JP4460032B2 - Scroll type fluid machine - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a scroll fluid machine suitable for use in an air compressor, a vacuum pump, or the like.
[0002]
[Prior art]
In general, a scroll type fluid machine is provided with a casing, a fixed scroll provided in the casing, a drive shaft rotatably provided in the casing, and a rotary shaft provided at a front end side of the drive shaft via a swivel bearing. A revolving scroll that defines a plurality of compression chambers between the fixed scroll and a thrust receiver that is provided on the casing to support a thrust load acting on the revolving scroll and is in sliding contact with the back side of the revolving scroll. It has.
[0003]
This type of conventional scroll type fluid machine is driven from the suction port provided on the outer peripheral side of the fixed scroll by rotating the drive shaft from the outside and rotating the orbiting scroll with a fixed eccentric dimension with respect to the fixed scroll. While sucking a fluid such as air, the fluid is sequentially compressed in each compression chamber between the fixed scroll and the orbiting scroll, and the compressed fluid is discharged toward the outside from a discharge port provided at the center of the fixed scroll.
[0004]
In another prior art, an oil tank for storing cooling fluid is provided on the lower side of the casing, and an oil supply pump that operates following the orbiting motion of the orbiting scroll is provided between the casing and the orbiting scroll. What is provided is known (for example, JP-A-5-44402, JP-A-5-44668, etc.).
[0005]
In this conventional technique, during the compression operation, the oil liquid stored in the oil tank of the casing is sucked by the oil supply pump, and the oil liquid is placed between the orbiting scroll and the thrust receiver and in the sliding portion such as the orbiting bearing. In this configuration, the liquid is discharged and cooled and lubricated. And the oil liquid which became high temperature by cooling and lubricating the sliding part in this way flows down in a casing, and is returned in an oil tank.
[0006]
[Problems to be solved by the invention]
By the way, in the scroll type fluid machine by the other prior art mentioned above, it is set as the structure which returns the oil liquid which became high temperature by cooling a turning scroll, a turning bearing, etc. in the compression operation in the oil tank of a casing. Then, by cooling the oil tank of this casing from the outside using a cooling fan or the like, the heat of the oil returned to the oil tank is taken away, and the temperature of the oil is kept low.
[0007]
However, the fact is that the temperature of the oil liquid in the oil tank cannot be kept sufficiently low only by cooling the oil tank using a cooling fan or the like as described above. For this reason, the temperature of the oil liquid in the oil tank rises, and the hot oil liquid from the oil tank is supplied from the oil tank to the sliding parts such as the orbiting scroll and the orbiting bearing, and these sliding parts are efficiently cooled. There is a problem that it is difficult to do.
[0008]
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 dissipate the heat of the oil liquid that has become a high temperature by cooling the orbiting scroll, the orbiting bearing, etc. It is an object of the present invention to provide a scroll type fluid machine that can keep the temperature of the oil liquid low and can cool sliding parts such as orbiting scrolls and orbiting bearings.
[0009]
[Means for Solving the Problems]
In order to solve the above-described problems, a scroll type fluid machine according to the present invention includes a casing whose lower side is an oil tank for storing a cooling oil, a fixed scroll provided in the casing, and a rotatable structure provided in the casing. An orbiting scroll having a plurality of compression chambers between the fixed scroll and a driving shaft having a boss portion fitted on the tip end side of the driving shaft via an orbiting bearing, and acting on the orbiting scroll And a thrust receiver that is provided on the casing and slidably contacts the back side of the orbiting scroll.
[0010]
The feature of the configuration adopted by the invention of claim 1 is that the oil supply pump that has a pump chamber defined between the back side of the orbiting scroll and the thrust receiver and is operated following the movement of the orbiting scroll. An oil liquid suction passage that is provided in the thrust receiver and guides the oil liquid in the oil tank toward the pump chamber of the oil pump, and an oil liquid that is provided in the orbiting scroll and sucked into the pump chamber of the oil pump. An oil supply passage that is supplied toward the orbiting bearing, and an end portion of the oil supply fluid that is supplied to the orbiting bearing is provided in the drive shaft so as to return the oil liquid to the casing, and the other end side of the orbiting scroll has an oil solution. And a return passage that opens into the casing as an ejection hole, and the ejection hole of the return passage is based on the axis of the drive shaft when the amount of oil discharged from the oil supply pump becomes maximum. did In that a configuration that opens upward than Tairasen.
[0011]
With this configuration, when the orbiting scroll is orbiting, the oil supply pump operates following the movement of the orbiting scroll, and the oil stored in the oil tank of the casing passes through the suction passage provided on the thrust receiving side. Led into the pump chamber. The oil liquid introduced into the pump chamber is supplied to the orbiting bearing in the boss portion through the oil supply passage provided in the orbiting scroll by the oil supply pump, and the orbiting bearing is cooled and lubricated. And the oil liquid which became high temperature by cooling the slewing bearing is ejected from the ejection hole into the casing through the return passage provided in the drive shaft, and returned to the oil tank.
[0012]
Here, the amount of oil discharged by the oil supply pump varies according to the turning operation of the orbiting scroll. For example, when the orbiting scroll turns from the top dead center side to the bottom dead center position, the amount of oil discharged is maximized. When the amount of oil discharged from the oil supply pump becomes maximum, the return passage ejection hole is opened upward from the horizontal line with reference to the axis of the drive shaft. Most of the oily liquid can be actively sprayed from the ejection holes toward the upper inner wall of the casing.
[0013]
Thereby, the oil liquid flows down from the upper side to the lower side along the inner wall of the casing, and the heat of the oil liquid can be radiated from the wall portion of the casing to the outer side, so that the oil liquid can be cooled.
[0014]
According to a second aspect of the present invention, a balance weight that balances the rotation of the drive shaft is provided on the outer peripheral side of the drive shaft, and the ejection hole of the return passage opens to the outer peripheral side of the balance weight. Thereby, the ejection hole provided in the balance weight can be brought close to the inner wall of the casing, and the oil from the ejection hole can be efficiently sprayed on the inner wall of the casing.
[0015]
According to a third aspect of the present invention, the ejection hole of the return passage is constituted by a plurality of small holes that open in different directions. Accordingly, the oil liquid in the return passage can be diffused and ejected from the plurality of small holes in different directions, and the oil liquid from the return passage can be sprayed over a wide range on the upper inner wall of the casing. it can.
[0016]
According to a fourth aspect of the present invention, a guide projection for adjusting the jet direction of the oil is provided in the vicinity of the jet hole. In this case, the oil liquid ejected from the ejection hole hits a guide projection provided in the vicinity of the ejection hole, and the ejection direction is changed (bent) by the resistance received from the guide projection at this time. Thereby, the ejection direction of the oil liquid from the ejection hole can be appropriately adjusted in accordance with the shape and size of the guide protrusion.
[0017]
Further, as in the fifth aspect of the invention, even when the balance weight is provided with an ejection protrusion that protrudes outward in the radial direction and ejects the oil from the return passage to the outside, The tip can be brought close to the inner wall of the casing, and the oil in the return passage can be efficiently sprayed from the ejection protrusion toward the inner wall of the casing.
[0018]
On the other hand, the invention of claim 6 is configured such that a plurality of cooling fins for cooling the oil liquid ejected from the ejection holes of the return passage are provided on the inner wall of the casing. Thereby, while the oil liquid sprayed on the inner wall of the casing flows down to the oil tank along the inner wall of the casing, the heat of the oil liquid can be efficiently taken away by the cooling fin, and the heat dissipation of the oil liquid is further enhanced. be able to.
[0019]
According to a seventh aspect of the present invention, the oil supply pump is provided between the sliding contact surface side of the orbiting scroll and the thrust receiving portion, and is provided between the sliding contact surface and the other sliding contact surface. A swirl receiving recess defining a chamber, and projecting from the other sliding contact surface side into the swirl receiving recess, and relative to the swirl scroll along the peripheral wall surface of the swivel receiving recess. And a movable partition wall which is provided so as to be relatively movable in the swirl accommodating recess and which defines the pump chamber in the swirl accommodating recess together with a suction chamber and a discharge chamber. The movable partition wall is constituted by a partition wall drive mechanism that moves relative to the swivel accommodating recess following the movement of the swirler.
[0020]
With this configuration, during the turning of the orbiting scroll, the revolving element projecting on the other sliding contact surface side is disposed along the peripheral wall surface in the revolving housing accommodating recess formed on the one sliding contact surface side. While relatively rotating, the movable partition moves relatively within the recess accommodating recess by following the movement of the swing by the partition drive mechanism. At this time, the pump chamber in the swirl accommodating recess is defined as a suction chamber and a discharge chamber by the swirler and the movable partition wall, so that the oil from the suction passage is sucked into the suction chamber from the discharge chamber. It can discharge toward an oil supply path and a return path.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a scroll type air compressor will be described as an example of a scroll type fluid machine according to an embodiment of the present invention and will be described in detail with reference to the accompanying drawings.
[0022]
Here, FIG. 1 to FIG. 9 show a first embodiment of the present invention. In the figure, reference numeral 1 denotes a casing that forms the outer frame of the scroll type air compressor. As shown in FIGS. 1 and 8, the casing 1 includes an upper surface portion 1A, a bottom surface portion 1B, left and right side surface portions 1C, 1C. And a rear surface portion 1D. A cylindrical bearing portion 1E projects from the inner peripheral side of the rear surface portion 1D. In the casing 1, the bottom 1 </ b> B side, which is the lower side, serves as an oil tank 2, and an oil liquid 3 is stored in the oil tank 2.
[0023]
Reference numeral 4 denotes a fixed scroll provided on the thrust receiver 14. The fixed scroll 4 is formed in a substantially disk shape as shown in FIG. 1, and its center coincides with an axis O1-O1 of a drive shaft 5 to be described later. An end plate 4A disposed, a spiral wrap portion 4B standing on the surface of the end plate 4A, and a cylindrical portion 4C protruding in the axial direction so as to surround the wrap portion 4B from the outer peripheral side of the end plate 4A The flange portion 4D protrudes radially outward from the outer peripheral side of the cylindrical portion 4C and is fixed to a thrust receiver 14 described later.
[0024]
A drive shaft 5 is rotatably supported in the casing 1 by bearings 6 and 7. The drive shaft 5 is connected to a drive source (not shown) on the base end side, and a crank 5A on the front end side. It extends into the casing 1. In the crank 5A of the drive shaft 5, the axis O2-O2 is eccentric with respect to the axis O1-O1 of the drive shaft 5 by a dimension δ.
[0025]
8 is a balance weight provided between the bearing portion 1E of the casing 1 and a boss portion 9C of the orbiting scroll 9 to be described later and provided on the outer peripheral side of the drive shaft 5. The balance weight 8 is shown in FIG. Thus, it is formed as a semicircular arc (fan-shaped) plate body projecting radially outward from the drive shaft 5.
[0026]
The balance weight 8 is arranged on the opposite side to the axis O2-O2 of the crank 5A across the axis O1-O1 of the drive shaft 5, and the drive shaft 5 rotates relative to the orbiting scroll 9 attached to the crank 5A. It is a balance.
[0027]
Reference numeral 9 denotes a orbiting scroll provided in the casing 1 so as to be opposed to the fixed scroll 4, and the orbiting scroll 9 includes an end plate 9A formed in a disc shape as shown in FIG. 1, and a surface of the end plate 9A. It is generally configured by a spiral wrap portion 9B standing in the axial direction from the side.
[0028]
The orbiting scroll 9 has a boss 9C protruding from the center of the rear side of the end plate 9A, and the boss 9C is fitted to the crank 5A of the drive shaft 5 via the orbiting bearing 10 accommodated therein. It is mounted so as to be rotatable in the state. The front surface side of the end plate 9A is in sliding contact with the flange portion 4D of the fixed scroll 4, and the back surface (back surface side) is a sliding surface 9D that is in sliding contact with a thrust receiver 14 described later.
[0029]
The orbiting scroll 9 is disposed so as to overlap the wrap portion 4B of the fixed scroll 4 by, for example, 180 degrees, and a plurality of compression chambers 11, 11,... Are defined between the wrap portions 4B, 9B. Made. During the operation of the scroll type air compressor, the air is sucked into the compression chamber 11 on the outer peripheral side from the suction port 12 provided on the outer peripheral side of the fixed scroll 4, while the revolving scroll 9 performs the revolving motion. The air is compressed sequentially in the compression chamber 11, and finally, compressed air is discharged from the compression chamber 11 on the center side to the outside through the discharge port 13 provided at the center of the fixed scroll 4.
[0030]
An annular thrust receiver 14 is provided on the front end side of the casing 1 and constitutes a part of the casing 1. An annular notch portion 14 </ b> A is formed on the inner peripheral side of the thrust receiver 14. The end plate 9A of the orbiting scroll 9 is slidably attached. An annular slidable contact surface 14B slidably contacting the end plate 9A is formed in the cutout portion 14A of the thrust receiver 14, and the slidable contact surface 14B applies a thrust load acting on the orbiting scroll 9 between the end plate 9A. It is configured to accept.
[0031]
As shown in FIG. 4, reference numerals 15 and 15 denote a pair of guide protrusions provided so as to protrude radially inward from the inner peripheral side of the thrust receiver 14, and each guide protrusion 15 moves an Oldham ring 17 described later left and right. The guide is slidable.
[0032]
3 and 5, guide grooves 16 are provided on the rear side of the end plate 9A of the orbiting scroll 9, and the guide grooves 16 guide the Oldham ring 17 so as to be slidable upward and downward. is there.
[0033]
Reference numeral 17 denotes an Oldham ring slidably provided between the orbiting scroll 9 and the thrust receiver 14. The Oldham ring 17 is guided in two directions orthogonal to each other by a guide projection 15 and a guide groove 16. Together with the guide protrusion 15 and the guide groove 16, a rotation prevention mechanism for preventing the rotation of the orbiting scroll 9 is configured.
[0034]
Reference numeral 21 denotes an oil supply pump provided between the sliding contact surfaces 9D and 14B of the orbiting scroll 9 and the thrust receiver 14, and the oil supply pump 21 includes an after-mentioned rotor accommodating recess 22, a swirler 24, a slide plate 25, and a slide. The plate drive mechanism 28 is generally configured. The oil supply pump 21 operates following the movement of the orbiting scroll 9 as described later, and the oil 3 sucked into the pump chamber 23 is transferred between the sliding contact surfaces 9D and 14B between the orbiting scroll 9 and the thrust receiver 14. The slewing bearing 10 is supplied toward the sliding part.
[0035]
Reference numeral 22 denotes a swirl receiving recess provided on the sliding contact surface 14B side of the thrust receiver 14, and the swivel receiving recess 22 is formed as a bottomed circular hole having a peripheral wall surface 22A as shown in FIGS. A pump chamber 23 (see FIG. 1) is defined with the sliding contact surface 9D of the orbiting scroll 9. Then, as shown in FIG. 6, a revolving element 24 is accommodated in the pump chamber 23 of the revolving element accommodating recess 22 so as to be capable of revolving motion.
[0036]
Reference numeral 24 denotes a swivel projecting on the rear surface side of the end plate 9A of the orbiting scroll 9, and the swirler 24 is a circular guide protrusion protruding from the end plate 9A of the orbiting scroll 9 into the swivel accommodating recess 22. The end surface on the protruding end side is substantially in sliding contact with the bottom surface of the swivel accommodating recess 22. Further, on the outer peripheral side of the swirler 24, a sliding contact surface 24A comprising a plane along a direction perpendicular to the length direction of a guide groove 31 to be described later, that is, the left and right directions (X-axis direction) in FIG. The sliding contact surface 24A is in sliding contact with the slide plate 25.
[0037]
The swirler 24 is arranged in an eccentric state in the swivel accommodating recess 22, and the outer peripheral surface thereof is substantially in sliding contact with the peripheral wall surface 22A. For this reason, the revolving element 24 moves following the revolving scroll 9 and is configured to revolve within the revolving element accommodating recess 22 along the peripheral wall surface 22A.
[0038]
Here, as shown in FIGS. 1 and 2, when the orbiting scroll 9 is arranged together with the crank 5A at the bottom dead center position which is eccentric to the lowermost side with respect to the axis O1-O1 of the drive shaft 5, As shown in FIG. 6, 24 is also arranged at the bottom dead center position that is eccentric to the lowermost side with respect to the swivel accommodating recess 22. At this time, the balance weight 8 is disposed above the drive shaft 5 as shown in FIG.
[0039]
On the other hand, when the orbiting scroll 9 is arranged at the top dead center position (not shown) that is eccentric to the uppermost side with respect to the axis O1-O1 of the drive shaft 5, the revolving element 24 is also shown in FIG. As shown, it is disposed at a top dead center position that is eccentric to the uppermost side with respect to the swivel accommodating recess 22. At this time, the balance weight 8 is disposed below the drive shaft 5.
[0040]
Reference numeral 25 denotes a slide plate as a movable partition wall which is movably provided in the swivel accommodating recess 22, and the slide plate 25 is formed as a rectangular flat plate, and is inserted into a guide groove 31 described later in FIG. It is arranged to be slidable along the upper and lower directions (Y-axis direction). Further, both ends of the slide plate 25 in the length direction are in sliding contact with a sliding contact surface 24A of the revolving element 24 and a sliding contact surface 30A of a driving protrusion 30 described later.
[0041]
For this reason, when the orbiting scroll 9 is revolving, the slide plate 25 is moved in the revolving unit accommodating recess 22 by following the movement of the revolving unit 24 by the later-described slide plate driving mechanism 28 as shown in FIG. A suction chamber 26 and a discharge chamber 27 define the inside of the pump chamber 23 of the swivel accommodating recess 22 with the child 24.
[0042]
Reference numeral 28 denotes a slide plate drive mechanism that serves as a partition wall moving mechanism for moving the slide plate 25 in the rotator accommodating recess 22 following the movement of the revolver 24. The slide plate drive mechanism 28 is a recess that will be described later. A portion 29, a drive protrusion 30 and a guide groove 31 are included.
[0043]
Reference numeral 29 denotes a recessed portion formed in the sliding contact surface 14B of the thrust receiver 14 so as to be separated from the swivel accommodating recessed portion 22, and the recessed portion 29 is formed as a recessed portion having a substantially rectangular shape. The drive protrusion 30 is accommodated in the.
[0044]
Reference numeral 30 denotes a drive protrusion that protrudes from the rear surface side of the end plate 9A of the orbiting scroll 9, and the drive protrusion 30 is formed as a rectangular guide protrusion that protrudes from the end plate 9A into the recess 29. ing. Further, the drive protrusion 30 is formed with a sliding contact surface 30A composed of a flat surface facing the sliding contact surface 24A of the revolving element 24 in the upper and lower directions and extending parallel to the left and right directions. Is in sliding contact with the slide plate 25.
[0045]
For this reason, the drive protrusion 30 orbits together with the revolving element 24 when the orbiting scroll 9 revolves, and guides the sliding plate 25 with the slide plate 25 sandwiched between the revolving element 24 from both sides. It is configured to slide upward and downward along the groove 31. The drive protrusion 30 constitutes another rotation prevention mechanism for preventing the rotation of the orbiting scroll 9 together with the revolving element 24 and the slide plate 25 for the reason described later.
[0046]
31 is a guide groove provided on the sliding contact surface 14B of the thrust receiver 14 between the swivel accommodating recess 22 and the recess 29, and the guide groove 31 extends in an elongated direction along the upper and lower directions. It is formed as a concave groove, and both end sides thereof are connected to the swivel accommodating concave portion 22 and the concave concave portion 29. The guide groove 31 is configured to guide the slide plate 25 so as to be slidable upward and downward.
[0047]
An oil sump 32 is located between the swivel accommodating recess 22 and the recessed recess 29 and is provided on the sliding contact surface 14B side of the thrust receiver 14. The oil reservoir 32 is a sliding contact surface 14B of the thrust receiver 14. 7 and is formed as a circular hole that is continuous with the swirl receiving recess 22 and is disposed at a position that always communicates with the swirl receiving recess 22 and the oil supply passage 34 as shown in FIG. . For this reason, the oil sump 32 is configured to always allow the oil 3 from the discharge chamber 27 to be discharged to the oil supply passage 34 side.
[0048]
33 is a suction passage formed in the thrust receiver 14. One end of the suction passage 33 is located on the lower side of the thrust receiver 14 and opens into the oil tank 2 of the casing 1, and the other end is the position of the suction chamber 26. Is open to the bottom surface of the swivel accommodating recess 22. The suction passage 33 is configured to guide the oil liquid 3 stored in the oil tank 2 by the operation of the oil supply pump 21 toward the suction chamber 26.
[0049]
34 is an oil supply passage formed in the end plate 9A of the orbiting scroll 9. The oil supply passage 34 passes through the back side of the orbiting scroll 9 and has one end opened into the oil reservoir 32 and the other end inside the boss portion 9C. It is open. The oil supply passage 34 discharges the oil 3 from the discharge chamber 27 stored in the oil reservoir 32 from the back surface side of the end plate 9A of the orbiting scroll 9 toward the orbiting bearing 10, and the orbiting bearing 10 and the like. Is cooled and lubricated, and the entire orbiting scroll 9 is cooled while the oil liquid 3 flows through the oil supply passage 34.
[0050]
The end plate 9A of the orbiting scroll 9 is provided with an oil supply passage (not shown) for supplying the oil liquid 3 between the sliding contact surfaces 9D and 14B with the thrust receiver 14, and this oil supply passage communicates with the oil supply passage 34. is doing.
[0051]
Reference numeral 35 denotes a return passage formed in the drive shaft 5. The return passage 35 includes an axial passage portion 35 </ b> A extending in the axial direction inside the drive shaft 5 and having one end opened in the boss portion 9 </ b> C of the orbiting scroll 9 and one end. The side is communicated with the other end side of the axial passage portion 35A, and is constituted by a radial passage portion 35B extending radially inside the drive shaft 5 and the balance weight 8 along a YY line to be described later. ing.
[0052]
Further, the other end side of the radial passage portion 35B becomes an ejection hole 35C for the oil liquid 3 and opens to the outer peripheral end face of the balance weight 8, and a part of the oil liquid 3 discharged from the oil supply passage 34 to the swivel bearing 10 is partly discharged. It is configured to discharge into the casing 1 and return to the oil tank 2.
[0053]
Here, when the revolving element 24 is placed at the bottom dead center position in FIG. 6, the ejection hole 35C of the return passage 35 becomes a horizontal line with reference to the axis O1-O1 of the drive shaft 5 as shown in FIG. It is configured to open upward toward the uppermost end of the upper surface portion 1A of the casing 1 along the YY line that is upward from the XX line, preferably perpendicular to the XX line.
[0054]
For this reason, as will be described later, when the discharge amount Q of the oil liquid 3 from the oil supply pump 21 becomes maximum, the oil liquid 3 in the return passage 35 is indicated by an arrow from the ejection hole 35C as shown in FIGS. It sprays on the upper surface part 1A side of the casing 1 toward A direction.
[0055]
Reference numeral 36 denotes a seal member mounted between the sliding contact surfaces of the fixed scroll 4 and the orbiting scroll 9, and the sealing member 36 blocks the infiltration of the oil liquid 3 between the sliding contact surfaces.
[0056]
The scroll type air compressor according to the present embodiment has the above-described configuration, and the operation thereof will be described next.
[0057]
First, when the drive shaft 5 is rotated by the electric motor, the orbiting scroll 9 performs a circular motion (orbiting motion) with a turning radius of the dimension δ around the drive shaft 5, and the orbiting scroll and the wrap portion 4 </ b> B of the fixed scroll 4. The compression chambers 11, 11,... Defined between the nine lap portions 9B are continuously reduced. As a result, the compressed air is stored in the external air tank (not shown) or the like from the discharge port 13 of the fixed scroll 4 while sequentially compressing the outside air sucked from the suction port 12 of the fixed scroll 4 in each compression chamber 11. Let
[0058]
Further, when the orbiting scroll 9 is revolving, the Oldham ring 17 slides along the guide protrusion 15 on the thrust receiver 14 side, and the Oldham ring 17 and the orbiting scroll 9 are formed in the guide groove 16 on the orbiting scroll 9 side. Accordingly, the rotational torque of the orbiting scroll 9 via the drive shaft 5 is received between the Oldham ring 17, the guide protrusion 15, and the guide groove 16, so that the orbiting scroll 9 does not rotate. A turning motion is performed with a turning radius of dimension δ.
[0059]
Next, the operation of the oil supply pump 21 will be described with reference to FIG. 7. When the orbiting scroll 9 is first orbited, the revolving element 24 and the drive protrusion 30 integrated with the orbiting scroll 9 are shown in FIG. (A) top dead center position, (b) intermediate position, (c) bottom dead center position, (d) intermediate position in order of the inside of the swivel accommodating recess 22 and the interior of the recessed recess 29 Rotate in a clockwise direction. At this time, the slide plate 25 slides along the guide groove 31 by following both movements in a state where both end sides are in sliding contact with the revolving element 24 and the driving protrusion 30 respectively.
[0060]
As a result, the pump chamber 23 of the oil supply pump 21 continuously expands with the volume of the suction chamber 26 following the movement of the slide plate 25 in the order of (a), (b), (c), (d). Thus, a suction stroke is performed in which the oil 3 in the oil tank 2 is sucked into the suction chamber 26 through the suction passage 33.
[0061]
On the other hand, the volume of the discharge chamber 27 is continuously reduced following the movement of the slide plate 25 in the order of (a), (b), (c), and (d). A discharge stroke is performed in which 3 is discharged from the oil reservoir 32 toward the oil supply passage 34.
[0062]
The volume of the suction chamber 26 is maximized until the swirler 24 returns from the position (d) to the position (a), and the volume of the discharge chamber 27 is minimized while the suction stroke is completed. 3 is completed, and the next cycle is started.
[0063]
Thus, in the present embodiment, the oil pump 3 can stably discharge the oil 3 in the casing 1 from the oil supply passage 34 toward the slewing bearing 10, and the slewing bearing 10 can be cooled and lubricated. Further, the oil liquid 3 discharged to the slewing bearing 10 is allowed to flow through the return passage 35, and the drive shaft 5 can be cooled during this time. And the oil liquid 3 which became the high temperature by cooling the slewing bearing 10 etc. in this way can be returned in the oil tank 2 of the casing 1 from the return channel | path 35. FIG.
[0064]
Next, the relationship between the rotation angle α of the swivel 24 from the top dead center position shown in FIG. 7A and the discharge amount Q of the oil liquid 3 from the oil supply pump 21 will be described with reference to FIG. .
[0065]
Here, in this characteristic diagram, when the revolving element 24 is at the top dead center position in FIG. 7A, the rotation angle α is set to zero or 360 degrees, and when the revolving element 24 is at the bottom dead center position in FIG. The angle α is 180 degrees. Further, the rotation angle α is α1 when the revolving element 24 is at the position indicated by the two-dot chain line in FIG. 7B, and the rotation angle α is α2 when it is at the position indicated by the two-dot chain line in FIG. It is said.
[0066]
As is apparent from this characteristic diagram, when the rotation angle α of the swirler 24 reaches 180 degrees, that is, when the swirler 24 turns to the bottom dead center position of (c), the discharge amount Q is It was found that Qmax was the maximum. When the rotation angle α of the swirler 24 is in the range from zero to α1 or in the range from α2 to 360 degrees, the discharge chamber 27 is in communication with the suction passage 33, so that the oil pump 21 The discharge amount Q is substantially zero.
[0067]
Here, in the present embodiment, when the swirler 24 is placed at the bottom dead center position of (c) and the discharge amount Q of the oil supply pump 21 is maximized, the ejection hole 35C of the return passage 35 is driven. It is configured to open upward toward the uppermost end of the upper surface portion 1A of the casing 1 along the YY line perpendicular to the XX line that is a horizontal line with the axis O1-O1 of the shaft 5 as a reference.
[0068]
Therefore, most of the high-temperature oil liquid 3 flowing in the return passage 35 is blown upward from the ejection hole 35C in the direction of arrow A shown in FIGS. 3 and 8 toward the inner wall surface of the upper surface portion 1A of the casing 1. The oil liquid 3 can be cooled by removing heat from the upper surface portion 1A. And the oil liquid 3 sprayed on the upper surface part 1A of the casing 1 flows down along the side surface parts 1C, 1C, etc. in the arrow B direction shown in FIG. 8, and during this time, the heat of the oil liquid 3 is transferred to the side surface part 1C. The heat can be efficiently radiated from the outside to the outside.
[0069]
Further, by spraying the oil liquid 3 on the upper surface portion 1A of the casing 1 in this way, the heat dissipation time of the oil liquid 3 until the oil liquid 3 flows down from the upper surface portion 1A through the side surface portion 1C to the oil tank 2 is increased. It can be set longer, and the heat dissipation of the oil liquid 3 can be further enhanced.
[0070]
Therefore, according to the present embodiment, the temperature of the oil liquid 3 in the oil tank 2 can always be kept low, and the cold oil liquid 3 in the oil tank 2 is fed between the orbiting scroll 9 and the thrust receiver 14 by the oil supply pump 21. It can supply to each sliding site | part, such as sliding surface 9D, 14B, the turning bearing 10, etc., These cooling efficiency can be improved and the performance, reliability, etc. of the said air compressor can be improved.
[0071]
Further, since the return passage 35 is provided in the balance weight 8 protruding in the radial direction from the drive shaft 5, the ejection hole 35C of the return passage 35 can be arranged closer to the upper surface portion 1A of the casing 1, and the ejection passage 35C can be disposed from the ejection hole 35C. The oil liquid 3 can be sprayed on the upper surface portion 1A of the casing 1 more effectively, and the heat dissipation efficiency of the oil liquid 3 can be further enhanced.
[0072]
Further, the oil supply pump 21 has a configuration in which the pump chamber 23 including the suction chamber 26 and the discharge chamber 27 is provided between the sliding contact surfaces 9D and 14B of the orbiting scroll 9 and the thrust receiver 14, so that the pump chamber 23 can be arranged on the opposite side of the compression chamber 11 with the end plate 9A of the orbiting scroll 9 interposed therebetween.
[0073]
Thereby, as described in the prior art, the pressure of the high-pressure oil liquid 3 pressurized in the pump chamber 23 does not act on the outer peripheral side sliding contact surfaces of the fixed scroll 4 and the orbiting scroll 9. Can be prevented from leaking into the compression chamber 11 through the seal member 36 from this time, and clean compressed air can always be discharged to the outside from the discharge port 13 to improve the performance and reliability of the apparatus. Can do.
[0074]
Further, the revolving element 24 and the driving protrusion 30 that are integrally provided on the orbiting scroll 9 respectively have two sliding contact surfaces 24A and 30A that are in sliding contact with the slide plate 25, orthogonal to the X-axis direction and sliding contact surfaces. Since 24A and 30A are arranged so as to be parallel to each other, the revolving element 24 and the drive protrusion 30 can be slid relative to the slide plate 25 in the X-axis direction.
[0075]
In this case, since the slide plate 25 slides in the Y-axis direction along the guide groove 31 on the thrust receiver 14 side as described above, the swing plate 24, the slide plate 25, the drive protrusion 30 and the guide groove 31 rotate. Another rotation prevention mechanism for preventing the rotation of the scroll 9 can be configured. Thereby, the rotation torque from the orbiting scroll 9 added to the rotation prevention mechanism consisting of the Oldham ring 17 and the like can be reduced by the other rotation prevention mechanism, and the durability and life of the Oldham ring 17 can be improved.
[0076]
Next, FIGS. 10 and 11 show a second embodiment of the present invention. In this embodiment, the same reference numerals are given to the same components as those in the first embodiment, and the description thereof will be given. Shall be omitted.
[0077]
However, in the present embodiment, a hemispherical cap 42 is provided on the outer peripheral end surface of the balance weight 8 so as to cover the opening end side of the radial passage portion 41B of the return passage 41 from the outside, and these caps 42 are directed in different directions. In this configuration, a plurality of small holes 43, 43,.
[0078]
Here, the return passage 41 has an axial passage portion 41A and a radial passage portion 41B in substantially the same manner as the return passage 35 according to the first embodiment. However, the return passage 41 is different from that of the first embodiment having only one ejection hole 35 </ b> C in that the oil liquid 3 is ejected from a plurality of small holes 43 formed in the cap 42. .
[0079]
The cap 42 is formed as a hemispherical body that covers the radial passage portion 41 </ b> B of the return passage 41 from the outside, and is fixed to the outer peripheral end surface of the balance weight 8. The cap 42 is formed with a plurality of small holes 43, 43,... (Only three are shown) smaller in diameter than the return passage 41, and the small holes 43 are directed upward in different directions. It is open.
[0080]
Thus, in the present embodiment configured as described above, it is possible to obtain substantially the same operational effects as those of the first embodiment.
[0081]
In particular, in the present embodiment, a cap 42 is provided on the outer peripheral end surface of the balance weight 8 and the cap 42 is formed with a plurality of small holes 43 that open in different directions. The oil liquid 3 can be ejected from the small holes 43 in the directions indicated by arrows A1, A2 and A3 as shown in FIG. In addition to 1A, it can be sprayed on the side surface portion 1C, the rear surface portion 1D, the thrust receiver 14 and the like, and the heat dissipation efficiency of the oil liquid 3 can be further enhanced.
[0082]
Next, FIG. 12 shows a third embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted. And
[0083]
However, in the present embodiment, a guide projection 51 is provided in the vicinity of the ejection hole 35C of the return passage 35 on the outer peripheral end surface of the balance weight 8, and the ejection direction of the oil 3 from the ejection hole 35C is determined by the guide projection 51. The configuration is adjusted.
[0084]
Here, the guide protrusion 51 is formed as a plate-like protrusion extending from the balance weight 8 along the length direction of the radial passage portion 35C (return passage 35). The guide protrusion 51 is fixed to the outer peripheral end surface of the balance weight 8 at a position closer to the rear surface portion 1D side of the casing 1.
[0085]
Thus, in the present embodiment configured as described above, it is possible to obtain substantially the same operational effects as those of the first embodiment. In particular, in the present embodiment, a guide protrusion 51 is provided on the outer peripheral end surface of the balance weight 8 in the vicinity of the ejection hole 35C of the return passage 35 and near the rear surface portion 1D side of the casing 1.
[0086]
For this reason, when the oil liquid 3 is ejected from the ejection hole 35 </ b> C of the return passage 35, the oil liquid 3 hits the guide protrusion 51 and receives resistance from the guide protrusion 51 at this time. As a result, the ejection direction of the oil liquid 3 is bent toward the guide projection 51 in the direction indicated by arrow A4 shown in FIG. 12, whereby the oil liquid 3 is blown not only to the upper surface portion 1A of the casing 1 but also to the rear surface portion 1D side. Can be attached.
[0087]
As described above, in the present embodiment, the ejection direction of the oil liquid 3 from the ejection hole 35C can be appropriately adjusted according to the shape, size, and the like of the guide protrusion 51, and the oil liquid 3 is spread over the wall surface of the casing 1 over a wide range. The heat dissipation efficiency of the oil liquid 3 can be increased.
[0088]
Next, FIG. 13 shows a fourth embodiment of the present invention. In this embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. And
[0089]
However, in the present embodiment, a guide projection 61 is provided on the outer peripheral end surface of the balance weight 8 so as to be positioned near the ejection hole 35C of the return passage 35 and adjust the ejection direction of the oil 3 from the ejection hole 35C. The guide protrusion 61 is disposed obliquely inwardly toward the ejection hole 35C side of the return passage 35.
[0090]
Here, the guide protrusion 61 is formed as a plate-like protrusion extending obliquely from the balance weight 8 with respect to the length direction of the radial passage portion 35B (return passage 35). The guide protrusion 61 is fixed to the outer peripheral end surface of the balance weight 8 at a position closer to the rear surface portion 1D side of the casing 1.
[0091]
Thus, in the present embodiment configured as described above, it is possible to obtain substantially the same functions and effects as those of the third embodiment. In particular, in the present embodiment, since the guide protrusion 61 is disposed obliquely inwardly toward the ejection hole 35C side of the return passage 35, the oil liquid 3 is ejected from the ejection hole 35C of the return path 35 and is guided. When it hits, the resistance from the guide protrusion 61 which the oil liquid 3 receives can be set larger. Thereby, the jet direction of the oil liquid 3 can be bent to the arrow A5 shown in FIG. 13, and the oil liquid 3 can be reliably sprayed by the rear surface part 1D side of the casing 1. FIG.
[0092]
Next, FIGS. 14 to 16 show a fifth embodiment of the present invention. The feature of the present embodiment is that the balance weight is provided with a projecting pipe as an ejection projection extending radially outward, The oil liquid in the return passage is ejected into the casing through the projecting pipe, and a plurality of cooling fins for cooling the oil liquid ejected from the projecting pipe are provided on the inner wall of the rear surface portion constituting the casing. is there.
[0093]
In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
[0094]
In the figure, reference numeral 71 denotes a return passage used in the present embodiment, and the return passage 71 includes an axial passage portion 71A and a radial passage portion 71B. 72 is a projecting pipe as a jet projection provided on the balance weight 8. The projecting pipe 72 is inserted into the opening end of the radial passage 71B of the return passage 71 on the base end side, and the outer peripheral side thereof will be described later. Male screws (not shown) that are screwed onto the fixing nuts 75 and 76 are formed. The protruding pipe 72 is attached to the balance weight 8 using fixing nuts 75, 76 and the like.
[0095]
The projecting pipe 72 extends in the casing 1 from the balance weight 8 outward in the radial direction of the drive shaft 5, and a tip end side thereof is an ejection hole 72 </ b> A. Further, another ejection hole 72 </ b> B that opens toward the rear surface portion 1 </ b> D side of the casing 1 is formed on the outer peripheral side of the distal end of the protruding pipe 72.
[0096]
73 are a plurality of upper cooling fins that are positioned above the bearing portion 1E of the casing 1 and are erected on the inner wall of the rear surface portion 1D. The cooling fins 73 are arranged at intervals in the upward and downward directions, It extends parallel to the left and right directions (horizontal direction). The height of each cooling fin 73 is formed so as to gradually increase from the upper side to the lower side.
[0097]
74, 74 are a plurality of lower cooling fins that are positioned on the lower side of the bearing portion 1E of the casing 1 and are erected on the inner wall of the rear surface portion 1D. The cooling fins 74 are also spaced upward and downward. It is arranged and extends parallel to the left and right direction (horizontal direction). The height of each cooling fin 74 is formed so as to gradually increase from the upper side to the lower side.
[0098]
Reference numerals 75 and 76 denote fixing nuts for fixing the protruding pipe 72 to the balance weight 8. The fixing nut 75 of the fixing nuts 75 and 76 is welded to the outer peripheral end side of the balance weight 8.
[0099]
Thus, in the present embodiment configured as described above, it is possible to obtain substantially the same operational effects as those of the first embodiment. In particular, in the present embodiment, since the protruding pipe 72 extending in the radial direction of the drive shaft 5 is provided at the opening end of the radial passage portion 71B of the return passage 71, the ejection hole 72A of the protruding pipe 72 is formed in the casing 1. The oil liquid 3 from the return passage 71 can be efficiently sprayed by the upper surface portion 1A of the casing 1 in the direction of arrow A6 in FIG. The heat dissipation of the oil liquid 3 can be further enhanced.
[0100]
Further, since another jet hole 72B that opens toward the rear surface portion 1D of the casing 1 is provided on the outer peripheral side of the projecting pipe 72, the oil liquid 3 from the return passage 71 is ejected through the projecting pipe 72 to the jet hole 72B. 16 can be directly ejected toward the cooling fin 73 in the direction of arrow A7 in FIG.
[0101]
In addition, a plurality of cooling fins 73 and 74 are provided on the rear surface portion 1D of the casing 1, and the cooling fins 73 and the cooling fins 74 are formed so as to gradually increase from the upper side to the lower side. As described above, the oil liquid 3 sprayed on the upper surface portion 1A of the casing 1 flows down along the cooling fins 73 and 74 along the arrows shown in FIG. Heat can be radiated more efficiently from the cooling fins 73 and 74 to the outside of the casing 1, and the heat dissipation of the oil liquid 3 can be further enhanced.
[0102]
Next, FIG. 17 and FIG. 18 show a sixth embodiment of the present invention. The feature of this embodiment is that an ejection protrusion extending radially outward of the drive shaft is provided on the outer peripheral side of the balance weight. In addition to the provision, a plurality of cooling fins for cooling the oil liquid ejected from the ejection protrusions are provided on the inner wall of the rear surface portion constituting the casing.
[0103]
In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
[0104]
In the figure, reference numeral 81 denotes a balance weight used in the present embodiment, and the balance weight 81 is formed of a semicircular plate-like body in substantially the same manner as the balance weight 8 described in the first embodiment. On the outer peripheral end side, an ejection projection 81A that projects outward in the radial direction of the drive shaft 5 is integrally formed. A part of a radial passage portion 82B constituting a return passage 82 described later is formed in the ejection protrusion 81A of the balance weight 8.
[0105]
Reference numeral 82 denotes a return passage used in the present embodiment, and the return passage 82 includes an axial passage portion 82A and a radial passage portion 82B. The radial passage portion 82B of the return passage 82 has an ejection hole 82C opened at the tip of the ejection projection 81A of the balance weight 81, and the rear surface portion 1D side of the casing 1 from the tip side of the ejection projection 81A. And another ejection hole 82D that opens.
[0106]
83 are located above the bearing portion 1E of the casing 1 and are a plurality of upper cooling fins erected on the inner wall of the rear surface portion 1D, and 84, 84, ... are located below the bearing portion 1E of the casing 1. And a plurality of lower cooling fins erected on the inner wall of the rear surface portion 1D. The cooling fins 83 and 84 are formed in substantially the same manner as the cooling fins 73 and 74 described in the fifth embodiment.
[0107]
Thus, in the present embodiment configured as described above, it is possible to obtain substantially the same functions and effects as those of the fifth embodiment.
[0108]
In the first embodiment, when the discharge amount Q of the oil supply pump 21 is maximized, the ejection hole 35C of the return passage 35 is opened upward along the YY line orthogonal to the XX line. However, the present invention is not limited to this. For example, as in the first modification shown in FIG. 19, the ejection hole 35C is set when the discharge amount of the oil supply pump becomes maximum. It may be configured to open obliquely upward with respect to the XX line.
[0109]
Even in this case, the oil liquid from the ejection hole 35C can be sprayed to the upper surface portion 1A side of the casing 1 as shown by the arrow in FIG. 19, and the heat of the oil liquid can be radiated well from the casing 1 to the outside. be able to. The same applies to the second to sixth embodiments.
[0110]
In the first embodiment, the case where the radial passage portion 35B of the return passage 35 is arranged along the YY line has been described as an example, but the present invention is not limited thereto. Instead, for example, as in the second modified example shown in FIG. 20, the radial passage portion 91A of the return passage 91 may be disposed obliquely with respect to the YY line.
[0111]
Even in this case, when the discharge amount of the oil supply pump becomes the maximum, the ejection hole 91B of the return passage 91 can be opened upward from the line XX, and the oil liquid from the ejection hole 91B is shown in FIG. It can be sprayed on the upper surface portion 1A side of the casing 1 as shown by the arrow shown in the figure. The same applies to the second to sixth embodiments.
[0112]
Furthermore, in each embodiment, the scroll type air compressor is described as an example of the scroll type fluid machine. However, the present invention is not limited to this, and can be widely applied to, for example, a vacuum pump, a refrigerant compressor, and the like.
[0113]
【The invention's effect】
As described in detail above, according to the first aspect of the present invention, an oil supply pump that is operated following the movement of the orbiting scroll is provided between the orbiting scroll and the thrust receiver, and the casing of the casing is provided by the oil supply pump. After the oil liquid accumulated in the oil tank is sucked from the suction passage, the oil liquid is supplied to the swivel bearing through the oil supply passage, and the oil liquid supplied to the swirl bearing is supplied from the ejection hole through the return passage provided on the drive shaft. It is configured to return to the inside. And, since the ejection hole of this return passage is configured to open upward from the horizontal line with the axis of the drive shaft as a reference when the discharge amount of oil from the oil supply pump becomes maximum, the orbiting scroll orbiting Sometimes, most of the hot oil liquid flowing through the return passage can be positively sprayed from the ejection hole toward the upper inner wall of the casing, and this sprayed oil liquid can be sprayed from the upper side along the inner wall of the casing. While flowing down, the heat of the oil can be efficiently radiated from the casing wall to the outside, and the oil can be cooled.
[0114]
Thus, the temperature of the oil liquid in the oil tank can be kept low, and the slewing bearing etc. can be cooled well by supplying the cold oil liquid in the oil tank to the sliding part such as the slewing bearing by the oil pump. The durability, life, etc. of the scroll fluid machine can be extended and the performance, reliability, etc. can be improved.
[0115]
Further, the invention according to claim 2 is configured such that the ejection hole of the return passage is opened to the outer peripheral side of the balance weight provided on the outer peripheral side of the drive shaft, so that the ejection hole can be brought close to the inner wall of the casing. The oil liquid from the hole can be reliably sprayed by the inner wall of the casing, and the heat of the oil liquid can be radiated to the outside more efficiently.
[0116]
In the invention of claim 3, since the ejection hole of the return passage is constituted by a plurality of small holes opening in different directions, the oil liquid in the return passage is diffused from the plurality of small holes in different directions. The oil liquid from the return passage can be sprayed over a wide range on the upper inner wall of the casing, and the heat of the oil liquid can also be radiated well to the outside.
[0117]
In the invention of claim 4, since the guide projection for adjusting the jet direction of the oil is provided in the vicinity of the jet hole, by adjusting the jet direction of the oil from the jet hole by the guide projection The oil liquid can be sprayed over the inner wall of the casing over a wide range, and the heat dissipation of the oil liquid can be enhanced.
[0118]
Further, as in the fifth aspect of the invention, even when the balance weight is provided with the ejection protrusion extending radially outward, the oil liquid in the return passage is directed from the ejection protrusion toward the inner wall of the casing. It can spray efficiently and can radiate the heat | fever of an oil liquid favorably outside.
[0119]
On the other hand, since the invention of claim 6 is provided with a plurality of cooling fins for cooling the oil liquid ejected from the ejection holes of the return passage on the inner wall of the casing, the oil liquid sprayed on the inner wall of the casing While the oil flows down to the oil tank along the inner wall of the casing, the heat of the oil liquid can be efficiently taken away by the cooling fins, and the heat dissipation of the oil liquid can be further enhanced.
[0120]
Further, in the invention of claim 7, a swivel accommodating recess is formed on either one of the sliding contact surfaces of the orbiting scroll on the back surface side and the thrust receiver, and on the other sliding contact surface side. A swirler that pivots relatively along the peripheral wall surface of the swirl receiving recess is provided so as to define a pump chamber in the swirl receiving recess into a suction chamber and a discharge chamber. Is configured to follow the movement of the swirler in the swivel housing recess by the partition wall drive mechanism and move relative to each other. While being able to always discharge smoothly from the discharge chamber toward the oil supply passage, the performance and reliability of the oil supply pump can be improved.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a scroll type air compressor according to a first embodiment of the present invention as viewed from the direction of arrows II in FIG.
FIG. 2 is a front view of the orbiting scroll, the thrust receiver, and the like viewed from the direction of arrows II-II in FIG. 1 with the fixed scroll removed.
FIG. 3 is a partially enlarged cross-sectional view showing the balance weight, the return passage and the like in FIG. 1 in an enlarged manner.
4 is a front view of only the thrust receiver as viewed from the direction of arrows IV-IV in FIG. 1. FIG.
5 is a rear view of only the orbiting scroll viewed from the direction of arrows VV in FIG. 1. FIG.
6 is an enlarged cross-sectional view of the oil supply pump as seen from the direction of arrows VI-VI in FIG. 1. FIG.
FIG. 7 is an operation explanatory view showing the operation of the oil supply pump according to the first embodiment.
8 is a cross-sectional view of the balance weight, the return passage, and the like as seen from arrows VIII-VIII in FIG.
FIG. 9 is a characteristic diagram showing the relationship between the rotation angle from the top dead center position of the swirler and the discharge amount of the oil supply pump.
10 is a partially enlarged cross-sectional view of a scroll type air compressor according to a second embodiment of the present invention as seen from the same position as in FIG. 3;
FIG. 11 is an enlarged cross-sectional view of a main part showing the balance weight and cap in FIG. 10 in an enlarged manner.
12 is a partially enlarged cross-sectional view of a scroll type air compressor according to a third embodiment of the present invention as seen from the same position as in FIG. 3;
13 is a partially enlarged cross-sectional view of a scroll type air compressor according to a fourth embodiment of the present invention as seen from the same position as in FIG.
FIG. 14 is a longitudinal sectional view showing a scroll type air compressor according to a fifth embodiment of the invention.
15 is a cross-sectional view of a balance weight, a return passage, a protruding pipe, a cooling fin, and the like when viewed from the direction of arrows XV-XV in FIG.
16 is a partially enlarged cross-sectional view showing a projecting pipe, a cooling fin, and the like in FIG. 15 in an enlarged manner.
FIG. 17 is a longitudinal sectional view showing a scroll type air compressor according to a sixth embodiment of the present invention.
18 is a cross-sectional view of the balance weight, the return passage, the cooling fin, and the like as seen from the direction of arrows XVIII-XVIII in FIG.
19 is a cross-sectional view of a scroll air compressor according to a first modification of the present invention as seen from the same position as in FIG.
20 is a cross-sectional view of a scroll type air compressor according to a second modification of the present invention as seen from the same position as in FIG.
[Explanation of symbols]
1 casing
1A Top surface
1B Bottom part
2 Oil tank
3 Oil
4 Fixed scroll
5 Drive shaft
8,81 Balance weight
9 Orbiting scroll
9C Boss
9D, 14B sliding surface
10 Slewing bearing
11 Compression chamber
14 Thrust receiving
21 Oil pump
22 Retractor recess
22A wall surface
23 Pump room
24 Swivel
25 Slide plate (movable bulkhead)
26 Suction chamber
28 Slide plate drive mechanism (partition wall drive mechanism)
33 Suction passage
34 Refueling passage
35, 41, 71, 82, 91 Return passage
35C, 72A, 72B, 82C, 82D, 91B
43 Small hole (ejection hole)
51, 61 Guide protrusion
72 Projection pipe (projection for ejection)
73, 74, 83, 84 Cooling fins
81A Projection for ejection
01 -O1 axis
XX horizontal line

Claims (7)

A casing whose lower side is an oil tank for storing cooling fluid, a fixed scroll provided in the casing, a drive shaft rotatably provided in the casing, and a swivel bearing on the tip side of the drive shaft A revolving scroll having a plurality of compression chambers formed between the fixed scroll and the fixed scroll, and a rear surface of the revolving scroll provided on the casing for supporting a thrust load acting on the revolving scroll. In a scroll type fluid machine comprising a thrust receiver that is in sliding contact with the side,
An oil supply pump having a pump chamber defined between a back side of the orbiting scroll and a thrust receiver and operated in accordance with the movement of the orbiting scroll, and an oil liquid provided in the thrust receiver and in the oil tank An oil liquid suction passage that guides oil toward the pump chamber of the oil supply pump, an oil supply passage that is provided in the orbiting scroll and supplies the oil liquid sucked into the pump chamber of the oil supply pump toward the orbiting bearing, and the swivel A return passage provided on the drive shaft for returning the oil supplied to the bearing into the casing, having one end opened in the boss portion of the orbiting scroll and the other end serving as an oil liquid ejection hole and opened in the casing. And the outlet hole of the return passage is configured to open upward from a horizontal line based on the axis of the drive shaft when the amount of oil discharged from the oil pump becomes maximum. Scroll fluid machine according to claim. The scroll fluid machine according to claim 1, wherein a balance weight for balancing the rotation of the drive shaft is provided on the outer peripheral side of the drive shaft, and the ejection hole of the return passage opens to the outer peripheral side of the balance weight. . The scroll type fluid machine according to claim 1 or 2, wherein the ejection hole of the return passage is configured by a plurality of small holes that open in different directions. The scroll type fluid machine according to claim 1 or 2, wherein a guide projection for adjusting a jet direction of the oil is provided in the vicinity of the jet hole. The scroll fluid machine according to claim 2, wherein the balance weight is provided with a jetting protrusion that protrudes radially outward and jets oil from the return passage to the outside. The scroll fluid machine according to claim 1, 2, 3, 4 or 5, wherein a plurality of cooling fins for cooling the oil liquid ejected from the ejection holes of the return passage are provided on the inner wall of the casing. The oil pump is a swivel that is recessed in one of the sliding contact surfaces of the back side of the orbiting scroll and the thrust receiver and that defines the pump chamber between the other sliding contact surface. And a swivel that pivots relative to the peripheral wall surface of the swivel receiving recess by the movement of the orbiting scroll. A movable partition that is provided in the swivel housing recess so as to be relatively movable in the swivel housing recess, and that defines the pump chamber into a suction chamber and a discharge chamber in the swivel housing recess, together with the movable partition The scroll type fluid machine according to claim 1, 2, 3, 4, 5 or 6, comprising a partition wall drive mechanism for relatively moving in accordance with movement of the swirler in a swirl receiving recess.

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