JP5096192B2 - Scroll type fluid machine - Google Patents

Description

  The present invention relates to a scroll fluid machine used as a positive displacement expander or compressor, and in particular, a pair of fixed scrolls are arranged on both sides in the axial direction of an orbiting scroll, and the pair of crankshafts are radially outward. The present invention relates to a scroll-type fluid machine of an outer periphery driving type arranged in the above.

  As described above, as the scroll type fluid machine, as described above, a pair of fixed scrolls are arranged on both sides in the axial direction of the orbiting scroll, and a peripheral drive type scroll type fluid machine in which a pair of crank shafts are arranged radially outward. (Patent Documents 1, 2 and 3) and a center-driven scroll fluid machine in which a fixed scroll is arranged only on one side in the axial direction of the end plate of the orbiting scroll and the crankshaft is arranged in the scroll shaft core (Patent Document) 4).

The former outer periphery-driven scroll fluid machine can secure approximately twice the capacity of the latter central-drive scroll fluid machine, and the axial direction applied to the mirror surface of the orbiting scroll from the internal working medium. Since the pressure is balanced both in the axial direction, as a result, the axial thrust force does not act on the orbiting scroll, and the mechanical loss can be reduced correspondingly.
Japanese Patent Laid-Open No. 5-52189 JP 2000-27773 A Japanese Patent Laid-Open No. 2001-227481 Japanese Patent Publication No. 6-3192

  However, the following problems remain in the outer periphery-driven scroll fluid machine such as the former.

  All of the conventional outer periphery-driven scroll fluid machines equipped with a pair of fixed scrolls have a constant rocking radius around the rotation axis of the crankshaft. In order to avoid an excessive radial pressing force between the fixed scroll wrap and the swing scroll wrap, a predetermined radial clearance is secured between the fixed scroll wrap and the swing scroll wrap. Must be designed to However, if such a gap is secured, the amount of leakage of the working medium from the high-pressure side chamber formed between the scroll wraps to the low-pressure chamber increases, causing a reduction in driving efficiency.

  In order to prevent leakage of the working fluid from the gap, for example, in Patent Document 1, a special bellows-like seal member is disposed between the fixed scroll and the orbiting scroll, but the life of the seal member is also maintained long. It is difficult to do.

(Object of invention)
The present invention improves the drive efficiency by reliably preventing leakage of working fluid between the chambers in the scroll, without providing a special seal member between the fixed scroll wrap and the swing scroll wrap. In addition, an object of the present invention is to provide an outer periphery-driven scroll fluid machine in which the orbiting scroll can be driven smoothly without causing malfunction due to frictional resistance or the like.

In order to solve the above-mentioned problems, the present invention provides an orbiting scroll having spiral orbiting scroll wraps on both sides of an end plate, and is disposed on both sides in the axial direction of the orbiting scroll and meshes with the orbiting scroll wrap. A pair of fixed scrolls having a fixed scroll wrap, a pair of rocking bearings attached to the radial outer peripheral end of the rocking scroll, and an output shaft having an eccentric shaft part into which the rocking bearing is fitted or In a scroll fluid machine having an input crankshaft, the balancer mechanism has a weight center of gravity having a phase difference of about 180 ° from the phase around the crankshaft core of the rocking bearing in the inner ring of each rocking bearing. The balancer mechanism is fitted to the outer peripheral surface of the eccentric shaft portion so as to have a radial gap, and is attached to the eccentric shaft portion by a rotation stopping member. And are rotation stop to prevent relative rotation, the balancer mechanism housing of the tubular for housing the balancer mechanism, provided in the vicinity rocking bearing of the end plate of said orbiting scroll, the polarization and the balancer mechanism housing A seal member is disposed between the outer periphery of the core shaft portion.

According to the above configuration, by forming a radial gap between the outer peripheral surface of the eccentric shaft portion of the crankshaft and the inner peripheral surface of the balancer mechanism, the revolution radius of the orbiting scroll is variable, and A balancer mechanism is attached to the inner ring of the oscillating bearing to suppress the excessive centrifugal force of the oscillating scroll, so that a working medium with an appropriate thickness is interposed between the fixed scroll wrap and the orbiting scroll wrap. Thus, smooth operation of the orbiting scroll can be ensured while maintaining sealing performance and ensuring high driving efficiency.
In addition, for example, even when the working medium leaks in the state of steam, the oil supplied to the rocking bearing, the grease filled in the gap, etc. are isolated from the working medium, thereby extending the life of the rocking bearing. be able to.

  According to the present invention, in the scroll fluid machine having the means for protecting the balancer mechanism as described above, a recess for oil sump is formed on the inner peripheral surface of the balancer mechanism housing, and the recess and the support member for the crankshaft are provided. As a lubricating oil passage, a lubricating oil pipe whose both ends are rotatably supported via a spherical bearing on the balancer mechanism housing and the support member can be disposed.

  According to the above configuration, for example, the lubricating oil that has passed through the oil supply passage in the crankshaft lubricates and cools the clearance between the eccentric piece and the balancer mechanism and the rocking bearing, and then the centrifugal force causes the balancer mechanism housing to It rotates along the inner peripheral surface and gathers in the oil sump recess, and is quickly discharged through the lubricating oil pipe by the centrifugal force of the swirling lubricating oil itself. As a result, the life of the rocking bearing and the like is extended, and it is not necessary to provide a special mechanism for oil pressurization, and power loss is reduced.

  According to the present invention, in each of the above scroll type fluid machines, the fixed scroll and a support member that supports the crankshaft, for example, a machine case or the like, are separated, and the swing scroll is sandwiched between the two fixed scrolls and both the fixed scrolls are fixed. The scrolls can be joined together, and the joined fixed scrolls can be attached to a support member such as the machine case.

  According to the above configuration, for example, even if the scroll is made of an aluminum alloy and the supporting member such as a machine case is cast iron, the difference in thermal expansion can be absorbed by the gap, so that an increase in size and cost can be achieved.

  According to the present invention, in each of the scroll type fluid machines, the end of each crankshaft protrudes outward from the support member, and the ends of the crankshafts are fixed to the end of each crankshaft. It can be connected so as to rotate synchronously by a synchronizer comprising a rotating wheel such as a gear and a cord-like body such as a timing belt wound between both rotating wheels.

  According to the above configuration, both crankshafts can be rotated synchronously with a simple structure, and maintenance of the synchronization device is easy.

  According to the present invention, in the scroll type fluid machine provided with the synchronization device as described above, an additional scroll type fluid machine having the same distance between the crankshafts as the distance between the two crankshafts is added, and the additional scroll type fluid machine is provided. The end of each crankshaft of the fluid machine can be connected to each crankshaft of the original scroll fluid machine.

  According to the above configuration, if the additional scroll fluid machine has the same specifications as the original scroll fluid machine, the capacity can be easily increased, and the additional scroll fluid machine has a low pressure specification. Then, a high expansion ratio can be achieved. That is, the capacity and expansion ratio (pressure ratio) can be widened.

  According to the present invention, in each of the scroll fluid machines described above, the pair of crankshafts are disposed so as to be positioned above and below the swing scroll, and the lower crankshaft is wound around the lower crankshaft to transmit power. Driven devices such as drives or generators connected by a mechanism can be arranged.

  According to the above configuration, since the force from the upper crankshaft that is not directly connected to the driven device such as the drive or the generator works to oppose the force from the drive device or the driven device, the lower crankshaft The load applied to the oscillating bearing can be reduced, and the life and size can be reduced. In addition, by arranging both crankshafts at intervals in the vertical direction, for example, the installation area can be reduced as an arrangement place of the condenser and the cooler.

The present invention provides a scroll fluid machine having the drive or driven device, comprising a mount having a mounting portion for mounting said support member such as a machine casing, the attachment portion includes a vertical of the support member It may comprise a vertical support surface in contact with the surface and a lower support portion for supporting the lower end surface of the support member.

  According to the above configuration, when installing the scroll fluid machine to be added, for example, it is lifted by a lifting hook, positioned at the lower end support surface and the vertical support surface, and slid along the lower end support surface and fixed in place. The crankshafts can be easily positioned with respect to the original scroll type fluid machine, and the attachment work, especially the extension work can be facilitated.

  In short, according to the present invention, the revolution radius of the orbiting scroll is variable, and the balancer mechanism is attached to the inner ring of the orbiting bearing to suppress excessive centrifugal force of the orbiting scroll. An operating medium having an appropriate thickness is interposed between the scroll wrap and the seal to maintain the sealing performance, and the smooth operation of the orbiting scroll can be ensured while ensuring high driving efficiency.

[First Embodiment]
(Basic structure of scroll type fluid machine)
FIG. 1 to FIG. 10 show a first embodiment of the present invention, which shows an outer peripheral drive type scroll expander 1 as an example of a scroll type fluid machine. The basic structure of the expander 1 will be described.

  FIG. 1 is an enlarged vertical cross-sectional view of an outer peripheral drive type scroll expander 2. The scroll expander 1 is placed in a storage chamber surrounded by a crankshaft support member such as a cup-shaped machine case 2 and a case cover 3. A single orbiting scroll 5 and a pair of fixed scrolls 6 and 6 are housed. Crank shafts 11 that are parallel to each other and are substantially horizontal are respectively disposed at the upper and lower ends of the machine case 2 and the case cover 3, and each crank shaft 11 is connected to the machine case 2 via bearings 15 and 16 on both axial sides. The case cover 3 is rotatably supported. The fixed scrolls 6 and 6 are disposed on both sides of the swing scroll 5 in the axial direction, and are fixed to substantially the center portions of the machine case 2 and the case cover 3 in the vertical direction.

  The orbiting scroll 5 is integrally provided with a spiral orbiting scroll wrap 25 on each mirror surface formed on both sides of the end plate 5a, and the orbiting scroll wrap 25 is integrated with the end plate 6a of the fixed scrolls 6 and 6, respectively. The fixed scroll wraps 26, 26 formed on 6 a are respectively meshed in the axial direction, and an expansion chamber 30 is formed between the oscillating scroll wrap 25 and the fixed scroll wraps 26, 26 in the radial direction. The expansion chamber 30 at the innermost end in the radial direction communicates with the working medium intake portion 32 of the machine case 2 and the case cover 3 via the working medium inlet 31 formed at the center of each fixed scroll 6, 6. Each working medium intake 32 is connected to a high temperature and high pressure working medium supply device (not shown). The expansion chamber 30 formed at the outermost end portion in the radial direction communicates with a working medium discharge passage (not shown).

  A pair of arm portions 41 extending upward and downward are formed integrally with the end plate 5a at the radially outer end of the end plate 5a of the orbiting scroll 5, and a cylindrical orbiting bearing is provided at the end of each arm portion 41. A housing 43 is integrally formed, and an output rocking bearing 44 is fitted on the inner peripheral surface of each rocking bearing housing 43. A balancer mechanism 37 for suppressing the centrifugal force of the swing scroll 5 is integrally attached to the inner peripheral surface of the inner ring 44 a of each swing bearing 44, and each swing bearing 44 is interposed via the balancer mechanism 37. The upper and lower crankshafts 11 are respectively fitted to the eccentric shaft portions (crank pin portions) 12. The pair of upper and lower oscillating bearing housings 43 is disposed around the basic circle center O2 of the oscillating scroll 5 with an interval of about 180 °. In addition to the balancer mechanism 37, the crankshaft 11 includes a crankshaft for suppressing the centrifugal force of the eccentric shaft portion 12 generated around the crankshaft core (rotating shaft core of the crankshaft 11) C1. The balancer weight 18 is directly fixed, and the crankshaft balancer weight 18 is eccentric in the direction opposite to the eccentric direction of the eccentric shaft portion 12 with respect to the crankshaft core C1.

A cylindrical balancer mechanism housing 48 that protrudes in the axial direction is integrally formed at both ends in the axial direction of each rocking bearing housing 43, and a housing cover 49 is attached to an end surface in the axial direction of each balancer mechanism housing 48. ing. That is, the oscillating bearing 44, the balancer mechanism 37, and the eccentric shaft portion 12 are accommodated in a storage space constituted by the oscillating bearing housing 43, the balancer mechanism housing 48, and the housing cover 49. Furthermore, between the inner peripheral end of the housing cover 49 and the outer peripheral surface of the eccentric shaft portion 12,
An annular seal 19 is provided as a seal member.

  Both end portions of each crankshaft 11 in the axial direction protrude from the machine case 2 and the case cover 3 in the axial direction, respectively, and timing gears 20 having the same diameter are provided at the end portions of the crankshaft 11 protruding from the machine case 2 side. A timing belt (toothed belt) 21 is wound around the upper and lower timing gears 20. That is, the timing gear 20 and the timing belt 21 constitute a synchronization device, and both the crankshafts 11 can be rotated synchronously by the synchronization device. Further, an output timing gear 38 is fixed to one end portion of the lower crankshaft 11 together with the timing gear 20, and the lower crankshaft 11 is a timing belt wound around the output timing gear 38. 39 is connected to an appropriate driven device such as a generator.

  On the other hand, an expansion machine coupling 22 is fixed to the protruding end of each crankshaft 11 on the case cover 3 side.

  2 is a cross-sectional view of the orbiting scroll 5 shown in FIG. 1 showing the state in which the orbiting scroll 5 has been swung (revolved) to the upper end position. FIG. FIG. 4 is an enlarged view of the core shaft 12 and the balancer mechanism 37 and the like, and FIG. 4 is a cross-sectional view corresponding to the IV-IV section of FIG. 1 showing the meshed state of the swing scroll wrap 25 and the fixed scroll wrap 26. 4, the base circle center O2 of the orbiting scroll 5 is separated from the base circle center O1 of the fixed scroll wrap 26 by a predetermined distance (revolution radius) r, and is press-fitted into the expansion chamber 30 near the base circle center O2. As the working medium expands, the orbiting scroll 5 swings (revolves) in the direction of the arrow R11 so that its basic circle center O2 revolves around the basic circle center O1 of the fixed scroll 6. Thereby, both the crankshafts 11 are synchronously rotated via the upper and lower rocking bearing housings 43, the rocking bearings 44, the balancer mechanism 37, and the eccentric shaft portion 12 of FIG.

(Structure of balancer mechanism, etc.)
In FIG. 2, the balancer mechanism 37 is fixed to the inner ring spacer 36 having a cylindrical inner ring spacer 36 fixed to the inner peripheral surface of the inner ring 44 a of each swing bearing 44 by an interference fit with a constant pressure. It is comprised from a pair of balancer weight 35 arrange | positioned at the axial direction both sides of the rocking bearing 44. As shown in FIG.

  In FIG. 3, a radial gap 23 having a constant dimension is formed between the inner peripheral surface of the inner ring spacer 36 and the outer peripheral surface of the eccentric shaft portion 12 in order to make the revolution radius r variable. . The balancer weight 35 is disposed at a position eccentric to the side opposite to the eccentric direction of the eccentric shaft portion core O2 with respect to the crankshaft core C1 so that the centrifugal force of the swing scroll 5 can be canceled efficiently. Yes. Furthermore, a key 28 is fixed to the inner ring spacer 36 and the balancer weight 35 as a rotation stop member at a phase difference of 90 ° with respect to the driving force F1 generated by the orbiting scroll 5. Is engaged with a key groove 28 formed at the end of the eccentric shaft portion 12 on the eccentric direction side with play in the radial direction and the circumferential direction. Thereby, the rocking bearing housing 43 and the rocking bearing 44 of the rocking scroll 5 with respect to the eccentric shaft portion 12 correspond to the gap 19 in the direction of the centrifugal force F2 from the balancer weight 35 and the opposite direction thereof. You can move as much as you want. In other words, if the key 28 is arranged at a phase difference of 90 ° with respect to the driving force F1 generated by the orbiting scroll 5, the driving force F1 generated by the orbiting scroll 5 by the expansion force of the working medium The inner ring spacer 36 is pressed against the eccentric shaft portion 12 to transmit the rotating force of the crankshaft 11 to the eccentric shaft portion 12, but the revolution radius r varies due to the radial sliding of the key 28 and the key groove 29. At the same time, the centrifugal force F2 of the balancer weight 35 for the orbiting scroll directly acts on the orbiting scroll 5 and cancels out the centrifugal force of the orbiting scroll 5 almost completely.

(Setting the center of gravity of the orbiting scroll 5)
FIG. 5 is a diagram showing the centrifugal force F3 and the like generated in the orbiting scroll 5. FIGS. 6 to 9 show the states of the orbiting bearing housing 43 and the balancer mechanism 37 during the oscillation of the orbiting scroll 5 every 90 °. 6 is a state in which the orbiting scroll 5 is positioned at the upper end, and FIG. 7 is a state in which the orbiting scroll 5 is swung 90 ° counterclockwise (around arrow R1) from the state of FIG. 8 is a state of swinging 90 ° counterclockwise (around arrow R1) from the state of FIG. 7, and is positioned at the lower end, and FIG. 9 is 90 ° counterclockwise from the state of FIG. A state of swinging around the arrow R1 and positioned at the right end is shown.

  In FIG. 2, the swing assembly that is separate from the crankshaft 11 and the eccentric shaft portion 12 and excludes the balancer mechanism 37 among the components that swing with the swing scroll 5 (including the swing bearing 44). The center of gravity G2 of the rocking scroll 5 is set to be positioned at the basic circle center O1 of the rocking scroll 5 by adjusting the shape and thickness of the constituent part of the rocking scroll 5, for example, the end plate 5a.

  As a result, the centrifugal force generated by the oscillating assembly such as the oscillating scroll 5 and the oscillating bearing 44 excluding the balancer mechanism 37 is always large during the oscillation of the oscillating scroll 5, as indicated by F3 in FIG. This occurs in a direction from the basic circle center O1 of the fixed scroll 6 toward the basic circle center O2 of the swing scroll 5. F12 is a circumferential component of the force (F1) acting on the orbiting scroll 5 due to the pressure of the working medium, and F13 is a circumferential component of the force (F1) acting on the orbiting scroll 5 due to the pressure of the working medium. It is. When the center of gravity G2 is set as described above, the rocking scroll 5 is provided in a predetermined eccentric direction (the direction opposite to the centrifugal force F3 of the rocking scroll 5) as shown in FIGS. The constant-weight rocking scroll balancer weight 35 can always efficiently cancel the centrifugal force F3 generated by the rocking scroll 5, and maintain the driving efficiency of the scroll expander 1. In other words, the swing scroll balancer weight 35 is always kept at a constant distance from the crankshaft core C1, and the centrifugal force F3 of the swing assembly can be canceled by a constant centrifugal force. As a result, the contact pressure at the contact portions of the scroll wraps 25 and 26 can be prevented from becoming excessive, and the contact portion can be prevented from becoming too large, and the drive efficiency can be maintained high.

(Setting the mass of the upper and lower balancer mechanism 37)
10 shows the distance L1 from the center circle center O2 of the orbiting scroll 5 to the center C3 of the upper orbiting bearing 44 (substantially the same as the axis C2 of the eccentric shaft portion 12) and the center circle center of the orbiting scroll 5. FIG. A relationship between the distance L2 from O2 to the center C3 of the lower rocking bearing 44 (substantially the same as the axis C2 of the eccentric shaft portion 12) and the mass of the upper and lower balancer mechanisms 37 is shown.

  The center of gravity G2 of the oscillating assembly such as the oscillating scroll 5 excluding the balancer mechanism 37 exists on a line that is orthogonal to the crankshaft 11 and connects the centers of the two oscillating bearings 44 in the width direction. The mass of the dynamic scroll balancer weight 35 is the inverse ratio of the distances L1 and L2 between the center circle center O2 (center of gravity G2) of the swing assembly and the center of each swing bearing 44 (eccentric shaft core C2). The size is set to be determined.

  That is, the mass of the rocking assembly excluding the balancer mechanism 37 is m, and the distance from the center circle center O2 of the rocking scroll 5 to the center C3 (C2) of the upper rocking bearing 44 is L1, and the rocking scroll 5 If the distance from the center circle center O2 to the center C3 (C2) of the lower rocking bearing 44 is L2, the mass m of the rocking assembly is the mass m1 of the center C3 of the upper rocking bearing 44 (= m × L2 / (L1 + L2)) and the mass m2 (= m × L1 / (L1 + L2)) of the center C3 of the lower rocking bearing 44. Here, each balancer weight is set so that the moment around the crankshaft core C1 of the upper balancer mechanism 37 is m1 × r and the moment around the crankshaft core C1 of the lower balancer mechanism 37 is m2 × r. Determine the mass of 35. In short, if the upper distance L1> the lower distance L2, the mass m1 of the upper balancer mechanism 37 <the mass m2 of the lower balancer mechanism 37, and conversely, the upper distance L1 <the lower distance L2. If there is, the mass m1 of the upper balancer mechanism 37> the mass m2 of the lower balancer mechanism 37.

  By setting in this way, even if the orbiting scroll 5 revolves around the center circle center O1 of the fixed scroll 6, the center of gravity G3 of the entire orbiting assembly including the balancer mechanism 37 is always in the fixed scroll 6. Since it is located at the base circle center O1 and does not move, no centrifugal force is generated in the entire swing assembly including the balancer mechanism 37.

  When the distance L1 and the distance L2 are equal, the masses m1 and m2 of the upper and lower balancer mechanisms 37 have the same value.

  In the above configuration, the size and mass of the balancer weight 35 of the balancer mechanism 37 are set to values that almost completely cancel out the centrifugal force generated in the orbiting scroll 5. A part of the centrifugal force may be set so as to leave a part, and the part of the remaining centrifugal force may be used as a seal pressure of the contact portion P1 between the fixed scroll wrap 26 and the swinging scroll wrap 25 illustrated in FIG. That is, as shown in FIG. 6, by leaving a part of the centrifugal force of the swing scroll 5 (arrow F31), the swing bearing 44 and the swing bearing housing 43 are separated from the eccentric shaft portion 12 by the gap 23. Is pressed to the key 28 side by an amount equivalent to the above, whereby the seal pressure can be improved at the contact portion P1 between the fixed scroll wrap 26 and the swing scroll wrap 25 shown in FIG. Thereby, it is possible to prevent the working medium from leaking between the expansion chambers 30 and to further improve the driving efficiency.

(Operation of balancer mechanism housing 48, housing cover 49 and seal 19)
In FIG. 1, an axial sliding gap 60 exists between the end plate 5 a of the swing scroll 5 and the axial direction of the fixed scroll wrap 26. For example, when the working medium is steam, the above may leak from the sliding gap 60 and the leaked steam may be applied to the rocking bearing 44. In order to prevent this, in the first embodiment, as described above, the balancer mechanism housing 48 and the housing cover 49 are provided so as to store the rocking bearing 44 and the balancer mechanism 37 separately from the outside. Since the seal 19 between the core shaft portion 12 and the inner ring spacer 36 is disposed, the lubricating oil supplied to the rocking bearing 44 and the grease filled in the gap 23 can be isolated from the working medium in the vapor state. Further, it is possible to extend the life of the rocking bearing 44 and the like.

[Second Embodiment]
FIGS. 11 to 13 show a second embodiment of the present invention. The structure different from the first embodiment of FIGS. 1 to 10 is that the engagement structure between the eccentric shaft portion 12 and the balancer mechanism 37 is a key. And a structure made up of key grooves are changed to an engagement structure between parallel plane portions. In the last explanation of the first embodiment, it is explained that the seal pressure between the scroll wraps 25 and 26 can be improved by leaving a part of the centrifugal force of the swing scroll 5. In the configuration, the rotational speed of the orbiting scroll 5 (the rotational speed of the crankshaft 11) is limited. Therefore, in the present embodiment, the centrifugal force of the orbiting scroll 5 is almost completely canceled and the scroll wraps 25 and 26 are disposed. The seal pressure is also improved. The configuration other than the engagement structure is the same as that of the first embodiment, and the same components are denoted by the same reference numerals (numbers).

  11 is an II-II arrow view of the swing scroll similar to FIG. 2, FIG. 12 is an enlarged view of the swing bearing 44 of the swing scroll in FIG. 11, and FIG. It is an operation explanatory view showing the relationship with the scroll wrap.

  In FIG. 11, a radial gap 23 is formed between the inner peripheral surface of the inner ring spacer 36 and the outer peripheral surface of the eccentric shaft portion 12, as in the first embodiment, and the eccentric shaft portion 12. A pair of parallel flat portions (notches) 50 are formed on the outer peripheral surface of the inner ring spacer, and a pair of chordal flat portions engaging with the two flat surface portions 50 are formed on the inner peripheral surface of the inner ring spacer 36. Thus, the inner ring spacer 36 can be moved in parallel with the flat surface portions 50 and 51 by an amount corresponding to the gap 23 with respect to the eccentric shaft portion 12.

  In FIG. 12, an arrow F12 is a circumferential component of a force acting on the orbiting scroll 5 due to the pressure of the working medium, and an arrow 13 is a radial component of a force acting on the orbiting scroll 5 due to the pressure of the working medium. The flat portions 50 and 51 are set so that, for example, an angle θ1 with respect to the direction of the circumferential direction component F12 is slightly larger than 90 °.

  Therefore, when the reaction force of the liquid film of the working medium at each contact portion P1 between the scroll wraps 25 and 26 shown in FIG. 13 is large, the reaction force swings with respect to the eccentric shaft portion 12 of FIG. When the scroll 5 moves in the direction of the arrow S1 parallel to the flat portions 50 and 51, and on the contrary, when the reaction force of the liquid film of the working medium at each contact portion P1 between the scroll wraps 25 and 26 in FIG. The orbiting scroll 5 moves in the direction of the arrow S2 parallel to the flat surface portions 50 and 51 with respect to the eccentric shaft portion 12. In this way, the orbiting scroll 5 can be moved relative to the eccentric shaft portion 12 in accordance with the reaction force of the liquid film of the working medium existing between the scroll wraps 25 and 26, and the seal pressure is maintained at a predetermined pressure. This is because the revolution radius r of the orbiting scroll 5 is automatically variable.

  Note that the pressing force of the orbiting scroll 5 can be adjusted by changing the angle θ1 of the parallel plane part, and even if the number of turns and the thickness of the scroll wraps 25 and 26 are changed, an appropriate liquid is obtained. The film thickness can be maintained, and even if there is a manufacturing error or thermal expansion, the same contact state is always maintained and the sealing performance is improved.

[Third Embodiment]
FIGS. 14 to 21 show a third embodiment of the present invention. The configuration different from the second embodiment uses an eccentric piece 56 as an engagement structure between the eccentric shaft portion 12 and the balancer mechanism 37. is doing. The configuration other than the engagement structure is the same as that of the first and second embodiments, and the same parts are denoted by the same reference numerals (numbers).

  14 is an enlarged view of the rocking bearing 44 of the rocking scroll 5, FIG. 15 is a sectional view taken along the line XV-XV in FIG. 14, FIG. 16 is an explanatory diagram of the operation of the eccentric piece, and FIGS. FIG. FIG. 20 is an operation explanatory diagram at the time of criticality, and FIG. 21 is an operation explanatory diagram of a state in which the crank angle is advanced more than at the critical time.

  In FIG. 14, an eccentric piece 56 is interposed between the inner peripheral surface of the inner ring spacer 36 and the outer peripheral surface of the eccentric shaft portion 12. The eccentric piece 56 is configured by connecting a pair of halved members 56 a and 56 b with bolts 52, and is a fitting hole that fits with an outer peripheral surface of the eccentric shaft portion 12 with a radial gap 23. 54 and a cylindrical outer peripheral surface that is eccentric from the center of the fitting hole 54 (axial core C2 of the eccentric shaft portion 12) and that is fitted to the inner peripheral surface of the inner ring spacer 36. Therefore, the center of the cylindrical outer peripheral surface coincides with the center C3 of the rocking bearing 44. The eccentric piece 56 is fixed with a restricting pin 53 for restricting rotation that protrudes into the fitting hole 54, and the restricting pin 53 has a pin length in a recess 55 formed on the outer peripheral surface of the eccentric shaft portion 12. Are engaged with each other with play in the direction of the pin and the radial direction of the pin, and thereby, the relative rotation of the balancer mechanism 37 with respect to the eccentric shaft portion 12 is restricted within a minute predetermined angle so that rough positioning can be performed. . The eccentric direction of the center C3 of the eccentric piece 56 with respect to the center of the fitting hole 54 of the eccentric piece 56 (axial core C2 of the eccentric shaft portion 12) is as follows. The eccentric piece 56 is set to be slightly rotatable around the axis C2 of the eccentric shaft portion 12 by a part of the pressing force applied to the eccentric shaft portion 12 via the circumferential component F12. Accordingly, in FIG. 15, the revolution radius r of the rocking bearing 44 around the crankshaft core C1 is made variable. The force for increasing the radius r can be changed by changing the angle β in the eccentric direction of FIG.

  FIGS. 17 to 19 show how the revolution radius r changes as the eccentric piece 56 rotates about the axis C2 of the eccentric shaft portion 12, and FIG. 17 shows the reference revolution radius r. FIG. 18 shows an operation state in which the eccentric piece 56 rotates in the direction of the arrow X1 around the axis C2 of the eccentric shaft portion 12 to have a revolution radius r1 larger than the reference radius r. FIG. 19 shows an operating state in which the eccentric piece 56 rotates in the direction of the arrow X2 around the axis C2 of the eccentric shaft portion 12 to have a revolution radius r2 smaller than the initial radius r. Even when the radius of revolving while the scroll wraps 25 and 26 are in contact with each other due to errors during manufacture and assembly, thermal expansion, etc., deviates from the aforementioned reference radius r, the deviation is caused by the rotation of the eccentric piece 56. You can follow.

  In FIG. 14, the reason why the radial gap 23 is provided between the eccentric shaft portion 12 and the fitting hole 54 of the eccentric piece 56 is as follows.

  As shown in FIG. 20, the upper line 56-1 connecting the center C3 of the upper rocking bearing 44 and the axis C2 of the upper eccentric shaft portion 12, and the center C3 of the lower rocking bearing 44 and the lower side The critical state is when the lower line 56-2) connecting the axis C2 of the eccentric shaft portion 12 on the upper side is parallel. When there is a liquid film of the working medium between the scroll wraps 25 and 26, the revolution radius r2 is smaller than the reference revolution radius r, so that the state shown in FIG. . In other words, the state in which the center C3 of the lower rocking bearing 44 is positioned at the position indicated by the symbol Y1 is a normal state in which the lines 56-1 and 56-2 are parallel to each other, but the symbol Y2 The center C3 of the rocking bearing 44 may move to the abnormal point indicated by. If the crank angle is advanced as it is, the revolution radius r2 increases, the scroll wraps 25 and 26 come into metal contact with each other, and the swing scroll 5 does not swing. On the other hand, by securing a radial gap 23 between the outer peripheral surface of the eccentric shaft portion 12 and the inner peripheral surface of the eccentric piece 56, the contact point between the scroll wraps 25 and 26 is Thus, the center symbol C3 of the rocking bearing 44 can be returned to the normal point Y1.

[Fourth Embodiment]
22 to 24 show a fourth embodiment of the present invention, which is an embodiment provided with an oil supply mechanism of the rocking bearing 44. 22 is an enlarged view of the rocking bearing 44 of the rocking scroll 5, FIG. 23 is a cross-sectional view taken along the line XXIII-XXIII in FIG. 22, and FIG. 24 is an enlarged view of a portion indicated by an arrow K in FIG. The configuration other than the oil supply mechanism is the same as that of the third embodiment, and the same parts are denoted by the same reference numerals (numbers).

  Except for the case where the oscillating bearing 44 is a grease-filled type or the case where it is made of a material that does not need to supply lubricating oil impregnated with a lubricant, it is usually necessary to supply oil. The embodiment includes an oil supply mechanism when the rocking bearing 44 requires oil supply.

  23, a lubricating oil passage 61 communicating with a lubricating oil supply section (not shown) is formed in the crankshaft 11, and the lubricating oil passage 61 is connected to the rocking bearing 44 via a radial passage 61a. Communicating with A recess 62 that is recessed outward (downward) in the radial direction is formed in the lower portion of the balancer mechanism housing 48, and a portion of the housing cover 49 at a position corresponding to the recess 62 is lubricated via a spherical bearing 65. One end of the oil pipe 63 is rotatably supported. The other end of the lubricating oil pipe 63 is rotatably supported by the machine case 2 and the case cover 3 via a spherical bearing 66 so that the lubricating oil can be discharged outside the machine case 2 and the case cover 3. Yes.

  In FIG. 24, the pipe support holes 67 of the spherical bearings 65 and 66 have a small diameter at the end opposite to the lubricating oil pipe 63 side via a stepped portion 67a. Also, the stepped portion 67a and the lubricating oil pipe 63 are arranged. Play is formed between the end surfaces of the two. Further, the outer peripheral surface of the lubricating oil pipe 63 is fitted in each pipe support hole 67 via an O-ring 68.

  According to the oil supply mechanism as described above, the lubricating oil that has passed through the lubricating oil passages 61 and 61a in the crankshaft 11 oscillates between the gap between the outer peripheral surface of the split eccentric piece 56 and the inner ring spacer 36, After the bearing 44 is lubricated and cooled, the bearing 44 is swung so as to stick along the inner peripheral surface of the balancer mechanism housing 48 by centrifugal force and collected in the recess 62. Although the pressure head required for discharging from the recess 62 is required to be larger than the swinging radius, the lubricating oil is promptly introduced to the outside through the lubricating oil pipe 63 by the centrifugal force of the rotating lubricating oil even if the pressure head is not obtained. Can be discharged. Thus, the oil stirring loss caused by the orbiting scroll balancer 35 can be reduced. Further, since the lubricating oil is discharged from the outermost side, the power loss required for turning the lubricating oil is small. Of course, it is possible to extend the service life by refueling.

  Further, since both end portions of the lubricating oil pipe 63 are supported by the spherical bearings 65 and 66, the lubricating oil pipe 63 can be moved following the swing of the swing scroll 5, and the swing scroll 5 can be swung. There is no risk of damage or damage to the lubricating oil pipe.

[Fifth Embodiment]
FIG. 25 to FIG. 26 show the fifth embodiment, but since it has already been disclosed in FIG. 1 of the first embodiment, the structure is substantially included in the first embodiment and has a large capacity. In order to achieve this, the shape of the fixed scroll 6 is devised. FIG. 25 is a view corresponding to FIG. 2 of the orbiting scroll 5 and the fixed scroll 6, and FIG. 26 is a cross-sectional view taken along the line XXVI-XXVI of FIG.

  In FIG. 25, outward flange portions 6b are integrally formed at the outer peripheral ends of the fixed scrolls 6, and the upper and lower arm portions 41 of the orbiting scroll 5 are formed on the flange portions 6a upward and downward from the fixed scroll 6. A notch 70 that can be passed downward is formed.

  At the time of assembly, in FIG. 1, the rocking scroll 5 is sandwiched between a pair of fixed scrolls 6, and the fixed scrolls 6 are positioned in the circumferential direction by positioning pins 71 inserted through the flange portion 6b. And after fixing both the fixed scrolls 6 by the flange part 6b, it fixes to the machine case 2 and the case cover 3. FIG.

  According to the said structure, it becomes possible to manufacture the machine case 2, the case cover 3, and the fixed scroll 6 by another member. For example, the fixed scroll 6 can be made of an aluminum alloy, and the machine case 2 and the case cover 3 can be made of cast iron. Even if configured as such, a structure that can absorb thermal expansion by the gap 23 or the like can be obtained. It can be increased in size and cost.

[Sixth Embodiment]
FIG. 27 shows a sixth embodiment. In the outer periphery driven scroll expander 1 (referred to as the first scroll expander 1 in this embodiment) described in the first to fifth embodiments, FIG. This is a double expander with an additional second outer peripheral drive scroll expander 101.

  The second scroll expander 101 to be added is of a low pressure specification, and the basic structure is the same as that of the first scroll expander 1 of the high pressure specification. The number of turns and the shape of the expansion chamber 30 are different. In the second scroll expander 101, the same parts (numbers) are assigned to the same parts as those in the first scroll expander 1.

  In FIG. 27, the vertical interval between the upper and lower crankshafts 11 of the second scroll expander 101 is the same as the vertical interval between the upper and lower crankshafts 11 of the first scroll expander 1. The upper crankshafts 11 and the lower crankshafts 11 of the scroll expanders 1 and 101 are connected to each other by a coupling 22.

  As described above, a high expansion ratio can be easily achieved by adding the second scroll expander 101 having a low pressure specification. Moreover, the upper and lower crankshafts 11 of the second scroll expander 101 are combined with the crankshaft 11 of the first scroll expander 1 by the synchronization device (timing belt 21 and the like) of the first scroll expander 1. Since it rotates synchronously, there is no need to add a new synchronization device.

  As the second scroll expander 101 to be added, a high-pressure specification similar to the first scroll expander 1 can be connected, and according to this, a large capacity can be achieved.

[Seventh Embodiment]
FIG. 28 shows a seventh embodiment, and in particular, a mounting base 81 suitable for mounting a double scroll fluid machine as in the sixth embodiment is provided. In FIG. 28, a driven device driven by the scroll expander 1 or the like, for example, a generator 75 or the like is installed at the lower part of the mounting base 81, and a column portion 83 that rises vertically upward at the upper part of the mounting base 81. In the column portion 83, a vertical mounting surface 82 is formed and a positioning projection 84 for vertical positioning is formed. On the other hand, the machine case 2 such as the scroll expander 1 is provided with a mounting bracket 80 having a vertical mounted surface 80a, and a suspension ring 86 is provided at the upper end.

  When the scroll expander 1 is attached to the mounting base 81, the scroll expander 1 is lifted by hooking a lifting hook on the suspension ring 86, and the mounted surface 80 a of the bracket 80 is pushed against the vertical mounting surface 82 of the column portion 83. At the same time, the lower end of the bracket 80 is placed on the positioning protrusion (lower end support surface) 84 to be positioned on the mounting base 81 and fixed to the mounting base 81 by appropriate fastening means such as bolts.

  When the second scroll expander 101 is added as shown in FIG. 27, the second scroll expander 101 is lifted by using a lifting hook, similarly to the first scroll expander 1. In a state where the mounted surface 80a of the machine 101 is pressed against the vertical mounting surface 82, it is placed on the positioning projection 84 and slid on the positioning projection 84 to the first scroll type expander 1 side, thereby expanding both scrolls. The machines 1 and 101 can be accurately connected at a predetermined relative position.

  As a mechanism for transmitting power from the scroll expander 1 to the generator 75, a timing gear 38 provided on the lower crankshaft 11, a timing gear 78 fixed to an input shaft 77 of the generator 75, A winding type power transmission mechanism comprising a timing belt 39 wound around both timing gears 38 and 78 is provided. By providing such a wrapping type power transmission mechanism, the force from the upper crankshaft 11 that is not connected to the generator 75 works so as to oppose the force from the generator 75, thereby The load applied to the bearing 15 and the like of the crankshaft 11 on the side can be reduced, and a long life and miniaturization can be achieved.

  By arranging the pair of crankshafts 11 at an interval in the vertical direction, the dimension in the upward direction is increased, but the installation area is reduced, and for example, a place for installing a condenser 76, a cooler, etc. is secured. be able to.

[Other Embodiments]
(1) The scroll fluid machine of the present invention is not limited to a scroll expander, and can be used as a scroll compressor.

It is a longitudinal cross-sectional enlarged view of 1st Embodiment of the outer periphery drive type scroll expander concerning this invention. FIG. 2 is an II arrow view showing a state in which the swing scroll of FIG. 1 swings to the upper end position. FIG. 3 is an enlarged view of an upper rocking bearing and a balancer mechanism in the state of FIG. 2. FIG. 4 is a cross-sectional view corresponding to the IV-IV section of FIG. 1 showing a state in which the swing scroll wrap and the fixed scroll wrap are engaged with each other. It is a figure which shows the centrifugal force etc. which generate | occur | produce in a rocking scroll. It is a figure which shows the state of the rocking | swiveling bearing housing and balancer mechanism in the state where the rocking scroll was located in the upper end. It is a figure which shows the state of a rocking | fluctuation bearing housing and a balancer mechanism in the state which the rocking | fluctuation scroll rock | fluctuated 90 degrees counterclockwise from the state of FIG. It is a figure which shows the state of a rocking | fluctuation bearing housing and a balancer mechanism in the state which rock | fluctuated scroll rock | fluctuated 90 degrees counterclockwise from the state of FIG. FIG. 9 is a diagram showing a state of the swing bearing housing and the balancer mechanism in a state where the swing scroll swings 90 ° counterclockwise from the state of FIG. 8. It is a figure showing the relationship between the distance from the center of the basic circle of the orbiting scroll to the axis of one eccentric shaft, the distance to the axis of the other eccentric shaft, and the mass of each of the upper and lower balancer mechanisms is there. It is 2nd Embodiment of the scroll type expander by this invention, and is the II arrow equivalent view similar to the said FIG. It is an enlarged view of the rocking | swiveling bearing of the rocking | fluctuating scroll of FIG. It is a figure similar to FIG. 4 which shows the relationship between the rocking scroll wrap and fixed scroll wrap of FIG. FIG. 9 is a third embodiment of the scroll expander according to the present invention, and is an enlarged view of a rocking bearing of a rocking scroll. It is XV-XV sectional drawing of FIG. It is operation | movement explanatory drawing of an eccentric piece. It is effect | action explanatory drawing which shows the revolution radius of an orbiting scroll. It is effect | action explanatory drawing which shows the change of the revolution radius of an orbiting scroll. It is effect | action explanatory drawing which shows the change of the revolution radius of an orbiting scroll. It is operation | movement explanatory drawing which shows the revolution radius of the rocking | fluctuation scroll at the time of a critical. FIG. 21 is an operation explanatory diagram in a state in which the crank angle has advanced even after the critical time of FIG. 20. FIG. 6 is a fourth embodiment of the scroll expander according to the present invention, and is an enlarged view of a rocking bearing of a rocking scroll. It is XXIII-XXIII sectional drawing of FIG. It is an enlarged view of the arrow K part of FIG. FIG. 8 is a fifth embodiment of the scroll type expander according to the present invention, and is a view corresponding to II arrow corresponding to FIG. 2. It is XXVI-XXVI sectional drawing of FIG. 6 is a sixth embodiment of the scroll expander according to the present invention, and is a longitudinal section corresponding to FIG. 1. FIG. 10 is a side view showing a seventh embodiment of the scroll expander according to the present invention and a state where the scroll expander is attached to a mounting base.

Explanation of symbols

1 Peripheral drive type scroll expander (an example of a scroll fluid machine)
2 Machine case (support member)
3 Case cover (support member)
DESCRIPTION OF SYMBOLS 5 Fixed scroll 5a End plate 6 Oscillating scroll 6a End plate 11 Crankshaft 12 Eccentric shaft part 15, 16 Crankshaft bearing 18 Crankshaft balancer weight 19 Seal (seal member)
20, 21 Timing gear, timing belt (synchronizer)
22 Coupling 23 Clearance 25 Oscillating scroll wrap 26 Fixed scroll wrap 28, 29 Key, key groove (rotation stop member)
30 Expansion chamber 35 Balancer weight 36 Inner ring spacer 37 Balancer mechanism 38, 39 Timing gear, timing belt (winding transmission mechanism)
41 Arm part 43 Bearing housing 44 Oscillating bearing 48 Housing for balancer assembly 49 Housing cover 50, 51 Planar part 53 Restriction pin (rotation range restriction means)
54 Clearance 56 Eccentric piece 62 Lubricating oil recess 63 Lubricating oil pipe 65, 66 Spherical bearing O1 Fixed scroll center circle center O2 Orbiting scroll center circle center C1 Crankshaft core C2 Eccentric shaft center axis C3 Swing Bearing center

Claims (7)

A swing scroll having spiral swing scroll wraps on both sides of the end plate, and a pair of fixed scrolls having fixed scroll wraps arranged on both sides in the axial direction of the swing scroll and meshing with the swing scroll wrap; A scroll comprising a pair of oscillating bearings attached to an outer peripheral end portion in the radial direction of the oscillating scroll, and an output or input crankshaft having an eccentric shaft portion with which the oscillating bearing is fitted. Type fluid machine,
A balancer mechanism having a weight center of gravity having a phase difference of approximately 180 ° from the phase around the crankshaft center of the rocking bearing is attached to the inner ring of each rocking bearing,
The balancer mechanism is fitted so as to have a radial gap on the outer peripheral surface of the eccentric shaft portion, and is prevented from rotating relative to the eccentric shaft portion by a rotation preventing member,
The balancer mechanism housing of the tubular housing the balancer mechanism, provided in the vicinity rocking bearing of the end plate of said orbiting scroll, distribution seal member between the outer periphery of the said balancer mechanism housing said eccentric shaft portion Scroll type fluid machine installed. The scroll fluid machine according to claim 1 ,
Forming an oil sump recess on the inner peripheral surface of the balancer mechanism housing;
As a lubricating oil passage between the concave portion and the support member of the crankshaft, both ends of the lubricating oil pipe are rotatably supported by the balancer mechanism housing and the support member via spherical bearings. Scroll type fluid machine. The scroll fluid machine according to claim 1 ,
The fixed scroll and the support member that supports the crankshaft are separated.
Wherein combining the two fixed scrolls each other with sandwiching said swing scroll between both the fixed scroll,
Scroll fluid machine that the combined the two fixed scrolls are attached to the support member. The scroll fluid machine according to claim 3 ,
The end of each crankshaft protrudes outward from the support member,
The ends of each crank shaft, wherein the coupled so as to rotate synchronously with each crankshaft end consisting of anchored rotating ring and the two rotary wheels between the wound around the wick member in the synchronizer Scroll fluid machine. The scroll fluid machine according to claim 4, wherein
Providing an additional scroll fluid machine having the same crankshaft distance as the distance between the two crankshafts;
Scroll fluid machine that the ends of the crankshaft of the additional scroll fluid machine, connected to the respective crankshaft of the original scroll fluid machine. The scroll fluid machine according to claim 5 ,
It said pair of crankshaft of the original scroll fluid machine is positioned above and below said swing scroll,
A scroll fluid machine in which a driving or driven device connected to the lower crankshaft by a winding transmission mechanism is disposed below the lower crankshaft. The scroll fluid machine according to any one of claims 3 to 6 ,
Comprising a mount having a mounting portion for mounting said support member,
The mounting portion, the vertical support surface in contact with the vertical surface of the support member, the scroll type fluid machine and a lower support portion for supporting the lower end surface of the support member.

Images