• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The object of the invention is to manufacture a fixed volute element at low cost and to facilitate the positioning between the fixed volute element and an orbital volute element. A fixed volute member 32 includes an end plate 32A and a support member 32B which are manufactured separately. The end plate 32A includes an inner end plate 32Aa, a spiral overlap 32Ab, and a group of cooling fins 52 which is formed on a rear surface 33 of the inner end plate 32Aa. Support member 32B has a circular hole 32Ba in its center into which inner end plate 32Aa is inserted, and housings 39 which house pin crank mechanisms 40 are integrally formed with support member 32B.
    公开号:BE1022576B1
    申请号:E2014/0210
    申请日:2014-03-27
    公开日:2016-06-09
    发明作者:Tamotsu Fujioka；Junichi Asami
    申请人:Anest Iwata Corporation；
    IPC主号:
    专利说明:

    Fixed volute element and volute fluid machine
    Background of the invention
    The present invention relates to a fixed scroll member which is applied to a compressor, a vacuum pump, an expansion machine, and the like, to enable cost reduction, and relates to a scroll fluid machine that includes the scroll element. fixed scroll.
    In a volute fluid machine, a fixed scroll member includes a volute portion which meshes with an overlapping portion of an orbital scroll element, into which a work medium is introduced and which defines a closed chamber such as a compression chamber or an expansion chamber, or a heat-dissipating portion where cooling fins are formed, a connecting portion where the fixed scroll member is fixedly connected to a housing, and a portion of suction where the workplace is sucked. Since a high sealing capacity is required on the volute part, it is necessary to provide the required sealing capacity. Furthermore, since the wear of a butt seal, which consists of a solid lubricant and which is provided at a distal end of the overlap portion, must be removed, it is necessary to reduce the number of cavities that would be produced in the volute part when it is poured. In addition, there is required on the volute portion a resistor which is sufficiently good to suppress deformation of the volute portion during a compression process or while it is being worked.
    In addition, good casting ability (moldability) which allows cooling fins to be formed at narrow intervals and good heat dissipation (thermal conductivity) capability which allows for efficient cooling are also required on the surface. fixed scroll element. In addition, good workability that can reduce work time while maintaining work precision and surface treatment capability that can prevent wear and corrosion while maintaining work precision and ensuring surface hardness are required. In order to satisfy these high required performances, a special Al alloy is used, to which a special surface treatment such as hard anodized aluminum treatment (hard alunite treatment) is applied. This increases the manufacturing cost of the volute element.
    The Japanese publication open to inspection No. H02-125 988 (Patent Document 1) describes a technique in which, in order to avoid the occurrence of seizure or wear on the sliding surfaces of overlapping parts of two elements. of volute which are made of an Al alloy, a hard anodized aluminum treatment (hard alunite treatment) is applied to the sliding surface of an overlapping part while a plating treatment which is Hard and rich in lubricating properties is applied to the sliding surface of the other overlapping part.
    In addition, the Japanese publication open for inspection No. H06-10858 (Patent Document 2) discloses a configuration in which an iron-based sandwich element which has a higher stiffness than an Al material is interposed between Al materials constituting an end plate of a fixed scroll member or an orbital scroll member to provide gas tightness by attenuating the pressure deformation of the end plate due to a pressure difference between the inside and the outside of a pressure chamber while ensuring a lightness and a machining capacity of the volute element concerned. Related Art Document Patent Document
    Patent Document 1 Japanese Publication Open for Inspection No. H02-125 988
    Patent Document 2 Japanese Publication Open for Inspection No. H06-10 858 Summary of Invention
    With the technique described in Patent Document 1, since the special surface treatment is applied to the overlapping part, the high cost is inevitable. Moreover, with the configuration described in Patent Document 2, since the method of inserting the iron-based sandwich element into the endplate must be involved, the working method is complicated, causing the problem that the cost becomes high. On the other hand, because of the closed chamber which is formed by the fixed scroll member and the orbital scroll member, both of the scroll members must be accurately positioned relative to each other. to the other. However, the fixed scroll member is attached to the housing, while the orbital scroll member is connected to the fixed scroll member through a rotation preventing mechanism such as a pin crank mechanism. . For this reason, when the overlapping portions of each of the volute elements are positioned relative to each other, since the overlapping portions of each of the elements volute are invisible from the outside, a significant amount of time must be spent in positioning the overlapping parts accurately.
    The present invention has been made in light of the problem, and an object thereof has been to manufacture a fixed volute element inexpensively. In addition, an object of the present invention is to allow easy and accurate positioning of a fixed scroll member and an orbital scroll member when mounted for a scroll fluid machine.
    In order to achieve the object, according to one aspect of the present invention, there is provided a fixed scroll member which constitutes a part of a scroll fluid machine and which meshes with an orbital scroll element to form a plurality of closed chambers in which a working medium is sealed, including an end face which has a spiral overlap portion which is formed on a surface facing the orbital scroll element and a cooling fin which is formed on the other surface thereof and a support member which has at its center a space in which the end plate is inserted, which support member is arranged to surround the end plate and supports the end plate inserted into the end plate. 'space.
    In accordance with one aspect of the present invention, a scroll fluid machine comprises an orbital scroll member, and a fixed scroll member adapted to mesh with the orbital scroll member to form a plurality of closed chambers sealing a medium of job. The fixed scroll member includes an end face that has a spiral overlap portion formed on a surface facing the orbital scroll member, and a support member that has a center at its center in which the end plate is inserted, which support member is arranged to surround the end plate and supports the terminal plate inserted into the space.
    Brief description of the drawings
    Figure 1 is an overall perspective view of a scroll compressor according to one embodiment of the invention.
    Figure 2 is a vertical cross-section of the scroll compressor.
    Figure 3 is a perspective view of a fixed scroll element which constitutes the scroll compressor.
    Figure 4 is an exploded perspective view of the fixed scroll member.
    Figure 5 is a perspective view of scroll elements of the scroll compressor.
    Detailed Description of the Preferred Embodiments
    Hereinafter, the present invention will be described in detail by the use of an illustrated embodiment thereof. However, the dimensions, materials, shapes, relative positions and the like of the constituent parts, which will be described in the present embodiment, are not intended to limit the scope of the invention exclusively to these, except description opposite.
    An embodiment in which the present invention is applied to a scroll compressor will be described based on FIGS. 1-5. FIG. 1 is an overall perspective view of a scroll compressor 10 according to this embodiment. In Fig. 1, the scroll compressor 10 includes a circular cylindrical housing 12a that covers a drive shaft side and a substantially elliptical cylindrical housing 12b that covers an orbital scroll element and a fixed scroll element. A circular opening portion 14 is formed in an axial end face of the housing 12a so that a drive shaft 18 is inserted and an electric motor (omitted) to rotate the drive shaft transmission 18 is mounted in it.
    A hollow cylindrical inlet conduit 16 is integrally provided at the center of an axial end face of the housing 12b to form an intake opening portion from which cooling air is captured. An outlet pipe 20, which is of quadrangular cross section, is integrally provided with the housing 12a in an outer circumferential surface of the housing 12a so as to form an outlet opening portion from which the cooling air is evacuated. In addition, five intake ducts (of which only 22a, 22b and 22c are shown), of quadrangular cross-section, are provided in an outer circumferential surface of the casing 12b in such a manner as to be dispersed in a circumferential direction and thus forming inlet opening portions from which the cooling air is captured.
    In Fig. 2, an eccentric shaft 24 is integrally formed on a distal end face of the drive shaft 18, and this eccentric shaft 24 has an axis thereof in a position which is parallel to and eccentric relative to an axis of the transmission shaft 18. Therefore, when the transmission shaft 18 rotates, the eccentric shaft 24 orbits (rotates) about the axis of the transmission shaft 18.
    An orbital scroll member 26 includes a circular end plate 26a and a spiral overlap portion 26b that is integrally formed with the end plate 16a. A cylindrical bearing 28 is mounted in a central portion of a rear surface 27 of the orbiting scroll member 26, and the eccentric shaft 24 is rotatably supported by the bearing 28 via a roller bearing. 30. This allows the orbital scroll element 26 to perform an orbital motion together with the eccentric shaft 24.
    Next, the configuration of a stationary scroll member 32 will be described with reference to FIGS. 3 and 4. The stationary scroll member 32 includes an end plate 32A and a support member 32B which are separately manufactured from one another. other. Terminal plate 32A includes a circular disk-shaped inner terminal plate 32Aa and a spiral overlap portion 32Ab which is integrally formed on a surface of inner end plate 32Aa. As illustrated in FIG. 4, a first group of cooling fins 52 is formed on a rear surface 33 of the inner end plate 32Aa. The first group of cooling fins 52 comprises a number of linear cooling fins 52a which extend radially from a circumference of a discharge port 36 (see FIG. is provided at a center of the inner end plate 32Aa towards the outer circumferential end.
    Rectangular parallelepiped type flanges 34 are provided on the inner end plate 32Aa at six locations which scatter in a circumferential direction thereof to project radially outwardly from the rear surface 33 of the housing. the inner terminal plate 32Aa. A bolt hole 34a is provided in each of the flanges 34. The end plate 32A consists of, for example, an Al alloy such as AC4A or AC4C. In this way, an interlocking construction on which the support member 32B is mounted is formed by an outer circumferential end face of the inner end plate 32Aa and the surfaces of the flanges 34 which protrude from the front face. outer circumferential end. The support member 32B has a circular disk shape which has a circular hole 32Ba in which an outer circumferential end of the inner end plate 32Aa is loosely installed. The end plate 32A and the support member 32B are arranged concentrically. The support member 32B is made of FC material. Enclosures 39 are integrally mounted on the support member 32B at three locations which are arranged at equal intervals in the circumferential direction, and the housings 39 are configured to individually accommodate pin crank mechanisms 40, which will be described later. Housings 39 are also installed on an outer circumferential end of the orbital scroll element 26 in positions that face the housings 39 provided on the support member 32B. In addition, a plurality of internally threaded holes 35 are provided in circumferential positions of the support member 32B which correspond to the bolt holes 34a of the flanges 34. The support member 32B is attached to the housing 12b therein of the housing 12b. The end plate 32A is attached to the support member 32B in a state such that the end plate 32A is inserted into the circular hole 32Ba of the support member 32B with bolts 37 which are inserted through the bolt holes 34a. to be screwed into the corresponding internally threaded holes 35. A tiny clearance is provided between the outer circumferential end face of the end plate 32A and the circular hole 32Ba of the support member 32B so as to absorb a difference in expansion thermal that would occur between the end plate 32A and the support member 32B due to a difference in material between them. In addition, this tiny clearance is also necessary for the positioning of the overlap portion 32Ab with the overlap portion 26b of the orbital scroll element 26.
    In Fig. 2, the fixed scroll member 32 forms a plurality of compression chambers "c" together with the orbital scroll element 26. The air is captured in the plurality of compression chambers "c" from a suction port (omitted from the illustration) due to orbital movement of the orbital scroll member 26 to be compressed therein, after which the compressed air is discharged from the discharge port 36 which is formed in the center of the fixed scroll member 32. The compressed air that is discharged from the drain port 36 is fed from a drain pipe 38 which is connected to the drain port. evacuation 36 to a destination where the compressed air is required. A central portion of the rear surface 33 of the fixed scroll member 32 is disposed to face the opening portion of the inlet pipe 16.
    Pin crank mechanisms 40, which function as anti-rotation mechanisms, are provided on the outer circumferential ends of the orbital scroll member 26 and the fixed scroll member 32 at three circumferential locations which are arranged at intervals of 120 °. The pin crank mechanisms 40 are housed within the housings 39 which are provided on the fixed scroll member 32 and the orbital scroll member 26. The pin crank mechanisms 40 each have a crank member 42 which comprises a pair of pin axes 44a and 44b whose axes are parallel and which are located in positions which are eccentric to one another. In this embodiment, the pair of pins pinned 44a and 44b is integrally formed with respect to each other. The pin 44a is rotatably supported in the housing 39 which is integrally formed with the end plate 26a via a roller bearing 46, while the other pin 44b is rotatably supported in the housing 39 which is integrally formed to the support member 32B via a roller bearing 48. The rotation of the orbital scroll member 26 on its own axis is prevented by the pin crank mechanisms 40 which are configured as previously described.
    A centrifugal fan 50 is mounted on the drive shaft 18. The centrifugal fan 50 comprises a circular end plate 50a which is attached to the drive shaft 18 and a plurality of blades 50b which are mounted on the end plate 50a in a circumferential direction. The centrifugal fan 50 rotates together with the transmission shaft 18 which sends to the outside the cooling air flowing along the transmission shaft 18 radially outwardly.
    A second group of cooling fins 54 is formed on the rear surface 27 of the end plate 26a of the orbital scroll element 26. The second group of cooling fins 54 comprises a number of linear cooling fins 54a. which are arranged around the bearing 28 so as to extend radially outwardly from a circumference of the bearing 28.
    In addition, a first cooling air duct and a second cooling air duct are formed in the scroll compressor 10. The first cooling air duct is configured to cool primarily the stationary scroll member. 32, while the second cooling air duct is configured to cool primarily the orbital scroll element 26. The cooling air is introduced into these cooling air lines by rotating the centrifugal fan 50. A pipe 56 is provided with a space defined relative to the rear surface 27 of the orbital scroll element 26 and a distal end portion of the drive shaft 18. The pipe 56 has a shape that covers the surface 27 and the distal end portion of the transmission shaft 18. An interior space of the pipe 56 forms the second cooling air duct which communicates with the pipes 22a to 22nd.
    In addition, a pipe 58 is formed outside the pipe 56 with a space defined between the pipe 56 and itself in such a way as to surround the pipe 56. The first cooling air duct, which comprises a plurality of ducts communicating with the intake duct 16 is formed at the outer circumferential ends of the fixed scroll member 32 and the orbital scroll member 26 between the inlet ducts 22a to 22e. An interior space of the duct 58 forms a first cooling air duct, which communicates the ducts communicating with the intake duct 16. In addition, the duct 56 and the duct 58 are arranged concentrically with respect to the duct 16. transmission shaft 18.
    First, the configuration of the first cooling air duct will be described. When the centrifugal fan 50 is rotating, the cooling air a1 is captured from the intake pipe 16. The cooling air a1 then reaches a central portion of the rear surface 33 of the fixed scroll member 32 and flows from the central portion toward the outer circumferential end of the fixed scroll member 32 between the cooling fins 52a to thereby cool the fixed scroll member 32. Cooling air a1 which reaches the outer circumferential end of the fixed scroll member 32 flows from the conduits formed between the inlet conduits 22a to 22e in the circumferential direction in the conduit which is formed between the pipe 56 and the pipe 58 to thereby cool the orbital scroll element 26 and the drive shaft 18. Thereafter, the cooling air reaches the centrifugal fan 50 and is then is expelled radially outwardly of the centrifugal fan 50 by the centrifugal fan 50 to be discharged from the outlet pipe 20.
    Then, the configuration of the second cooling air duct will be described. When the centrifugal fan 50 is rotating, the cooling air a2 is captured within the housing 12b from the intake pipes 22a to 22e. The cooling air a2 flows through the second cooling air duct which is formed inside the duct 56, and as this proceeds, the orbital scroll member 26 is cooled by the cooling air a2 flowing between the cooling fins 54a. In addition, the cooling air a2 changes direction to flow around the circumference of the transmission shaft 18, which cools the transmission shaft 18. Thereafter, the cooling air a2 reaches the centrifugal fan 50. Next, the cooling air a2 is expelled radially outwardly of the centrifugal fan 50 by the centrifugal fan 50, which evacuates it from the outlet pipe 20.
    Figure 5 shows a state in which the support member 32B of the fixed scroll member 32 and the orbital scroll element 26 are tied together before the end plate 32A is mounted.
    In this embodiment, when the fixed scroll member 32 and the orbital scroll member 26 are mounted in the housing 12b, firstly, only the support member 32B of the fixed scroll member 32 is mounted in the 12b, and the orbital scroll member 26 is mounted on the support member 32B via the pin crank mechanisms 40. Next, a height "t" of the plate-based support member 32B terminal 26a of the orbital scroll element 26 is measured to thereby control a mounting height so that no gap exists between the end plates and the distal ends of the overlapping portions of each other. volute elements. Then, the end plate 32A is finally mounted on the support member 32B using the bolts 37.
    According to this embodiment, since the fixed scroll member 32 is configured such that the end plate 32A and the support member 32B are made separately and the support member 32B is made of the FC material which is very rigid and inexpensive, the manufacturing cost of the fixed scroll member 32 can be reduced while maintaining the required strength.
    Further, when the fixed scroll member 32 and the orbital scroll member 26 are mounted in the housing 12b, first, only the support member 32B is connected to the orbital scroll member 26. This allows the assembling the two parts by viewing the inner portion of the scroll member, and for this reason, the precise positioning between the fixed scroll member 32 and the orbital scroll member 26 can be facilitated.
    In addition, the end plate 32A is formed in a circular disk shape, and the end plate 32A and the support member 32B are arranged concentrically with respect to each other. This not only facilitates the formation of the overlap portion 32Ab on the end plate 32A, but also the attachment between the end plate 32A and the support member 32B and the attachment of the support member 32B to the volute member orbital 26.
    Further, since the housings 39 are integrally formed on the support member 32B and the end plate 26a of the orbital scroll member 26, not only is the mounting of the pin crank mechanisms 40 possible, but mounting the orbital scroll member 26 on the support member 32B through the pin crank mechanisms 40 is also facilitated.
    The connecting portion between the end plate 32A and the support member 32B of the fixed scroll member 32 is configured as an interlocking construction. This facilitates attachment and detachment between the end plate 32A and the support member 32B and prevents the axial dimension increase of the fixed scroll member 32 when compared with a case where the scroll member stationary 32 is not constructed to be divided into two independent parts, whereby the increase in size of the fixed scroll member 32 can be omitted, allowing the stationary scroll member 32 to be made to a compact size.
    Further, since the pin crank mechanisms 40 are adopted as anti-rotation mechanisms, the anti-rotation mechanisms can be housed in the housings 39 which are integrally formed with the support member 32B, and this facilitates the positioning of the fixed scroll member 32 with the orbital scroll element 26.
    In the first cooling air duct, since the central portion of the fixed scroll member 32 which is, in particular, heated to a high temperature can be cooled with the cooling air al which comes from flow from the intake pipe 16 and which is cold, it is possible to enhance the cooling effect. Further, the cooling air α flowing through the first cooling air duct flows between the cooling fins 52a, and this may enhance the cooling of the stationary scroll member 32.
    In the second cooling air duct, the cooling air a2 which is captured from the intake ducts 22a to 22e flows between the cooling fins 54a, and this can enhance the cooling of the cooling element. Orbital volute 26. In addition, cooling airs al and a2 flowing along lines 56 and 58 are directed to be collected at the central portion, and this may increase the cooling airflow at the central part, which reinforces the cooling of the central part.
    The cooling air duct is divided into the first cooling air duct and the second cooling air duct and the cooling fins 52a and the cooling fins 54a are arranged so as to be oriented in the direction in which flows the cooling air. This can reduce the pressure loss of the cooling air. For this reason, the power consumption of the scroll compressor 10 can be reduced.
    In addition, the intake ducts 22a to 22e are arranged to scatter in the circumferential direction of the housing 12b and the first cooling air duct is disposed so as to be dispersed between the intake ducts 22a. at 22nd in the circumferential direction. This can prevent enlargement of the case 12b. In addition, since the lines 56 and 58 are arranged concentrically with respect to the drive shaft 18, the housing 12a can be made compact in size, whereby the housing 12a can be given a small size. Since the pin crank mechanisms 40 are provided as anti-rotation mechanisms, the anti-rotation mechanisms can be of simplified construction and can be made inexpensive in terms of cost, whereby the enlargement of the housing size can be achieved. prevented.
    Further, since the centrifugal fan 50 which can increase the static pressure is provided as a cooling fan, the flow rate of the cooling air a1 and a2 can be increased, and this can also improve the cooling effect.
    It should be noted that a similar cooling effect can also be achieved even in the event that a centrifugal fan of a different type, for example, a sirocco fan, is used. Since the end plate and the support member are separately manufactured in the previously described embodiment, when assembled to a housing, the end plate and the support member can be releasably connected to one another. to the other.
    Compared with the end face which constitutes an inner circumferential portion of the fixed scroll member, the support member which represents an outer circumferential portion does not require any higher performance than that required on the end plate, except a performance regarding strength. As in the previous embodiments, the support member can be made of inexpensive material by manufacturing the support member separately from the end plate, whereby the manufacturing cost of the fixed scroll member can be reduced. .
    In addition, when the fixed scroll member and the orbital scroll member are mounted in the housing, the support member is first mounted in the housing. Then, the orbital scroll element is mounted in the housing, after which the end plate of the fixed scroll member can be mounted. By executing the editing work according to this editing procedure, the editing work can be performed while viewing the overlapping portion of the orbital scroll element. This facilitates the mounting work of the two scroll members and allows the overlapping portions of either of the scroll members to be accurately positioned relative to each other.
    It is important to eliminate any clearance between a distal end of the overlap portion and the end plate that faces the overlap portion to ensure sealing performance of the closed chamber. According to the previous embodiment, the orbital scroll element is first mounted to the support member, whereby a relative position between a distal end of the overlap portion of the orbital scroll element and the end plate Fixed volute element can be measured directly. This can facilitate precise positioning between the distal end of the overlap portion and the end plate.
    According to one aspect of the present invention, the end plate is formed into a circular disk shape, and the end plate and the support member may be concentrically disposed relative to each other. By adopting this configuration, the overlap portion can easily be formed at the end plate, and the connection of the end plate with the support member and the connection of the support member with the orbital scroll element are facilitated.
    According to one aspect of the present invention, a plurality of housings may be integrally formed with the support member at a plurality of circumferential locations on the support member, each of these housings housing an anti-rotation mechanism to prevent a rotation of the orbital scroll element on its own axis. By adopting this configuration, not only can the anti-rotation mechanisms be easily mounted, but the orbital scroll element can also be easily mounted on the support member via the anti-rotation mechanisms.
    According to one aspect of the present invention, a support portion of the support member which supports the end plate forms an interlocking construction between itself and an outer circumferential end of the end plate, together with a flange which is provided on at least one of the end plate or the support member, and the end plate and the support member are attached together through the flange by means of a fastener (e.g., a bolt, or the like). In other words, a support portion of the support member that supports the end plate, an outer circumferential end of the end plate, and a flange on at least one or the end plate or the support member can form an interlocking construction between them, and the end plate and the support member may be attached together through the flange by means of a fastener (eg, a bolt or the like).
    By adopting this configuration, not only the terminal plate and the support member can easily be attached to each other in a detachable manner, but it is also possible to prevent an axial dimension increase of the fixed scroll element, whereby the fixed scroll element can be manufactured to a compact size.
    According to a further aspect of the invention, the end plate is formed of an Al alloy, and the support member may be formed of a member which is stiffer than the Al alloy. By adopting this configuration, the end plate can satisfy the required performance to a sufficient extent, and by using the element, which is formed of the material which is stiffer than the Al alloy, for the support element, the strength that is required on the outer part can be satisfied.
    For example, the support member may be formed of a FC material (gray cast iron). By adopting this configuration, the outer part can be manufactured at low cost.
    In addition, a volute fluid machine according to one aspect of the present invention is a scroll fluid machine which includes the fixed scroll member which has been previously described. For example, in the case of a scroll compressor, volute vacuum pump, or the like, the work environment is compressed into the plurality of closed chambers that are formed by the fixed scroll member and the scroll member. orbital, whereas in the case of a volute expansion machine, the working environment is dilated in the plurality of closed chambers.
    According to the volute fluid machine of one aspect of the present invention, including the fixed scroll member which is configured as previously described, not only can the low-cost fixed scroll member be manufactured, but can also position the fixed scroll member and the orbital scroll member accurately relative to each other when assembled for the scroll fluid machine.
    According to one aspect of the invention, the scroll fluid machine may include an anti-rotation mechanism which is provided between the fixed scroll member and the orbital scroll element to prevent rotation of the orbital scroll member on its own axis. Then, this anti-rotation mechanism is housed in an inner part of a housing which is formed on the support member and in an inner part of a housing which is formed on an end plate of the orbital scroll element which facing the support member, and has a crank member which includes a pair of shafts whose axes are eccentric to each other and which are integrally formed relative to each other. 'other. The pair of shafts can be individually rotatably supported through a bearing in the respective casings of the fixed scroll member and the orbital scroll member.
    By adopting this configuration, the anti-rotation mechanism can be housed in the housings that are formed on the support member and the orbital scroll element, and for this reason, not only can the anti-rotation mechanisms be rendered compact, but the positioning between the fixed scroll member and the orbital scroll member is also facilitated in the method of attaching the orbital scroll member to the support member through the anti-rotation mechanism.
    According to the embodiment described above, since the fixed scroll member is formed to be separated into the end plate and the support member, the low-cost fixed scroll element can not only be made, but one can also perform the positioning between the fixed scroll element and the orbital scroll element easily and accurately.
    Industrial applicability
    According to the previously described embodiment, the manufacturing cost of the fixed scroll member can be reduced, and the positioning between the fixed scroll member and the orbital scroll member can be performed easily and accurately.
    Although only a few exemplary embodiments of the present invention have been described in detail above, those skilled in the art will readily be aware that many modifications are possible in the exemplary embodiments without deviate materially from the teaching and advantages of a new type of the present invention. Thus, all such modifications are intended to be included within the scope of the present invention.
    The present application claims priority over Japanese Patent Application No. 2013-072383 filed March 29, 2013.
    Description of numbers and reference characters 10 scroll compressor; 12a, 12b casing; 14 opening party; 16, 22a to 22nd intake duct; 18 drive shaft; Outlet pipe; 24 eccentric shaft; 26 orbital scroll element; 26a end plate; 26b overlapping part; 27 rear surface; 28 landing; 30, 46, 48 roller bearing; 32 fixed scroll element; 32A end plate; 32Aa internal terminal plate; 32Ab overlapping part; 32B support element; 32Ba circular hole; 33 rear surface; 34 flange; 34a bolt hole; 35 internally threaded hole; 36 vent hole; 37 bolt; 38 drain pipe; 39 casing; 40 pin crank mechanism; 42 crank element; 44a, 44b pinned pin; 50 centrifugal fan; 50a end plate; 50b dawn; First group of cooling fins; 52a cooling fin; 54 second group of cooling fins; 54a cooling fin; 56, 58 conduct; a1, a2 cooling air; c compression chamber.
    权利要求:
    Claims (17)
    [1]
    1. - Fixed scroll element (32) which is part of a scroll fluid machine (10) and which meshes with an orbital scroll element (26) to form a plurality of closed chambers (c) in which a work environment is sealed, comprising: an end plate (32A) having a spiral overlap portion (32Ab) formed on a surface facing the orbital scroll member (26); and a support member (32B) which has at its center a space (32Ba) in which the end plate (32A) is inserted, which support member (32B) is arranged to surround the end plate (32A) and supports the end plate (32A) inserted in the space (32Ba) characterized in that the end plate (32A) has a cooling fin (52a) formed on the other surface of the end plate (32A).
    [2]
    The fixed scroll member (32) of claim 1, wherein the end plate (32A) is formed into a circular disk shape, and the end plate (32A) and the support member (32B) are disposed concentrically with each other.
    [3]
    The fixed scroll member (32) according to any one of claims 1 and 2, wherein a plurality of housings (39) are integrally formed with the support member (32B) at a plurality of locations. circumferential on the support member (32B), each of these housings (39) housing an anti-rotation mechanism (40) to prevent rotation of the orbital scroll element (26) on its own axis.
    [4]
    The fixed scroll member according to any one of claims 1 and 2, wherein a support portion of the support member (32B) which supports the end plate (32A), an outer circumferential end of the end plate. (32A), and a flange (34) provided on at least one of the end plate (32A) or the support member (32B) form an interlocking construction therebetween, and the end plate (32A) and the support member (32B) are attached together via the flange (34) by means of a fastener (37).
    [5]
    5. - Fixed scroll element according to any one of claims 1 and 2, wherein the end plate (32A) is formed of an aluminum alloy, and the support member (32B) is formed of a element that is stiffer than the aluminum alloy.
    [6]
    The fixed scroll member according to claim 5, wherein the member which is stiffer than the Al alloy is made of gray cast iron material.
    [7]
    7. - Volute fluid machine comprising: an orbital scroll element (26); and a fixed scroll member (32) adapted to mesh with the orbital scroll member (26) to form a plurality of closed chambers (c) sealing a work environment, wherein the fixed scroll member (32) ) comprises an end plate (32A) having a spiral overlap portion (32Ab) formed on a surface facing the orbital scroll member (26); and a support member (32B) which has at its center a space (32Ba) in which the end plate (32A) is inserted, which support member (32B) is arranged to surround the end plate (32A) and supports the end plate (32A) inserted in the space. characterized in that the end plate (32A) has a cooling fin (52a) formed on the other surface of the cooling plate (32A).
    [8]
    The volute fluid machine according to claim 7, wherein the end plate (32A) is formed into a circular disk shape, and the end plate (32A) and the support member (32B) are arranged concentric with each other.
    [9]
    The volute fluid machine according to any one of claims 7 and 8, wherein a plurality of housings (39) are integrally formed with the support member (32B) at a plurality of circumferential locations on the support member (32B), each of said housings (39) housing an anti-rotation mechanism (40) to prevent rotation of the orbital scroll element (26) on its own axis.
    [10]
    10. - volute fluid machine according to any one of claims 7 and 8, wherein a support portion of the support member (32B) which supports the end plate (32A), an outer circumferential end of the plate terminal (32A), and a flange (34) provided on at least one of the end plate (34A) or the support member (32B) form an interlocking construction therebetween, and the terminal plate (32A) and the support member (32B) are attached together via the flange (34) by means of a fastening device (37).
    [11]
    11. - volute fluid machine according to any one of claims 7 and 8, wherein the end plate (32A) is formed of an aluminum alloy, and the support element is formed of an element which is stiffer than aluminum alloy.
    [12]
    The fixed scroll fluid machine according to claim 11, wherein the element which is stiffer than the aluminum alloy is made of gray cast iron material.
    [13]
    The volute fluid machine according to any one of claims 7 and 8, including an anti-rotation mechanism (40) which is provided between the fixed scroll member (32) and the orbital scroll element (26). ) to prevent rotation of the orbital scroll element (26) on its own axis, wherein the anti-rotation mechanism (40) is housed in an inner portion of a housing (39) which is formed on the element a support (32B) and an inner portion of a housing (39) formed on an end plate (26a) of the orbital scroll element (26) facing the support member (32B), and the anti-rotation mechanism (40) has a crank member (42) which comprises a pair of shafts (42a, 42b) integrally formed with each other, the shafts of the shafts (42a, 42b) being eccentric relative to each other, and wherein the pair of shafts (42a, 42b) are individually supported in a manner by a bearing (46, 48) in the respective housings (39) of the fixed scroll member (32) and the orbital scroll member (26).
    [14]
    The volute fluid machine of claim 9 including an anti-rotation mechanism (40) which is provided between the fixed scroll member (32) and the orbital scroll member (26) to prevent rotation of the the orbital scroll member (26) on its own axis, wherein the anti-rotation mechanism (40) is housed in an interior portion of a housing (39) which is formed on the support member (32B) and in an inner portion of a housing (39) which is formed on an end plate (26a) of the orbital scroll member (26) facing the support member (32B), and the anti-rotation mechanism (40) has a crank member (42) which comprises a pair of shafts (42a, 42b) integrally formed with each other, the shafts of the shafts (42a, 42b) being eccentric one to the other. to the other, and wherein the pair of shafts (42a, 42b) is individually rotatably supported by means of bearing area in the respective housings (39) of the fixed scroll member (32) and the orbital scroll member (26).
    [15]
    The volute fluid machine of claim 10 including an anti-rotation mechanism (40) which is provided between the fixed scroll member (32) and the orbital scroll member (26) to prevent rotation of the the orbital scroll member (26) on its own axis, wherein the anti-rotation mechanism (40) is housed in an interior portion of a housing (39) which is formed on the support member (32B) and in an inner portion of a housing (39) which is formed on an end plate (26a) of the orbital scroll member (26) facing the support member (32B), and the anti-rotation mechanism (40) has a crank member (42) which comprises a pair of shafts (42a, 42b) integrally formed with each other, the shafts of the shafts (42a, 42b) being eccentric one to the other. relative to each other, and wherein the pair of shafts (42a, 42b) is individually rotatably supported by the intermediate a bearing (46, 48) in the respective housings (39) of the fixed scroll member (32) and the orbital scroll member (26).
    [16]
    The volute fluid machine of claim 11 including an anti-rotation mechanism (40) which is provided between the fixed scroll member (32) and the orbital scroll member (26) to prevent rotation of the the orbital scroll member (26) on its own axis, wherein the anti-rotation mechanism (40) is housed in an interior portion of a housing (39) which is formed on the support member (32B) and in an inner portion of a housing (39) which is formed on an end plate (26a) of the orbital scroll member (26) facing the support member (32B), and the anti-rotation mechanism (40) has a crank member (42) which includes a pair of formed shafts (42a, 42b) integrally with each other, the shafts of the shafts (42a, 42b) being eccentric, one being to the other, and wherein the pair of shafts (42a, 42b) is individually rotatably supported by means of bearing area (46, 48) in the respective housings (39) of the fixed scroll member (32) and the orbital scroll member (26).
    [17]
    A volute fluid machine according to claim 12, including an anti-rotation mechanism (40) which is provided between the fixed scroll member (32) and the orbital scroll member (26) to prevent rotation of the the orbital scroll member (26) on its own axis, wherein the anti-rotation mechanism (40) is housed in an interior portion of a housing (39) which is formed on the support member (32B) and in an inner portion of a housing (39) which is formed on an end plate (26a) of the orbital scroll member (26) facing the support member (32B), and the anti-rotation mechanism (40) has a crank member (42) which comprises a pair of shafts (44a, 44b) integrally formed with each other, the shafts of the shafts (44a, 44b) being eccentric, one being relative to each other, and wherein the pair of shafts (44a, 44b) is individually rotatably supported by means of bearing area (46, 48) in the respective housings (39) of the fixed scroll member (32) and the orbital scroll member (26).
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    同族专利:
    公开号 | 公开日
    JP2014196690A|2014-10-16|
    CN104074756B|2018-03-23|
    CN104074756A|2014-10-01|
    JP6170320B2|2017-07-26|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2013072383A|JP6170320B2|2013-03-29|2013-03-29|Fixed scroll body and scroll type fluid machine|
    JP723832013|2013-03-29|
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