JP2021046811A - Horizontal scroll compressor - Google Patents

Abstract

To inhibit deterioration of mechanical efficiency and improve lubrication performance of a crank chamber in a horizontal scroll compressor.SOLUTION: A horizontal scroll compressor includes: a front housing 220 forming a part of a housing; a fixed scroll fixed to the front housing 220; a revolving scroll 340 which is disposed so as to revolve around an axis of the fixed scroll; and a driving force transmission mechanism which causes the revolving scroll 340 to revolve around the axis of the fixed scroll. A first groove part 220G extending from an inner peripheral end part to an outer peripheral end part is formed at a lower part of a step part 220E functioning as an annular thrust receiving surface of the front housing 220 which receives thrust force of the revolving scroll 340. A tapered second groove part 342C is formed in an area ranging from an outer peripheral surface to a back surface which is located at a lower part of a bottom plate 342 of the revolving scroll 340.SELECTED DRAWING: Figure 2

Description

The present invention relates to a horizontal scroll compressor that compresses a compressible fluid such as a gaseous refrigerant.

In the horizontal scroll compressor, the swivel scroll revolves around the axis of the fixed scroll to change the volume of the compression chamber partitioned by the swivel scroll and the fixed scroll, which is an example of a compressible fluid gas. It is configured to suck, compress and discharge the refrigerant. In the horizontal scroll compressor, as described in Japanese Patent Application Laid-Open No. 2006-226147 (Patent Document 1), a crank mechanism that revolves a swivel scroll around the axis of a fixed scroll by a lubricating oil contained in a gaseous refrigerant. The crank chamber where such things are housed is lubricated.

Japanese Unexamined Patent Publication No. 2006-226147

As the lubricating oil contained in the gaseous refrigerant, the lubricating oil separated from the gaseous refrigerant compressed in the compression chamber by the oil separator is used. At this time, the lubricating oil separated by the oil separator is supplied to the upper part of the crank chamber through the oil passage formed in the upper part of the fixed scroll, but the gas sucked from the suction port formed in the vicinity thereof. It is easily flowed by the refrigerant and supplied to the space near the outer peripheral end of the fixed scroll and the swivel scroll. For this reason, the absolute amount of lubricating oil supplied to the crank chamber is reduced, and lubrication of moving parts and the like in the crank chamber tends to be insufficient. In the prior art, the above-mentioned problems are less likely to occur by devising the formation position of the suction port, but the suction port is introduced into the space near the outer end of the fixed scroll and the swivel scroll. There was a risk that the amount of gaseous refrigerant would be reduced, leading to a decrease in the mechanical efficiency of the horizontal scroll compressor.

Therefore, an object of the present invention is to provide a horizontal scroll compressor in which the lubrication performance of the crank chamber is improved while suppressing a decrease in mechanical efficiency.

The horizontal scroll compressor is a housing, a fixed scroll fixed to the housing, a swivel scroll arranged so as to revolve around the axis of the fixed scroll, and a drive that revolves the swivel scroll around the axis of the fixed scroll. It is equipped with a force transmission mechanism. A first groove extending from the inner peripheral end to the outer peripheral end is formed at the lower part of the ring-shaped thrust receiving surface of the housing that receives the thrust force of the swivel scroll, and is located at the lower part of the bottom plate of the swivel scroll. A tapered second groove is formed from the outer peripheral surface to the back surface.

According to the present invention, with respect to the horizontal scroll compressor, it is possible to improve the lubrication performance of the crank chamber while suppressing a decrease in mechanical efficiency.

It is sectional drawing which shows an example of the horizontal scroll compressor. It is sectional drawing of the main part which shows the method of supplying the lubricating oil to a crank chamber. It is a perspective view which shows the swivel scroll arranged in the front housing. It is a perspective view which shows the 2nd groove part formed in the swivel scroll.

Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the attached drawings.
FIG. 1 shows an example of a horizontal scroll compressor (hereinafter referred to as “scroll compressor”) 100.

The scroll compressor 100 is incorporated into, for example, a refrigerant circuit of a vehicle air conditioner, sucks low-pressure gas refrigerant (compressible refrigerant) from the refrigerant circuit, compresses it, and discharges high-pressure gas refrigerant to the refrigerant circuit. The scroll compressor 100 includes a housing 200, a compression mechanism 300 that compresses a low-pressure gaseous refrigerant, and a driving force transmission mechanism 400 that transmits a rotational driving force to the compression mechanism 300 from the outside. Here, a predetermined amount of lubricating oil for lubricating the moving parts of the compression mechanism 300 and the driving force transmission mechanism 400 is stored in the lower part of the housing 200.

The housing 200 includes a front housing 220 that houses the compression mechanism 300 and the driving force transmission mechanism 400, and a rear housing 240 that is joined to the open end of the front housing 220.

The outer peripheral surface of the front housing 220 is formed in a stepped cylindrical shape whose outer diameter is reduced in four steps as the distance from the joint surface with the rear housing 240 increases. Here, the cylindrical shape may be such that it can be visually recognized as a cylindrical shape, and for example, a reinforcing rib, a mounting boss, or the like may be provided on the outer peripheral surface thereof (the shape is the same below). Further, the inner peripheral surface of the front housing 220 is formed in a stepped cylindrical shape whose outer diameter is reduced in four stages as the distance from the joint surface with the rear housing 240 increases. Therefore, the front housing 220 has a similar shape to the outer peripheral surface and the inner peripheral surface thereof, and is formed in a cylindrical shape having substantially the same outer shell thickness as a whole and having a diameter reduced in four stages. Further, a suction port P1 for sucking low-pressure gaseous refrigerant from the refrigerant circuit is formed at a predetermined position on the peripheral wall of the front housing 220. The details of the suction port P1 will be described later.

In the following description, for convenience of explanation, regarding the stepped cylindrical inner peripheral surface of the front housing 220, from the large diameter portion to the small diameter portion, the first inner peripheral surface 220A, the second inner peripheral surface 220B, and the third inner surface are described. It will be referred to as the peripheral surface 220C and the fourth inner peripheral surface 220D.

The rear housing 240 has a hemispherical shape in which the central portion thereof bulges outward as the distance from the joint surface with the front housing 220 increases. Therefore, the rear housing 240 cooperates with the compression mechanism 300 to form a discharge chamber H1 having a predetermined volume. Further, the rear housing 240 incorporates a centrifugal oil separator (not shown) that separates the lubricating oil from the gaseous refrigerant in the discharge chamber H1. Further, a discharge port P2 is formed at a predetermined position on the peripheral wall of the rear housing 240 to discharge the high-pressure gaseous refrigerant from which the lubricating oil is separated by the oil separator to the refrigerant circuit.

The front housing 220 and the rear housing 240 can be separated by a plurality of bolts 500, which can be mentioned as an example of a fastener, in a state where the open end of the front housing 220 and the open end of the rear housing 240 are joined. It has been concluded.

The compression mechanism 300 is arranged in a cylindrical space partitioned by the first inner peripheral surface 220A of the front housing 220. The compression mechanism 300 includes a fixed scroll 320 arranged so as to close the opening on the large diameter side of the front housing 220, and a ring-shaped step portion that transitions from the first inner peripheral surface 220A to the second inner peripheral surface 220B. It is configured to include a swivel scroll 340 arranged between the 220E and the fixed scroll 320.

The fixed scroll 320 includes a disk-shaped bottom plate 322 fitted to the open end of the first inner peripheral surface 220A of the front housing 220, and an involute-shaped wrap 324 extending from one surface of the bottom plate 322 toward the swivel scroll 340. have. Further, the fixed scroll 320 has a thin ring shape that extends outward from the outer peripheral surface of the bottom plate 322 at the open end of the first inner peripheral surface 220A and is sandwiched between the joint surfaces of the front housing 220 and the rear housing 240. Further has a flange 326 of. The outer peripheral edge of the flange 326 is formed in a shape that follows the outer shape of the open end of the front housing 220, and through holes through which the shaft portion of the bolt 500 can penetrate are formed at a plurality of positions on the plate surface thereof. Therefore, the fixed scroll 320 is sandwiched between the joint surface between the front housing 220 and the rear housing 240 via its flange 326 to close the open end on the large diameter side of the front housing 220 and the rear housing 240. The discharge chamber H1 is partitioned in cooperation with.

The swivel scroll 340 has a disc-shaped bottom plate 342 arranged at a position facing the step portion 220E of the front housing 220, and an involute-shaped wrap 344 extending from one surface of the bottom plate 342 toward the fixed scroll 320. There is. The bottom plate 342 has an outer diameter smaller than that of the bottom plate 322 of the fixed scroll 320, and the thin ring-shaped thrust plate 510 is provided so that the outer peripheral portion of the other surface transmits the thrust force to the step portion 220E of the front housing 220. It is in contact with the step portion 220E via. The thrust plate 510 is fixed to the stepped portion 220E of the front housing 220.

The fixed scroll 320 and the swivel scroll 340 are meshed with each other so that the side walls of the laps 324 and 344 are partially in contact with each other in a state where the circumferential angles of the laps 324 and 344 are deviated from each other. At this time, a tip seal (not shown) that ensures airtightness with one surface of the bottom plate 342 of the swivel scroll 340 can be attached to the tip of the lap 324 of the fixed scroll 320. On the other hand, a tip seal (not shown) that ensures airtightness with one surface of the bottom plate 322 of the fixed scroll 320 can be attached to the tip of the lap 344 of the swivel scroll 340. Therefore, in the compression mechanism 300, a compression chamber H2 that sucks in and compresses the gaseous refrigerant, which is a crescent-shaped closed space, is partitioned between the fixed scroll 320 and the swivel scroll 340.

At the center of the bottom plate 322 of the fixed scroll 320, a discharge hole 322A for discharging the gaseous refrigerant compressed by the compression chamber H2 to the discharge chamber H1 is formed. On the other surface of the bottom plate 322 facing the discharge chamber H1, the flow of the gas refrigerant from the compression chamber H2 to the discharge chamber H1 is permitted, but the flow of the gas refrigerant from the discharge chamber H1 to the compression chamber H2 is blocked, for example. A check valve 328 consisting of a reed valve is attached.

A concave groove 322B is formed on the outer peripheral surface of the bottom plate 322 of the fixed scroll 320 over the entire circumference thereof, and an O-ring 322C for ensuring airtightness with the front housing 220 is fitted therein. Further, a concave groove 240A is formed on the open end surface of the rear housing 240 over the entire circumference thereof, and an O-ring 240B for ensuring airtightness with the front housing 220 is fitted therein.

The driving force transmission mechanism 400 includes a driving shaft 410, a crank pin 420, an eccentric bush 430, a balancer weight 440, an electromagnetic clutch 450, and a pulley 460.

The drive shaft 410 has a stepped cylindrical shape having a small diameter portion 410A and a large diameter portion 410B, and the tip portion of the small diameter portion 410A protrudes outward from the small diameter side end portion of the front housing 220, and the drive shaft 410 is attached to the front housing 220. It is housed freely in rotation. Specifically, the small diameter portion 410A of the drive shaft 410 is rotatably supported by a ball bearing 520 with respect to the opening side end portion of the fourth inner peripheral surface 220D of the front housing 220. Further, the large diameter portion 410B of the drive shaft 410 is rotatably supported by a roller bearing 530 with respect to the third inner peripheral surface 220C of the front housing 220. The small-diameter portion 410A of the drive shaft 410, which is located between the ball bearing 520 and the large-diameter portion 410B, is the fourth inner circumference of the front housing 220 by, for example, a sealing member 540 such as a mechanical seal or a lip seal. Airtightness with the surface 220D is ensured. The drive shaft 410 is not limited to rolling bearings such as ball bearings 520 and roller bearings 530, and may be rotatably supported by cylindrical slide bearings.

A cylindrical crankpin 420 extending from the large-diameter portion 410B of the drive shaft 410 toward the compression mechanism 300 is erected at a position eccentric from the axial center of the end surface in the axial direction. An eccentric bush 430 having a cylindrical outer shape is fixed to the outer peripheral surface of the crank pin 420 in a relative rotatable and eccentric state. The outer peripheral surface of the eccentric bush 430 is press-fitted into the inner peripheral surface of the annular boss portion 342A extending from the other surface (rear surface) of the bottom plate 342 of the swivel scroll 340 toward the small diameter side of the front housing 220. It is rotatably supported via a plain bearing 550. Further, a balancer weight 440 is attached to the outside of the radius of the boss portion 342A of the swivel scroll 340 in consideration of the weight of the swivel portion in order to reduce the vibration caused by the revolution of the swivel scroll 340.

As a rotation prevention mechanism for preventing the rotation of the rotation scroll 340, a plurality of rotation prevention pins 560 extending from the step portion 220E of the front housing 220 toward the rotation scroll 340 are press-fitted and fixed. The plurality of rotation prevention pins 560 are arranged equidistantly and equidistantly with respect to the axis of the drive shaft 410. In the scroll compressor 100 shown in FIG. 1, four rotation prevention pins 560 are press-fitted and fixed to the stepped portion 220E of the front housing 220, but the number thereof can be arbitrary.

Circular holes 342B extending from the other surface of the bottom plate 342 toward one surface at a plurality of locations facing the rotation prevention pin 560 protruding from the step portion 220E of the front housing 220 on the other surface of the bottom plate 342 of the swivel scroll 340. Are formed respectively. The tips of the plurality of rotation prevention pins 560 are fitted so as to revolve around the axis of the circular hole 342B of the swivel scroll 340 while being inscribed in the circular hole 342B. Therefore, the swivel scroll 340 revolves around the axis of the fixed scroll 320 in a state where its rotation is prevented. A plurality of through holes through which the rotation prevention pin 560 penetrates are formed on the plate surface of the thrust plate 510.

The tip of the drive shaft 410 is connected to a pulley 460 that is rotated by external power via an electromagnetic clutch 450 that is idlely attached to the outer peripheral surface of the small diameter portion of the front housing 220. Therefore, when the electromagnetic clutch 450 is operated, the pulley 460 and the drive shaft 410 are connected, and the drive shaft 410 is rotated by the rotational force of the pulley 460. On the other hand, when the operation of the electromagnetic clutch 450 is stopped, the pulley 460 and the drive shaft 410 are disconnected, and the rotation of the drive shaft 410 is stopped. By appropriately controlling the electromagnetic clutch 450 in this way, the operation of the scroll compressor 100 can be controlled.

Next, the operation of the scroll compressor 100 will be described.
When the drive shaft 410 is rotated by external power, the rotational force is transmitted to the swivel scroll 340 via the crank pin 420 and the eccentric bush 430, and the shaft center of the fixed scroll 320 is prevented from rotating while the swivel scroll 340 is prevented from rotating. Revolve around. As a result, the volume of the compression chamber H2 of the compression mechanism 300 changes, and the low-pressure gaseous refrigerant sucked into the internal space from the suction port P1 of the front housing 220 is guided to the central portion while being compressed by the compression chamber H2. .. The gaseous refrigerant guided to the central portion of the compression mechanism 300 is discharged to the discharge chamber H1 via the discharge hole 322A and the check valve 328 formed in the bottom plate 322 of the fixed scroll 320. The high-pressure gaseous refrigerant discharged into the discharge chamber H1 is separated into a gaseous refrigerant and a lubricating oil by an oil separator.

Then, the gaseous refrigerant from which the lubricating oil is separated is discharged to the refrigerant circuit via the discharge port P2 formed in the rear housing 240. On the other hand, the lubricating oil separated from the gaseous refrigerant is a cylindrical space defined by the second inner peripheral surface 220B of the front housing 220 via an oil passage (not shown) formed in the fixed scroll 320, that is, , The crank pin 420 of the driving force transmission mechanism 400, the eccentric bush 430, and the like are supplied to the crank chamber. At this time, the lubricating oil discharged from the oil passage of the fixed scroll 320 is mixed with a part of the gaseous refrigerant sucked from the suction port P1 and is formed in the upper portion of the step portion 220E of the front housing 220. It is supplied to the crank chamber through 220F. Then, the gaseous refrigerant containing the mist of the lubricating oil supplied to the crank chamber lubricates the movable parts such as the crank pin 420, the eccentric bush 430, the roller bearing 530, the seal member 540, and the slide bearing 550.

The lubricating oil that lubricates the movable part of the crank chamber passes through a lubricating oil discharge path (not shown) formed at a predetermined position on the step portion 220E of the front housing 220, and is provided by the first inner peripheral surface 220A of the front housing 220. It is returned to the bottom of the cylindrical space to be partitioned. The lubricating oil returned here is mixed with the gaseous refrigerant sucked from the suction port P1 of the front housing 220 and used for lubricating the compression mechanism 300.

By the way, the suction port P1 of the front housing 220 uses a part of the gaseous refrigerant sucked from the suction port P1 of the swivel scroll 340 so as to guide the lubricating oil separated from the gaseous refrigerant by the oil separator to the crank chamber. It is formed at a position that straddles the back surface. Further, since the suction port P1 is required to mainly guide the gaseous refrigerant to the space near the outer peripheral end of the fixed scroll 320 and the swivel scroll 340, the direction along the first inner peripheral surface 220A of the front housing 220, In short, it extends in its tangential direction. Therefore, most of the gaseous refrigerant sucked from the suction port P1 flows along the first inner peripheral surface 220A of the front housing 220. In this case, the lubricating oil discharged from the oil passage formed in the fixed scroll 320 is mixed with a part of the gaseous refrigerant sucked from the suction port P1 and flows, but the flow direction of the gaseous refrigerant is the front housing 220. Since it is along the first inner peripheral surface 220A of the above, the amount of lubricating oil supplied to the crank chamber is reduced. In the scroll compressor 100 of the prior art, the opening area on the back side of the swivel scroll 340 is increased to prevent insufficient lubrication, but the gaseous refrigerant introduced near the outer peripheral end of the fixed scroll 320 and the swivel scroll 340. For example, it has become a factor of lowering the mechanical efficiency of the compression mechanism 300.

Therefore, as shown in FIG. 2, a first groove portion 220G extending from the inner peripheral end to the outer peripheral end thereof is formed in the lower part of the step portion 220E of the front housing 220. Further, a tapered second groove portion 342C whose width gradually narrows toward the other surface of the bottom plate 342 is formed from the outer peripheral surface located below the bottom plate 342 of the swivel scroll 340 to the back surface. Here, the first groove portion 220G has a cross section of the same shape over the entire length, and is a position facing at least a cylindrical space partitioned by the first inner peripheral surface 220A regardless of the turning position of the swivel scroll 340. It suffices to extend to. Further, the second groove portion 342C may have a tapered shape that is symmetrical in the front view.

As shown in FIGS. 2 and 3, the lubricating oil OIL is stored in the lower part of the cylindrical space partitioned by the first inner peripheral surface 220A of the front housing 220. When the swivel scroll 340 swivels, it scoops up the lubricating oil OIL accumulated in the lower part of the cylindrical space partitioned by the first inner peripheral surface 220A, and lubricates from the second groove portion 342C to the first groove portion 220G. Supply OIL. At this time, since the second groove portion 342C has a tapered shape in which the width gradually narrows toward the back surface of the swivel scroll 340, the lubricating oil OIL enters from the wider side and the narrower side. Since the lubricating oil OIL is discharged from the above, a so-called pumping action can be expected, and it becomes easy to introduce the lubricating oil OIL from the second groove portion 342C to the first groove portion 220G.

Then, the lubricating oil OIL introduced into the first groove 220G is supplied to the crank chamber from the opening at the inner peripheral end thereof, and the crank pin 420, the eccentric bush 430, the roller bearing 530, the seal member 540, and the slide bearing 550. After lubricating the movable portion such as the above, it is returned to the lower part of the cylindrical space partitioned by the first inner peripheral surface 220A by gravity.

Therefore, even if the lubricating oil OIL is not sufficiently supplied to the crank chamber by the gaseous refrigerant sucked from the suction port P1 of the front housing 220, the first groove 220G formed in the step portion 220E of the front housing 220, The lubricating oil OIL is semi-forcedly supplied to the crank chamber by the second groove portion 342C formed in the swivel scroll 340. Therefore, the lubrication performance of the crank chamber can be improved. Further, since the lubricating oil OIL is semi-forcedly supplied to the crank chamber, the position of the suction port P1 formed in the front housing 220 can be optimized, and the mechanical efficiency of the compression mechanism 300 can be improved. it can. Further, as an additional effect, when assembling the scroll compressor 100, by making the second groove portion 342C formed in the swivel scroll 340 downward, the positioning becomes easy and the manufacturing efficiency is improved. You can also let it.

The first groove 220G formed in the stepped portion 220E of the front housing 220 may extend obliquely in the turning direction of the swivel scroll 340. In this way, when the lubricating oil OIL scraped up in the turning direction of the turning scroll 340 is introduced into the first groove 220G, it can be supplied to the crank chamber by utilizing the momentum.

Although the embodiments for carrying out the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea of the present invention. Please note.

As an example, the compression mechanism 300 of the scroll compressor 100 is not limited to the configuration operated by external power, but may be configured to be operated by an electric motor housed in the housing 200. In this case, the driving force transmission mechanism 400 includes a driving shaft 410, a crank pin 420, an eccentric bush 430, a balancer weight 440, and an electric motor. Further, the oil separator incorporated in the rear housing 240 is not limited to the centrifugal oil separator, and may be a known oil separator such as an inertial collision type.

100 Scroll compressor 200 Housing 220E Step part (thrust receiving surface)
220G 1st groove 320 Fixed scroll 340 Swivel scroll 342 Bottom plate 342C 2nd groove 400 Driving force transmission mechanism

Claims (3)

With the housing
With a fixed scroll fixed to the housing,
A swivel scroll that is revolved around the axis of the fixed scroll,
A driving force transmission mechanism that revolves the swivel scroll around the axis of the fixed scroll, and
With
A first groove extending from the inner peripheral end portion toward the outer peripheral end portion is formed in the lower portion of the ring-shaped thrust receiving surface of the housing that receives the thrust force of the swivel scroll.
A tapered second groove was formed from the outer peripheral surface located at the lower part of the bottom plate of the swivel scroll to the back surface.
Horizontal scroll compressor. The width of the tapered second groove gradually narrows toward the back surface of the swivel scroll.
The horizontal scroll compressor according to claim 1. The first groove portion extends obliquely in the turning direction of the turning scroll.
The horizontal scroll compressor according to claim 1 or 2.

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