JP2011149383A - Scroll type fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To retain a temperature of a turning bearing at a proper temperature, and to secure high reliability of the turning bearing even when compression operation is performed at a rotation and load higher than conventional by carrying out heat radiation via a balance weight. <P>SOLUTION: In the scroll type fluid machine including a fixed scroll, a turning scroll provided facing the fixed scroll, a drive shaft connected to a drive source and carrying out rotational movement, a crank part provided in a tip side of the drive shaft and offset toward a radial outer side from the rotation center of the drive shaft, the turning bearing provided in the crank part and supporting the crank part, and the balance weight attached to the crank part via an engagement part and stabilizing the turning movement of the turning scroll, the balance weight is composed of a plurality of plates, and a space is provided between the respective plates. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a scroll fluid machine, and more particularly to a scroll fluid machine for air-cooling a slewing bearing.

  In the scroll fluid machine of Patent Document 1, the balance weight is integrally disposed on the drive shaft in the vicinity of the slewing bearing, and rotates integrally with the drive shaft during compressor operation. In addition, the drive shaft receives a load in the circumferential direction such as gas force and centrifugal force, so a metal such as iron with high rigidity is used, and the balance weight is also made of the same metal from the viewpoint of cost. It is constituted by.

  In the electric compressor described in Patent Document 2, the balance weight is constituted by a plurality of plates.

  Further, in the scroll compressor for a fuel cell disclosed in Patent Document 3, the drive shaft is made of steel, whereas the balance weight is made of brass and is constituted by a single plate.

JP 2006-17013 A JP-A-4-237991 JP2002-235680

  The scroll type fluid machine of Patent Document 1 has insufficient heat dissipation through the balance weight, so that the slewing bearing becomes hot, and the reliability of the slewing bearing is improved when the slewing bearing is operated at higher speed and higher load than before. It was difficult to secure.

  Moreover, since the electric compressor of patent document 2 does not provide the space between several board | plates, it cannot fully radiate heat | fever via a balance weight.

  In the scroll compressor for a fuel cell of Patent Document 3, the balance weight is made of a material having a higher thermal conductivity than the drive shaft, but the crank portion provided with the slewing bearing is in contact with the balance weight. Therefore, when much heat is generated in the slewing bearing, it is not possible to sufficiently radiate heat through the balance weight.

  The present invention keeps the temperature of the slewing bearing at an appropriate temperature by dissipating heat through the balance weight, and ensures high reliability of the slewing bearing even when the compressor is operated at a higher speed and higher load than before. The purpose is to do.

  In order to solve the above-mentioned problems, the present invention provides a fixed scroll, a turning scroll provided to face the fixed scroll, a drive shaft connected to a power source and performing a rotational motion, and the drive shaft. A crank part that is offset from the rotation center of the drive shaft to the outside in the radial direction, a slewing bearing that is provided in the crank part and supports the crank part, and a fitting part in the crank part via a fitting part A scroll type fluid machine having a balance weight which is attached and stabilizes the turning operation of the orbiting scroll, wherein the balance weight is composed of a plurality of plates, and a space is provided between the plurality of plates. A scroll fluid machine is provided.

  In another aspect, the present invention provides a fixed scroll, an orbiting scroll provided opposite to the fixed scroll, and a crank portion whose center is offset radially outward on the distal end side, and performs a rotational motion. A shaft, a orbiting bearing provided on the crank portion for connecting the crank portion and the orbiting scroll, and a balance weight attached to the crank portion via a fitting portion and stabilizing the orbiting operation of the orbiting scroll. The scroll-type fluid machine is provided with a scroll-type fluid machine characterized in that the balance weight has a structure that is sandwiched between members of the balance weight and has a space for the outside air to enter.

  As described above, the heat of the slewing bearing can be maintained at an appropriate temperature by dissipating heat through the balance weight. Therefore, the reliability of the slewing bearing is high even when the compressor is operated at a higher speed and higher load than before. Can be secured.

Compressor sectional view of the present invention The figure which shows the drive shaft and balance weight in Example 1 of this invention. The figure which shows the drive shaft and balance weight in Example 2 of this invention. The figure which shows the drive shaft and balance weight in Example 3 of this invention. The figure which shows the drive shaft and balance weight in the modification of Example 1 of this invention. The figure which shows the drive shaft and balance weight in the modification of Example 1 of this invention. The figure which shows the drive shaft and balance weight in the modification of Example 1 of this invention. The figure which shows the attachment method of the balance weight in Example 1 of this invention. The figure which shows the drive shaft and balance weight in the modification of Example 1 of this invention. The graph which shows the temperature rise of the slewing bearing in each Example of this invention

A first embodiment of the present invention will be described below with reference to FIGS. Here, FIG. 1 and FIG. 2 show a scroll type fluid machine in Embodiment 1 of the present invention. In the figure, reference numeral 1 denotes a compressor body, and the compressor body 1 uses a scroll type air compressor. A casing 2, a fixed scroll 3, a turning scroll 4, a drive shaft 8, a crank portion 9 and rotation prevention are described later. It consists of a mechanism 15 and the like.
Reference numeral 2 denotes a casing that constitutes the outer shell of the compressor body 1, and the casing 2 is formed as a bottomed cylindrical body that is closed on one side in the axial direction and opened on the other side in the axial direction as shown in FIG. . That is, the casing 2 has a cylindrical portion 2A that is open on the other side in the axial direction (the fixed scroll 3 side described later) and an annular bottom portion that is integrally formed on one axial direction side of the cylindrical portion 2A and extends radially inward. 2B and a cylindrical bearing mounting portion 2C protruding from the inner peripheral side of the bottom portion 2B toward both axial sides.

  Further, in the cylindrical portion 2A of the casing 2, a turning scroll 4, a crank portion 9, a rotation prevention mechanism 15 and the like, which will be described later, are accommodated. Further, on the bottom 2B side of the casing 2, a plurality of rotation prevention mechanisms 15 (only one is shown in FIG. 1) are arranged at predetermined intervals in the circumferential direction between the revolving scroll 4 and the end plate 4A side which will be described later. Has been.

  Reference numeral 3 denotes a fixed scroll as one scroll member fixedly provided on the opening end side of the casing 2 (cylinder portion 2A). The fixed scroll 3 includes an end plate 3A formed in a disk shape as shown in FIG. 1, a spiral wrap portion 3B standing on the surface of the end plate 3A, and the wrap portion 3B on the outer side in the radial direction. And a cylindrical support portion 3C which is provided on the outer peripheral side of the end plate 3A so as to be surrounded by a plurality of bolts (not shown) and is fixed to the opening end side of the casing 2 (cylinder portion 2A). ing.

  Reference numeral 4 denotes a orbiting scroll constituting another scroll member. The orbiting scroll 4 faces the fixed scroll 3 in the axial direction and is provided in the casing 2 so as to be orbitable. As shown in FIG. 1, the orbiting scroll 4 includes a disc-shaped end plate 4A, a spiral wrap portion 4B standing on the surface of the end plate 4A, and a rear surface of the end plate 4A (the side opposite to the wrap portion 4B). And a cylindrical boss portion 4C that is attached to a crank portion 9 (described later) via a swivel bearing 11.

  A rotation prevention mechanism 15 (described later) is disposed at a predetermined interval in the circumferential direction of the orbiting scroll 4 on the outer diameter side of the back surface of the orbiting scroll 4 (end plate 4A). The center of the boss 4C of the orbiting scroll 4 is eccentric in the radial direction by a predetermined dimension (orbiting radius) that is predetermined with respect to the center of the fixed scroll 3.

Reference numeral 5 denotes a plurality of compression chambers defined between the wrap portion 3B of the fixed scroll 3 and the wrap portion 4B of the orbiting scroll 4, and each compression chamber 5 has a wrap portion of the orbiting scroll 4 as shown in FIG. By disposing 4B so as to overlap with the wrap portion 3B of the fixed scroll 3, the wrap portions 3B and 4B are sandwiched between the end plates 3A and 4A, respectively.
Reference numeral 6 denotes a suction port provided on the outer peripheral side of the fixed scroll 3. The suction port 6 sucks air from the outside through, for example, an intake filter (not shown), and the air swirls in each compression chamber 5. The scroll 4 is continuously compressed along with the turning operation.

  Reference numeral 7 denotes a discharge port provided on the center side of the fixed scroll 3, and the discharge port 7 is directed toward the storage tank storing compressed air from the compression chamber 5 on the innermost diameter side among the plurality of compression chambers 5. To be discharged. In other words, the orbiting scroll 4 is driven by an electric motor (not shown) or the like via a drive shaft 8 to be described later, and performs an orbiting motion with respect to the fixed scroll 3 in a state in which the rotation is restricted by an after-mentioned rotation prevention mechanism 15. .

  As a result, the compression chamber 5 on the outer diameter side of the plurality of compression chambers 5 sucks air from the suction port 6 of the fixed scroll 3, and this air is continuously compressed in each compression chamber 5. The compression chamber 5 on the inner diameter side discharges compressed air from the discharge port 7 located on the center side of the end plate 3A toward the outside.

  Reference numeral 8 denotes a drive shaft provided rotatably on the bearing mounting portion 2C of the casing 2 via a bearing. The drive shaft 8 has a base end side (one side in the axial direction) protruding outside the casing 2 not shown. It is detachably connected to a power source (drive source) such as an electric motor, and is rotationally driven by this electric motor. A distal end side of the drive shaft 8 is a crank portion 9 described later. Further, a boss portion 4C of the orbiting scroll 4 is connected to the front end side (the other side in the axial direction) of the drive shaft 8 via a crank portion 9 and a revolving bearing 11 which will be described later.

  Reference numeral 9 denotes a crank portion provided integrally with the drive shaft 8 on the tip end side of the drive shaft 8, and the crank portion 9 is connected to a boss portion 4 </ b> C of the orbiting scroll 4 via an orbiting bearing 11 described later. The crank portion 9 is rotated integrally with the drive shaft 8, and the rotation at this time is converted into a turning operation of the orbiting scroll 4 via the orbiting bearing 11. The drive shaft 8 and the crank portion 9 are made of a metal such as iron having high rigidity in order to receive a circumferential load such as gas force or centrifugal force.

  The crank portion 9 is provided with a balance weight 10 for stabilizing the orbiting operation of the orbiting scroll 4, and rotates integrally with the drive shaft 8 when the compressor is operated. The balance weight 10 has a fitting portion, and is attached to the crank portion 9 via the fitting portion. Here, the balance weight described in Patent Document 2 is in contact only with the portion corresponding to the drive shaft 8 of the present embodiment. Therefore, since the balance weight described in Patent Document 2 is in contact only with a slewing bearing, which will be described later, at a position away from the slewing bearing, when heat is generated in the slewing bearing, it is not possible to efficiently dissipate heat through the balance weight. It has become. On the other hand, the balance weight 10 in the present embodiment is in contact with the crank portion 9 between a slewing bearing 9 and a drive shaft 8 which will be described later. Thus, since the balance weight 10 is in contact with the crank portion 9 at a position close to the slewing bearing 11, heat generated in the slewing bearing 11 can be efficiently radiated through the balance weight 10 as compared with Patent Document 2. Can do. Note that the balance weight 10 may be configured to contact the slewing bearing 11. Thereby, the heat generated in the slewing bearing 11 can be radiated directly through the balance weight 10, and more efficiently radiated.

  Reference numeral 11 denotes a orbiting bearing disposed between the boss portion 4C of the orbiting scroll 4 and the crank portion 9. The orbiting bearing 11 supports the boss portion 4C of the orbiting scroll 4 so as to be orbitable with respect to the crank portion 9. The orbiting scroll 4 is compensated for the orbiting operation with a predetermined orbiting radius with respect to the axis of the drive shaft 8.

  The slewing bearing 11 in this embodiment is a cylindrical roller bearing. The orbiting bearing 11 holds the orbiting bearing inner ring 11a provided in the crank portion 9 of the drive shaft 8, the orbiting bearing outer ring 11b provided in the boss portion 4D of the orbiting scroll 4, and the cylindrical roller 11c and the cylindrical roller 11c. It comprises a device (not shown), and transmits the driving force from the crank portion 9 to the orbiting scroll 4 while converting the rotation / revolution motion of the crank portion 9 into the revolution motion of the orbiting scroll 4.

  The slewing bearing 11 is filled with a lubricant, such as grease, etc., so that the slewing bearing can be smoothly rotated, and is enclosed in the slewing bearing 11 by an oil seal 17 and a ring 12 mounted concentrically with the crank portion 9. The grease does not leak to the outside of the slewing bearing 11.

  Recently, there is an increasing demand for higher rotation, particularly in a scroll fluid machine. Accordingly, the slewing bearing 11 has been increased in size as the rotation speed has been increased to improve the reliability of the slewing bearing 11. However, due to an increase in bearing self-heat generation due to an increase in the size of the slewing bearing 11 and an increase in the rotational speed of the drive shaft 8, the slewing bearing inner ring 11 a becomes very hot when the drive shaft 8 rotates. For this reason, the reliability and life of the slewing bearing are reduced. Therefore, a cooling method with higher efficiency than before has become necessary.

  Here, in the scroll fluid machine, when the orbiting bearing 11 is cooled from the orbiting bearing outer ring 11b by applying cooling air to the back side of the orbiting scroll 4, the orbiting bearing inner ring 11a is not directly exposed to the cooling air. For this reason, the slewing bearing 11 is cooled only by being cooled through the slewing bearing outer ring 11b or by radiating heat from the slewing bearing inner ring 11a through the crank portion 9, and thus is easily affected by heat.

  Therefore, in this embodiment, in order to achieve high reliability and long life of the slewing bearing 11 regardless of the influence of heat due to high rotation and high load, the inner ring of the slewing bearing 11 is passed through the crank portion 9 and the balance weight 10. It was set as the structure which can thermally radiate efficiently.

  Reference numeral 14 denotes a discharge pipe provided connected to the discharge port 7 of the fixed scroll 3, and the discharge pipe 14 constitutes a discharge passage for communicating between a storage tank (not shown) and the discharge port 7. It is.

  Reference numeral 15 denotes a plurality of rotation prevention mechanisms (only one is shown in FIG. 1) provided between the bottom 2B of the casing 2 and the back side of the orbiting scroll 4, and each rotation prevention mechanism 15 is, for example, an auxiliary crank mechanism. It is comprised by. The rotation prevention mechanism 15 prevents the turning scroll 4 from rotating and allows the thrust load from the turning scroll 4 to be received on the bottom 2B side of the casing 2. The rotation prevention mechanism 15 may be configured using, for example, a ball coupling mechanism or an Oldham coupling instead of the auxiliary crank mechanism.

  Here, heat dissipation through the crank portion 9 and the balance weight 10 of the slewing bearing 11 in the present embodiment will be described. During the operation of the compressor, the self-heating due to the rotation of the slewing bearing 11 and the heat generated by the sliding between the oil seal 17 and the ring 12 are transferred from the crank portion 9 via the slewing bearing inner ring 11a and the ring 12, respectively. The heat is dissipated by exchanging heat with the atmosphere. When the slewing bearing 11 and the balance weight 10 are brought into contact with each other, heat generated in the slewing bearing 11 is transmitted to the balance weight 10 without passing through the crank portion 9.

  The heat radiation through the balance weight 10 in the present embodiment will be described with reference to FIG. The present embodiment is characterized in that the balance weight 10 is configured by laminating a plurality of thin plates 13 and providing spaces between the plurality of thin plates 13. As a result, a structure is provided in which a space is provided between the balance weight 10 (thin plate 13) and the outside air enters, so that the area in which the outside air contacts the balance weight 10 is dramatically increased. Furthermore, air passes between the thin plate 13 and the thin plate 13 when the drive shaft 8 is rotated by the structure of the present embodiment. As a result, the air that is in contact with the balance weight 10 and is warmed is exchanged with air that is not warmed by the rotation of the drive shaft 8, so that the balance weight 10 can be brought into contact with the air that has not been warmed. By adopting such a structure, heat exchange is performed as compared with the case where the balance weight is configured by a single plate as in Patent Document 1 or 3, and the case where no space is provided between a plurality of plates as in Patent Document 2. Efficiency can be improved.

  5 to 7 show modifications of the structure of the balance weight 10 in this embodiment. Here, the balance weight 10 shown in FIG. 2 considers the positional relationship with the member such as the slewing bearing 11 and compares the inner diameter portion including the fitting portion with the outer diameter portion on the outer diameter side from the inner diameter portion. Thinly formed. That is, there is a step between the inner diameter portion and the outer diameter portion. In the modification shown in FIG. 5, a portion of the outer diameter portion that is thicker than the inner diameter portion is formed by a plurality of thin plates 13. Thereby, the balance weight 10 can be formed without using a plate with a step, and the processing can be facilitated as compared with the structure shown in FIG.

  In the modified example shown in FIG. 6, the outer diameter portion includes not only the portion of the outer diameter portion that is thicker than the inner diameter portion but also the portion where the inner diameter portion exists on the inner diameter side of the outer diameter portion. It is a thing. Compared with the modification shown in FIG. 5, the number of outer diameter portions is increased, so the area in contact with the outside air is increased, and the heat exchange efficiency can be further improved.

  The modification shown in FIG. 7 includes not only a portion of the outer diameter portion that is thicker than the inner diameter portion but also a plurality of thin plates 13 that have no step including a portion where the inner diameter portion exists on the inner diameter side of the outer diameter portion. It is composed. Since the balance weight is formed without using a thin plate having a step, the processing can be further facilitated as compared with the modification shown in FIG.

  FIG. 8 shows a method of attaching the thin plate 13 in the modification of FIG. In this embodiment, as shown in FIG. 8, the balance weight is formed only by the thin plate 13 having a simple shape as compared with the configuration of FIG. 9 described later by making a screw hole in the thin plate 13 and fixing the thin plate 13 with a bolt or the like. 10 can be formed, and the balance weight 10 can be easily processed.

  FIG. 9 shows another modification of the structure of the balance weight 10 in the present embodiment. FIG. 9 shows that the balance weight 10 is composed of a single plate, and when the fixed scroll 3 and the orbiting scroll 4 are on the upper side and the drive shaft 8 is on the lower side, The outer periphery and the inner periphery are provided with a plurality of slits having a circular arc shape (a shape obtained by cutting out a sector having a small radius from a sector having a large radius). As shown in FIG. 9, if the structure is provided with a space that is sandwiched between members of the balance weight 10 and enters the outside air between the upper surface and the lower surface of the balance weight 10, the area in contact with the outside air can be dramatically increased. As shown in FIG. 6, the balance weight need not be constituted by a plurality of plates. By configuring the balance weight 10 with a single plate as shown in FIG. 9, heat can be easily conducted to the entire balance weight 10 as compared with a configuration in which a plurality of plates are screwed, and the heat exchange efficiency is further improved. be able to.

  Here, the balance weight 10 may be made of a material having higher thermal conductivity than the drive shaft 8 and the crank portion 9. In this case, the drive shaft 8 and the crank portion 9 receive a centrifugal force due to rotation, and need to support the orbiting scroll 4 and the like, and need to be made of a material having a certain degree of strength. Therefore, it is not realistic to make the material of the drive shaft 8 and the crank part 9 with a material having a higher thermal conductivity than that of the conventional scroll fluid machine. Therefore, in this embodiment, the drive shaft 8 and the crank portion 9 are made of a material containing iron. On the other hand, the balance weight 10 is not required to be as strong as the drive shaft 8 and the crank portion 9 as long as it has a function of stabilizing the turning operation. Therefore, in this embodiment, the balance weight 10 is made of brass (thermal conductivity 123 W / m · K) or pure copper (400 W / m · K), which has a higher thermal conductivity than iron (thermal conductivity 53.5 W / m · K). K). Thereby, compared with the case where the balance weight 10 is made of iron, the heat exchange efficiency is improved, and the temperature of the slewing bearing 11 can be reduced.

  Note that a cooling fan may be provided at a position where the wind strikes the balance weight 10 and the cooling air generated by the cooling fan may be guided to the balance weight 10, the drive shaft 8, and the crank portion 9. Thereby, the heat exchange efficiency can be further improved by exchanging the air in contact with the balance weight 10, and the heat generated in the slewing bearing 11 can be radiated more efficiently.

  Next, Embodiment 2 of the present invention will be described with reference to FIG. 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. In the first embodiment, the outer periphery of the thin plate 13 has an arc shape. However, in this embodiment, the thin plate 14 in which the outer periphery of each of the thin plates 13 in the first embodiment has a circular shape and the overall shape is a disk shape is used. By making the outer periphery of the thin plate 14 into a circular shape and the entire shape into a disk shape, the heat radiation area per sheet of the thin plate 14 can be increased. Therefore, the number of the thin plates 14 can be reduced from the number of the thin plates 13 while making the heat dissipation area equal to or greater than that of the third embodiment. By reducing the number of the thin plates 14, it is possible to reduce the axial dimension for attaching the heat exchanger between the balance weight 10 and the thin plate 14 to the crank portion 9. Thereby, the space between the some thin plate 14 can be enlarged, more air can pass between the thin plates 13, and it improves heat exchange efficiency further compared with Example 1. FIG. Can do. On the other hand, when a part of the balance weight is formed of the thin plate 14, there is a possibility that a problem occurs in the balance weight and the original function of stabilizing the turning operation of the turning scroll 4. Therefore, in this embodiment, the outer circumferential circle of the thin plate 14 is concentric with the drive shaft 8, and the center of the fitting portion with the crank portion 9 of the thin plate 14 is concentric with the crank portion 9. That is, the center of the fitting portion with the crank portion of the thin plate 14 is formed at a position offset radially outward from the center of the outer peripheral circle of the thin plate 14 or the center of the drive shaft 8. Thereby, since the center of gravity of the thin plate 14 is shifted in the opposite direction to the crank portion 9, the balance of the crank portion can be maintained, and the turning operation of the orbiting scroll 4 can be stabilized. As described above, in the present embodiment, it is possible to dissipate the heat generated in the slewing bearing 11 more efficiently than in the first embodiment, while preventing the problem of the original function of the balance weight.

  The balance weight 10 may be configured by combining a thin plate 13 having an arcuate outer periphery and a thin plate 14 having a disk shape as a whole, by combining the first embodiment and the present embodiment. Thereby, it is possible to achieve both the function of stabilizing the turning operation of the orbiting scroll 4 with respect to the balance weight 10 and the function of radiating the heat generated by the orbiting bearing 11.

  Next, Embodiment 3 of the present invention will be described with reference to FIG. In the present embodiment, the same components as those in the first embodiment or the second embodiment are denoted by the same reference numerals, and the description thereof is omitted. In the present embodiment, radial slits are provided in the thin plate 14 in the second embodiment. Thereby, air can be easily distributed between the thin plates 14. In particular, even when there is no room for the balance weight 10 and the space between the thin plates 14 is narrow, air can be easily circulated between the thin plates 14 as compared with the third embodiment, so that heat is exchanged by the balance weight 11. Efficiency can be improved. Moreover, the heat exchange efficiency by the balance weight 11 can be further improved as compared with the second embodiment by stirring the surrounding air by inserting a slit in the thin plate 14.

  In this embodiment, the thin plate 14 is slitted, but a rib may be provided instead of the slit or together with the slit. Thereby, it is possible to agitate the surrounding air and increase the area in contact with the air, and the heat exchange efficiency by the balance weight 10 can be further improved as compared with the second embodiment.

  FIG. 10 summarizes the effects of the embodiments of the present invention. FIG. 10 is a graph showing the temperature rise (calculated value) of the slewing bearing inner ring 11a when the balance weight 10 having the conventional structure is used and when the balance weight having the structure shown in FIGS. 2 to 4 is used. The calculated values in FIG. 10 are obtained by operating the scroll fluid machine at a predetermined rotational speed, stopping the temperature increase of the slewing bearing 11a, and obtaining the temperature increase value from before the operation when the steady state is reached. In FIG. 10, the vertical axis shows how much the temperature rise value can be reduced by using the balance weight 10 of the conventional structure as a reference. From FIG. 10, when using the balance weight 10 having a structure in which a plurality of thin plates shown in FIGS. 2 to 4 are provided and a space in contact with the outside air is provided between the thin plates, a single plate is used as in the prior art. The temperature rise of the slewing bearing inner ring 11a can be reduced by 20% or more than in the case of the configuration. Further, when the balance weight 10 is made of brass having a higher thermal conductivity than iron, the temperature rise of the slewing bearing inner ring 11a can be further reduced by 5% or more. As described above, if the balance weight 10 having the structure in each embodiment is used, even if the size of the slewing bearing 11 is increased along with the increase in the rotation speed of the scroll type fluid machine, the life of the slewing bearing 11 is increased and the life is increased. Reliability can be realized.

  Although the first to third embodiments have been described for the scroll fluid machine, the present invention can be applied to a system including the scroll fluid machine as one component. For example, you may apply to the nitrogen gas generator provided with the scroll type fluid machine.

  Further, the present invention is not limited to a scroll fluid machine, for example, reciprocating, as long as there is a drive shaft that performs a rotational motion, a bearing for supporting the drive shaft, and a balance weight for balancing the drive shaft. It can also be applied to other types of compressors such as dynamic compressors. Also in this case, the life of the bearing is increased and the reliability is improved by performing heat dissipation through a balance weight for balancing the drive shaft.

  The embodiments described so far are merely examples of implementation in carrying out the present invention, and the technical scope of the present invention is not limitedly interpreted by these. That is, the present invention can be implemented in various forms without departing from the technical idea or the main features thereof. Further, the present invention may be implemented by combining the first to third embodiments.

1 Compressor body
2 Casing
3 Fixed scroll (scroll member)
3A, 4A end plate
3B, 4B lap part
4 Orbiting scroll (scroll member)
5 Compression chamber
6 Suction port
7 Discharge port
8 Drive shaft
9 Crank part 10 Balance weight 11 Slewing bearing
12 Ring 13 Thin plate 14 Heat radiating plate 15 Anti-rotation mechanism 16 Discharge piping (discharge flow path)
17 Oil seal

Claims (16)

A fixed scroll, a turning scroll provided opposite to the fixed scroll, a drive shaft connected to a power source and performing a rotational movement, and provided at a tip end side of the drive shaft and having a diameter from a rotation center of the drive shaft A crank portion offset outward in the direction, a swing bearing provided on the crank portion and supporting the crank portion, a balance weight attached to the crank portion via a fitting portion and stabilizing the turning operation of the orbiting scroll; In a scroll fluid machine with
A scroll type fluid machine, wherein the balance weight is composed of a plurality of plates, and a space is provided between the plurality of plates.   2. The scroll fluid machine according to claim 1, wherein the balance weight is provided with radial ribs or slits.   Of the balance weight composed of the plurality of plates, some of the plates are substantially circular, and the fitting portion of the substantially circular plate with the crank portion is radially from the rotation center of the drive shaft. The scroll fluid machine according to claim 1, wherein the scroll fluid machine is formed at a position offset outward.   4. The scroll fluid machine according to claim 1, wherein the balance weight is configured to come into contact with the crank portion between the swivel bearing and the drive shaft. 5.   The scroll fluid machine according to claim 4, wherein the balance weight is in contact with the swivel bearing.   The scroll fluid machine according to any one of claims 1 to 5, wherein the balance weight is made of a material having a higher thermal conductivity than the drive shaft.   The scroll fluid machine according to any one of claims 1 to 6, further comprising a cooling fan, for guiding cooling air from the cooling fan to the balance weight and the crank portion. A fixed scroll, a turning scroll provided to face the fixed scroll, a crank portion whose center is offset radially outwardly on the tip side, a drive shaft that performs rotational movement, and a crank portion provided on the crank portion; In a scroll type fluid machine comprising a swing bearing that connects the crank portion and the orbiting scroll, and a balance weight that is attached to the crank portion via a fitting portion and stabilizes the orbiting operation of the orbiting scroll.
The scroll fluid machine according to claim 1, wherein the balance weight has a structure that is sandwiched between members of the balance weight so that outside air enters.   When the balance weight is constituted by a single plate and the side where the orbiting scroll is located is the upper side and the side where the drive shaft is located is the lower side, the outer and inner circumferences between the upper and lower surfaces of the balance weight The scroll fluid machine according to claim 8, wherein a plurality of slits having a circular arc shape are inserted.   The scroll fluid machine according to claim 8, wherein the balance weight is constituted by a plurality of plates, and the plurality of plates are screwed.   The scroll fluid machine according to any one of claims 8 to 10, wherein radial ribs or slits are provided on the balance weight.   At least a part of a horizontal cross section of the balance weight has a substantially circular outer periphery, and a fitting portion with respect to the crank portion of a portion of the balance weight having a substantially circular outer periphery is formed from a rotation center of the drive shaft. The scroll fluid machine according to any one of claims 8 to 11, wherein the scroll fluid machine is formed at a position offset radially outward.   The scroll fluid machine according to any one of claims 8 to 12, wherein the balance weight is configured to contact the crank portion between the swivel bearing and the drive shaft.   The scroll fluid machine according to claim 13, wherein the balance weight is brought into contact with the swivel bearing.   The scroll fluid machine according to any one of claims 8 to 14, wherein the balance weight is made of a material containing brass, and the drive shaft and the crank portion are made of a material containing iron.   The scroll fluid machine according to any one of claims 8 to 15, further comprising a cooling fan, for guiding cooling air from the cooling fan to the balance weight and the crank portion.

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