding unit (21) for guiding lubricating oil to the drive bearing (67). An oil path (86) connecting first openings (86a) that open at an outer circumferential surface and second openings (86b) that open inside the drive bearing accommodation part (66) is formed in the interior of the orbiting end plate (62a).

Description

Open type compressor

The present invention relates to an open type compressor.
This application claims priority on Japanese Patent Application No. 2016-174902 filed in Japan on September 7, 2016, the contents of which are incorporated herein by reference.

The open-type compressor is supported in a metal housing by a crankshaft that is rotationally driven by an electric motor or an engine, an eccentric shaft that is offset from the crankshaft, and a shaft that is rotatably supported by the eccentric shaft. And a fixed scroll facing the orbiting scroll (see, for example, Patent Document 1). The orbiting scroll revolves around the axis of the crankshaft without rotating, that is, orbits. Thereby, the volume of the compression chamber formed between the fixed scroll and the orbiting scroll is changed, and the fluid introduced into the compression chamber is compressed.

In the open type compressor of Patent Document 1, the eccentric shaft is rotatably provided via a drive bearing inside a bottomed cylindrical boss formed on the end plate of the orbiting scroll.

JP 2000-352377 A

In an open type compressor, the drive bearing is lubricated by mist-like lubricating oil that is fed from the outside of the housing into the housing together with the fluid to be compressed. This drive bearing is housed inside the orbiting end plate of the orbiting scroll. Therefore, depending on the operating condition of the open type compressor, it may be difficult to sufficiently supply mist-like lubricating oil to the drive bearing. If the supply of lubricating oil is insufficient, poor lubrication occurs, and abnormal wear may occur in the drive bearing due to the load generated when fluid is compressed between the fixed scroll and the orbiting scroll.

The present invention provides an open type compressor capable of stably supplying lubricating oil to a drive bearing.

The open type compressor according to the first aspect of the present invention is formed integrally with a drive shaft that is rotationally driven around a central axis and an end portion of the drive shaft, and extends in a direction perpendicular to the central axis from the central axis. An eccentric crank pin, a drive bearing into which the crank pin is inserted, a revolving end plate having a drive bearing accommodating portion in which the drive bearing is accommodated, and the central shaft with respect to a side where the crank pin is disposed The orbiting scroll having an orbiting lap extending from the orbiting end plate toward the opposite side of the extending axial direction, the drive shaft, the crankpin, and the orbiting scroll are accommodated and supplied to the drive bearing. A housing having an oil introduction portion for introducing lubricating oil from the outside, wherein the swivel end plate includes a first opening that opens at an outer peripheral surface of the swivel end plate, and the dry end plate. An oil passage for communicating the second opening that opens in the bearing receptacle formed therein.

With this configuration, the fluid is sucked into the compression chamber while the swiveling end plate is swiveling, and the pressure of the first opening that opens on the outer peripheral surface of the swiveling end plate is opened in the drive bearing housing portion. It becomes lower than the pressure of the part. Therefore, a flow from the second opening toward the first opening occurs in the oil passage. Thereby, the lubricating oil in the drive bearing housing portion is sucked from the second opening portion opened in the drive bearing housing portion. As a result, the flow of the lubricating oil around the drive bearing is made smooth, and the lubricating oil is prevented from staying.

In the open type compressor according to the second aspect of the present invention, in the first aspect, the oil passage may extend in the radial direction within the swivel end plate.

This configuration makes it possible to match the flow direction of the lubricating oil in the oil passage with the direction of the centrifugal force acting on the swivel end plate. Therefore, it is possible to flow the lubricating oil in the oil passage by efficiently using the centrifugal force of the turning end plate. As a result, the lubricating oil flow around the drive bearing can be made smoother.

In the open type compressor which concerns on the 3rd aspect of this invention, in the 1st or 2nd aspect, the said 1st opening part is a position where the position of the circumferential direction centering on the said center axis differs from the said oil introduction part. It may be formed.

</ RTI> By configuring in this way, the first opening and the oil introduction part are separated. Therefore, it is difficult for the refrigerant flowing from the oil introduction portion to flow into the oil passage from the first opening. Therefore, it is possible to prevent the lubricating oil that lubricates the drive bearing from being washed away by the refrigerant that flows back in the oil passage and the lubricating oil in the vicinity of the drive bearing being reduced.

In the open type compressor according to the fourth aspect of the present invention, in any one of the first to third aspects, the oil passage is on the surface of the swivel end plate on the side where the swirl wrap is provided. You may be provided avoiding the formed step part.

By configuring in this way, it is possible to prevent the step portion of the swivel end plate and the oil passage where stress is concentrated from being formed at the same position, and the swivel end plate from being partially thinned. Therefore, it is possible to suppress a decrease in strength in the vicinity of the step portion of the turning end plate where the stress is concentrated.

In the open type compressor according to the fifth aspect of the present invention, in any one of the first to fourth aspects, the drive shaft is opened facing the space into which the lubricating oil is introduced in the housing. An oil supply passage having a first oil supply opening and a second oil supply opening that faces the space where the drive bearing is disposed may be formed inside.

With this configuration, the lubricating oil can be supplied to the drive bearing housing portion from the space where the lubricating oil is introduced into the housing through the oil supply passage. As a result, new lubricating oil can be stably supplied to the drive bearing.

In the open type compressor according to the sixth aspect of the present invention, in the fifth aspect, the second oil supply opening may be formed at a position facing the drive bearing in the axial direction.

With this configuration, the lubricating oil can be supplied directly to the drive bearing through the oil supply passage.

In the open type compressor according to the seventh aspect of the present invention, in the fifth or sixth aspect, the oil supply passage extends in the axial direction at a position offset to the opposite side of the crank pin across the central axis. Also good.

With this configuration, it is easy to secure a space for forming the oil supply path at a position close to the drive bearing in the radial direction. Therefore, the oil supply path can be formed at a position close to the drive bearing.

In the open type compressor according to an eighth aspect of the present invention, in any one of the fifth to seventh aspects, the oil supply path is provided on the drive shaft, the drive shaft, the crankpin and the swivel It may be formed by communicating with a balance weight that cancels the eccentric force generated by the turning of the scroll.

With this configuration, it is possible to supply lubricating oil to the drive bearing even when a balance weight is provided.

In the open type compressor according to the ninth aspect of the present invention, in any one of the fifth to eighth aspects, the second oil supply opening is formed at a tip end portion of the crank pin located in the drive bearing. It may be formed.

An open type compressor according to a tenth aspect of the present invention is formed integrally with a drive shaft that is rotationally driven around a central axis and an end of the drive shaft, and extends in a direction perpendicular to the central axis from the central axis. An eccentric crank pin, a drive bearing into which the crank pin is inserted, a revolving end plate having a drive bearing accommodating portion in which the drive bearing is accommodated, and the central shaft with respect to a side where the crank pin is disposed The orbiting scroll having an orbiting lap extending from the orbiting end plate toward the opposite side of the extending axial direction, the drive shaft, the crankpin, and the orbiting scroll are accommodated and supplied to the drive bearing. A housing having an oil introduction portion for introducing the lubricating oil from the outside, and the drive shaft faces a space in the housing where the lubricating oil is introduced. A first oil supply opening that opens, the oil supply passage and a second oil supply opening which opens facing the space where the drive bearing is disposed is formed inside.

According to the above open type compressor, lubricating oil can be stably supplied to the drive bearing.

It is sectional drawing which shows the structure of the open type scroll compressor in 1st embodiment of this invention. It is the figure which looked at the turning scroll of the said open type scroll compressor from the axial direction. It is an expanded sectional view showing some composition of the above-mentioned open type scroll compressor. It is sectional drawing which shows the structure of the open type scroll compressor of 2nd embodiment of this invention. It is sectional drawing which shows the structure of the open type scroll compressor of 3rd embodiment of this invention. It is sectional drawing which shows the structure of the open type scroll compressor in 4th embodiment of this invention. It is sectional drawing which shows the structure of the open type scroll compressor in 5th embodiment of this invention.

Hereinafter, an open type compressor according to an embodiment of the present invention will be described with reference to the drawings.
(First embodiment)
FIG. 1 is a cross-sectional view showing a configuration of an open scroll compressor in the first embodiment. FIG. 2 is a view of the orbiting scroll of the open scroll compressor as viewed from the axial direction. FIG. 3 is an enlarged cross-sectional view illustrating a partial configuration of the open scroll compressor.

As shown in FIG. 1, an open type scroll compressor (open type compressor) 1A of the present embodiment includes a housing 2, a front housing 3, a drive shaft 5, a scroll compression mechanism 6, a main bearing 7, A sub-bearing 8.

The housing 2 accommodates a drive shaft 5, a crank pin 51 described later, a scroll compression mechanism 6 including a rotating scroll 62 described later, a main bearing 7, and a sub bearing 8. The housing 2 extends in the axial direction Da along the central axis X. The housing 2 has a bottomed cylindrical shape with one end 2a opened and the other end 2b closed. A suction port (oil introduction portion) 21 and a discharge port 22 are formed on the outer peripheral surface of the housing 2. The suction port (oil introduction part) 21 introduces refrigerant (refrigerant gas) and mist-like lubricating oil, which are fluids, into the housing 2 from the outside. The discharge port 22 discharges the refrigerant compressed by the crawl compression mechanism 6 to the outside of the housing 2.

In the following, the direction in which the central axis X extends is defined as the axial direction Da. A radial direction based on the central axis X is simply referred to as a radial direction Dr. Further, a direction around the drive axis centering on the central axis X is defined as a circumferential direction Dc.

The front housing 3 is attached to the housing 2 so as to close the opening on the one end 2a side of the housing 2. The front housing 3 is fixed to the housing 2 so as to form a sealed space together with the housing 2. The scroll compression mechanism 6 and the drive shaft 5 are accommodated in this sealed space. The front housing 3 has a bearing holding portion 31 at a portion inserted inside the housing 2. The bearing holding portion 31 extends in a cylindrical shape toward the other end 2 b of the housing 2. The bearing holding portion 31 is formed with a first oil supply passage 81 that penetrates the inside and outside of the bearing holding portion 31. The first oil supply passage 81 communicates with the inner space S3 in the bearing holding portion 31 between the main bearing 7 and the sub bearing 8. The front housing 3 is formed with a second oil supply passage 82 that communicates the inner space S 3 with the outer peripheral side of the sub-bearing 8 in the through hole 32. Further, a through hole 32 penetrating in the axial direction Da is formed in the central portion of the front housing 3.

The drive shaft 5 is driven to rotate around the central axis X. The drive shaft 5 extends in the axial direction Da. The drive shaft 5 is rotatably supported by the front housing 3 via a main bearing 7 and a sub bearing 8. One end portion 5a, which is one side of the drive shaft 5 in the axial direction Da, protrudes from the front housing 3 to the outside in a state where the drive shaft 5 is inserted through the through hole 32. A lip seal 9 is provided between the drive shaft 5 and the through hole 32 to maintain the sealing performance. The drive shaft 5 has a disk-shaped disk portion 5d at the other end in the axial direction Da (on the other end 2b side of the housing 2).

On the other side in the axial direction Da of the disk portion 5d of the drive shaft 5, a crank pin 51 is provided at a position eccentric by a predetermined dimension in the radial direction Dr, which is a direction orthogonal to the central axis X of the drive shaft 5. . The crank pin 51 protrudes from the end of the disk portion 5 d of the drive shaft 5 toward the other end 2 b of the housing 2. Therefore, the crank pin 51 is formed integrally with the other end portion of the drive shaft 5 in the axial direction Da. When the drive shaft 5 rotates about the central axis X, the crankpin 51 turns along a circular orbit with a radius that is an eccentric dimension in the radial direction Dr with respect to the central axis X.

The main bearing 7 is fixed inside the bearing holding portion 31 of the front housing 3. The disk portion 5d is fitted inside the main bearing 7 and is rotatably supported.

The sub bearing 8 is arranged on the front housing 3 side with respect to the main bearing 7. The sub bearing 8 is provided inside the through hole 32 of the front housing 3. The drive shaft 5 is rotatably supported via a sub-bearing 8 at an intermediate portion in the axial direction Da between the one end portion 5a and the disk portion 5d.

A pulley 11 is rotatably provided in the front housing 3 via a bearing 10. A belt that transmits driving force from a driving source such as a motor or an engine is wound around the pulley 11. The pulley 11 and the one end 5 a of the drive shaft 5 are connected via an electromagnetic clutch 12. The drive shaft 5 rotates about the central axis X when power from the outside that drives the pulley 11 is transmitted via the electromagnetic clutch 12.

The scroll compression mechanism 6 is connected to the drive shaft 5. The scroll compression mechanism 6 includes a fixed scroll 61 and a turning scroll 62.

The fixed scroll 61 integrally includes a disk-shaped fixed end plate 61a and a spiral fixed wrap 61b that rises toward the front housing 3 (one side in the axial direction Da) with respect to the fixed end plate 61a. .

The fixed end plate 61a is fixed to the other end 2b of the housing 2 via a bolt 63. A discharge port 64 that discharges the refrigerant compressed by the scroll compression mechanism 6 is formed at the center of the fixed end plate 61a.

The fixed wrap 61b is formed such that the height in the axial direction Da decreases stepwise from the outer peripheral side toward the inner peripheral side. Further, in the fixed end plate 61a, the groove bottom surface 61c, which is the surface on which the fixed wrap 61b is formed, is formed so as to increase stepwise from the outer peripheral side toward the inner peripheral side toward the side where the fixed lap 61b rises. Has been. An O-ring 69 is provided on the other side of the outer peripheral surface of the fixed end plate 61a in the axial direction Da. The O-ring 69 is in close contact with the inner peripheral surface of the housing 2. As a result, the space between the inner peripheral surface of the housing 2 and the outer peripheral side of the fixed end plate 61 a is the discharge chamber S 2 on the other side in the axial direction Da with respect to the O ring 69 and the front housing with respect to the O ring 69. 3 is divided into a suction chamber S1 on one side in the axial direction Da in which 3 is disposed.

The suction chamber S1 communicates with a suction port 21 formed in the housing 2. The low-pressure refrigerant that has circulated through the refrigeration cycle is sucked from the suction port 21, and the refrigerant is sucked into the compression chamber 65 through the suction chamber S1.

As shown in FIG. 2, the orbiting scroll 62 includes a disc-shaped orbiting end plate 62a, a spiral orbiting wrap 62b that stands on the fixed scroll 61 side (the other side in the axial direction Da) with respect to the orbiting end plate 62a, Is integrated.

The turning wrap 62b extends toward the side where the crank pin 51 is disposed and the opposite side of the axial direction Da with respect to the turning end plate 62a. The turning wrap 62b is formed so that the height in the axial direction Da decreases stepwise from the outer peripheral side toward the inner peripheral side. Further, the groove bottom surface 62c, which is the surface on the side where the turning wrap 62b is provided, is formed so as to increase stepwise from the outer peripheral side toward the inner peripheral side toward the rising side of the turning wrap 62b. Accordingly, the groove bottom surface 62c is formed with a step portion 62t in which the length of the turning end plate 62a in the axial direction Da changes.

As shown in FIG. 1, a drive bearing accommodating portion 66 for accommodating a drive bearing 67 is formed on the surface opposite to the groove bottom surface 62c of the turning end plate 62a in the axial direction Da. The drive bearing housing portion 66 has a cylindrical shape protruding to one side in the axial direction Da.

The crank pin 51 is inserted into the drive bearing 67 through the drive bush 68. That is, the drive bearing 67 is provided in a cylindrical shape so as to cover the crank pin 51 from the outside in the radial direction Dr. The drive bearing 67 accommodates a drive bush 68 fixed to the outer peripheral surface of the crankpin 51 in a rotatable state. As a result, the orbiting scroll 62 can be smoothly revolved around the fixed scroll 61 together with the crankpin 51 that revolves along the circular orbit as the drive shaft 5 rotates about the central axis X.

Further, as shown in FIG. 3, the swivel end plate 62a is formed therein with an oil passage 86 extending from the central portion of the swivel end plate 62a in the radial direction Dr toward the outside in the radial direction Dr. As shown in FIG. 2, two oil passages 86 of the present embodiment are formed at positions where the positions in the circumferential direction Dc are 180 ° different from each other so as to sandwich the center axis X with respect to the turning end plate 62a.

Note that the two oil passages 86 are not limited to being formed on the turning end plate 62a. For example, only one oil passage 86 may be formed for the turning end plate 62a, or three or more oil passages 86 may be formed.

As shown in FIG. 3, each oil passage 86 communicates a first opening 86 a that opens at the outer peripheral surface 62 f of the turning end plate 62 a and a second opening 86 b that opens in the drive bearing housing 66. Yes. The oil passage 86 extends in the radial direction Dr in a straight line from the turning end plate 62a to the outer peripheral surface 62f.

The second opening 86 b is formed on a surface facing the one side in the axial direction Da of the drive bearing housing portion 66 so as to face the drive bearing 67. The second opening 86b is formed so as to protrude toward the inside in the radial direction Dr from the inner peripheral surface to which the drive bearing 67 of the drive bearing housing 66 is attached. Accordingly, the second opening 86b is formed in the drive bearing housing 66 so that it can be seen when the drive bearing housing 66 is viewed from one side in the axial direction Da. For example, it is preferable that the opening area of the second opening 86b has an opening area having a size of ½ or more of the flow path cross section parallel to the axial direction Da of the oil path 86.

As shown in FIG. 2, such an oil passage 86 is formed in the revolving end plate 62a at a position avoiding the step portion 62t of the groove bottom surface 62c. That is, the oil passage 86 is formed so that the step 62t of the groove bottom surface 62c and the position in the circumferential direction Dc are different.

As shown in FIGS. 1 and 3, the drive shaft 5 is provided with a main balance weight 71 and a sub balance weight 72 that cancel the eccentric force generated by the turning of the crank pin 51 and the turning scroll 62.

The main balance weight 71 is provided between the drive shaft 5 and the orbiting scroll 62 in order to eliminate the unbalance due to the orbiting scroll 62 that rotates eccentrically with respect to the central axis X. The main balance weight 71 is disposed adjacent to the other side of the axial direction Da with respect to the disk portion 5d.

The sub-balance weight 72 is provided between the disk portion 5d of the drive shaft 5 and the sub-bearing 8 in order to eliminate the unbalance due to the orbiting scroll 62 that rotates eccentrically with respect to the central axis X. The sub balance weight 72 is disposed adjacent to one side of the axial direction Da with respect to the disk portion 5d.

The fixed wrap 61b of the fixed scroll 61 and the orbiting wrap 62b of the orbiting scroll 62 are provided so as to mesh with each other. A pair of compression chambers 65 are formed symmetrically with respect to the scroll center between the fixed scroll 61 and the orbiting scroll 62. The compression chamber 65 is partitioned by the fixed end plate 61a and the fixed wrap 61b, and the swivel end plate 62a and the swirl wrap 62b, and continues in a spiral shape. Thereby, when the compression chamber 65 moves from the outer peripheral side to the center side while reducing the volume and compresses the refrigerant, the refrigerant is compressed in both the circumferential direction Dc and the axial direction Da of the fixed wrap 61b and the swirl wrap 62b. . Therefore, the scroll compression mechanism 6 is configured to be so-called three-dimensionally compressible.

Such a scroll compression mechanism 6 is driven by the drive shaft 5 and sucks the refrigerant flowing into the housing 2 from the suction port 21 formed in the housing 2 into the compression chamber 65 from the outer peripheral side. The refrigerant sucked into the compression chamber 65 is compressed by moving the compression chamber 65 from the outer peripheral position to the center position while gradually reducing the volume. The compressed refrigerant flows from a discharge port 64 formed in the fixed end plate 61a of the fixed scroll 61 into a discharge chamber S2 formed in a gap between the fixed end plate 61a of the fixed scroll 61 and the other end 2b of the housing 2. Sent. Then, it discharges from the discharge port 22 to the refrigeration cycle side outside the housing 2.

Further, in such an open scroll compressor 1A, mist-like lubricating oil is introduced into the housing 2 from the suction port 21 together with the fluid. As shown in FIG. 3, a part of the mist-like lubricating oil introduced into the housing 2 from the suction port 21 is introduced into the inner space S 3 of the bearing holding portion 31 through the first oil supply passage 81. The lubricating oil is supplied to the main bearing 7 by a part of the lubricating oil introduced into the inner space S3.

Further, a part of the mist-like lubricating oil introduced into the inner space S3 is supplied into the through hole 32 through the second oil supply passage 82. Thereby, lubricating oil is supplied to the sub bearing 8.

According to the open scroll compressor 1A of the first embodiment described above, when the orbiting scroll 62 revolves by the rotation of the drive shaft 5, the scroll compression mechanism 6 causes the refrigerant to enter the compression chamber 65 from the suction chamber S1 on the outer peripheral side. Inhale. As a result, the pressure of the first opening 86a that opens on the outer peripheral surface 62f of the turning end plate 62a is lower than the pressure of the second opening 86b that opens in the drive bearing housing 66. Therefore, in the oil passage 86, a flow in which refrigerant or lubricating oil is sucked out from the second opening 86b on the drive bearing housing 66 side toward the first opening 86a on the outer peripheral side communicating with the suction chamber S1 occurs. Thereby, the lubricating oil in the drive bearing housing 66 is sucked from the second opening 86b opened in the drive bearing housing 66. As a result, a part of the mist-like lubricating oil introduced into the housing 2 from the suction port 21 is sucked into the drive bearing housing portion 66 in which the drive bearing 67 is housed. Therefore, the flow of the lubricating oil around the drive bearing 67 is made smooth, and the lubricating oil is prevented from staying. Thereby, the lubricating oil can be stably supplied to the drive bearing 67.

The oil passage 86 is formed so as to extend linearly in the radial direction Dr in the turning end plate 62a to the outer peripheral surface 62f. Therefore, if the hole extending in the radial direction Dr from the outer peripheral surface 62f is formed in the turning end plate 62a, the oil passage 86 can be formed, and the oil passage 86 can be easily processed.

Further, since the oil passage 86 extends in the radial direction Dr, the flow direction of the lubricating oil in the oil passage 86 can coincide with the direction of the centrifugal force acting on the turning end plate 62a. Therefore, the lubricating oil in the oil passage 86 can be flowed from the second opening 86b toward the first opening 86a by efficiently using the centrifugal force of the turning end plate 62a. As a result, the lubricating oil flow around the drive bearing 67 can be made smoother.

Furthermore, the oil passage 86 is provided avoiding the stepped portion 62t of the turning end plate 62a. Therefore, the stepped portion 62t of the turning end plate 62a whose thickness is changed and the oil passage 86 are formed at the same position, and the turning end plate 62a can be prevented from being partially thinned. Therefore, it is possible to suppress a decrease in strength in the vicinity of the stepped portion 62t of the turning end plate 62a where stress is concentrated.

Further, the opening area of the second opening 86b that opens into the drive bearing housing 66 through the oil passage 86 is set to be 1/2 or more of the cross-sectional area of the portion 86c extending in the radial direction Dr of the turning end plate 62a. Therefore, clogging can be prevented from occurring when the lubricating oil flows into the second opening 86b. Therefore, the lubricating oil in the drive bearing housing 66 can be efficiently sucked out from the second opening 86b, and the flow of the lubricating oil can be reliably generated around the drive bearing 67.

(Second embodiment)
Next, a second embodiment of the open type compressor of the present invention will be described. The open type compressor shown in the second embodiment has a different oil path. Therefore, in the description of the second embodiment, the same portions as those in the first embodiment are denoted by the same reference numerals and redundant description is omitted. That is, the description of the configuration of the open type compressor common to the configuration described in the first embodiment is omitted.

As shown in FIG. 4, the oil passage 86 A of the second embodiment is provided so as to avoid a position overlapping not only the stepped portion 62 t but also the suction port 21 in the circumferential direction Dc around the central axis X. Accordingly, the first opening 860 a of the second embodiment is formed at a position where the position in the circumferential direction Dc is different from the suction port 21.

When the open-type scroll compressor 1A is stopped and the orbiting scroll 62 is not rotating, the refrigerant may flow backward (liquid back). However, in the second embodiment, the positions of the first opening 860a and the suction port 21 are separated in the circumferential direction Dc. Therefore, even if the refrigerant flows backward, the refrigerant flowing from the suction port 21 is less likely to flow into the oil passage 86A from the first opening 860a. Therefore, it is possible to prevent the lubricating oil that lubricates the drive bearing 67 from being washed away by the refrigerant that flows back in the oil passage 86A and the lubricating oil in the vicinity of the drive bearing 67 is reduced.

(Third embodiment)
Next, a third embodiment of the open type compressor according to the present invention will be described. In the third embodiment described below, the configuration differs from the first embodiment and the second embodiment in that an oil supply path is provided on the drive shaft. Therefore, the same parts as those in the first embodiment and the second embodiment are denoted by the same reference numerals, and redundant description is omitted.

FIG. 5 is a cross-sectional view showing the configuration of the open scroll compressor of this embodiment.
As shown in FIG. 5, in the open scroll compressor 1 B of the third embodiment, a drive shaft oil supply path (oil supply path) 83 that supplies lubricating oil to the drive bearing 67 is formed inside the drive shaft 5. The drive shaft oil supply path 83 supplies the lubricating oil from the inner space S3, which is a space where the lubricating oil is introduced, to the drive bearing housing portion 66, which is a space where the drive bearing 67 is disposed. The drive shaft oil supply passage 83 of the third embodiment extends linearly in the axial direction Da. The drive shaft oil supply path 83 is formed at a position that is offset to the opposite side of the circumferential direction Dc from the crank pin 51 with the central axis X interposed therebetween. The drive shaft oil supply path 83 of the present embodiment is formed at a position that is 180 degrees out of phase with the crankpin 51 in the circumferential direction Dc around the central axis X. The drive shaft oil supply passage 83 has a first oil supply opening 83a that opens toward the inner space S3 in the housing 2 and a second oil supply opening 83b that opens toward the drive bearing housing 66. Yes. The drive shaft oil supply path 83 includes a third oil supply path 831 formed in the disk portion 5 d, a fourth oil supply path 832 formed in the main balance weight 71, and a fifth oil supply path 833 formed in the subbalance weight 72. It is constituted by.

The first oiling opening 83a and the second oiling opening 83b of the third embodiment are formed at positions offset to the opposite side of the crank pin 51 with the central axis X therebetween. The first oil supply opening 83a is formed at the same position as the second oil supply opening 83b in the circumferential direction Dc and the radial direction Dr. The second oil supply opening 83b is formed so as to face a surface of the drive bearing 67 facing the one side in the axial direction Da.

The third oil supply path 831 passes through the disk portion 5d in the axial direction Da. The third oil supply path 831 extends in a straight line parallel to the central axis X.

The fourth oil supply path 832 penetrates the main balance weight 71 in the axial direction Da. The fourth oil supply path 832 extends in a straight line parallel to the central axis X. The fourth oil supply path 832 is formed at a position communicating with the third oil supply path 831. The opening on the other side in the axial direction Da of the fourth oil supply path 832 is the second oil supply opening 83b.

The fifth oil supply passage 833 passes through the subbalance weight 72 in the axial direction Da. The fifth oil supply passage 833 extends in a straight line parallel to the central axis X. The fifth oil supply passage 833 is formed at a position communicating with the third oil supply passage 831. An opening on one side of the fifth oil supply passage 833 in the axial direction Da is a first oil supply opening 83a.

Here, the fourth oil supply path 832 of the main balance weight 71 and the fifth oil supply path 833 of the subbalance weight 72 are connected to the main oil balance weight 71 and the subbalance weight with respect to the third oil supply path 831 formed in the disk portion 5d. It is preferable to increase the inner diameter in consideration of 72 assembly tolerances and the like.

Part of the lubricating oil introduced into the inner space S3 of the bearing holding portion 31 flows into the fifth oil supply passage 833 from the first oil supply opening 83a. Thereafter, the fifth oil supply passage 833, the third oil supply passage 831, and the fourth oil supply passage 832 are circulated in this order and supplied to the drive bearing 67 from the second oil supply opening 83b.
As a result, new lubricating oil is supplied to the drive bearing 67.

Therefore, according to the open-type scroll compressor 1B of the third embodiment described above, the drive from the inner space S3 into which the lubricating oil is introduced through the third oil supply path 831, the fourth oil supply path 832, and the fifth oil supply path 833. Lubricating oil can be supplied to the drive bearing 67 in the bearing housing portion 66. As a result, new lubricating oil can be stably supplied to the drive bearing 67.

In addition, the third oil supply path 831, the fourth oil supply path 832, and the fifth oil supply path 833 are offset to the opposite side of the crankpin 51. Therefore, a space for forming the third oil supply path 831, the fourth oil supply path 832, and the fifth oil supply path 833 with respect to the disk portion 5 d, the main balance weight 71, and the subbalance weight 72 is provided with respect to the drive bearing 67. It becomes easy to ensure the position near the radial direction Dr. Therefore, the third oil supply path 831, the fourth oil supply path 832, and the fifth oil supply path 833 can be formed at positions close to the drive bearing 67.

Also, the second oil supply opening 83b opens so as to face the drive bearing 67 in the axial direction Da. Therefore, the lubricating oil can be directly supplied to the drive bearing 67 through the drive shaft oil supply passage 83. As a result, the lubricating oil can be reliably supplied by the drive bearing 67.

Furthermore, a part of the drive shaft oil supply path 83 is formed in the main balance weight 71 and the sub balance weight 72. Therefore, even when the main balance weight 71 and the sub balance weight 72 are provided, the lubricating oil can be supplied to the drive bearing 67 by forming the fourth oil supply path 832 and the fifth oil supply path 833. .

(Fourth embodiment)
Next, a fourth embodiment of the open type compressor according to the present invention will be described. In the fourth embodiment described below, only the configuration of the oil supply passage is different from that of the third embodiment. For this reason, the same parts as those in the first to third embodiments are denoted by the same reference numerals, and redundant description is omitted.

FIG. 6 is a cross-sectional view showing a configuration of an open scroll compressor according to the fourth embodiment.
As shown in FIG. 6, in the open type scroll compressor 1 C of the fourth embodiment, a drive shaft oil supply passage (oil supply passage) 88 that supplies lubricant to the drive bearing 67 is formed in the drive shaft 5 and the crankpin 51. Yes.

The drive shaft oil supply path 88 passes through the disk portion 5d and the crank pin 51 in the direction including the axial direction Da. The drive shaft oil supply path 88 of the present embodiment extends in a straight line in a direction inclined with respect to the axial direction Da. The drive shaft oil supply path 88 has a first oil supply opening 88a that faces the inner space S3 and opens at the disk portion 5d, and a second oil supply opening 88b that opens within the drive bearing housing 66. The drive shaft oil supply path 88 of the fourth embodiment is not formed in the main balance weight 71 or the subbalance weight 72. The first oil supply opening 88a is formed in the surface 5g on the front housing 3 side of the disk portion 5d. The second oil supply opening 88 b is formed at the tip of the crank pin 51 located in the drive bearing 67. The second oil supply opening 88b of the present embodiment is formed in the distal end surface 51g, which is the end surface facing the other side in the axial direction Da, among the distal ends.

Part of the lubricating oil introduced into the inner space S3 of the bearing holder 31 flows into the drive shaft oil supply path 88 from the first oil supply opening 88a. Thereafter, the oil flows through the drive shaft oil supply passage 88 and is supplied to the drive bearing 67 from the second oil supply opening 88b. As a result, new lubricating oil is supplied to the drive bearing 67.

Therefore, according to the open scroll compressor 1 C of the fourth embodiment described above, the inner space S 3 in which the lubricating oil is introduced into the housing 2 through the drive shaft oil supply path 88 is located in the back of the drive bearing 67. Lubricating oil can be supplied up to the tip surface 51g. Therefore, the lubricating oil can be directly supplied to the drive bearing 67. As a result, new lubricating oil can be stably supplied to the drive bearing 67.

In the present embodiment, the drive shaft oil supply path 88 is formed so as to be inclined with respect to the center axis X. However, the drive shaft oil supply path 88 is closer to the drive bearing 67 from the center axis X in the radial direction Dr. You may incline and form so that it may space apart outside. If it does in this way, it will become easy to discharge the mist-like lubricating oil which flows in the drive shaft oil supply path 88 toward the drive bearing 67 from the 2nd oil supply opening part 88b with a centrifugal force.

(Fifth embodiment)
Next, a fifth embodiment of the open type compressor according to the present invention will be described. In the fifth embodiment described below, the oil passage and the oil supply passage shown in the first embodiment, the third embodiment, and the fourth embodiment are provided.

FIG. 7 is a cross-sectional view showing a configuration of an open scroll compressor in the fifth embodiment.
As shown in FIG. 7, the open scroll compressor 1 D of the fifth embodiment includes an oil passage 86, a drive shaft oil supply passage 83, and a drive shaft oil supply passage 88.

Therefore, according to the open scroll compressor 1D of the fifth embodiment described above, the lubricating oil can be supplied from the inner space S3 to the drive bearing 67 by the different drive shaft oil supply passage 83 and the drive shaft oil supply passage 88. . Therefore, the lubricating oil can be directly supplied to the drive bearing 67. As a result, new lubricating oil can be stably supplied to the drive bearing 67. Further, since the oil passage 86 is formed, the lubricating oil in the drive bearing housing 66 is sucked from the second opening 86b. As a result, the lubricating oil flows around the drive bearing 67 more smoothly. Therefore, it is possible to prevent the lubricating oil from staying around the drive bearing 67 while supplying new lubricating oil to the drive bearing 67.
As a result, new lubricating oil can be supplied stably by the drive bearing 67.

Although the embodiments of the present invention have been described in detail with reference to the drawings, the configurations and combinations of the embodiments in the embodiments are examples, and the addition and omission of configurations are within the scope not departing from the gist of the present invention. , Substitutions, and other changes are possible. Further, the present invention is not limited by the embodiments, and is limited only by the scope of the claims.

In the fourth embodiment, the oil passage 86 shown in the first embodiment, the drive shaft oil supply passage 88 shown in the third embodiment, and the drive shaft oil supply passage 88 shown in the fourth embodiment are provided. Although all are provided, it is good also as a structure provided with at least two of these.

1A, 1B, 1C, 1D Open type scroll compressor (open type compressor)
2 housing 2a one end 2b other end 3 front housing 5 drive shaft 5a one end 5d disk 5g surface 6 scroll compression mechanism 7 main bearing 8 sub bearing 9 lip seal 10 bearing 11 pulley 12 electromagnetic clutch 21 inlet (oil introduction part) )
22 Discharge port 31 Bearing holding portion 32 Through hole 51 Crank pin 51g Tip surface 61 Fixed scroll 61a Fixed end plate 61b Fixed lap 61c Groove bottom surface 62 Turning scroll 62a Turning end plate 62b Turning lap 62c Groove bottom surface

62f Outer surface

62t Step portion 63 Bolt 64 Discharge port 65 Compression chamber 66 Drive bearing housing portion 67 Drive bearing 68 Drive bush 69 O-ring 71 Main balance weight 72 Sub balance weight 81 First oil supply passage 82 Second

oil supply passage

83, 88 Drive shaft

oil supply passage

83a, 88a First

Oil supply openings

83b, 88b Second oil supply opening 831 Third oil supply path 832 Fourth oil supply path 833 Fifth

oil supply path

86, 86A Oil path S1 Suction chamber S2 Discharge chamber S3 Inner space (space)
X Center axis Da Axial direction Dr Radial direction Dc Circumferential direction

Claims

A drive shaft that is driven to rotate about a central axis;
A crank pin formed integrally with an end of the drive shaft and eccentric from the central axis in a direction perpendicular to the central axis;
A drive bearing into which the crankpin is inserted;
A revolving end plate having a drive bearing accommodating portion for accommodating the drive bearing, and extending from the revolving end plate toward a side opposite to the axial direction in which the central axis extends with respect to a side on which the crank pin is disposed. A orbiting scroll having an orbiting wrap,
A housing that houses the drive shaft, the crankpin, and the orbiting scroll, and has an oil introduction portion that introduces lubricating oil supplied to the drive bearing from the outside,
The swivel end plate is an open type compression in which an oil passage is formed inside to communicate a first opening that opens at the outer peripheral surface of the swivel end plate and a second opening that opens in the drive bearing housing. Machine.
The open type compressor according to claim 1, wherein the oil passage extends in a radial direction in the revolving end plate.
The open-type compressor according to claim 1 or 2, wherein the first opening is formed at a position different from the oil introduction part in a circumferential direction around the central axis.
4. The open compression according to claim 1, wherein the oil passage is provided in the orbiting end plate so as to avoid a step portion formed on a surface on the side where the orbiting wrap is provided. 5. Machine.
The drive shaft includes a first oil supply opening that faces the space where the lubricant is introduced in the housing, and a second oil supply opening that faces the space where the drive bearing is disposed. The open type compressor as described in any one of Claim 1 to 4 in which the oil supply path which has is formed in the inside.
The open type compressor according to claim 5, wherein the second oil supply opening is formed at a position facing the drive bearing in the axial direction.
The open type compressor according to claim 5 or 6, wherein the oil supply passage extends in the axial direction at a position offset to the opposite side of the crank pin across the central shaft.
8. The fuel supply passage according to claim 5, wherein the oil supply passage is formed by communicating the drive shaft with a balance weight provided on the drive shaft and canceling an eccentric force generated by turning of the crank pin and the orbiting scroll. An open type compressor according to claim 1.
The open type compressor according to any one of claims 5 to 8, wherein the second oil supply opening is formed at a tip end portion of the crank pin located in the drive bearing.
A drive shaft that is driven to rotate about a central axis;
A crank pin formed integrally with an end of the drive shaft and eccentric from the central axis in a direction perpendicular to the central axis;
A drive bearing into which the crankpin is inserted;
A revolving end plate having a drive bearing accommodating portion for accommodating the drive bearing, and extending from the revolving end plate toward a side opposite to the axial direction in which the central axis extends with respect to a side on which the crank pin is disposed. A orbiting scroll having an orbiting wrap,
A housing that houses the drive shaft, the crankpin, and the orbiting scroll, and has an oil introduction portion that introduces lubricating oil supplied to the drive bearing from the outside,
The drive shaft includes a first oil supply opening that faces the space where the lubricant is introduced in the housing, and a second oil supply opening that faces the space where the drive bearing is disposed. An open-type compressor in which an oil supply passage having the inside is formed.