JP2006009776A - Scroll type fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a through hole suppressing transmission heat generated in a compression chamber to a rotation prevention mechanism. <P>SOLUTION: A fixed scroll 5A and a revolving scroll 20a are oppositely arranged. A plurality of compression chambers 26A are defined between lap parts 7A, 22A thereof, and an auxiliary crank 28 for preventing rotation of the revolving scroll 20A is provided between a flange part 9A and a projection part 24A. A fixed side through hole 31 suppressing transmission of heat from the lap part 7A side to the auxiliary crank 28 is provided on a cylinder part 8A, and a turning side through hole 32 suppressing transmission of heat from the lap part 22A to the auxiliary crank 28 is provided on a projection part 24A. Consequently, transmission of heat generated in the compression chamber 26A to the auxiliary crank 28 is suppressed and life of a bearing 30 and the like is extended to improve durability. <P>COPYRIGHT: (C)2006,JPO&NCIPI

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 Documents 1 and 2).

JP-A-8-93674 Japanese Unexamined Patent Publication No. 63-50691

  In this type of conventional scroll type fluid machine, a fixed scroll is provided in a casing, and the fixed scroll has a spiral wrap portion standing at the center of the surface of the end plate.

  In addition, a rotating shaft is rotatably supported in the casing, and a rotating scroll having a spiral wrap portion standing at the center of the surface of the end plate is connected to the rotating shaft. In this case, the orbiting scroll is disposed so as to face the fixed scroll, and these lap portions overlap each other to define a plurality of compression chambers.

  In the scroll type fluid machine, when the rotary shaft is rotationally driven by a drive source such as a motor, the orbiting scroll revolves, and thereby fluid such as air and refrigerant is sequentially compressed in each compression chamber.

  Here, in the prior art of Patent Document 1, a metal plate or the like is attached to the back surface of the end plate of the orbiting scroll, and a cooling air passage is formed between the metal plate and the end plate. Further, three auxiliary cranks for preventing the rotation of the orbiting scroll are provided between the metal plate and the casing, and these auxiliary cranks are constituted by, for example, a crank-shaped pin member, a plurality of bearings, and the like. Yes.

  In the prior art of Patent Document 2, three auxiliary cranks are provided between the fixed scroll and the orbiting scroll, and the scrolls are connected to each other on the outer side in the radial direction of the end plate by these auxiliary cranks.

  By the way, in the prior art of Patent Document 1 described above, a metal plate that forms a cooling air passage is attached to the back side of the orbiting scroll, and an auxiliary crank is provided between the metal plate and the casing.

  For this reason, in the prior art of Patent Document 1, even if the heat conduction from the lap portion of the orbiting scroll to the auxiliary crank or the like can be suppressed to some extent, the structure of the orbiting scroll is complicated by the metal plate or the like, and the entire machine is enlarged. There is a problem.

  Moreover, in the prior art of patent document 2, it is set as the structure which provides an auxiliary | assistant crank between a fixed scroll and a turning scroll. However, in this case, the heat generated in the compression chamber or the like is transmitted to the auxiliary crank via the fixed scroll and the orbiting scroll.

  For this reason, in the prior art of Patent Document 2, the auxiliary crank bearings and the like become hot due to the heat transmitted from each scroll, and the deterioration of the bearings due to the heat is likely to occur, so the life of the auxiliary crank is shortened and the durability is reduced. There is a problem of doing.

  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 protect the rotation prevention mechanism against the heat generated on the center side of the fixed scroll and the orbiting scroll. It is an object of the present invention to provide a scroll type fluid machine that can be made compact while improving durability.

  In order to solve the above-mentioned problems, the invention of claim 1 is a casing, a fixed scroll provided on the casing and having a spiral wrap portion standing on the surface of the end plate, and a rotationally driven by a drive source supported by the casing. A rotating scroll that is connected to the rotating shaft at a position facing the fixed scroll, and a revolving scroll having a wrap portion standing on the surface of the end plate that overlaps the wrap portion to define a plurality of compression chambers, and a fixed scroll Is applied to a scroll fluid machine including a rotation prevention mechanism that connects the orbiting scroll and the end of each end plate in the radial direction to prevent rotation of the orbiting scroll.

  A feature of the configuration adopted by the invention of claim 1 is that the fixed scroll is provided with a first through hole that is located between the wrap portion and the rotation prevention mechanism and penetrates the fixed scroll, so that the orbiting scroll Is that a second through hole is provided between the wrap portion and the rotation prevention mechanism so as to penetrate the orbiting scroll.

  According to the invention of claim 2, the first or second through hole is formed as a long hole extending in the circumferential direction of the end plate.

  According to the invention of claim 3, a plurality of the first or second through holes are arranged in the circumferential direction of the end plate.

  According to a fourth aspect of the present invention, the first and second through holes overlap each other and communicate with each other between the back side of the fixed scroll and the back side of the orbiting scroll.

  Furthermore, according to invention of Claim 5, it is set as the structure which provides the circulation port which distribute | circulates cooling air in the position of a rotation prevention mechanism in a casing.

  On the other hand, according to the invention of claim 6, a plurality of the first through holes are arranged at intervals in the circumferential direction of the end plate, and the fixed scroll is located between the two adjacent through holes and is on the back side of the end plate. The reinforcing ribs projecting from each other are provided.

  According to the invention of claim 7, at least some of the reinforcing ribs are configured as a suction port for sucking air into the compression chamber.

  Furthermore, according to the invention of claim 8, a plurality of the second through holes are arranged at intervals in the circumferential direction of the end plate, and the orbiting scroll is located between the two adjacent through holes and is on the back side of the end plate. The reinforcing ribs projecting from each other are provided.

  According to the first aspect of the present invention, when the heat generated on the wrap portion (compression chamber) side of the fixed scroll is transmitted to the rotation prevention mechanism via the end plate or the like, the first through-hole rotates with the compression chamber side. It is possible to reduce the cross-sectional area of the heat conduction path interposed between the prevention mechanism and the heat conduction to the rotation prevention mechanism side. Similarly, the second through hole can reduce the cross-sectional area of the heat conduction path reaching the rotation prevention mechanism via the orbiting scroll, and can suppress heat conduction to the rotation prevention mechanism side.

  Therefore, the rotation prevention mechanism can be prevented from becoming hot due to heat conduction from the compression chamber side, and each component of the rotation prevention mechanism can be protected from deterioration due to heat, etc., and the cooling efficiency can be improved with a simple structure using a through hole. Can be increased. Thereby, durability and reliability can be improved, forming the whole machine compactly.

  According to the invention of claim 2, for example, when the first through hole is a long hole, the radial straight line interposed between the wrap portion of the fixed scroll and the rotation preventing mechanism by the through hole. It is possible to block the heat conduction path. As a result, it is possible to lengthen the heat conduction path between the two and make it difficult to transmit heat, and to block the heat on the wrap part side from reaching the rotation prevention mechanism side along the short heat conduction path in the radial direction. it can. Similarly, when the second through hole is a long hole, heat can be hardly transmitted between the lap portion side and the rotation prevention mechanism.

  According to the invention of claim 3, the plurality of through holes can be arranged side by side in the circumferential direction so as to block the heat conduction path between the wrap portion and the rotation prevention mechanism. Thereby, the cross-sectional area of the heat conduction path from the wrap portion side of the fixed scroll (or the turning scroll) to the rotation prevention mechanism can be reduced, and heat conduction to the rotation prevention mechanism side can be suppressed. In addition, even if a relatively large through hole is required due to heat resistance restrictions, for example, it can be formed by dividing it into a plurality of through holes, and the portion located between each through hole in the scroll is made into a solid structure Since it can be formed, the strength can be increased.

  According to the invention of claim 4, for example, if the first and second through holes are formed so as to be able to overlap and communicate with each other on the sliding surface of each scroll, the back side of the fixed scroll is formed by these through holes. And the back side of the orbiting scroll can communicate with each other. Thereby, for example, cooling air is generated using a cooling fan or the like, and this cooling air is sucked from the back side of the fixed scroll to the back side of the orbiting scroll via each through hole, or sucked to the back side of the orbiting scroll. Cooling air can flow out to the back side of the fixed scroll via each through hole.

  Accordingly, since the heat insulating through hole can be used as the cooling air passage, the cooling air passage can be formed compactly in the vicinity of the scroll, and the cooling structure of the entire machine can be simplified. Further, since the cooling air circulates through each through-hole, the heat dissipation of the fixed scroll and the orbiting scroll can be enhanced, and thereby the cooling efficiency of not only each scroll but also the rotation prevention mechanism can be improved.

  Further, according to the invention of claim 5, the cooling air is sucked into the position of the rotation prevention mechanism from the circulation port of the casing, or the cooling air sucked into the position of the rotation prevention mechanism is allowed to flow outside from the circulation port of the casing. it can. For this reason, the rotation prevention mechanism can be directly and efficiently cooled by the cooling air, and the heat resistance can be enhanced.

  On the other hand, according to the invention of claim 6, even in the state where the first through holes are provided in a plurality of locations of the fixed scroll, the reinforcing ribs can be disposed between these through holes, and the rigidity is likely to be relatively lowered. The fixed scroll can be reinforced at a position between the through holes. Thereby, the reduction in the rigidity of the scroll due to the provision of the first through hole can be compensated by the reinforcing rib. For example, even when the first through hole is formed large, the rigidity of the fixed scroll can be enhanced as a whole.

  Therefore, during operation of the machine, for example, even if a load in the thrust direction is applied to the fixed scroll, it is possible to reliably prevent the end plate and the lap portion from being deformed by this load, and the cooling performance by the first through-hole is sufficient. It is possible to operate the machine stably while exhibiting it. In addition, the reinforcing rib projecting to the back side of the end plate can have a function as a cooling fin. For example, the cooling efficiency of the fixed scroll can be increased by circulating cooling air along the reinforcing rib.

  According to the invention of claim 7, at least a part of the reinforcing ribs among the reinforcing ribs can be formed as a portion serving as both a reinforcing rib that reinforces the fixed scroll and a suction port that sucks air into the compression chamber. it can. Therefore, for example, by changing the shape of the existing suction port and arranging it between the first through holes, the suction port can be used as a reinforcing rib, and the number, size, etc. of the dedicated reinforcing rib can be increased accordingly. Since it can be kept small, the shape of the fixed scroll can be simplified.

  Further, according to the eighth aspect of the invention, since the reinforcing ribs can be disposed between the through holes even in the state where the second through holes are provided at a plurality of locations of the orbiting scroll, they are substantially the same as in the case of the sixth aspect. In addition, the orbiting scroll can be reinforced at positions between the through holes where the rigidity is likely to be relatively lowered, and the rigidity can be enhanced as a whole.

  Therefore, for example, the end plate of the orbiting scroll, the lap portion, etc. can be reliably prevented from being deformed by a load in the thrust direction, etc., and the machine can be stably operated while sufficiently exhibiting the cooling performance by the second through hole. Can do. In addition, the reinforcing rib protruding to the rear surface side of the end plate can be provided with a function as a cooling fin, thereby improving the cooling efficiency of the orbiting scroll.

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

  Here, FIG. 1 to FIG. 7 show a first embodiment, and in this embodiment, a twin wrap type scroll type air compressor will be described as an example.

  In the figure, reference numeral 1 denotes a substantially cylindrical casing constituting the outer frame of the scroll type air compressor. The casing 1 constitutes a fixed member together with fixed scrolls 5A and 5B described later. As shown in FIGS. 1 and 2, the casing 1 is formed in a substantially cylindrical shape and has an intermediate case 2 that is open on both sides in the axial direction, and a first case provided on one side (left side) of the intermediate case 2 in the axial direction. 1A, and the second outer case 3B provided on the other side (right side) in the axial direction of the intermediate case 2.

  Here, the left and right outer cases 3A and 3B are formed in a stepped bottomed cylindrical shape. Further, the first outer case 3A constitutes a low-pressure stage compression section 4A together with a first fixed scroll 5A, a first orbiting scroll 20A, etc., which will be described later, and the second outer case 3B is a second fixed scroll. 5B, the 2nd turning scroll 20B, etc. comprise the compression part 4B of a high voltage | pressure stage. In this case, since the compression units 4A and 4B of the low pressure stage and the high pressure stage have substantially the same constituent elements, in the following description, the constituent elements of the low pressure stage will be described with reference numeral “A”. The constituent elements of the high-pressure stage will be described with the symbol “B”, and the description overlapping with the low-pressure stage will be omitted.

  5A is a low-pressure stage fixed scroll provided in the outer case 3A of the casing 1, and the fixed scroll 5A is an end plate formed in a substantially disc shape centering on the axis O1-O1 as shown in FIGS. 6A, a spiral wrap portion 7A erected at the center of the surface of the end plate 6A, and a substantially triangular tube portion that protrudes in the axial direction from the outer peripheral side of the end plate 6A and surrounds the wrap portion 7A from the outside in the radial direction 8A, and a part of the cylindrical portion 8A, which protrudes radially outward from the end plate 6A and is attached to, for example, three flange portions 9A attached to the outer case 3A.

  Here, as shown in FIGS. 5 and 6, the end plate 6 </ b> A has two suction ports 10 </ b> A that are located on the radially outer side of the wrap portion 7 </ b> A and suck air into the compression chamber 26 </ b> A described later, and the wrap portion 7 </ b> A. A discharge port 11 </ b> A that discharges compressed air is provided in the center (in the radial direction). A plurality of cooling fins 12A extending in the vertical direction along the flow direction of the cooling air (indicated by the arrow A4 in FIG. 3) is provided on the rear surface of the end plate 6A.

  The flange portion 9A is formed as a substantially triangular projection, for example, joined to the outer peripheral side of the end plate 6A, and spaced apart from each other in the circumferential direction with an interval of about 120 °, for example. Each flange portion 9A is provided with an attachment hole 13 to which an auxiliary crank 28 described later is attached. Further, the flange portion 9A is in sliding contact with the end plate 21A of the orbiting scroll 20A at a portion radially inward of the mounting hole 13, and a fixed-side through hole 31 described later is provided in this sliding contact portion.

  On the other hand, 5B is a high-pressure stage fixed scroll provided in the outer case 3B of the casing 1, and the fixed scroll 5B is substantially the same as the low-pressure stage fixed scroll 5A, as shown in FIG. The cylindrical portion 8B, the flange portion 9B, and the like, and a plurality of cooling fins 12B are provided upright on the back side of the end plate 6B. Further, the end plate 6B is provided with a suction port (not shown) for sucking air into a compression chamber 26B described later, and a discharge port 11B for discharging compressed air.

  Here, the low-pressure stage discharge port 11A is connected to a high-pressure stage suction port via a cooler 39 and piping, which will be described later, as shown in FIG. 1, and the high-pressure stage discharge port 11B is connected to the cooler 39, etc. Is connected to an air tank (not shown) or the like via a pipe or the like. Thereby, the air compressor is configured to sequentially compress the air sucked from the suction port 10A through the silencer or the like by the compression portions 4A and 4B.

  Reference numeral 14 denotes, for example, an electric motor as a drive source provided in the intermediate case 2 of the casing 1, and the motor 14 is located between the fixed scrolls 5A and 5B and is fixed in the intermediate case 2. And a cylindrical rotor or the like fixed to the outer peripheral side of the rotating shaft 15 to be described later, and the rotating shaft 15 is rotationally driven.

  Reference numeral 15 denotes a rotating shaft rotatably provided on the casing 1, and the rotating shaft 15 is composed of, for example, a stepped cylindrical hollow rod, and rotates integrally with the rotor of the motor 14 about the axis O 1 -O 1. is there. The rotating shaft 15 is rotatably supported on the outer cases 3A and 3B via rotating bearings 16A and 16B on both sides in the axial direction.

  Reference numeral 17A denotes a substantially cylindrical eccentric bush attached to one end of the rotary shaft 15. The eccentric bush 17A is fitted and fixed to the outer peripheral side of the rotary shaft 15 by means such as press-fitting as shown in FIG. The rotary shaft 15 rotates integrally with the axis O1-O1.

  Further, a part of the inner side of the eccentric bush 17A is formed eccentrically from the axis O1-O1, and a connecting shaft 18 described later is rotatably fitted to the eccentric part via an eccentric bearing 19A. Yes. On the other hand, another eccentric bush 17B is attached to the other end of the rotating shaft 15, as shown in FIG.

  Reference numeral 18 denotes a connecting shaft that is inserted through the rotating shaft 15. The connecting shaft 18 is formed of, for example, a stepped columnar metal rod or the like, and both end sides in the axial direction protrude from the rotating shaft 15. And the boss | hub parts 23A and 23B of the turning scroll 20A and 20B mentioned later are connected with these protrusion end sides.

  Further, the connecting shaft 18 is attached to the rotary shaft 15 via eccentric bearings 19A and 19B and eccentric bushes 17A and 17B so as to be relatively rotatable, and the dimension (the amount of eccentricity) δ from the axis O1-O1 of the rotary shaft 15 or the like. It is arranged around an eccentric axis O2-O2. The connecting shaft 18 orbits together with the orbiting scrolls 20A and 20B when the rotating shaft 15 rotates.

  Reference numeral 20A denotes a low-pressure stage orbiting scroll which is provided in the casing 1 so as to face the fixed scroll 5A. The low-pressure stage orbiting scroll 20A is centered on an axis O2-O2 as shown in FIGS. End plate 21A formed in a substantially disc shape and housed in outer case 3A, spiral wrap portion 22A standing at the center of the surface of end plate 21A, and cylinder standing at the center of the back surface of end plate 21A A substantially boss portion 23A and, for example, three projecting portions 24A (see FIG. 7) projecting from the outer peripheral side of the end plate 21A.

  Here, the radially outer portion of the end plate 21A is in sliding contact with the cylindrical portion 8A (flange portion 9A) of the fixed scroll 5A, and a turning-side through hole 32 described later is provided in this sliding contact portion. A plurality of cooling fins 25A extending in the vertical direction, for example, are erected on the back side of the end plate 21A.

  Further, the wrap portion 22A is disposed so as to overlap with the wrap portion 7A of the fixed scroll 5A by a predetermined angle (for example, 180 degrees), and thus, the lap portions 7A and 22A in the low pressure stage are arranged from the outer peripheral side. A plurality of compression chambers 26A are defined over the inner peripheral side. Further, the boss portion 23A is fixed to one end side of the connecting shaft 18 in a state where rotation is restricted using a pin or the like.

  Further, as shown in FIG. 7, the protruding portion 24A is formed, for example, as a substantially triangular protruding portion, the proximal end side is joined to the outer peripheral side of the end plate 21A, and the distal end side protrudes radially outward from the end plate 21A. Yes. In this case, the protrusions 24A are disposed at positions corresponding to the flanges 9A of the fixed scroll 5A, and are separated from each other in the circumferential direction of the end plate 21A with an interval of about 120 °, for example. Each protrusion 24A is provided with a mounting hole 27.

  On the other hand, 20B is a high-pressure stage orbiting scroll provided facing the fixed scroll 5B. The orbiting scroll 20B is substantially the same as the low-pressure stage orbiting scroll 20A as shown in FIG. The boss portion 23B, the cooling fin 25B, and the like, and a plurality of compression chambers 26B are defined between the high pressure wrap portions 7B and 22B. Further, the boss portion 23B is fixed to the other end side of the connecting shaft 18 in a state where rotation is restricted using a pin or the like.

  The orbiting scrolls 20A and 20B are driven by the motor 14 through the rotating shaft 15, the connecting shaft 18 and the like, and perform the orbiting motion with a constant orbiting radius corresponding to the eccentricity δ, thereby causing the compression chambers 26A and 26B to move. The air is compressed.

  Reference numeral 28 denotes, for example, three auxiliary cranks as an anti-rotation mechanism, and each auxiliary crank 28 includes a flange portion 9A of the fixed scroll 5A and a protruding portion 24A of the orbiting scroll 20A as shown in FIGS. For example, they are spaced apart from each other in the circumferential direction with an interval of about 120 °, for example.

  Here, the auxiliary crank 28 includes, for example, a crank pin 29 bent in a crank shape, and, for example, two bearings 30 that rotatably support one side in the axial direction of the crank pin 29 in the mounting hole 13 of the fixed scroll 5A. The other side of the crank pin 29 in the axial direction is constituted by another bearing 30 or the like that rotatably supports the mounting hole 27 of the orbiting scroll 20A.

  The auxiliary crank 28 connects the fixed scroll 5A and the orbiting scroll 20A outside the end plates 6A and 21A in the radial direction, thereby preventing the orbiting scroll 20A from rotating, and via the connecting shaft 18, the orbiting scroll 20B. This also prevents the rotation.

  Reference numeral 31 denotes fixed side through holes as first through holes provided at, for example, three locations of the cylindrical portion 8A of the fixed scroll 5A. The fixed side through holes 31 are arranged on the wrap portion 7A side of the fixed scroll 5A (particularly, Further, the heat generated in the compression chamber 26A in the central compression chamber) is prevented from being transmitted to the auxiliary cranks 28 on the radially outer side through the fixed scroll 5A, and the bearings 30 of the auxiliary crank 28 are deteriorated due to high temperature. It protects from.

  Here, as shown in FIGS. 4 to 6, the fixed-side through hole 31 is formed as, for example, an elongated slit, a long hole, or the like, and moves the cylindrical portion 8A of the fixed scroll 5A in the axial direction at a position corresponding to each flange portion 9A. It penetrates in the direction of the axis O1-O1), and opens on the sliding surface between the cylindrical portion 8A and the end plate 21A of the orbiting scroll 20A.

  In addition, the fixed side through hole 31 is disposed between the lap portion 7A and each auxiliary crank 28 in the radial direction of the end plate 6A, and for example, the end of the end plate 6A of the end plate 6A so as to block the heat conduction path interposed therebetween. It extends in an arc shape in the circumferential direction. Thereby, the fixed side through hole 31 can reliably block the heat generated on the center side of the end plate 6A from being transmitted to the auxiliary crank 28 side along a short radial path.

  In particular, in the present embodiment, as shown in FIG. 5, when a straight line in the radial direction connecting the center O1 (axis O1-O1) of the end plate 6A and the auxiliary crank 28 is an imaginary line L, for example, a fixed-side through hole Since 31 extends across the virtual line L on both sides in the circumferential direction, the heat conduction path between the end plate 6A side and the auxiliary crank 28 can be reliably blocked.

  Further, since the fixed-side through hole 31 passes through the cylindrical portion 8A at a position radially inward of the auxiliary crank 28, the radial cross-sectional area of the cylindrical portion 8A is fixed at the fixed-side through hole 31 at this portion. It is smaller by Thereby, the fixed side through-hole 31 can reduce the cross-sectional area of the heat conduction path from the end plate 6A side to the auxiliary crank 28 via the cylindrical portion 8A.

  For this reason, the fixed side through hole 31 does not necessarily need to be formed across the virtual line L, and has a shape that reduces the cross-sectional area in the radial direction of the cylindrical portion 8A even at a position away from the virtual line L. If present, heat conduction to the auxiliary crank 28 can be suppressed.

  32 shows, for example, orbiting side through holes as second through holes provided at three locations on the end plate 21A of the orbiting scroll 20A. The orbiting side through holes 32 are fixed on the fixed side as shown in FIGS. Substantially similar to the through-hole 31, it is formed as, for example, an arc-shaped elongated slit, a long hole, etc., and heat generated in the compression chamber at the center of each compression chamber 26 </ b> A is transmitted to each auxiliary crank 28 through the orbiting scroll 20 </ b> A. It is to suppress.

  The turning-side through hole 32 penetrates the end plate 21A in the axial direction at a position radially inward of the auxiliary crank 28, and blocks a heat conduction path interposed between the lap portion 22A and each auxiliary crank 28. Further, for example, it extends in the circumferential direction of the end plate 21A and, as shown in FIG. 7, straddles both sides in the circumferential direction across the radial imaginary line L 'connecting the center O2 (axis O2-O2) of the end plate 21A and the auxiliary crank 28. Is arranged.

  Thereby, the turning-side through hole 32 blocks, for example, heat generated on the center side of the end plate 21A from being conducted to the auxiliary crank 28 along a short radial path. Further, since the turning side through hole 32 penetrates the end plate 21A at the position where each projection 24A is joined, the cross-sectional area of the heat conduction path from the end plate 21A side to the auxiliary crank 28 via the projection 24A. It is the composition which decreases.

  Further, the three orbiting side through holes 32 open to the sliding surface between the end plate 21A of the orbiting scroll 20A and the cylindrical portion 8A (flange portion 9A) of the fixed scroll 5A. Even in the position, as shown in FIG. 3, at least one turning side through hole 32 is held in communication with the fixed side through hole 31.

  Thereby, the fixed side through hole 31 and the orbiting side through hole 32 always communicate the back surface side of the fixed scroll 5A and the back surface side of the orbiting scroll 20A, and cooling air generated by a cooling fan 33A described later is supplied to each scroll 5A. , 20A is constituted.

  In this case, in order for the through holes 31 and 32 to communicate with each other at all times, when the turning radius of the orbiting scroll 20A is Δ, the radial dimension Lr of one of the through holes 31 and 32 is set to the other. It is formed to be larger than twice the turning radius Δ with respect to the radial dimension Lr ′ of the through hole (Lr> Lr ′ + 2Δ), and the circumferential dimension Lc of the one through hole is set to the circumferential dimension of the other through hole. It may be formed larger than twice the turning radius Δ with respect to Lc ′ (Lc> Lc ′ + 2Δ).

  During operation of the compressor, as indicated by an arrow A1, cooling air is sucked from the back side of the fixed scroll 5A through the through holes 31 and 32 to the back side of the orbiting scroll 20A (inside the outer case 3A). Be turned. For this reason, when the cooling air flows through the through holes 31 and 32, the scrolls 5 and 20 can be efficiently cooled, and the temperature rise of the scrolls 5 and 20 and the auxiliary crank 28 can be suppressed.

  Next, the cooling structure of the air compressor will be described. First, 33A is a low-pressure stage cooling fan provided on one axial side of the rotating shaft 15, and the cooling fan 33A is, for example, a centrifugal fan as shown in FIG. Etc. are constituted.

  The cooling fan 33A is positioned between the motor 14 and the orbiting scroll 20A at the low pressure stage, is fitted in a rotating state on the outer peripheral side of the eccentric bush 17A, and is accommodated in the outer case 3A. In this case, an annular partition plate 34A is provided in the outer case 3A at a position for partitioning between the orbiting scroll 20A and the cooling fan 33A.

  On the other hand, 33B is a high-pressure stage cooling fan provided on the other side in the axial direction of the rotating shaft 15. As shown in FIG. 2, the cooling fan 33B is disposed on the outer peripheral side of the eccentric bush 17B in substantially the same manner as the cooling fan 33A. An annular partition plate 34B is disposed between the cooling fan 33B and the orbiting scroll 20B in the high pressure stage.

  The cooling fans 33 </ b> A and 33 </ b> B are rotationally driven together with the rotating shaft 15 by the motor 14. As a result, the low-pressure cooling fan 33A sucks cooling air from the back side of the fixed scroll 5A via the through holes 31 and 32, and sucks cooling air from the inlet 35A described later to the position of each auxiliary crank 28. These cooling winds are supplied to the back side of the orbiting scroll 20A, the back side of the fixed scroll 5A, and a cooler 39, which will be described later. The high-pressure stage cooling fan 33B also sucks cooling air into the outer case 3B from the inflow port 35B, and supplies this cooling air to the back surfaces of the scrolls 5B and 20B and the cooler 39, respectively.

  Reference numeral 35A denotes, for example, three inlets (only two parts are shown) provided in the outer case 3A. Each of the inlets 35A is connected to three auxiliary cranks 28 as shown in FIGS. The openings are respectively opened at corresponding positions, and the cooling air is circulated to the positions of the auxiliary cranks 28.

  Thereby, when the cooling fan 33A is operated, the cooling air flows into the positions of the auxiliary cranks 28 from the three inflow ports 35A. Therefore, the auxiliary cranks 28 can be efficiently cooled by being exposed to the flow of the cooling air. it can. On the other hand, a cooling air inlet 35B is also provided in the outer case 3B of the high-pressure stage.

  36A is, for example, two low-pressure stage outlets provided on the upper and lower sides of the outer case 3A. The lower outlet of each outlet 36A is, for example, a fixed scroll 5A using a substantially box-shaped duct 37A. Is connected to the rear surface side (position of the cooling fin 12A). Further, the upper outlet 36A is connected to a cooler 39 described later using another duct 38A.

  On the other hand, as shown in FIG. 2, the outer case 3B of the high-pressure stage is also provided with upper and lower outlets 36B and ducts 37B and 38B. In FIG. 1, reference numeral 39 denotes a cooler provided on the upper side of the casing 1, and the cooler 39 compresses an intermediate pressure discharged from the low pressure stage compression section 4 </ b> A toward the high pressure stage compression section 4 </ b> B, for example. The air and the high-pressure compressed air discharged from the compression unit 4B are cooled.

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

  First, when power is supplied to the motor 14, the rotary shaft 15 is driven to rotate about the axis O1-O1. As a result, when the connecting shaft 18 attached in an eccentric state in the rotating shaft 15 performs the orbiting motion, the orbiting scrolls 20A and 20B coupled to both ends thereof perform the orbiting operation with respect to the fixed scrolls 5A and 5B. .

  As a result, the compression unit 4A in the low pressure stage sequentially compresses the air in each compression chamber 26A while sucking outside air from the suction port 10A via a silencer or the like, and discharges compressed air of intermediate pressure from the discharge port 11A. . The intermediate-pressure compressed air is sucked into the high-pressure stage compression section 4B and compressed, thereby becoming high-pressure compressed air, discharged from the discharge port 11B, and stored in an air tank or the like.

  Further, during the operation of the compressor, heat is generated in the compression chamber on the center side among the compression chambers 26A and 26B. In this case, in the compression section 4A of the low pressure stage, the through holes 31 and 32 can prevent the heat on the center side from being transmitted to the auxiliary crank 28 via the fixed scroll 5A and the orbiting scroll 20A. It can be kept at a low temperature.

  On the other hand, during the compression operation, the cooling fans 33 </ b> A and 33 </ b> B are rotated together with the rotating shaft 15. As a result, the low-pressure stage cooling fan 33A sucks cooling air into the outer case 3A from the back side of the fixed scroll 5A via the through holes 31 and 32, as indicated by an arrow A1 in FIG. As shown in A 2, cooling air is sucked into the position of each auxiliary crank 28 from the inlet 35 A.

  As a result, since the cooling air flows through the through holes 31 and 32, the fixed scroll 5A and the orbiting scroll 20A can be brought into contact with the cooling air in a wide area. Can be increased. Further, when the cooling air flows into the position of each auxiliary crank 28 from the inlet 35A, the auxiliary crank 28 can be directly and efficiently cooled by this cooling air.

  Further, the cooling air sucked into the outer case 3A flows along the back side (cooling fins 25A) of the orbiting scroll 20A, cools the end plate 21A and the like, and then cools through the inner peripheral side of the partition plate 34A. It flows into the position of the fan 33A, and flows out in the direction of arrow A3 from the upper and lower outlets 36A.

  Then, the cooling air flowing out from the lower outlet 36A is guided to the duct 37A so as to flow along the back side (cooling fins 12A) of the fixed scroll 5A as shown by the arrow A4, and the fixed scroll 5A. Can be efficiently cooled. Further, the cooling air flowing out from the upper outlet 36A is guided to the duct 38A and flows into the cooler 39, so that the cooler 39 can be cooled.

  On the other hand, as shown in FIG. 2, the high-pressure stage cooling fan 33B also sucks cooling air from the inlet 35B of the outer case 3B in the direction indicated by the arrow B1 in the same manner as in the low-pressure stage, By flowing out from the outlet 36B in the direction of arrow B2, the cooling air is circulated in the direction of arrow B3 along the back side of the fixed scroll 5B. Thereby, the fixed scroll 5B, the turning scroll 20B, and the cooler 39 can be cooled efficiently.

  Thus, according to the present embodiment, the cylindrical portion 8A of the fixed scroll 5A is provided with the fixed side through-holes 31 between the lap portion 7A and the auxiliary cranks 28, and each protruding portion 24A of the orbiting scroll 20A is provided with each protruding portion 24A. Is configured such that a turning-side through hole 32 is provided between the lap portion 22A and the auxiliary crank 28, respectively.

  Thereby, the fixed side through-hole 31 allows the compression chamber 26A when the heat generated on the side of the wrap portions 7A, 22A (compression chamber 26A) of each scroll 5A, 20A is transmitted to the auxiliary crank 28 via the fixed scroll 5A. The cross-sectional area of the heat conduction path interposed between the side and the auxiliary crank 28 can be reduced, and heat conduction to the auxiliary crank 28 side can be reliably suppressed.

  Similarly, the orbiting through hole 32 can reduce the cross-sectional area of the heat conduction path that reaches the rotation prevention mechanism via the orbiting scroll 20A, and can suppress heat conduction to the auxiliary crank 28 side.

  Accordingly, it is possible to prevent the auxiliary crank 28 from becoming hot due to heat conduction from the compression chamber 26A side, and it is possible to protect components such as the bearing 30 from thermal deterioration, and cooling efficiency with a simple structure using the through holes 31 and 32. Can be increased. Thereby, durability and reliability can be improved, forming the whole compressor compactly.

  In this case, since the through holes 31 and 32 are formed as arc-shaped long holes, the fixed side through hole 31 can block the radial heat conduction path interposed between the lap portion 7A and the auxiliary crank 28, The heat conduction path between them can be made substantially longer to make it difficult to transfer heat. As a result, the heat on the compression chamber 26A side can be blocked from reaching the auxiliary crank 28 side along the short heat conduction path in the radial direction. Similarly, in the case of the turning-side through hole 32, the heat conduction path between the lap portion 22A and the auxiliary crank 28 can be substantially lengthened, so that it is difficult to transfer heat.

  Moreover, since the fixed side through hole 31 and the orbiting side through hole 32 are formed as arc-shaped long holes that open to the sliding surfaces of the scrolls 5A and 20A, the orbiting scroll 20A is located at any position on the orbit. Even in this case, the through holes 31 and 32 can be held in communication with each other.

  And since it was made to distribute | circulate the cooling air by the cooling fan 33A in each through-hole 31 and 32, it passes from the back surface side of the fixed scroll 5A to the back surface side of the turning scroll 20A via each through-hole 31 and 32. Cooling air can be sucked in.

  Therefore, since the through holes 31 and 32 for heat insulation can also be used as cooling air passages, the cooling air passages can be formed in the vicinity of the scrolls 5A and 20A, and the cooling structure of the entire compressor can be simplified. . Further, since the cooling air circulates through the through holes 31 and 32, the heat dissipation of the fixed scroll 5A and the orbiting scroll 20A can be improved, thereby cooling not only the scrolls 5A and 20A but also the auxiliary crank 28. Can be improved.

  Further, since the cooling air inlet 35A is provided in the outer case 3A at a position corresponding to each auxiliary crank 28, when the cooling fan 33A is operated, the cooling air is supplied by the through holes 31 and 32 and the inlet 35A. Each can be sucked in, and a sufficient amount of cooling air can be introduced into the casing 1.

  In this case, since the cooling air can flow into the position of each auxiliary crank 28 from the three inlets 35A, the auxiliary crank 28 can be directly and efficiently cooled by this cooling air, and its heat resistance can be improved. it can.

  Next, FIGS. 8 and 9 show a second embodiment according to the present invention, and the feature of this embodiment is that a plurality of through holes are arranged side by side. 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.

  Reference numeral 41 denotes a fixed side through hole as a first through hole, and the fixed side through hole 41 is provided in the cylindrical portion 8A ′ of the fixed scroll 5A ′ at the low pressure stage in substantially the same manner as in the first embodiment. ing. In this case, the fixed scroll 5A ′ includes an end plate 6A ′, a wrap portion 7A ′, a cylinder portion 8A ′, a flange portion 9A ′, a suction port 10A ′, a discharge port 11A ′, a mounting hole 13 ′, and the like.

  The fixed-side through hole 41 is formed as, for example, an elongated slit, a long hole, etc., and penetrates the cylinder portion 8A ′ in the axial direction at a position corresponding to each flange portion 9A ′, and the wrap portion 7A ′ and each auxiliary crank. 28, respectively, and extends, for example, in a circular arc shape in the circumferential direction of the end plate 6A '.

  However, the fixed side through holes 41 are arranged at two positions, for example, at positions corresponding to the individual flange portions 9A ′, and these two fixed side through holes 41 are located between the lap portion 7A ′ and the auxiliary crank 28. Are arranged at intervals in the circumferential direction so as to block the heat conduction path.

  Reference numeral 42 denotes a orbiting side through hole as a second through hole. As shown in FIG. 9, the orbiting side through hole 42 is provided at each protrusion 24A ′ of the orbiting scroll 20A ′ at the low pressure stage. 20A 'includes a mirror plate 21A', a wrap portion 22A ', a protruding portion 24A', a mounting hole 27 ', and the like, almost the same as in the first embodiment.

  Each projecting portion 24A ′ is provided with two turning-side through holes 42 at intervals in the circumferential direction. These two turning-side through holes 42 are substantially the same as in the case of the fixed-side through hole 41. The lap portion 22A 'and the auxiliary crank 28 are arranged at intervals in the circumferential direction.

  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. That is, the through holes 41 and 42 reduce the cross-sectional area of the heat conduction path from the wrap portions 7A 'and 22A' of the scrolls 5A 'and 20A' to the auxiliary crank 28 in substantially the same manner as in the first embodiment. And heat conduction to the auxiliary crank 28 side can be suppressed.

  Particularly in the present embodiment, for example, two fixed side through holes 41 are arranged in the circumferential direction between the lap portion 7A ′ and the auxiliary crank 28, and the two turning side through holes 42 are arranged in the lap portion. 22A 'and the auxiliary crank 28 are arranged side by side in the circumferential direction.

  Thus, for example, even if the fixed scroll 5A ′ requires a relatively large through hole due to heat resistance restrictions or the like, the fixed scroll 5A ′ can be divided into a plurality of fixed side through holes 41. Since the part located between the through holes 41 can be formed as a solid structure, the strength of the fixed scroll 5A 'can be increased. Similarly, in the case of the orbiting scroll 20A ′, the portion located between the through holes 42 can be formed as a solid structure, and sufficient strength can be ensured.

  Next, FIGS. 10 to 17 show a third embodiment according to the present invention. The feature of the present embodiment is that a reinforcing rib is provided on the fixed scroll and the orbiting scroll. 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.

  Reference numeral 51A denotes a low-pressure stage fixed scroll provided on the outer case 3A 'of the casing 1, and the fixed scroll 51A is made of aluminum or the like, as shown in FIGS. It is made of a metal material and is integrally formed by means such as casting. The outer case 3A 'has a configuration in which the inflow port 35A of the first embodiment is omitted.

  The fixed scroll 51A includes an end plate 52A formed in a substantially disc shape with the axis O1-O1 as a center, a spiral wrap portion 53A provided upright at the center of the surface of the end plate 52A, and an outer peripheral side of the end plate 52A. A cylindrical portion 54A having a substantially triangular shape that surrounds the wrap portion 53A from the outside in the radial direction, and a portion of the cylinder portion 54A that protrudes radially outward from the end plate 52A. For example, three flange portions 55A that are attached to '.

  Here, on the back surface of the end plate 52A, a plurality of cooling fins 56A extending in the vertical direction, for example, along the flow direction of the cooling air (the direction indicated by the arrow a4 in FIG. 10), for example, are substantially the same as in the first embodiment. It is erected. Further, the flange portions 55A are spaced apart from each other at an interval of about 120 ° in the circumferential direction of the end plate 52A, for example, and protrude in the radial direction from the outer peripheral side of the end plate 52A. Each flange portion 55A is provided with a stepped attachment hole 57 (see FIG. 14) to which the auxiliary crank 28 is attached, in substantially the same manner as in the first embodiment.

  On the other hand, as shown in FIGS. 11 and 12, each flange portion 55 </ b> A is provided with a plurality of ventilation holes 58 that penetrate the fixed scroll 51 </ b> A in the axial direction at positions that surround the individual attachment holes 57 (auxiliary crank 28). ing.

  These vent holes 58 can circulate external air around the auxiliary crank 28 when the cooling fan 33A is operated, whereby the auxiliary crank 28 can be efficiently cooled. In addition, the vent hole 58 can allow external air to flow into the outer case 3A ′ at a position different from through-holes 59 to 61 and 76 described later, thereby improving the cooling efficiency of the orbiting scroll 67A and the like. .

  Reference numerals 59, 60, 61 denote fixed side through holes as first through holes provided at, for example, three locations of the cylindrical portion 54A of the fixed scroll 51A. These fixed side through holes 59, 60, 61 are the first through holes. In substantially the same manner as in the first embodiment, the heat conduction path between the end plate 52A and the auxiliary crank 28 is blocked or the cross-sectional area of the heat conduction path is reduced, so that the heat generated on the lap portion 53A side is fixed. Transmission to the auxiliary cranks 28 on the radially outer side through the scroll 51A is suppressed.

  As shown in FIG. 11, each of the fixed side through holes 59 to 61 is disposed between the lap portion 53A and each auxiliary crank 28 in the radial direction of the end plate 52A, and is spaced apart from each other in the circumferential direction of the end plate 52A. ing. Further, the fixed side through holes 59 to 61 have, for example, radial lines connecting the center O1 of the end plate 52A and the individual auxiliary cranks 28 as imaginary lines L, for example, on both sides in the circumferential direction across the imaginary line L. It is formed as an extending arc-shaped slit, a long hole or the like.

  Further, the fixed side through holes 59 to 61 penetrate the cylindrical portion 54A in the axial direction (axial direction O1-O1 direction) at a position corresponding to each flange portion 55A, and the cylindrical portion 54A and the end plate 68A of the orbiting scroll 67A. Open to the sliding surface. In this case, when the orbiting scroll 67A performs the orbiting operation, at least one of the fixed side through holes 59 to 61 is always in communication with the later-described orbiting side through hole 76, as in the first embodiment. It is the composition to do.

  As described above, in the present embodiment, the cooling performance of the fixed scroll 51A is enhanced by the fixed side through holes 59 to 61 and the like, and the fixed scroll 51A is fixed by the rib serving inlet 62, the fin-type reinforcing rib 65, and the extension rib 66 described later. The structure has a sufficient rigidity.

  Reference numeral 62 denotes, for example, two rib-use suction ports 62 integrally formed on the end plate 52A and the cylindrical portion 54A of the fixed scroll 51A. Each of the rib-use suction ports 62 is combined with a fin-type reinforcing rib 65 described later. A reinforcing rib (fixed side reinforcing rib) of the fixed scroll 51A is formed. That is, the rib combined suction port 62 is formed as a portion serving as a reinforcing rib that reinforces the fixed scroll 51A and a suction port that sucks air into the compression chamber 73A described later. In this respect, the suction port of the first embodiment is formed. It is different from the mouth 10A.

  Then, as shown in FIG. 12, the rib combined suction port 62 is formed between, for example, two adjacent fixed side through holes 59 and 60 among the three fixed side through holes 59 to 61, and two adjacent fixed side through holes. It arrange | positions between the holes 59 and 61, and is extended in radial direction toward the center of the end plate 52A from the cylinder part 54A in these positions.

  Further, as shown in FIGS. 13 and 14, the rib serving inlet 62 is formed, for example, as a hollow structure having a rectangular tube shape so as to function as a reinforcing rib having high strength (rigidity). It protrudes to the back side of 54A.

  As described above, the rib combined suction port 62 has the end plate 52A and the cylindrical portion 54A between the fixed side through holes 59 and 60 and between the fixed side through holes 59 and 61 in which the rigidity of the fixed scroll 51A is relatively low. Are integrally connected, and the rigidity of the fixed scroll 51A is reinforced by these portions to enhance the rigidity as a whole.

  Further, as shown in FIG. 11, suction holes 63 that open to the front surface and the back surface of the end plate 52 </ b> A are provided on the inner peripheral side of each rib serving suction port 62. Of these suction holes 63, one suction hole 63 is disposed close to the outermost peripheral end of the wrap portion 53A of the fixed scroll 51A, and the other suction hole 63 is the outermost lap portion 69A of the orbiting scroll 67A described later. It is arranged close to the outer peripheral edge.

  For this reason, the individual suction holes 63 can allow external air to be sucked into the two compression chambers 73A located on the outermost peripheral side of the compression chambers 73A at a short distance, thereby increasing the temperature of the suction air. It is possible to suppress the compression efficiency and increase the compression efficiency. The air sucked into the outermost circumferential compression chamber 73A from the rib serving suction port 62 is compressed between the wrap portions 53A and 69A and then compressed air from the discharge port 64A provided on the center side of the end plate 52A. Is discharged to the outside.

  Reference numeral 65 denotes a fin-type reinforcing rib that constitutes a fixed-side reinforcing rib together with the rib serving inlet 62, and the fin-type reinforcing rib 65 is formed to protrude from the rear surface side of the end plate 52A and the cylindrical portion 54A. Although it is connected to some fins, it is formed wider than the cooling fins 56A. The fin-type reinforcing rib 65 is formed as a portion serving as both a reinforcing rib that reinforces the fixed scroll 51A between the fixed side through holes 60 and 61 and a part of the cooling fin 56A.

  Further, the fin-type reinforcing rib 65 is formed integrally with the end plate 52A and the cylindrical portion 54A between the fixed side through holes 60 and 61, and connects the end plate 52A and the cylindrical portion 54A. As a result, at the three positions between the fixed side through holes 59 to 61, the three reinforcing ribs composed of the rib serving suction ports 62 and the fin-type reinforcing rib 65 are circumferentially spaced at an interval of 120 °, for example. It is arranged evenly and can secure sufficient rigidity at all these positions.

  The fin-type reinforcing rib 65 extends in the vertical direction along with the cooling fin 56A along the flow direction of the cooling air (the direction of arrow a4 in FIG. 10). For this reason, when the cooling fan 33A is operated, the cooling air comes into stable contact with the cooling fins 56A and the fin-type reinforcing ribs 65, so that the fixed scroll 51A can be efficiently cooled.

  Reference numeral 66 denotes, for example, two extension ribs connected to each of the rib combined suction ports 62. Each extension rib 66 is formed as a ridge that is wider than the cooling fin 56A, and the end plate between the cooling fins 56A. The rib 52A is erected on the back surface of 52A and extends in the vertical direction from the rib serving inlet 62 toward the fin-type reinforcing rib 65.

  Thus, the extension rib 66 increases the cooling efficiency of the fixed scroll 51A by contacting the cooling air while increasing the rigidity of the fixed scroll 51A between the rib combined suction port 62 and the fin-type reinforcing rib 65. .

  On the other hand, 67A is a low-pressure stage orbiting scroll provided in the casing 1 so as to face the fixed scroll 51A. The orbiting scroll 67A is the same as that of the first embodiment as shown in FIGS. In substantially the same manner, a mirror plate 68A formed in a substantially disc shape with the axis O2-O2 as a center, a spiral wrap 69A standing at the center of the front surface of the mirror plate 68A, and a back surface center of the mirror plate 68A The cylindrical boss portion 70A fixed to the one end side of the connecting shaft 18 in a non-rotating state and the outer peripheral side of the end plate 68A are projected and, for example, three pieces spaced apart from each other in the circumferential direction with an interval of about 120 °, for example. The protrusion 71A is generally configured.

  Here, as shown in FIG. 16, a plurality of cooling fins 72 </ b> A extending radially about the boss portion 70 </ b> A are provided on the rear surface of the end plate 68 </ b> A. In this case, when the cooling fan 33A is operated, as indicated by an arrow a2 in FIG. 10, the cooling air flows radially inward from the outer peripheral side of the back surface of the end plate 68A toward the center, so the cooling fins 72A are arranged radially. As a result, the cooling air can be stably brought into contact with each cooling fin 72A, whereby the end plate 68A and the like can be efficiently cooled.

  The wrap portion 69A defines a plurality of compression chambers 73A between the wrap portion 69A and the wrap portion 53A of the fixed scroll 51A. Further, as shown in FIGS. 15 and 16, each protrusion 71 </ b> A is provided with an attachment hole 74 to which the auxiliary crank 28 is attached. Further, a large number of auxiliary cooling fins 75 are erected on the back surface and the end surface of the protruding portion 71A in order to increase the cooling efficiency as much as possible.

  Reference numeral 76 denotes, for example, turning side through holes as second through holes provided at three positions on the end plate 68A of the turning scroll 67A, and each turning side through hole 76 is substantially the same as the fixed side through holes 59 to 61. For example, heat formed on the side of the wrap portion 69A of the orbiting scroll 67A (the compression chamber at the center of the compression chambers 73A) is formed in each auxiliary crank 28 through the orbiting scroll 67A. It suppresses the transmission.

  The turning-side through hole 76 is positioned between the lap portion 69A and each auxiliary crank 28, penetrates the end plate 68A in the axial direction, and covers, for example, the end plate 21A so as to block the heat conduction path interposed therebetween. Extends on both sides in the circumferential direction across a radial imaginary line L '(see FIG. 15) connecting the center O2 (axis O2-O2) and the auxiliary crank 28.

  Reference numeral 77 denotes a turning-side reinforcing rib as a plurality of reinforcing ribs provided on the back side of the end plate 68A of the turning scroll 67A. Each turning-side reinforcing rib 77 is formed by cooling fins 72A as shown in FIGS. Is also formed as a thick protrusion, and protrudes from the rear surface side of the end plate 68A.

  Further, for example, two turning-side reinforcing ribs 77 are arranged in pairs between two adjacent turning-side through holes 76. Each pair of reinforcing ribs 77 is evenly spaced in the circumferential direction with an interval of 120 °, for example, and gives high rigidity to the orbiting scroll 67A at these positions.

  Furthermore, the turning-side reinforcing ribs 77 are arranged radially along the flow of the cooling air, as in the case of the cooling fins 72A. Thereby, the turning side reinforcing rib 77 and the cooling fin 72A can be stably brought into contact with the cooling air, and the cooling efficiency can be further increased. As described above, the turning-side reinforcing rib 77 is formed as a portion serving as both a reinforcing rib for reinforcing the turning scroll 67A and a part of the cooling fin 72A.

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

  First, during the operation of the compressor, as in the first embodiment, when the orbiting scroll 67A orbits with respect to the fixed scroll 51A, the compression unit 4A in the low pressure stage compresses from the rib combined suction port 62. Air is sucked into the chamber 73A. The air is compressed between the wrap portions 53A and 69A of the scrolls 51A and 67A to become compressed air, and is discharged from the discharge port 64A toward the compression portion (not shown) of the high-pressure stage.

  At this time, heat is likely to be generated in the compression chamber 73A on the center side, but this heat can be prevented from being transmitted to the auxiliary crank 28 via the scrolls 51A and 67A by the through holes 59 to 61 and 76, and the bearing 30 and the like. Can protect the parts.

  Further, when air is compressed in the compression chamber 73A, a load in the thrust direction is easily applied to the end plates 52A, 68A and the like. However, the fixed scroll 51A is provided with a rib serving suction port 62, a fin-type reinforcing rib 65, and an extension rib 66 that increase its rigidity, and the orbiting scroll 67A is also provided with the orbiting side reinforcing rib 77. , 68A and the wrap portions 53A, 69A can be prevented from being deformed by a load in the thrust direction.

  On the other hand, during the compression operation, the cooling fan 33A is rotationally driven in substantially the same manner as in the first embodiment. As a result, cooling air is sucked into the outer case 3A 'from the back side of the fixed scroll 51A through the through holes 59 to 61, 76 as shown by an arrow a1 in FIG. Cooling air is also sucked from the air holes 58 around the air 28. For this reason, the through holes 59 to 61 and 76 not only provide the same cooling effect as in the first embodiment, but also each component in the auxiliary crank 28 and the outer case 3 </ b> A ′ can be efficiently connected by the air holes 58. Can be cooled.

  Further, the cooling air sucked into the outer case 3A ′ flows radially inward along the cooling fins 72A and the turning-side reinforcing ribs 77 of the orbiting scroll 67A, as indicated by an arrow a2 in FIG. After cooling the end plate 68A and the like, it flows into the position of the cooling fan 33A through the inner peripheral side of the partition plate 34A, and flows out from the upper and lower outlets 36A in the direction of arrow a3. Since the cooling air flowing out from the lower outlet 36A flows in the vertical direction along the cooling fins 56A and the fin-type reinforcing ribs 65 as shown by the arrow a4, the fixed scroll 51A is efficiently cooled. Can do.

  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, the fixed scroll 51A is provided with the rib serving inlet 62 and the fin-type reinforcing rib 65, and the orbiting scroll 67A is provided with the orbiting side reinforcing rib 77.

  Thereby, even in the state where the fixed side through holes 59, 60, 61 are provided in a plurality of locations of the fixed scroll 51A, the rib serving suction port 62 and the fin-type reinforcing rib 65 are between the through holes 59 to 61. Reinforcing ribs made of either one of the members can be disposed, and the fixed scroll 51A can be reliably reinforced at positions between the through holes 59 to 61 whose rigidity is likely to be relatively lowered.

  As a result, the reduction in scroll rigidity due to the provision of the fixed-side through holes 59 to 61 can be easily compensated by the rib-purpose suction port 62 and the fin-type reinforcing rib 65, and even when the fixed-side through holes 59 to 61 are formed large. The rigidity of the fixed scroll 51A can be improved as a whole.

  Therefore, during operation of the compressor, for example, even if a load in the thrust direction is applied to the fixed scroll 51A, it is possible to reliably prevent the end plate 52A and the lap portion 53A from being deformed by this load. And a compressor can be operated stably, fully exhibiting the cooling performance by fixed side through-holes 59-61.

  In this case, since a part of the reinforcing rib is formed as the rib combined suction port 62 that also serves as the suction port of the compressor, for example, the shape of the existing suction port is changed and this is fixed between the fixed side through holes 59 to 61. By disposing in this way, the suction port can be used as a reinforcing rib, and the number, dimensions, etc. of the dedicated reinforcing rib can be kept small accordingly. Thereby, the shape of 51 A of fixed scrolls can be simplified, and this can be reduced in weight.

  Further, since the other part of the reinforcing rib is formed as a fin-type reinforcing rib 65 that also functions as a cooling fin, the reinforcing rib can be used as a part of the cooling fin 56A, and is fixed by the fin-type reinforcing rib 65 and the cooling fin 56A. The cooling efficiency of the scroll 51A can be increased.

  Moreover, since the two rib serving inlets 62 and the fin-type reinforcing ribs 65 are evenly arranged in the circumferential direction with an interval of 120 °, for example, the rigidity of the fixed scroll 51A can be improved in a well-balanced manner. it can. Thereby, the load in the thrust direction can be stably received by the entire fixed scroll 51A, and for example, it is possible to prevent the end plate 52A and the wrap portion 53A from being easily deformed in a specific direction.

  On the other hand, similarly in the case of the orbiting scroll 67A, even when the orbiting through holes 76 are provided at a plurality of locations, the orbiting side reinforcing ribs 77 can be disposed between the through holes 76, so that the rigidity is likely to be relatively lowered. The orbiting scroll 67A can be reinforced at positions between the through holes 76, and the rigidity thereof can be enhanced as a whole.

  Therefore, for example, the end plate 68A, the lap portion 69A and the like can be reliably prevented from being deformed by a load in the thrust direction and the like, and the compressor can be stably operated while exhibiting sufficient cooling performance by the through hole 76. .

  In the second embodiment, two fixed-side through holes 41 are provided for each flange portion 9A ′ of the fixed scroll 5A ′, and the orbiting-side through holes 42 are provided in the protruding portions 24A ′ of the orbiting scroll 20A ′. Are provided at two locations. However, the number of through holes in the present invention is not limited to the embodiment, and may be configured as a modification shown in FIG. 18, for example. In this case, the cylinder portion 8A ′ of the fixed scroll 5A ′ is provided with four fixed-side through holes 41 ′ for each flange portion 9A ′. Moreover, what is necessary is just to comprise similarly about this in the turning side through-hole.

  Of course, for example, three through holes and five or more through holes may be provided in each flange portion 9A ′ (each projecting portion 24A ′). Furthermore, the hole shape of the through hole is not limited to the arc-shaped long hole illustrated in the embodiment, and may be any hole shape including, for example, a circle and a square.

  Moreover, in 1st Embodiment, it was set as the structure which the through-holes 31 and 32 of a fixed side and a turning side always communicate. However, the present invention is not limited to this. For example, when the space in which the through-holes can be formed is narrow or it is difficult to form a large through-hole due to strength restrictions, these through-holes have the minimum necessary size. For example, when the rotating shaft 15 makes one rotation, a configuration in which the through holes communicate with each other and a state in which the through holes are cut off may be intermittently repeated. Furthermore, in the present invention, the through hole of the fixed scroll and the through hole of the orbiting scroll may be configured not to communicate with each other.

  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 including a refrigerant compressor for compressing a refrigerant, a vacuum pump, and the like.

1 is an external perspective view showing a scroll type air compressor according to a first 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. It is a principal part expanded sectional view in FIG. 2 which expands and shows the compression part of a low voltage | pressure stage. It is a principal part expanded sectional view shown in the state before assembling a fixed scroll, a turning scroll, an auxiliary | assistant crank, etc. of a low voltage | pressure stage. It is the front view which looked at the fixed scroll from the surface side. It is the rear view which looked at the fixed scroll from the back side. It is the front view which looked at the turning scroll from the surface side. It is a front view which shows the fixed scroll of the scroll type air compressor by the 2nd Embodiment of this invention. It is a front view which shows a turning scroll. It is the principal part expanded sectional view which looked at the scroll type air compressor by the 3rd Embodiment of this invention from the same position as FIG. It is the front view which looked at the fixed scroll from the surface side. It is the rear view which looked at the fixed scroll from the back side. It is the top view which looked at the fixed scroll from the arrow XIII-XIII direction in FIG. It is sectional drawing which looked at the fixed scroll from the arrow XIV-XIV direction in FIG. It is the front view which looked at the turning scroll from the surface side. It is the rear view which looked at the turning scroll from the back side. It is sectional drawing which looked at the turning scroll from the arrow XVII-XVII direction in FIG. It is a front view which shows the fixed scroll of the scroll type air compressor by the modification of this invention.

Explanation of symbols

1 Casing 4A, 4B Compression section 5A, 5A ', 5B, 51A Fixed scroll 6A, 6A', 6B, 21A, 21A ', 21B, 52A, 68A End plate 7A, 7A', 7B, 22A, 22A ', 22B, 53A , 69A Lapping unit 14 Motor (drive source)
15 Rotating shaft 20A, 20A ', 20B, 67A Orbiting scroll 26A, 26B, 73A Compression chamber 28 Auxiliary crank (rotation prevention mechanism)
31, 41, 41 ', 59, 60, 61 Fixed side through hole (first through hole)
32, 42, 76 Turning side through hole (second through hole)
35A, 35B Inlet (distribution port)
62 Rib combined suction port (reinforcing rib)
65 Fin-type reinforcement ribs (reinforcement ribs)
77 Revolving side reinforcing rib (Reinforcing rib)

Claims (8)

A casing, a fixed scroll provided with a spiral wrap on the surface of the end plate, a rotating shaft supported by the casing and driven to rotate by a drive source, and a position facing the fixed scroll A rotating scroll connected to the rotating shaft and having a wrap portion standing on the surface of the end plate overlapping the wrap portion to define a plurality of compression chambers, and the fixed scroll and the orbiting scroll are arranged radially outward of the end plates. In a scroll type fluid machine comprising a rotation prevention mechanism connected with
The fixed scroll is provided with a first through hole that is located between the wrap portion and the rotation prevention mechanism and penetrates the fixed scroll,
A scroll type fluid machine characterized in that the orbiting scroll is provided with a second through hole that is located between the lap portion and the rotation preventing mechanism and penetrates the orbiting scroll.   The scroll fluid machine according to claim 1, wherein the first or second through hole is formed as a long hole extending in a circumferential direction of the end plate.   The scroll fluid machine according to claim 1 or 2, wherein a plurality of the first or second through holes are arranged side by side in a circumferential direction of the end plate.   4. The scroll fluid according to claim 1, wherein the first and second through holes are configured to be able to communicate with each other so as to overlap each other and communicate between the back side of the fixed scroll and the back side of the orbiting scroll. machine.   5. The scroll fluid machine according to claim 1, 2, 3, or 4, wherein the casing is provided with a flow port through which cooling air flows at a position of the rotation prevention mechanism.   A plurality of the first through holes are disposed at intervals in the circumferential direction of the end plate, and the fixed scroll is provided with a reinforcing rib that is located between two adjacent through holes and protrudes from the back side of the end plate. The scroll fluid machine according to claim 1, 2, 3, 4 or 5.   The scroll fluid machine according to claim 6, wherein at least a part of the reinforcing ribs is configured as a suction port for sucking air into the compression chamber.   A plurality of the second through holes are arranged at intervals in the circumferential direction of the end plate, and the orbiting scroll is provided with a reinforcing rib that is located between two adjacent through holes and protrudes from the back side of the end plate. The scroll fluid machine according to claim 1, 2, 3, 4, 5, 6 or 7.

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