JP4444629B2 - Scroll type fluid machine - Google Patents

Description

  The present invention relates to a scroll fluid machine suitable for use in a compressor such as air or refrigerant, a vacuum pump, or the like.

  Generally, a scroll type fluid machine performs compression or pump operation of air, a refrigerant, or the like by orbiting a revolving scroll with respect to a fixed scroll (see, for example, Patent Document 1).

JP-A-8-93674

  In this type of conventional scroll type fluid machine, a fixed scroll that constitutes a fixed side member together with a casing, and a orbiting scroll disposed in the casing are provided to face each other. The fixed scroll and the orbiting scroll are each composed of a disc-shaped end plate and a spiral wrap portion standing in the axial direction on the surface of the end plate. A plurality of compression chambers are defined.

  Further, a metal plate or the like is attached to the back surface of the end plate of the orbiting scroll with an interval, and a cooling air passage is formed between them. Further, a cylindrical connecting portion is provided on the back surface of the metal plate, and the crank portion of the drive shaft is connected to the inner peripheral side of the connecting portion via a swivel bearing. In the scroll type fluid machine, when the drive shaft is rotationally driven by a drive source such as a motor, the orbiting scroll performs the orbiting motion, thereby sequentially compressing fluid such as air and refrigerant in each compression chamber.

  Further, for example, three auxiliary cranks are provided on the back surface of the metal plate attached to the orbiting scroll so as to be positioned between the casing and these auxiliary cranks rotate when the orbiting scroll performs an orbiting motion. Is preventing. In this case, the auxiliary cranks are arranged at equal intervals in the circumferential direction with an interval of, for example, about 120 ° so as to surround the connecting portion at the center of the metal plate.

  On the other hand, the casing is provided with an inlet and an outlet for cooling air at positions facing the connecting portion of the orbiting scroll, and cools the connecting portion and the like that easily rise in temperature due to compression heat or the like during operation of the compressor. It has a configuration.

  In this case, each auxiliary crank arranged around the connecting portion is arranged such that one auxiliary crank covers the upstream side of the connecting portion with respect to the flow direction of the cooling air when viewed from the inlet of the cooling air. The other two auxiliary cranks are located on the downstream side of the connecting portion and arranged side by side on both sides of the connecting portion.

  By the way, in the prior art mentioned above, it is set as the structure which arrange | positions three auxiliary | assistant cranks around a connection part, for example. However, since these auxiliary cranks are projecting structures that protrude side by side in the vicinity of the connecting portion, the flow of cooling air flowing in from the inlet of the casing collides with the auxiliary crank when the compressor is in operation. There is a problem that it is difficult to cool the connecting portion efficiently.

  That is, the cooling air flowing in from the inlet of the casing does not easily come into contact with the connecting portion by hitting, for example, the auxiliary crank disposed on the upstream side of the connecting portion or the cooling fin of the auxiliary crank.

  As another problem, the cooling air that is about to flow out of the casing may be prevented from flowing out to the outside by the auxiliary cranks arranged side by side on both sides of the connecting portion, so that the cooling air stays in the casing. Then, there exists a problem of causing a temperature rise.

  Further, in the conventional technology, since the metal plate is attached to the back surface of the end plate of the orbiting scroll, even if the cooling performance is improved to some extent by this, the structure of the orbiting scroll becomes complicated and the whole machine becomes larger. is there.

  The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to efficiently cool the connection part of the orbiting scroll with the end plate and the drive shaft, and not only the orbiting scroll but also the entire machine. It is an object of the present invention to provide a scroll fluid machine that can improve the cooling efficiency with a simple structure.

  In order to solve the above-described problems, the present invention provides a fixed-side member comprising a casing, a fixed scroll provided on the casing and having a spiral wrap portion standing on the surface of the end plate, and can be swung in the casing. A rotating scroll provided on the surface of the end plate and having a spiral wrap portion that overlaps with the wrap portion of the fixed scroll, and a rotating scroll provided on the casing and connected to the rotating scroll. A rotating shaft for rotating the orbiting scroll, three auxiliary cranks provided between the casing and the rear surface of the end plate of the orbiting scroll, and the end plate of the orbiting scroll. The swivel scroll and the drive shaft are connected to the casing to allow cooling air to flow in and out along the back surface of the casing. Inlet port provided on both sides of the position, is applied to a scroll fluid machine comprising a flow outlet.

A feature of the configuration adopted by the invention of claim 1 is that a crank boss portion having a bearing receiving hole is provided at a position deviated from the rotational axis on the tip side of the drive shaft, and on the back side of the orbiting scroll. , An eccentric shaft extending in the axial direction toward the bearing housing hole of the crank boss portion and rotatably connected in the bearing housing hole is provided, and a plurality of radiating fins are provided on the back surface of the end plate of the orbiting scroll, from the tip of the radiation fins is provided a pivot bearing for rotatably supporting the eccentric shaft at a position apart in the axial direction of the eccentric shaft from said end plate, said three auxiliary crank, between the orbiting scroll and the drive shaft around the connecting portion, wherein with respect to the cooling air flow direction 2 disposed on both sides of the inlet port on the upstream side of the connecting portion between the orbiting scroll and the drive shaft, against the flow direction of the cooling air In that a configuration in which one disposed on the outlet side on the downstream side of the connecting portion between the orbiting scroll and the drive shaft Te.

The feature of the configuration invention of claim 2 is employed, the distal end side of the drive shaft, the crank boss portion having a bearing receiving hole in the eccentric position from the rotation axis is provided, on the back side of the orbiting scroll , An eccentric shaft extending in the axial direction toward the bearing housing hole of the crank boss portion and rotatably connected in the bearing housing hole is provided, and a plurality of radiating fins are provided on the back surface of the end plate of the orbiting scroll, from the tip of the radiation fins is provided a pivot bearing for rotatably supporting the eccentric shaft at a position apart in the axial direction of the eccentric shaft from the end plate, the three auxiliary crank, with respect to the flow direction of the cooling air Thus, the upstream side of the connection portion between the orbiting scroll and the drive shaft is arranged so as not to overlap the connection portion between the orbiting scroll and the drive shaft.

Further, according to the invention of claim 3, wherein the heat radiating fins is a configuration Ru extending along the flow direction of the cooling air.

Further, according to the invention of claim 4, wherein the eccentric shaft, the heat is configured to provide a hollow bore extending axially to suppress from being transferred to the orbiting bearing side through the eccentric shaft by the compression action.

  According to a fifth aspect of the present invention, a cooling fan that is rotated by the output shaft to generate cooling air is provided between the output shaft and the drive shaft of the motor, and the cooling air generated by the cooling fan is fixed to the motor. A fan casing that leads to the back surface of the scroll and the back surface of the orbiting scroll is provided.

Further, according to the invention of claim 6, wherein the motor case provided motor side suction port for sucking a cooling air to the opposite side of the cooling fan and the axial direction, to the fan casing sucks cooling air to the position of the cooling fan toward the fan-side inlet provided, wherein the cooling fan is set to suck constituting the cooling air from the motor side inlet and the fan-side inlet.
Furthermore, according to the invention of claim 7, the slewing bearing is arranged between the tip end side of the eccentric shaft extending in the axial direction toward the bearing housing hole and the bearing housing hole.

According to the first aspect of the present invention, the eccentric shaft can be extended in the axial direction from the back surface of the end plate of the orbiting scroll, and the drive shaft can be connected to the front end side via the orbiting bearing. As a result, the slewing bearing can be axially separated from the end plate where the compression heat is easily transmitted, and heat conduction to the slewing bearing can be reduced. In addition, for example, three auxiliary cranks can be arranged in a triangular shape around the connection portion between the orbiting scroll and the drive shaft. The two auxiliary cranks arranged on the upstream side of the connecting portion are located on the left and right sides away from the straight line connecting the inlet and the outlet through the connecting portion (that is, when viewed from the cooling air inlet). It can be disposed at a position that does not overlap with the connecting portion.

  Thereby, when the cooling air flows from the inflow port, the flow of the cooling air toward the connection part is not blocked by the auxiliary crank on the upstream side, so that the cooling air can be efficiently contacted with the connection part, Since it is located at the center of the end plate, it is possible to efficiently cool the connected portion where compression heat is easily transmitted.

  In addition, one auxiliary crank disposed on the downstream side of the connecting portion is, for example, a position on a straight line connecting the inlet and the outlet through the connecting portion (that is, the connecting portion as viewed from the inlet and the outlet of the cooling air). Can be disposed at a position overlapping with each other. In this case, since the auxiliary crank does not protrude to the side of the eccentric shaft with respect to the flow direction of the cooling air, the cooling air flows smoothly without disturbing the flow of the cooling air from the inlet to the outlet. It can be distributed.

  Therefore, even when these three auxiliary cranks are arranged in a well-balanced manner around the connecting portion, the flow of cooling air can be stabilized on the back side of the orbiting scroll, the connecting portion with the end plate of the orbiting scroll, the drive shaft, etc. Can be efficiently cooled, and the cooling performance can be improved.

  According to the second aspect of the present invention, each auxiliary crank can be disposed at a position that does not overlap with the connecting portion when viewed from the cooling air inlet, so that the cooling air flow from the inlet to the connecting portion is assisted. It is no longer blocked by the crank, and the flow of cooling air can be stabilized on the back side of the orbiting scroll. Thereby, the connection part where compression heat is easy to be transmitted can be efficiently cooled by the cooling air, and the cooling performance can be improved.

  According to the invention of claim 3, the contact area (heat radiation area) of the mirror plate with respect to the cooling air can be increased by the radiation fins provided on the back surface of the mirror plate, and the heat dissipation of the orbiting scroll can be enhanced.

Further, the cross-sectional area of the claimed according to the invention of claim 4, since the eccentric shaft is provided with a hollow bore extending in the axial direction, it is possible to enhance the heat dissipation by increasing the surface area of the eccentric shaft, also eccentric shaft It is possible to make it difficult for heat to be transmitted. Thereby, the temperature rise of a slewing bearing etc. by compression heat can be suppressed, and the heat resistance and lifetime can be improved.

  According to the invention of claim 5, the output shaft of the motor and the drive shaft can be connected by the cooling fan disposed between them, and the cooling fan can be driven together with the drive shaft. Since the cooling air generated by the cooling fan can be supplied to the back surface of the fixed scroll and the back surface of the orbiting scroll through the fan casing, each scroll can be efficiently cooled.

  Moreover, the part which accommodates a cooling fan among fan casings can be interposed between a casing and a motor, and it can suppress that the compression heat generate | occur | produced in the position of each scroll is transmitted from a casing to the motor side. Thereby, the temperature rise of a motor can be suppressed and the heat resistance and lifetime can be improved.

  Furthermore, according to the invention of claim 6, when the cooling fan operates, the cooling air can be sucked into the motor case from the motor side suction port, and the components in the case can be efficiently cooled. At this time, the cooling air can be sucked into the fan casing from the fan side suction port, and the fixed scroll and the orbiting scroll can be efficiently cooled by the cooling air and the cooling air sucked from the motor side suction port. it can.

  Therefore, since both the motor and each scroll can be cooled by the cooling fan, the number of parts related to the cooling system can be reduced, a wide range of cooling system can be realized with a simple structure, and the miniaturization of the machine can be promoted. .

  Hereinafter, the scroll type fluid machine according to the embodiment of the present invention will be described in detail with reference to FIGS.

  Reference numeral 1 denotes a scroll casing constituting the outer shell of the compressor. The scroll casing 1 is made of a metal material such as aluminum, and constitutes a fixed side member together with a fixed scroll 2 described later. As shown in FIGS. 2 and 3, the scroll casing 1 includes a large-diameter cylindrical portion 1A and a bottom portion 1B that closes one axial side of the cylindrical portion 1A. It is formed in an open substantially bottomed cylindrical shape.

  In the center of the bottom 1B, there is provided a bearing mounting cylinder 1C having a small diameter located on one side and a bearing mounting cylinder 1D having a large diameter positioned on the other side, which are described later as rotational axis O1-O1. It is formed around. Further, as shown in FIG. 6, three bearing mounting cylinders 1 </ b> E to which bearings 18 of auxiliary cranks 14, 15, and 16 to be described later are mounted are provided on the radially outer side of the bottom portion 1 </ b> B so as to be spaced apart in the circumferential direction. An annular (arc-shaped) step portion 1F is provided to which a cylindrical projection 22C of a fan casing 21 (casing body 22) described later is fitted.

  Further, as shown in FIGS. 3 and 4, the scroll casing 1 has an inlet 1 </ b> G that allows cooling air to flow into the back surface side of the end plate 3 </ b> A of the orbiting scroll 3, which will be described later, and an outlet 1 </ b> H that causes the cooling air to flow out. And are provided. And the inflow port 1G and the outflow port 1H open to the outer peripheral side of the cylinder part 1A, and are arrange | positioned on both sides of radial direction on both sides of the eccentric shaft 10 mentioned later. In this case, the scroll casing 1 is formed so that a straight line L-L in FIG. 4 connecting the center of the inflow port 1G and the center of the outflow port 1H passes through a position substantially equal to the eccentric shaft 10.

  When the compressor is in operation, a cooling fan 20 described later is operated, and when cooling air is sucked in the directions indicated by arrows A and B from the suction ports 23 and 28 in FIG. Flows in the direction of arrow C along the back side of the fixed scroll 2. The remaining cooling air flows from the inlet 1G of the casing 1 and flows in the direction indicated by the arrow D along the back surface side of the orbiting scroll 3 and then flows out from the outlet 1H.

  Reference numeral 2 denotes a fixed scroll that is fixed to the cylindrical portion 1A of the scroll casing 1, and the fixed scroll 2 is attached to the other side (opening side) of the cylindrical portion 1A and closes the cylindrical portion 1A. The fixed scroll 2 includes a substantially disc-shaped end plate 2A disposed so that the center thereof coincides with the rotation axis O1-O1, and a spiral wrap portion 2B provided upright on the surface of the end plate 2A. It is roughly constituted by a short cylindrical portion 2C formed surrounding the wrap portion 2B. A plurality of heat radiation fins 2D are provided upright on the back surface of the end plate 2A.

  3 is a orbiting scroll accommodated in the scroll casing 1 in a state of facing the fixed scroll 2, and the orbiting scroll 3 includes, as shown in FIG. 3 and FIG. A spiral wrap portion 3B is provided on the surface of the end plate 3A and is erected in the axial direction toward the fixed scroll 2.

  Here, three boss portions 3C (see FIG. 6) to which the bearings 19 of the auxiliary cranks 14, 15, 16 are attached are provided on the rear surface of the end plate 3A with a gap in the circumferential direction. Each boss portion 3 </ b> C is formed in a bottomed cylindrical shape and protrudes toward the bottom portion 1 </ b> B of the scroll casing 1 in the axial direction. Further, on the back surface of the end plate 3A, a plurality of radiating fins 3D extending along the flow direction of cooling air (the direction indicated by the arrow D in FIG. 4) are erected, and an eccentric shaft 10 described later is integrally provided. ing.

  Reference numeral 4 denotes a plurality of compression chambers formed between the fixed scroll 2 and the orbiting scroll 3. Each compression chamber 4 shifts the wrap portion 2B of the fixed scroll 2 and the wrap portion 3B of the orbiting scroll 3 by a predetermined angle. By being arranged so as to overlap each other, as shown in FIG. 2, they are formed between the lap portions 2B and 3B. Each compression chamber 4 is continuously reduced between the wrap portions 2B and 3B when the orbiting scroll 3 performs the orbiting motion, and compresses while sucking outside air from the suction port 5 (see FIG. 6) on the outer peripheral side. Air is discharged from the discharge port 6 at the center to the outside.

  A drive shaft 7 is rotatably provided on the scroll casing 1. The drive shaft 7 is driven to rotate by a motor 26 described later via a cooling fan 20, and rotates about a rotation axis O1-O1. As a result, the drive shaft 7 causes the orbiting scroll 3 to orbit through the crank boss portion 9 and the eccentric shaft 10 described later.

  The drive shaft 7 is rotatably supported by a bearing mounting cylinder 1 </ b> C of the scroll casing 1 via an auxiliary bearing 8 described later. Further, the base end side of the drive shaft 7 protrudes outside the scroll casing 1, and the crank boss portion 9 is provided on the front end side of the drive shaft 7 so as to be located in the casing 1.

  Reference numeral 8 denotes an auxiliary bearing that rotatably supports the drive shaft 7, and the auxiliary bearing 8 is composed of, for example, a grease-filled deep groove ball bearing or the like, between the bearing mounting cylinder 1 </ b> C of the scroll casing 1 and the outer periphery of the drive shaft 7. Is provided. In this case, the auxiliary bearing 8 and a later-described main bearing 11 are arranged coaxially with the rotation axis O1-O1 as the center.

  Reference numeral 9 denotes a crank boss portion integrally provided on the front end side of the drive shaft 7, and the crank boss portion 9 is formed in a large-diameter and thick disc shape as shown in FIG. The bearing 1 is rotatably supported in the bearing mounting cylinder 1D of the casing 1 and rotates integrally with the drive shaft 7 about the rotation axis O1-O1. Further, the crank boss portion 9 is spaced apart from the end plate 3A (radiation fin 3D) of the orbiting scroll 3 in the axial direction with a sufficient interval.

  Here, the crank boss portion 9 is provided with a bearing housing hole 9A that opens to the other side in the axial direction. The bearing housing hole 9A is formed as a shallow bottomed circular hole, and the axis O2-O2 of the bearing housing hole 9A is eccentric from the rotation axis O1-O1 of the drive shaft 7 by an eccentric amount δ. As a result, when the drive shaft 7 is driven to rotate, the bearing housing hole 9A of the crank boss portion 9 turns with an eccentric amount δ, and the orbiting scroll 3 turns with respect to the fixed scroll 2 via the eccentric shaft 10 and the like which will be described later. Can be made.

  Reference numeral 10 denotes an eccentric shaft integrally provided on the back side of the end plate 3A of the orbiting scroll 3, and the eccentric shaft 10 constitutes a connecting portion between the orbiting scroll 3 and the drive shaft 7. The eccentric shaft 10 is formed as a stepped cylindrical body whose inner peripheral side is hollow, and extends from the center of the back surface of the end plate 3A toward the bearing housing hole 9A of the crank boss portion 9 in one axial direction. Further, the distal end side of the eccentric shaft 10 enters the bearing housing hole 9A of the crank boss portion 9 and is rotatably connected to the crank boss portion 9 via a swing bearing 12 described later.

  Reference numeral 11 denotes a main bearing that rotatably supports the crank boss portion 9 (drive shaft 7). The main bearing 11 is composed of, for example, a grease-filled deep groove ball bearing or the like, and a bearing mounting cylinder 1D of the scroll casing 1 and the crank boss. It is provided between the outer periphery of the part 9. Moreover, the main bearing 11 is arrange | positioned on the plane FF orthogonal to the rotating shaft O1-O1 of the drive shaft 7, for example.

  Reference numeral 12 denotes a slewing bearing that rotatably supports the eccentric shaft 10, and the slewing bearing 12 is composed of, for example, a cylindrical roller bearing or the like, and is provided between the bearing housing hole 9 </ b> A of the crank boss portion 9 and the tip end side of the eccentric shaft 10. It has been.

Here, in this embodiment, since the eccentric shaft 10 is provided on the back surface of the end plate 3A of the orbiting scroll 3, the orbiting bearing 12 is positioned away from the end plate 3A in the axial direction by the protruding dimension of the eccentric shaft 10 . That is, as shown in FIG. 3, it is disposed at a position farther from the end plate 3A in the axial direction of the eccentric shaft 10 than the tip of the radiating fin 3D, and is in the same axial position as the main bearing 11 (almost the same as the plane FF On the plane). For this reason, heat conduction from the compression chamber 4 to the slewing bearing 12 can be reduced.

  Reference numeral 13 denotes a hollow hole provided in the eccentric shaft 10 so as to extend in the axial direction. The hollow hole 13 has a function of increasing the surface area of the eccentric shaft 10 to increase heat dissipation and reducing the cross-sectional area of the eccentric shaft 10. It has a function to make it difficult to transmit heat. Thereby, the hollow hole 13 can suppress that the compression heat which generate | occur | produced in the compression chamber 4 is transmitted to the turning bearing 12 side through the eccentric shaft 10, and can prevent the turning bearing 12 grade | etc., Temperature rising.

  14, 15, and 16 are three auxiliary cranks provided between the scroll casing 1 and the back surface of the orbiting scroll 3, and these auxiliary cranks 14, 15, and 16 are used when the orbiting scroll 3 performs an orbiting motion. The rotation is prevented.

  Here, as shown in FIG. 4, the auxiliary cranks 14 to 16 (and the boss portions 3C of the orbiting scroll 3) are arranged at positions corresponding to the apexes of the equilateral triangle with the eccentric shaft 10 as the center, and are fixed to each other. The eccentric shaft 10 is surrounded at intervals. Thereby, when the orbiting scroll 3 performs the orbiting motion, the rotation operation can be stably regulated by the three auxiliary cranks 14 to 16 at a well-balanced position.

  In this case, the two auxiliary cranks 14 and 15 among the auxiliary cranks 14 to 16 are arranged on the upstream side of the eccentric shaft 10 with respect to the flow direction of the cooling air (the direction indicated by the arrow D in FIG. 4). 10 is centered on the left and right sides of the inlet 1G of the casing 1. In other words, the auxiliary cranks 14 and 15 are located on the left and right sides away from the straight line LL connecting the inflow port 1G and the outflow port 1H through the eccentric shaft 10 (that is, with respect to the eccentric shaft 10 as viewed from the inflow port 1G). (Positions that do not overlap). Thereby, when the cooling air flows from the inlet 1G, the flow of the cooling air toward the eccentric shaft 10 is not blocked by the auxiliary cranks 14 and 15, so that the cooling air is efficiently brought into contact with the eccentric shaft 10. The cooling efficiency can be increased.

  On the other hand, one of the auxiliary cranks 14 to 16 is disposed on the downstream side of the eccentric shaft 10 with respect to the flow direction of the cooling air, and is positioned on the above-described straight line LL (that is, the inlet 1G). And the position overlapping with the eccentric shaft 10 when viewed from the outlet 1H) is arranged at the center of the outlet 1H. Thereby, since the auxiliary crank 16 does not protrude to the side of the eccentric shaft 10 with respect to the flow direction of the cooling air, the cooling air flow from the inlet 1G to the outlet 1H is not disturbed. Wind can be distributed smoothly.

  The auxiliary cranks 14 to 16 have substantially the same structure as each other, and as shown in FIGS. 3 and 6, a crank-shaped shaft portion 17 formed such that one side and the other side in the axial direction are eccentric from each other. A bearing 18 that rotatably supports one side of the shaft portion 17 in the bearing mounting cylinder 1E of the scroll casing 1, and a shaft 18 that rotatably supports the other side of the shaft portion 17 in the boss portion 3C of the orbiting scroll 3. The bearings 19 are respectively configured.

  Next, reference numeral 20 denotes a cooling fan provided between an output shaft 26B of the motor 26, which will be described later, and the drive shaft 7, and the cooling fan 20 is composed of, for example, a centrifugal fan or the like. 27 and the other side in the axial direction are connected to the drive shaft 7 in a non-rotating state by means such as key coupling.

  The cooling fan 20 is rotationally driven together with the drive shaft 7 by the motor 26, thereby sucking outside air from a motor-side suction port 28 and a fan-side suction port 23, which will be described later, and the fixed scroll 2 and the orbiting scroll 3. The cooling air is generated on the back surface and the inside of the motor 26.

  A fan casing 21 is provided so as to cover the back side of the fixed scroll 2 from the periphery of the cooling fan 20, and the fan casing 21 transmits the cooling air generated by the cooling fan 20 to the back side of the fixed scroll 2 and the orbiting scroll 3. To the back of each. The fan casing 21 includes a casing body 22, a duct 24, and a scroll cover 25, which will be described later.

  Reference numeral 22 denotes a bottomed cylindrical casing body provided between the scroll casing 1 and the motor 26. The casing body 22 is made of a metal material such as aluminum, for example, and as shown in FIGS. 20 is covered.

  Here, on one side in the axial direction of the casing body 22, a motor mounting hole 22 </ b> A that opens in a circular shape and an annular step portion 22 </ b> B that extends along the peripheral portion of the motor mounting hole 22 </ b> A are provided. Further, on the other side in the axial direction of the casing main body 22, as shown in FIG. 3, a cylindrical protrusion 22 </ b> C that is cylindrical and protrudes in the axial direction is provided.

  The casing main body 22 has a cylindrical projection 22C fitted into the stepped portion 1F of the scroll casing 1, and a cylindrical projection 26E of the motor 26 (motor case 26A) fitted into the stepped portion 22B. . Thereby, the scroll casing 1, the fan casing 21 (casing main body 22), and the motor 26 have the rotation axis O1-O1 by fitting the stepped portions 1F, 22B and the cylindrical protrusions 22C, 26E, respectively. It is aligned coaxially as the center, and in this state is fixed integrally by means such as screwing.

  Further, the casing body 22 is interposed between the scroll casing 1 and the motor case 26 </ b> A, thereby suppressing the compression heat generated on the casing 1 side from being transmitted to the motor 26 side and improving the heat resistance of the motor 26. It has become.

  Reference numeral 23 denotes a plurality of fan side suction ports provided on the outer peripheral side of the casing body 22, and each fan side suction port 23 sends cooling air into the fan casing 21 at a position near the cooling fan 20 as shown in FIG. 2. Inhale.

  A duct 24 is attached to the casing main body 22, and the duct 24 extends from the casing main body 22 to the other side in the axial direction on the side of the scroll casing 1, and the leading end side is connected to the inlet 1 </ b> G of the scroll casing 1. At the same time, the fixed scroll 2 extends to a position beyond the end plate 2A.

  Reference numeral 25 denotes a flat scroll cover provided so as to cover the rear surface side of the end plate 2A of the fixed scroll 2, and the scroll cover 25 forms a cooling air passage between the end plate 2A and the passage. Is connected to a duct 24.

  Reference numeral 26 denotes, for example, an electric motor provided on the other side in the axial direction of the fan casing 21 (casing main body 22). The motor 26 rotationally drives the drive shaft 7 and the cooling fan 20 together. As shown in FIG. 2, the motor 26 includes a motor case 26A formed of a metal material such as aluminum in a bottomed cylindrical shape, and an output shaft 26B rotatably supported at the center position of the motor case 26A. The substantially cylindrical stator 26C fixed to the inner peripheral side of the motor case 26A, and the rotor 26D provided on the outer peripheral side of the output shaft 26B and disposed with a gap on the inner peripheral side of the stator 26C. Yes.

  In this case, the motor case 26A is formed such that one side in the axial direction is closed and the other side is opened, and a motor side suction port 28 to be described later is formed on one side. Further, on the other side of the motor case 26A, as shown in FIG. 5, a cylindrical protrusion 26E that is cylindrical and protrudes in the axial direction is provided. The output shaft 26 </ b> B is connected to the drive shaft 7 via the shaft coupling 27 and the cooling fan 20.

  Reference numeral 28 denotes a plurality of motor-side suction ports provided in the motor case 26A of the motor 26. Each motor-side suction port 28 is disposed on the opposite side of the cooling fan 20 in the axial direction with the motor case 26A interposed therebetween. The stator 26C and the rotor 26D in the motor case 26A are cooled by sucking cooling air.

  The scroll type air compressor according to the present embodiment has the above-described configuration, and the operation thereof will be described next.

  First, when the motor 26 is operated, the drive shaft 7 is rotationally driven by the output shaft 26B via the cooling fan 20, and the crank boss portion 9 is rotated together with the drive shaft 7, whereby the eccentric shaft 10 is rotated along the axis O1- It turns with an eccentric amount δ with respect to O1. Thereby, the orbiting scroll 3 can orbit with respect to the fixed scroll 2 in a state where the rotation is restricted by the auxiliary cranks 14, 15 and 16.

  The compression chamber 4 defined between the wrap portion 2B of the fixed scroll 2 and the wrap portion 3B of the orbiting scroll 3 is continuously reduced by the orbiting motion of the orbiting scroll 3. Thereby, each compression chamber 4 discharges this compressed air toward the external air tank (not shown) etc. from the discharge port 6, compressing the air suck | inhaled from the suction inlet 5 one by one.

  On the other hand, during operation of the compressor, as shown in FIG. 2, when the cooling fan 20 is rotationally driven by the motor 26, outside air is sucked in the direction of arrow A from the fan-side suction port 23, and the cooling air flows into the fan casing 21. Occurs. In addition, outside air is also sucked in the direction indicated by arrow B from the motor-side suction port 28 and becomes cooling air. This cooling air flows between the stator 26C and the rotor 26D of the motor 26 to cool each component, and then the fan casing. 21 flows in.

  Then, the cooling air sucked into the fan casing 21 is guided along the duct 24 to reach the positions of the scrolls 2 and 3. Thereby, a part of cooling air flows into the back surface side of the end plate 2A of the fixed scroll 2, and cools the end plate 2A etc. by flowing in the arrow C direction along each radiation fin 2D.

  The remaining cooling air flows from the inlet 1G of the scroll casing 1 to the back surface side of the end plate 3A of the orbiting scroll 3 and flows in the direction indicated by the arrow D along each heat dissipating fin 3D. After 10 is cooled, it flows out from the outlet 1H.

  In this case, although the three auxiliary cranks 14 to 16 protrude from the rear surface side of the end plate 3A, these are arranged on the left and right sides of the inlet 1G on the upstream side of the eccentric shaft 10 or eccentric. Since it is arranged in the center of the outlet 1H on the downstream side of the shaft 10, the cooling air flowing from the inlet 1G toward the outlet 1H is not blocked by the auxiliary cranks 14 to 16, and the cooling air is circulated stably. Can be made.

  On the other hand, even when the scrolls 2 and 3 are cooled in this way, the compression heat generated in each compression chamber 4, particularly the compression heat generated in the compression chamber 4 on the center side, is easily transmitted to the eccentric shaft 10 of the orbiting scroll 3. . However, the eccentric shaft 10 protrudes in the axial direction from the back surface of the end plate 3A of the orbiting scroll 3, and the main bearing 11 and the orbiting bearing 12 are planes F− separated from the end plate 3A in the axial direction by the protruding dimension of the eccentric shaft 10. Are arranged together on F. Therefore, these bearings 11 and 12 can be sufficiently separated from the end plate 3A, and it is possible to prevent the compression heat from being transmitted to the respective bearings 11 and 12 from the end plate 3A side.

  Moreover, since the eccentric shaft 10 has a hollow structure having the hollow holes 13, the surface area can be increased to facilitate the release of compression heat, and the sectional area of the eccentric shaft 10 can be reduced to reduce the compression heat. Can be made difficult to be transmitted in the axial direction. As a result, heat conduction through the eccentric shaft 10 can be reliably reduced, and temperature rise of the bearings 11 and 12 can be suppressed.

  Thus, according to the present embodiment, the auxiliary cranks 14 and 15 are arranged on both sides of the inlet 1G on the upstream side of the eccentric shaft 10, and the auxiliary crank 16 is arranged on the downstream side of the eccentric shaft 10 in the center of the outlet 1H. For example, the three auxiliary cranks 14 to 16 can be arranged in a triangular shape around the eccentric shaft 10. The upstream side auxiliary cranks 14 and 15 are located on the left and right sides away from the straight line LL connecting the inlet 1G and the outlet 1H through the eccentric shaft 10 (that is, the cooling air inlet 1G). (Position not overlapping with the eccentric shaft 10 when viewed from the side).

  Thus, when the cooling air flows from the inlet 1G in the direction indicated by the arrow D, the flow of the cooling air toward the eccentric shaft 10 is not blocked by the auxiliary cranks 14 and 15 on the upstream side. The eccentric shaft 10 can be efficiently brought into contact with the shaft 10 and can be efficiently cooled because it is located in the center of the end plate 3A.

  Further, the downstream auxiliary crank 16 can be disposed at a position on the straight line LL (that is, a position overlapping the eccentric shaft 10 when viewed from the inflow port 1G and the outflow port 1H). Thereby, since this auxiliary crank 16 does not protrude to the side of the eccentric shaft 10 with respect to the flow direction of the cooling air, it does not disturb the flow of the cooling air from the inlet 1G to the outlet 1H. Cooling air can be circulated smoothly.

  Therefore, even when these three auxiliary cranks 14 to 16 are arranged in a well-balanced manner around the eccentric shaft 10, the flow of cooling air can be stabilized on the back side of the orbiting scroll 3, and the end plate 3A of the orbiting scroll 3 and The eccentric shaft 10 and the like can be efficiently cooled and the cooling performance can be improved.

  In addition, since a plurality of radiating fins 3D extending along the flow direction of the cooling air are provided on the rear surface of the end plate 3A of the orbiting scroll 3, the contact area (heat radiating area) of the end plate 3A with respect to the cooling air by these radiating fins 3D ) And the heat dissipation of the orbiting scroll 3 can be further enhanced.

  Further, a crank boss portion 9 having a bearing receiving hole 9A at a position eccentric from the rotation axis O1-O1 is provided on the front end side of the drive shaft 7, and the bearing of the crank boss portion 9 is provided on the back side of the orbiting scroll 3. Since the eccentric shaft 10 extending in the axial direction toward the housing hole 9A and rotatably connected to the bearing housing hole 9A via the orbiting bearing 12 is provided, the eccentric shaft 10 is pivoted from the back surface of the end plate 3A of the orbiting scroll 3. The drive shaft 7 can be connected to the front end side of the drive shaft 7 via the swivel bearing 12.

  Thereby, the main bearing 11 and the slewing bearing 12 can be separated in the axial direction with respect to the end plate 3A where the compression heat is easily transmitted, and heat conduction to these bearings 11 and 12 can be reduced. As a result, the life of the lubricant that lubricates the bearings 11 and 12 can be extended. Accordingly, the life of the bearings 11 and 12 can also be extended and the reliability, durability, and the like are improved. be able to.

  Moreover, since the eccentric shaft 10 is provided with a hollow hole 13 extending in the axial direction, the surface area of the eccentric shaft 10 can be increased to increase heat dissipation, and the cross-sectional area of the eccentric shaft 10 can be decreased to generate heat. It can be difficult to communicate. Thereby, the temperature rise of the bearings 11 and 12 and the like due to the compression heat can be more reliably suppressed.

  On the other hand, a cooling fan 20 is provided between the output shaft 26B of the motor 26 and the drive shaft 7, and cooling air from the cooling fan 20 is supplied between the motor case 26A of the motor 26 and the scroll casing 1 for each scroll 2. , 3 are provided with fan casings 21 respectively leading to the back surfaces of the three.

  Thus, the drive shaft 7 and the cooling fan 20 can be driven together by the motor 26, and the cooling air generated by the cooling fan 20 is supplied to the back surface of the fixed scroll 2 and the back surface of the orbiting scroll 3 through the fan casing 21, respectively. Therefore, the scrolls 2 and 3 can be efficiently cooled.

  Further, the casing body 22 of the fan casing 21 can be interposed between the scroll casing 1 and the motor 26, and the casing body 22 transmits the compression heat generated in the compression chamber 4 from the scroll casing 1 to the motor 26 side. Can be suppressed. Thereby, the temperature rise of the motor 26 can be suppressed and its heat resistance and life can be improved.

  In this case, since the casing body 22 is provided with a plurality of fan-side suction ports 23 and the motor case 26A is provided with a plurality of motor-side suction ports 28, when the cooling fan 20 is operated, the motor-side suction ports 28 Cooling air can be smoothly drawn into the motor case 26A, and the stator 26C, the rotor 26D, the bearing, and the like can be efficiently cooled.

  Further, at this time, since the cooling air can be sucked into the fan casing 21 from each fan side suction port 23, the scrolls 2 and 3 are efficiently moved by this cooling air and the cooling air sucked from the motor side suction port 28. The cooling air can be cooled and a sufficient amount of cooling air can be generated.

  Accordingly, since both the motor 26 and each of the scrolls 2 and 3 can be cooled by the cooling fan 20, the number of parts related to the cooling system can be reduced, a wide range of cooling systems can be realized with a simple structure, and the size of the air compressor can be reduced. Can be promoted.

  Further, the scroll casing 1 is provided with a stepped portion 1F, the casing main body 22 of the fan casing 21 is provided with a cylindrical projection 22C fitted to the stepped portion 1F and another stepped portion 22B, and a motor 26 Since the motor case 26A is provided with a cylindrical protrusion 26E fitted to the step 22B of the casing body 22, for example, when assembling the air compressor, the step 1F and the cylindrical protrusion 22C, and The step portion 22B and the cylindrical protrusions 22C and 26E can be easily fitted to each other.

  Thereby, the scroll casing 1, the fan casing 21 (casing body 22) and the motor 26 are coaxially positioned around the rotation axis O1-O1 using the step portions 1F, 22B and the cylindrical protrusions 22C, 26E. As a result, the assembly accuracy can be increased, and a highly accurate assembly operation can be easily performed.

  In the embodiment, the eccentric shaft 10 is integrally provided on the back surface of the end plate 3A of the orbiting scroll 3, and the drive shaft 7 and the crank boss portion 9 are integrally formed. However, the present invention is not limited to this. For example, the orbiting scroll and the eccentric shaft may be provided separately, and these may be integrally attached using fixing means such as screwing, press-fitting, and welding. Similarly, the drive shaft and the crank boss can be assembled after being formed as separate parts.

  In the embodiment, the scroll type air compressor is taken as an example of the scroll type fluid machine. However, the present invention is not limited to this, and may be applied to other scroll type fluid machines such as a refrigerant compressor for compressing a refrigerant.

1 is an external view showing a scroll type air compressor according to an embodiment of the present invention. It is the longitudinal cross-sectional view which looked at the air compressor from the arrow II-II direction in FIG. FIG. 3 is a partially enlarged cross-sectional view showing a fixed scroll, a turning scroll, and the like in FIG. 2 in an enlarged manner. FIG. 4 is an enlarged cross-sectional view of the air compressor when the back side of the orbiting scroll is viewed from the direction of arrows IV-IV in FIG. 3. FIG. 3 is a partially enlarged cross-sectional view showing an enlarged attachment site between a motor case and a fan casing in FIG. 2. It is a disassembled perspective view shown in the state before assembling an air compressor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Scroll casing 1G Inlet 1H Outlet 2 Fixed scroll 2A, 3A End plate 2B, 3B Lapping part 2D, 3D Radiation fin 3 Orbiting scroll 4 Compression chamber 5 Suction port 6 Discharge port 7 Drive shaft 9 Crank boss part 9A Bearing accommodation hole 10 Eccentric shaft (connection part)
12 slewing bearing 13 hollow hole 14, 15, 16 auxiliary crank 20 cooling fan 21 fan casing 22 casing body 23 fan side suction port 24 duct 25 scroll cover 26 motor 26A motor case 26B output shaft 28 motor side suction port O1-O1 rotation axis

Claims (7)

A fixed side member including a casing and a fixed scroll provided on the surface of the end plate provided with a spiral wrap portion; and a wrap portion of the fixed scroll provided on the surface of the end plate so as to be turnable in the casing. A orbiting scroll having a spiral wrap portion that overlaps with the rotating scroll, and a drive shaft that is rotatably provided in the casing and is rotationally driven by a motor in a state of being connected to the orbiting scroll, thereby rotating the orbiting scroll. And three auxiliary cranks provided between the casing and the rear surface of the end plate of the orbiting scroll to prevent the orbiting scroll from rotating, and cooling air flows in and out along the rear surface of the end plate of the orbiting scroll. Therefore, an inlet and a flow port provided on both sides of the casing with the connecting portion between the orbiting scroll and the drive shaft interposed therebetween. In the scroll fluid machine comprising a mouth,
Provided on the tip side of the drive shaft is a crank boss portion having a bearing receiving hole at a position eccentric from the rotation axis,
On the back side of the orbiting scroll, an eccentric shaft that extends in the axial direction toward the bearing housing hole of the crank boss portion and is rotatably connected to the bearing housing hole is provided.
A plurality of heat radiation fins are provided on the back surface of the end plate of the orbiting scroll,
A swivel bearing that rotatably supports the eccentric shaft at a position away from the end plate in the axial direction of the eccentric shaft than the tip of the radiating fin is provided,
The three auxiliary cranks are connected to the inlet of the inlet, which is located upstream of the connection portion between the orbiting scroll and the drive shaft with respect to the flow direction of the cooling air, with the connection portion between the orbiting scroll and the drive shaft as a center. Two scrolls are arranged on both sides, and one scroll is arranged on the outlet side, which is downstream from the connecting portion of the orbiting scroll and the drive shaft with respect to the flow direction of the cooling air. Fluid machine. A fixed side member including a casing and a fixed scroll provided on the surface of the end plate provided with a spiral wrap portion; and a wrap portion of the fixed scroll provided on the surface of the end plate so as to be turnable in the casing. A orbiting scroll having a spiral wrap portion that overlaps with the rotating scroll, and a drive shaft that is rotatably provided in the casing and is rotationally driven by a motor in a state of being connected to the orbiting scroll, thereby rotating the orbiting scroll. And three auxiliary cranks provided between the casing and the rear surface of the end plate of the orbiting scroll to prevent the orbiting scroll from rotating, and cooling air flows in and out along the rear surface of the end plate of the orbiting scroll. Therefore, an inlet and a flow port provided on both sides of the casing with the connecting portion between the orbiting scroll and the drive shaft interposed therebetween. In the scroll fluid machine comprising a mouth,
Provided on the tip side of the drive shaft is a crank boss portion having a bearing receiving hole at a position eccentric from the rotation axis,
On the back side of the orbiting scroll, an eccentric shaft that extends in the axial direction toward the bearing housing hole of the crank boss portion and is rotatably connected to the bearing housing hole is provided.
A plurality of heat radiation fins are provided on the back surface of the end plate of the orbiting scroll,
A swivel bearing that rotatably supports the eccentric shaft at a position away from the end plate in the axial direction of the eccentric shaft than the tip of the radiating fin is provided,
A configuration in which the three auxiliary cranks are arranged so as not to overlap the connecting portion between the orbiting scroll and the drive shaft on the upstream side of the connecting portion between the orbiting scroll and the drive shaft with respect to the flow direction of the cooling air. A scroll type fluid machine characterized by that. The radiating fins scroll fluid machine according to claim 1 or 2 comprising a structure extending along the flow direction of the cooling air. Before the Kihen arbor, scroll fluid according to claim 1, 2 or 3 heat of compression action is provided with a hollow bore extending axially to suppress from being transferred to the orbiting bearing side through the eccentric shaft machine.   A cooling fan that is rotated by the output shaft and generates cooling air is provided between the output shaft of the motor and the drive shaft, and the cooling air generated by the cooling fan is provided between the back surface of the fixed scroll and the orbiting scroll. The scroll type fluid machine according to claim 1, 2, 3, or 4, wherein a fan casing is provided for guiding to the back surface.   The motor case is provided with a motor side suction port for sucking cooling air on the opposite side of the cooling fan in the axial direction, and the fan casing is provided with a fan side suction port for sucking cooling air at a position near the cooling fan, The scroll fluid machine according to claim 5, wherein the cooling fan is configured to suck cooling air from the motor side suction port and the fan side suction port. The swivel bearing is disposed between a tip end side of the eccentric shaft extending in the axial direction toward the bearing receiving hole and the bearing receiving hole. Or the scroll type fluid machine of 6.

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