比利时专利BE1023436B1 scroll fluid machine

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专利摘要:
A scroll expansion device includes: a driving scroll body having a first axis as a pivot axis; a driven scroll body having, as a pivot axis, a second axis offset from the first axis; a support plate having the second axis as a pivot axis; a cylindrical drive pin attached to the drive scroll body; and a cylindrical guide ring attached to the support plate and having an inner diameter greater than an outer diameter of the drive pin. Four drive pins are placed on the circumference of a circle around the first axis line at equal intervals. Four guide rings are placed on the circumference of a circle around the second axis line at equal intervals to match the four drive pins.
公开号:BE1023436B1
申请号:E2015/5717
申请日:2015-11-04
公开日:2017-03-20
发明作者:Tamotsu Fujioka；Atsushi Unami；Hiroshi Ito；Takaaki Izumi
申请人:Anest Iwata Corporation；
IPC主号:

专利说明:

SCROLL FLUID MACHINE TECHNICAL FIELD 10001] The present invention relates to a scroll fluid machine.
BACKGROUND
Scroll fluid machines compress or expand a working medium by relative movement between scroll bodies including helical wrappers. A scroll expansion device is a type of scroll fluid machine. The scroll expansion device comprises an expansion chamber formed by a pair of scroll bodies. The scroll expansion device converts energy into rotational energy through expansion of a high pressure working medium in the expansion chamber. As a technology in such a fall area, a scroll expansion device such as described in JP 2011-252434 A is known. SUMMARY
Scroll bodies of a scroll fluid machine rotate about respective axis of rotation. One of the scroll bodies circles relative to the other scroll body.
For example, a scroll-fluid machine described in JP 2011-252434 A has a rotation-regulating mechanism for a relative circular motion. A mechanism that tolerates the circular motion has a more complex structure that of a mechanism that tolerates a rotary motion (e.g., a bearing). In addition, a mechanism that tolerates circular motion tends towards an increasing number of mechanical contact pieces. Therefore, since force and a moment vary easily during the circular motion, it is difficult for the scroll fluid machine to maintain a preferred rotation state.
The present invention has been made in consideration of the problem described above. An object of the present invention is to provide a scrub fluid machine that can maintain a preferred rotational state.
A scroll fluid machine according to an embodiment of the present invention comprises: a driving scroll body comprising a pair of driving end plates and a driving winding formed on each of the pair of driving end plates, and having a first axis line as the axis of rotation ; a driven scroll body comprising a driven end plate and a driven wrap formed on each of both surfaces of the driven end plate, which is placed between the pair of driving end plates and which, as a pivot axis, has a second axis that is offset from of the first axis; a support plate placed on each of both sides of the driven scroll body, which comprises a pair of plates coupled to the driven scroll body, and having the second axis as a pivot axis; a cylindrical drive pin attached to the driving scroll body and projecting from the driving end plate to the support plate; and a cylindrical guide ring attached to the support plate, and comprising an inner diameter greater than an outer diameter of the drive pin. n drive pins (n> 4) or more are placed on a circumference of a circle around the first axis over equal intervals, and m guide rings (m = n> 4) or more are placed on a circumference of a circle around the second axis over the equal intervals to match the drive pins. 10007] In the scroll fluid machine described above, the drive pin revolves around the first axis. One end of this drive pin is placed in the guide ring. The drive pin thus revolves around the first axis while pressing on an inner peripheral surface of the guide ring. A direction of force caused by this rotation (hereinafter also referred to as pin input) always corresponds to a tangential direction of a circle around the first axis. A vertical component of the pin input (hereinafter also referred to as action force on the guide ring) acts on the guide ring from the drive pin. Meanwhile, a direction of the pin input varies depending on a turning position of the drive pin. For example, when the vertical component of the pin input is directed in a vertical downward direction, force acts on the guide ring. In contrast, when the vertical component of the pin input is directed in a vertical upward direction, no force acts on the guide ring. Here, four or more sets of the drive pin and the guide ring are placed at equal intervals. Thus, there are two sets of the guide ring and the drive pin that generate the force in the vertical downward direction so as to press the guide ring. Therefore, at least two sets of the drive pin and the guide ring support the driving scroll body during the circular movement of the scroll body. According to this configuration, since carrying capacity of the driving scroll body is smoothly received, a variation of the carrying capacity during the circular motion is suppressed. Therefore, the scroll fluid machine according to an embodiment of the present invention can maintain a preferred rotation state.
In one embodiment, the number of drive pins (n) and the number of guide rings (m) can be an even number. A description in which the center of the pair of driving end plates is defined as a standard of a turning motion will be given. A moment, different from the action force on the guide ring described above, acts from the driving scroll body to the driven scroll body. This moment is based on a distance between the first axis and a position where the acoustical force is exerted on the guide ring (hereinafter also referred to as an action distance) and magnitude of the action force on the guide ring. The drive pin is placed on a circumference of a circle around the second axis. In the meantime, the guide ring pushed by the drive pin is placed on a circumference of a circle around the second axis. The moment varies periodically with the position of the drive pin. Here the number of drive pins and the number of guide rings is an even number. The number of sets of the guide ring and the driving pin that generates the action force on the guide ring in the vertical downward direction is constant regardless of a turning angle. Accordingly, the periodic variation of the moment is suppressed, and then the periodic variation of the moment generated by the circular motion is suppressed. Therefore, the scroll fluid machine according to the one embodiment of the present invention can maintain a more favorable rotational state. 10009] In one embodiment, the number of drive pins (n) and the number of guide rings (m) can be six (n = m = 6). Since the number of drive pins and the number of guide rings are even numbers, the periodic variation of the moment generated by the circular motion is suppressed. In addition, when the number of drive pins and the number of guide rings is six, the driving scroll body is constantly supported by two sets or more of the driving pin and the articulation ring in the circular motion of the driven scroll body relative to the driving scroll body. body. Therefore, the scroll fluid machine according to the one embodiment of the present invention can preferably suppress the periodic variation of the moment and the variation of the action force on the guide ring generated during the circular motion. As a result, a more favorable rotational state can be maintained.
A scroll-fluid machine according to one embodiment of the present invention can maintain a favorable rotational state.
BRIEF DESCRIPTION OF THE FIGURES
FIG. 1 is a sectional view of a scroll expansion device according to an embodiment of the present invention;
FIG. 2 is a front view of the placement of a drive pin and a guide ring taken along line II-II of FIG. 1;
FIG. 3 is an enlarged sectional view showing the drive pin and the guide ring;
FIG. 4A, 4B, 4C, 4D, 4E and 4F are schematic diagrams showing a pin input, action force on a guide ring, and a component in the scroll expansion device according to the one embodiment;
FIG. 5A is a graphical representation of action force on the guide ring; FIG. 5B is a graphical representation of an input moment; FIG. 5C is a graphical representation of a component; FIG. 5D is a graphical representation of a component moment;
FIG. 6A is a graphical representation of action force on a guide ring in a scroll expansion device according to a first modification; FIG. 6B is a graphical representation of an input moment of the scroll expansion device according to the first modification; FIG. 6C is a graphical representation of a component of the scroll expansion device according to the first modification; FIG. 6D is a graphical representation of a component moment of the scroll expansion device according to the first modification;
FIG. 7A is a graphical representation of an input moment of a scroll expansion device according to a second modification; FIG. 7B is a graphical representation of a component moment of the scroll expansion device according to the second modification;
FIG. 8A is a graphical representation of an action force on a guide ring of a scroll expansion device according to a comparative example; FIG. 8B is a graphical representation of an input moment of the scroll expansion device according to the comparative example; FIG. 8C is a graphical representation of a component of the scroll expansion device according to the comparative example; and FIG. 8D is a graphical representation of a component moment of the scroll expansion device according to the comparative example. DETAILED DESCRIPTION.
An embodiment of the present invention will be described below with reference to the accompanying drawings. In descriptions of the drawings, the substantially same elements are designated with the same reference marks, and unnecessary repetition of their description will be omitted.
As shown in FIG. 1, a power generating system 100 comprising a scroll expansion device 1 drives a dynamo 101 by using the scroll expansion device as a power source. A working medium-supplying portion 102 supplies steam V as working medium to the scroll expansion apparatus 1. Examples of steam V include water vapor, and a cooling agent used in a rankin cycle. The scroll expansion device 1 converts energy that appears with expansion of the supplied steam V in the scroll expansion device into rotation energy. The scroll expansion device 1 transmits the rotation energy to the dynamo 101 via a drive shaft. The steam V is ejected after the expansion to the outside of the scroll expansion device 1. A temperature of the steam V to be emitted is lower than that of the steam V to be supplied. The scroll expansion device 1 extracts, as rotation energy, energy corresponding to a difference between the temperature of the steam V supplied and the temperature of the steam emitted V.
The scroll expansion device 1 comprises, as main components, a housing 2, an input drive shaft 3, an output drive shaft 4, a driving scroll body 6, a driven scroll body 7, a support plate 8, and a engaging mechanism 9.
The housing 2 comprises a pair of cabinets 11 and 12. The housing 2 forms a housing space S1. The housing space S1 accommodates the driving scroll body 6, the driven scroll body 7, the support plate 8 and the engaging mechanism 9. The housing 11 comprises a shaft hole 11a. The input drive shaft 3 is inserted into the shaft hole 1a. A central axis of the shaft hole 11a defines a first axis Al. A driving bearing 1 lb and a driving bearing are placed in the housing 11. The driving bearing 1 lb pivotally supports the input drive shaft 3. The driving bearing 11c supports the bearing plate 8. A central axis of the driving bearing 11b corresponds to the first axis Al. Meanwhile, a central axis of the driven bearing 1 lb corresponds to a second axis line A2. The second axis A2 is offset by a distance t with respect to the first axis A1. The second axis A2 is defined by a central axis of a bearing section 11f. The driven bearing 11c is fitted in the bearing-holding part 11f. A cap 13 is connected to an opening end 11 of the case 11. The cap 13 serves as an interface with the working medium supplying portion 102. In a direction of a first axis Al, an oil seal 13 is placed between the driving bearing 11 lb and the opening end 11 ld. The case 12 has essentially the same structure as case 11. That is to say, the case 12 includes the shaft hole 11a. The driving bearing 1 lb and the driven bearing 1 lc are placed in the case 12. In addition, case 12 comprises an outlet 1 Ie. The outlet 11e ejects the steam V after the expansion.
The input drive shaft 3 is inserted into the shaft hole 11a of case 11. Therefore, a pivot axis of the input drive shaft 3 corresponds to the first axis Al. An end of the input drive shaft 3 is connected to the driving scroll body 6. The input drive shaft 3 comprises a working medium introducing hole 3d. The steam V is introduced through the working medium introducing hole 3a. The working medium introducing hole 3a penetrates from one end to the other end of the input drive shaft 3. The output feed shaft 4 is inserted into the shaft hole 11a of cabinet 12. Therefore, an axis of rotation of the output drive shaft 4 corresponds to the first axis Al. One end of the output drive shaft 4 is connected to the driving scroll body 6. In addition, the other end of the output drive shaft 4 is coupled to the dynamo 101.
The housing space S1 accommodates the driving scroll body 6. The driving scroll body 6 is rotatable about the first axis line A1. The driving scroll body 6 comprises a pair of driving end plates 16 and a pair of driving wrappers 17. Each of the pair of driving end plates 16 comprises a disc-like shape. An outer circumferential edge portion 16c of one of the driving end plates 16 is coupled to the outer circumferential edge portion 16c of the other driving end plate 16. The input drive shaft 6 is connected to an outer surface 16a of the one driving end plate 16. Furthermore, the one driving end plate comprises 16 a working medium introducing hole 16b. The steam V is introduced through the working medium introducing hole 16b. The working medium introducing hole 16b communicates with the working medium introducing hole 3a of the input drive shaft 3. The output drive shaft 5 is connected to the outer surface 16a of the other driving end plate 16. The driving winding 17 is formed on an inner surface 16d of the driving end plate 16 The driving wrapper 17 comprises a helical shape or a spiral shape. The driving wrappers 17 are thus placed between the pair of driving end plates 16. The above-described input drive shaft 3 and the above-described output drive shaft 4 are integrally formed by the driving scroll body 6.
The input drive shaft 3, the output drive shaft 4, and the driving scroll body 6 rotate integrally about the first axis Al. The housing space S1 accommodates the driven scroll body 7. The driven scroll body 7 is rotatable about the second axis A2. The driven scroll body 7 comprises a driven end plate 18 and a driven wrapper 19. The driven end plate 18 comprises a disc-like shape. The driven end plate 18 is placed between the driving end plates 16 of the driving scroll body 6. The driven end plate 18 is coupled to the carrier plate 8. The driven winding 19 is formed on each surface of the driven end plate 18 in a direction in the direction of the driving end plates 16. The driven winding 19 comprises a helical shape or a spiral shape. The driving end plates 16, the driven end plate 18, the driving wrappers 17 and the driven wrappers 19 form an expansion chamber S2. The expansion chamber S2 for expanding the steam V comprises a helical shape or a spiral shape.
The carrier plate 8 rotatably supports the driven scroll body 7 around the second axis A2. The carrier plate 8 comprises a pair of plates 21. The plates 21 each have a substantially disc-like shape. In one direction of the first axis line A1 (or the second axis line A2), one of the pair of plates 21 is placed between the one driving end plate 16 and the case 11. The other plate 21 is placed between the other driving end plate 16 and the case 12 The carrier plate 8 is thus positioned so that the driving scroll body 6 and the driven scroll body 7 are inserted. An outer circumferential edge portion of the plate 21 is coupled to an outer circumferential edge portion of the driven end plate 18. The plate 21 includes a pivot axis portion 21a. A rotatable central shaft of the rotary axis portion 21a is the second axis A2. The pivot axis portion 21a is formed on the side of a surface of the plate 21, with the surface facing the case 11. The pivot axis portion 21a fits into the driven bearing 11c. Therefore, the support plate 8 and the driven scroll body 7 rotate around the second axis A2. This driven scroll body 7 is coupled to the support plate 8. 10021] The engaging mechanism 9 ensures the engaging scroll body 6 and the driven scroll body 7. Specifically, the engaging mechanism 9 ensures the synchronous rotation of the driving scroll body 6 and the driven scroll body 7. The engaging mechanism 9 comprises a drive pin 22 and a guide ring 23. The drive pin 22 is connected to the driving scroll body 6. The guide ring 23 is connected to the support plate 8. Therefore, it is number of drive pins 22 in the scroll expansion device 1 four (n = 4). Furthermore, the number of guide rings 23 is also four (m = 4). As shown in FIG. 2, the scroll expansion device 1 comprises four interlocking mechanisms 9. The four interlocking mechanisms 9 are positioned over an 90 ° interval along a circumference direction of a circle about the first axis A1. Each of the four interlocking mechanisms 9 is placed on a virtual axis parallel to the first axis A1. Four interlocking mechanisms 9 are placed on the side of the input drive shaft 3. Another four interlocking mechanisms 9 are placed on the side of the output drive shaft 4.
As shown in FIG. 3, one end side of the driving pin 22 is connected to the driving end plate 16 of the driving scroll body 6. The other end side of the driving pin is located inside the guide ring 23. The driving pin 22 comprises a pin portion 24 and a flange portion 26. The pin portion 24 includes a column shape that extends along the direction of the first axis Al. The flange portion 26 is formed on the other end side of the drive pin 22. The pin portion 24 and the flange portion 26 are integrally formed. The drive pin 22 comprises a metallic material (e.g. SUS303 material). An end of the pin portion 24 is fitted into a cavity portion of the driving end plate 16. The flange portion 26 is secured to the outer surface 16a of the driving end plate 16 by, for example, a bolt. The other end side of the pin portion 24 is disposed within the guide ring 23.
An outer peripheral surface 22s on the other end side of the pin portion 24 comes into contact with an inner peripheral surface 23a of the guide ring 23. The outer peripheral surface 22s comprises a hard layer 27. The hard layer 27 is formed of an amorphous material substantially a hydrocarbon or an isotope of carbon. Specifically, the hard layer 27 is formed from diamond-like carbon (DLC). The hard layer has a thickness of 1 μηι or more and 5μιη or less, for example. The hard layer 27 comprising diamond-like carbon provides spreadability and wear resistance to a contact portion of the drive pin 22 with the guide ring 23. The hard layer 27 may further comprise other components as an added material other than the hydrocarbon or the isotope which is the main component is. For example, a plasma CVD method or a PVD method can be used to form the hard layer 27.
The drive pin 22 includes a condensate-supplying hole 22a as a condensate-supplying portion. The condensate-providing hole 22a guides the steam V or the condensate to the inside of the guide ring 23. The condensate-providing hole 22a supplies the condensate to a space between the guide ring 23 and the drive pin 22. When the steam V is water vapor, the condensate water. The condensate-supplying hole 22a is a through hole that goes from one cind surface to the other end surface of the pin portion 24. The one end side of the pin portion 24 is fitted into the driving end plate 16. The condensate-supplying hole 22a communicates with a condensate-supplying hole 16e of the driving end plate 16 on one side of the pin portion 24. The expansion chamber S2 is connected to the inside of the guide ring 23 via the condensate-supplying hole 16e and the condensate-supplying hole 22a. As a result, the steam V or the condensate from the expansion chamber S2 is introduced into the inside of the guide ring 23. Note that the steam V is preferably introduced into the guide ring after the expansion. Therefore, the condensate-supplied hole 16e of the driving end plate 16 can be provided at a position that communicates with a space S2a formed of the driving winding 17. The space S2a is a space between an outer circumferential driving winding portion 17a of the driving scroll body 6 and a driving winding portion 17b adjacent to the driving winding portion 17a. In addition, the drive pin 22 which connects the condensate-supplying hole 22a that communicates with the condensate-supplying hole 16e at the same position as the condensate-supplying hole 16e on the driving end plate 16. Specifically, the driving pin 22 is connected to the driving end plate 16 that an axis of the condensate-supplying hole 16e is disposed between the driving coil portions 17a and 17b.
The guide ring 23 is connected to an inner surface 21b of the plate 21. The inner surface 21b of the plate 21 faces the outer surface 16a of the driving scroll body 6. The guide ring 23 comprises a polymeric resin material that is self-spreadable. An example of the polymer resin material comprises a polyether ether ketone (PEEK) resin. Note that the guide ring 23 may comprise a polyphenylene sulfide (PPS) resin. The guide ring 23 comprises a cylindrical shape. The guide ring 23 comprises a ring portion 28 and a flange portion 29. The flange portion 29 is formed on an end side of the ring portion 28. The ring portion 28 is fitted in a cavity portion of the plate 21. The flange portion is attached to the plate 21 with a bolt. The ring portion 28 includes a guide hole 23b. The drive pin 22 is placed in the guide hole 23b. The guide hole 23b is defined by the inner peripheral surface 23a of the guide ring 23. A biimeter diameter of the guide hole 23b is larger than an outer diameter of the pin portion 24 of the drive pin 22. A central axis of the drive pin 22 is offset from a central axis of the guide ring 23. A magnitude of this shift is essentially the same as that of the second axis line A2 relative to the first axis line A1 (distance t, see Fig. 1). Therefore, the hard layer 27 of the drive pin 22 comes into contact with the inner peripheral surface 23a of the ring portion 28.
As shown in FIG. 1, the working medium supplying portion 102 supplies the steam V to the scroll expansion device 1 including the configuration described above by the cap 13. The steam V is introduced into the expansion chamber S2 through a through hole of the cap 13 and the working medium introducing hole 3a of the input drive shaft 3. The steam V introduced into the expansion chamber S2 expands in a space formed by the driving coil 17 and the driven coil 19. Thereafter, the steam V moves from the center of the expansion chamber S2 to an outer periphery of the expansion chamber S2. expansion chamber S2. The steam V ejected from the expansion chamber S2 to the inside of the housing 2 is ejected via outlet 1 Ie. Relative circumferential movement of the driven scroll body with respect to the driving scroll body 6 (bypass movement) takes place as a result of this expansion. Viewed from the housing 2, this circumferential movement is observed as the rotational movement of the driving scroll body 6 about the first axis A1 and the rotational movement of the driven scroll body 7 about the second axis A2. Therefore, the output drive shaft 4 connected to the driving scroll body 6 rotates about the first axis A1. This rotational movement of the output drive shaft 4 is transmitted to the dynamo 101. 10027] The scroll expansion device 1 controls the relative rotational movement of the driven scroll body 7 relative to the driving scroll body 6 via the drive pin 22 and the guide ring 23, and tolerates the relative rotational movement. The scroll expansion device 1 based on this principle is simple and has few components. That is why a reduction in manufacturing costs is achieved. Furthermore, the drive pin 22 and the guide ring 23 regulate the relative rotational movement of the driven scroll body 7 relative to the driving scroll body 6. Then, in a state where the outer peripheral surface 22s of the drive pin 22 is in close contact with the inner circumferential surface 23a of the guide ring, a sliding in a tangential direction of the inner circumferential surface 23a or the outer circumferential surface 22s takes place between the outer circumferential surface 22s of the drive pin 22 and the inner circumferential surface 23a of the guide ring 23. This sliding tolerates the circumferential movement of the driven scroll body 7 relative to the driving scroll body 6. Therefore, the scroll expansion device 1 does not require a bearing comprising a rolling element to define the relative movement between the driving scroll body 6 and the driven scroll body 7 . Therefore, the scroll expansion device 1 can suppress an increase in the mechanical energy loss. Further, the hard layer 27 comprising diamond-like carbon formed on the outer peripheral surface 22s of the drive pin 22 is formed. The guide ring 23 comprises the polyether ether ketone resin. An advantageous sliding state is achieved by contact between the hard layer 27 and the polyetherether ketone resin. Therefore, a stable circulation movement can be achieved with low abrasion over a long period. Furthermore, if the condensate is present in the space between the drive pin 22 and the guide ring 23, further reduction of mechanical energy loss can be achieved, since a coefficient of friction between the drive pin 22 and the guide ring 23 decreases. Therefore, the scroll expansion device 1 can maintain an advantageous rotation state.
The drive pin 22 includes the condensate-supplying hole 22a. The condensate formed by condensation of the steam V is supplied to the space between the drive pin 22 and the guide ring 23 via the condensate-supplying hole 22a. The steam V or the condensate is forcefully supplied by expansion pressure of the steam V in the expansion chamber S2 towards an opening on the side of a top of the drive pin 22 via the condensate-supplying hole 22a.
Therefore, the condensate is forcefully supplied to the space between the drive pin 22 and the guide ring 23. Since a melting state between the drive pin 22 and the guide ring 23 becomes advantageous, this condensate allows a reduction in the mechanical energy loss associated with relative rotational movement of the driven scroll body 7 relative to the driving scroll body 6 can be achieved. Furthermore, a stable supply of the condensate, the required power and the noise production can be reduced. In short, the scroll expansion device 1 uses, as a lubricant, the condensate formed by the condensation of evaporated gas through the expansion.
Next, the operation of the scroll expansion device 1 according to the present embodiment will be described in detail. Figures 4A, 4B, 4C, 4D, 4E, and 4F are schematic diagrams showing engagement mechanisms 9A, 9B, 9C, and 9D that revolve around the first axis line A1. The engaging mechanism 9A is carefully observed. As shown in FIG. 4A, a drive pin 22 of the engaging mechanism 9A is driven in a tangential direction of a virtual circle C1 around the first axis line A1. Force caused by rotation of the drive pin 22 will be referred to as pin input F1 in the following descriptions.
As shown in FIG. 4B, the engaging mechanism 9A rotates 30 ° counterclockwise. In this case, a turning angle α is 30 °. In this case, the direction of the pin input F1 also corresponds to the tangential direction of the virtual circle C1. Furthermore, the size of the pin input F1 is substantially the same as that of the pin input F1 in FIG. 4A. Regardless of the turning angle α of the engaging mechanism 9A, the direction of the pin input F1 remains in the tangential direction of the virtual circle C1. Furthermore, the size of the pin input F1 remains constant regardless of the turning angle α of the engaging mechanism 9A. Meanwhile, in a state in FIG. 4B, a direction of a vertical component of the pin input F1 corresponds to a direction toward the inner peripheral surface 23a of the guide ring 23 (referring to F2 in Fig. 4B). Therefore, the guide ring 23 presses the drive pin 22. The vertical component of the pin input F1 will be referred to as action force F2 on a guide ring in the following descriptions.
As shown in FIG. 4C, the engaging mechanism 9A further rotates counterclockwise through 60 ° from the state in FIG. 4B. The engaging mechanism 9A is in a position where the revolution is made through 90 ° from the starting position. In this case the turning angle α is 90 °. In a state in FIG. 4C, the tangential direction of the virtual circle C1 corresponds to the vertical direction. Therefore, the magnitude of the action force F2 on a guide ring is substantially equal to that of the pin input F1.
As shown in FIG. 4D, the engaging mechanism 9A further rotates counterclockwise through 60 ° from the state in FIG. 4C. The engaging mechanism 9A is in a position where the revolution is made over 150 ° from the starting position. In this case the turning angle α is 150 °. In a state in FIG. 4 D, is a direction of the vertical component of the pin input F1 in the direction toward an inner peripheral surface 23a of the guide ring 23. Therefore, the vertical component of the pin input F1 acts on the guide ring 23 like the action force F2 on a guide ring. In this case, the action force on a guide ring is smaller than that in FIG. 4C.
As shown in FIG. 4E, the engaging mechanism 9A further rotates counterclockwise by 30 ° from the state in FIG. 4D. The engaging mechanism 9A is in a position where the revolution is made through 180 ° from the starting position. In a state in FIG. 4E corresponds to the direction of the pin input F1 with the horizontal direction. Therefore, the size of the vertical component of the pin input F1 is zero. In other words, the magnitude of the action force F2 on a guide ring is zero.
As shown in FIG. 4F. the engaging mechanism 9A further rotates counterclockwise by 30 ° from the state in FIG. 4E. The engaging mechanism 9A is in a position where the revolution is carried out through 210 ° from the starting position. In this case the turning angle α is 210 °. In a state in FIG. 4F. is the direction of the vertical component of the pin input F1 in a vertical upward direction. Therefore, the guide ring 23 does not press against the drive pin 22. The direction of the vertical component of the pin input F1. shown in FIG. 4F is retained until the engagement mechanism 9 returns to the position in FIG. 4A. 10035] The pin input F1 described above will be discussed with reference to Figures 5A, 5B, 5C, and 5D. FIG. 5A is a graphical representation of a relationship between the turning angle α and the action force F2 on a guide ring. The vertical axis indicates the magnitude of the action force. The horizontal axis represents the turning angle α. A graph G5a is the action force F2 on a guide ring, of the engaging mechanism 9A. When the graph G5a is viewed closely, in a case when the turning angle α is 0 °, the magnitude of the action force F2 is zero. The magnitude of the action force F2 increases when the turning angle α is close to 90 °. When the turning angle α is 90 °, the magnitude of the action force F2 becomes the maximum value. Thereafter, if the turning angle α is between 90 ° and 180 °, the magnitude of the action force F2 decreases. When the turning angle α is 180 °, the magnitude of the action force F2 becomes zero. Thereafter, when the turning angle α is between 180 ° and 360 °, the magnitude of the action force F2 becomes negative.
A graph G5b shows the action force F2 on a guide ring, of an engaging mechanism 9B (referring to Fig. 4A). The engaging mechanism 9B is positioned at a position separated by 90 ° from the engaging mechanism 9A. Therefore, the graph G5b of the engaging mechanism 9B deviates in terms of phase 90 ° from the graph G5a of the engaging mechanism 9A. A graph G5c shows the action force F2 on a guide ring of an engaging mechanism 9C (referring to Fig. 4A). The engaging mechanism 9C is positioned at a position that is 180 ° apart from the engaging mechanism 9A. Therefore, the graph G5c of the engaging mechanism 9C deviates in terms of phase 180 ° from the graph G5a of the engaging mechanism 9A. A graph G5d shows an action force F2 on a guide ring, of an engaging mechanism 9D (referring to Fig. 4A). The engaging mechanism 9D is placed at a position that is separated by 270 ° from the engaging mechanism 9A. Therefore, the graph G5d of the engaging mechanism 9D deviates in terms of phase 270 ° from the graph G5a of the engaging mechanism 9A. Note that graph G5e shows total action power. The total action force is the resulting force taking the sum of the action force F2 of the engaging mechanism 9A, the action force F2 of the engaging mechanism 9B, the action force F2 of the engaging mechanism 9C and the action force F2 of the engaging mechanism 9D.
As shown in FIG. 5A, in the scroll expansion device 1 according to the present embodiment, the action force F2 occurs on a guide ring for each of at least two of the engaging mechanisms 9A, 9B, 9C and 9D, in a direction in which the drive pin 22 presses the guide ring 23 (vertical downward direction) except the turning angles α of the engaging mechanisms 9A of 0 °, 90 °, 180 °, and 270 °. In other words, during the relative circular movement of the driven scroll body 7 relative to the driving scroll body 6, the driving scroll body 6 is supported by at least two sets of the drive pin 22 and the guide ring 23.
The drive pin 22 of the scroll expansion device 1 revolves around the first axis Al. The end of the drive pin 22 is placed in the guide ring 23. The drive pin 22 thus revolves around the first axis Al, pressing the inner peripheral surface 23a of the guide ring 23. A direction of the force caused by the rotation constantly corresponds to a tangential direction of a circle around the first axis Al. When the plate 21 with the guide ring 23 placed therein rotates, a direction of force acting on the guide ring 23 from the drive pin 22 varies. The force that acts on the guide ring 23 sometimes corresponds to the vertical component of the pin input F1. Meanwhile, the direction of the pin input F1 varies depending on a pivotal position of the drive pin 22. For example, when the vertical component of the pin input F1 is in the vertical downward direction, the force intervenes on the guide ring 23. In contrast, when the vertical component of the pin input is in the vertically upward direction, no force intervenes on the guide ring 23. Here four sets of the drive pin 22 and the guide ring 23 are placed over an interval of 90 °. As a result, there are at least two sets of the guide ring 23 and the drive pin 22 that generate the action force F2 on a guide ring in the vertically downward direction. During the relative circular movement of the driven scroll body 7 with respect to the driving scroll body 6, the driving scroll body 6 is supported by at least two sets of the drive pin 22 and the guide ring 23. According to this configuration, since carrying capacity of the driving scroll body is gently received, a variation of the carrying capacity during the circular movement is counteracted. As a result, the scroll expansion device 1 according to the one embodiment of the present invention can maintain a favorable rotational state.
The scroll expansion device 1 tolerates a revolutionary movement of the drive pin 22 with the sliding of the drive pin 22 relative to the guide ring 23. The engaging mechanism 9 with the drive pin 22 and the guide ring 23 has a dimension error of the respective parts and a assembly error that may occur during assembly. These errors cause a small play between a plurality of engaging mechanisms 9. The drive pin 22 has a hard film 27. The hard film 27 comes into contact with the inner peripheral surface 23a of the guide ring 23 made of resin. According to this configuration, the friction between the drive pin 22 and guide ring 23 abrasion of the inner peripheral surface of the guide ring 23. Thus, since the small play between the plurality of interlocking mechanisms 9 is eliminated, the relative circular movement of the driven scroll body 7 relative to the driving scroll body 6 are more fluid.
FIG. 5B is a graphical representation of a relationship between the turning angle α and an input moment. The input moment is based on a distance from the first axis line A1 to a position where action force F2 is executed on a guide ring (action distance), and magnitude of the action force F2 on a guide ring. In other words, the action distance is a distance between the center of the driving end plate 16 with the drive pin 22 placed therein and the position where the action force F2 is performed on a guide ring. The drive pin 22 is placed on the virtual circle C1. In the meantime, the guide ring 23 is placed on a virtual circle C2 around the second axis A2. With this arrangement, the input moment varies periodically. A graph G5f shows an input moment of the engaging mechanism 9A. A graph G5g shows an input moment of the engaging mechanism 9B. A graph G5h shows an input moment of the engaging mechanism 9C. A graph G5i represents an input moment of the engaging mechanism 9D. A graph G5j shows a total input moment. The total input moment is a total moment that takes the sum over the input moment of the interlock mechanism 9A, the input moment of the interlock mechanism 9B, the input moment of the interlock mechanism 9C, and the input moment of the interlock mechanism 9D. The number of drive pins 22 and the number of guide rings 23 are even numbers. The number of interlocking mechanisms 9 in an area where the action force F2 is on a guide ring in the vertical downward direction (turning angle α of 0 ° or more and 180 ° or less) is therefore constant (two). With this arrangement, as shown in graph G5j, the periodic variation of the input moment, which is caused by a periodic variation of the action distance, is suppressed. That is why the total input moment remains constant.
More specifically, the action distance varies periodically while the engaging mechanisms 9A, 9B, 9C, and 9D rotate through 360 °. A positional relationship and a force relationship between the driving scroll body 6 and the driven scroll body 7 appear to vary depending on a chosen standard. For example, Figures 4A, 4B, 4C, 4D, 4E, and 4F are diagrams with, as a standard for rotational movement, the center of the driving end plate 16 including the drive pin 22 disposed therein (namely, the first axis Al). Similarly, for example, Figures 5A, 5B, 5C, and 5D are also diagrams with the center of the driving end plate 16 as the standard for rotational movement. On the other hand, when the center of the plate 21 with the guide ring 23 placed therein (namely, the second axis A2) is defined as the standard for rotational movement, a different result than that of FIG. 4A observed.
As shown in, for example, FIG. 4B, the pin input F1 is split into the action force F2 on a guide ring as the vertical component and a component F3 as the horizontal component. FIG. 5C is a graphical representation of a relationship between the turning angle α and a component F3. A graph G5k shows the component F3 of the engaging mechanism 9A. A graph G5m shows the component F3 of the engaging mechanism 9B. A graph G5n shows the component F3 of the engaging mechanism 9C. A graph G 50 shows the component F 3 of the engaging mechanism 9 D. Phase differences of the graphs G5k, G5m, G5n and G5o correspond to placement angles of the engaging mechanisms 9A, 9B, 9C, and 9D, respectively. A G5p graph shows a total component. The total component takes the sum of the component F3 of the engagement mechanism 9A, the component F3 of the engagement mechanism 9B, the component F3 of the engagement mechanism 9C, and the component F3 of the engagement mechanism 9D. For example, as shown by graph G5k, if the turn angle a is zero (a = 0 °), the component F3 corresponds to the pin input F1 in terms of magnitude. When the turning angle α is 90 ° (a = 90 °), the size of the component F3 is zero. When the turning angle α is 180 ° (α = 180 °), the component F3 corresponds to the pin input F1 in terms of size. In this case, a direction of the component F3 is opposite to that of the case where the turning angle α is zero (α = 0 °).
Here, a condition is assumed where there is no gap between the driving winding 17 and the driven winding 19 (namely zero leakage). Under this assumption, when the driven scroll body 7 rotates relative to the driving scroll body 6, the component F3 is the horizontal component. Thus, since there is no vertical component, the F3 component can be omitted. However, the state where there is no gap between the driving winding 17 and the driven winding 19 is an ideal state. There is a gap between the driving winding 17 and the driving winding 19 in a state similar to an actual environment. In this case, the direction of the component F3 is not horizontal. Since the component F3 has a vertical component, the component F3 cannot be omitted.
FIG. 5D is a graphical representation of a relationship between the angle of rotation α and a component moment. The component moment is based on a distance from the first axis line A1 to a position where the component F3 is applied, and the magnitude of the component F3. A graph G5q represents a component moment of the engaging mechanism 9A. A graph G5r shows a component moment of the engaging mechanism 9B. A graph G5s shows a component moment of the engaging mechanism 9C. A graph G5t represents a component moment of the engaging mechanism 9D. Phase differences of the graphs G5q, G5r, G5s, and G5t correspond to the placement angles of the engaging mechanisms 9A, 9B, 9C, and 9D, respectively. A graph G5u shows a total component moment. The total component moment is a total moment that takes the sum of the component moment of the engaging mechanism 9A, the component moment of the engaging mechanism 9B, the component moment of the engaging mechanism 9C, and the component moment of the engaging mechanism 9D. As shown by the graph G5u, the total component moment remains constant regardless of the turn angle α, just like the input moment (referring to graph G5j in Fig. 5B). Thus, even in the state where the component F3 cannot be omitted, the scroll expansion device 1 with four interlocking mechanisms 9A, 9B, 9C, and 9D (even number) prevents the change of the total component moment. The scroll expansion device can therefore maintain a favorable rotational position.
Here, the operation of a scroll expansion device according to a comparative example will be shown, and an effect of the scroll expansion device 1 according to the present embodiment will be further described. The scroll expansion device according to the comparative example is different from the scroll expansion device 1 according to the present embodiment since three interlocking mechanisms are provided. The interlocking mechanisms of the scroll expansion device of the comparative example are spaced apart at 120 ° intervals along a circumference direction of a circle about a first axis A1. A configuration of the single engagement mechanism and other configurations in the scroll expansion device according to the comparative example are substantially the same as those in the scroll expansion device 1 according to the present embodiment. Differences in operation between the scroll expansion device with four interlocking mechanisms 9 and the scroll expansion device with three interlocking mechanisms will be precisely noted and described below.
FIG. 8A is a graphical representation of a relationship between a turn angle α and action force F2 on a guide ring in the scroll expansion device according to the comparative example. A graph G8a shows action force F2 on a guide ring of a first engagement mechanism. A graph G8b shows action force F2 on a guide ring of a second engagement mechanism. A graph G8c shows action force F2 on a guide ring of a third engagement mechanism. Furthermore, a graph G8d shows total action force. An angle range L where the turning angle α is 60 ° or more. and 120 ° or less is accurately observed. In the corner region L, the action force F2 on a guide ring in accordance with the graph G8a only occurs on the first engagement mechanism in the vertically downward direction. 10047] With the scroll expansion device with three interlocking mechanisms 9, the driving scroll body 6 is supported for a period by a set of the drive pin 22 and the guide ring 23 (angle range L). In contrast, in the scroll-expansion device 1 with four interlocking mechanisms 9, at least two sets of the drive pin 22 and the guide ring 23 generate carrying capacity. Thus, since the carrying capacity of the driving scroll body 6 is readily received, the scroll expansion device 1 can maintain a favorable rotational state. Furthermore, when the total action force according to the comparative example (graph G8d in Fig. 8A) and the total action force according to the current embodiment (graph G5e in Fig. 5A) are compared, the total action force according to the current embodiment is completely greater than that according to the comparative example. The configuration according to the present embodiment is therefore smaller than that according to the comparative example in terms of a load that one interlocking mechanism 9 receives. The scroll expansion device 1 according to the present embodiment can improve the flexibility of design for the engaging mechanism 9. 10048] FIG. 8B is a graphical representation of a relationship between the turn angle α and an input moment of the scroll expansion device according to the comparative example. A graph G8e shows an input moment of the first engagement mechanism. A graph G8f shows an input moment of the second engagement mechanism. A graph G8g shows an input moment of the third engagement mechanism. A graph G8h shows a total input moment.
The total input moment (graph G8h) is accurately observed. The total input moment according to the comparative example varies depending on the turning angle α. While the total input moment according to the present embodiment (graph G5j in Fig. 5B) remains constant regardless of the turning angle a. Since the change of the total input moment caused by the turning angle α is prevented, the scroll expansion device 1 according to the present embodiment maintain a favorable rotational state.
FIG. 8C is a graphical representation of a relationship between the turn angle α and a component F3 of the scroll expansion device according to the comparative example. A graph G8i represents a component F3 of the first engagement mechanism. A graph G8j shows a component F3 of the second engagement mechanism. A graph G8k represents a component F3 of the third engagement mechanism. A G8m graph shows a total component. FIG. 8D is a graphical representation of a relationship between the turning angle α and a component moment of the scroll expansion device according to the comparative example. A graph G8n represents a component moment of the first engagement mechanism. A graph G8o shows a component moment of the second engagement mechanism. A graph G8p represents a component moment of the third engagement mechanism. A G8q graph shows a total component moment. The total component moment (graph G8q in Fig. 8D) is accurately observed. The total component moment according to the comparative example varies depending on the turning angle a. It can be deduced that since the scroll-expanding apparatus according to the comparative example has three interlocking mechanisms, the number of drive pins 22 pressing the guide ring 23 changes to, for example, one and then two during one revolution. In contrast, the total component moment according to the current embodiment (graph G5u in Fig. 5D) remains constant regardless of the turning angle a. Thus, since the change of the total component moment caused by the turning angle a is prevented, the scroll expansion device 1 according to the present embodiment maintain a favorable rotational state.
The embodiment of the present invention has been described above. However, the present invention is not limited to the embodiment described above. The present invention can include an adaptation without changing the idea described in the claims.
(Initial adjustment)
The scroll expansion device may, for example, have five engagement mechanisms 9, each having the drive pin 22 and the guide ring 23, in this case the engagement mechanisms 9 are spaced apart at intervals of 72 ° around the first axis line A1. FIG. 6A is a graphical representation of a relationship between a turn angle α and action force F2 on a guide ring in the scroll expansion device with the five engagement mechanisms 9 (hereinafter also referred to as scroll expansion device according to a first adaptation). Graphs Góa, Gób, Góc, Gód, and G6e each correspond to each of the five interlocking mechanisms 9. A graph Góf shows total action power. When the action force F2 on a guide ring of each of the engaging mechanisms 9 (graphs G6a, Gób, Góc, Gód, and G6e) is accurately observed, it can be determined that at least two engaging mechanisms 9 generate carrying power at the turning angle α between 0 ° and 360 °. For example, when the turning angle α is 90 °, three interlocking mechanisms 9 including the interlocking mechanism 9 corresponding to the graph Góa, the interlocking mechanism 9 corresponding to the graph Gób, and the interlocking mechanism 9 corresponding to the graph G6e generate separate carrying capacity. At any turning angle α, therefore, two or three interlocking mechanisms 9 generate carrying capacity in a separate manner. In other words, there is no case where only one interlock mechanism contributes to the support. The scroll expansion device according to the first adjustment can therefore maintain a favorable rotational position. Furthermore, if observed accurately, the total action force (graph Gf in Fig. 6A) becomes entirely greater than the total action force according to the embodiment described above (graph G5e in Fig. 5A). A load on one engaging mechanism 9 can thus be further reduced.
FIG. 6B is a graphical representation of a relationship between the turning angle α and an input moment of the scroll expansion device according to the first adjustment. FIG. 6C is a graphical representation of a relationship between the turn angle α and a component F3 of the scroll expansion device according to the first adjustment. FIG. 6D is a graphical representation of a relationship between the turn angle α and a component moment of the scroll expansion device according to the first adjustment. In each of the graphs, graphs Góh, G6i, G6j, G6k, and G6m, graphs G6o, G6p, Góq, Gór, and Gós, and graphs Góu, G6v, G6w, Góx, and G6y each correspond to the five interlocking mechanisms 9 A graph G6n in FIG. 6B shows a total input moment. A graph G6t in FIG. 6C represents a total component. A graph G6z in FIG. 6D represents a total component moment. When the total input moment (graph G6n in Fig. 6B) and the total component moment (graph Góz in Fig. 6D) are carefully studied, the total input moment and the total component moment vary periodically depending on the turning angle α.
(Second adaptation)
The scroll expansion device may, for example, have six interlocking mechanisms 9, each having the drive pin 22 and the guide ring 23. In this case the engagement mechanisms 9 are spaced apart at intervals of 60 ° around the first axis Al. FIG. 7A is a graphical representation of a relationship between a turning angle α and an input moment of the scroll expansion device with the six interlocking mechanisms 9 (hereinafter also referred to as scroll expansion device according to a second adjustment). FIG. 7B is a graphical representation of a relationship between the turning angle α and a component moment of the scroll expansion device according to the second adjustment. Graphs G7a, G7b, G7c, G7d, G7e, and G7f each correspond to the six interlock mechanisms 9. Graphs G7h, G7i, G7j, G7k, G7m, and G7n each correspond to the six interlock mechanisms 9. A graph G7g in Figs. 7A shows a total input moment. A graph G 70 in FIG. 7B represents a total component moment. When the total input moment (graph G7g in Fig. 7A) and the total component moment (graph G7o in Fig. 7B) are carefully studied, the magnitude of the total input moment and the magnitude of the total component moment remain unchanged, regardless of the turning angle α. As with the scroll expansion device according to the first adaptation, with the scroll expansion device according to the second adaptation, at least two interlocking mechanisms 9 generate carrying capacity at a turning angle α between 0 ° and 360 °. Therefore, with any turning angle α, two or three interlocking mechanisms 9 contribute to the support. In other words, there is no case where only one interlock mechanism contributes to the support at a given time. The scroll expansion device according to the second adjustment can therefore maintain a more favorable rotational position.
(Third adaptation)
In the embodiment described above, the scroll expansion device was described by way of example as a specific example of a scroll fluid machine. The scroll fluid machine according to an embodiment of the present invention is not limited to the scroll expansion device. The scroll fluid machine may, for example, have a scroll compressor or a scroll vacuum pump.
FIGURES 5A
FIG. 5B
FIG. 5C
FIG. 5D
FIG. 6A
FIG. 6B
FIG. 6C
FIG. 6D
FIG. 7A
FIG. 7B
FIG. 8A
FIG. 8B
FIG. 8C
FIG. 8D

权利要求:
Claims (3)
[1]
CONCLUSIONS
A scroll fluid machine comprising a driving scroll body comprising a pair of driving end plates and a driving winding formed on each of the pair of driving end plates, and having a first axis of line as a pivot axis; a driven scroll body comprising a driven end plate and a driven wrap formed on each of both surfaces of the driven end plate, which is placed between the pair of driving end plates and which, as a pivot axis, has a second axis that is offset from of the first axis; a support plate placed on each of both sides of the driven scroll body, which comprises a pair of plates coupled to the driven scroll body, and having the second axis as a pivot axis; a cylindrical drive pin attached to the driving scroll body and projecting from the driving end plate to the support plate; and a cylindrical guide ring attached to the support plate, and comprising an inner diameter greater than an outer diameter of the drive pin, wherein n drive pins (n> 4) or more are placed on a circumference of a circle around the first axis at equal intervals, and m guide rings (m = n> 4) or more are placed on a circumference of a circle around the second axis over the equal intervals to correspond to the drive pins.
[2]
The scroll fluid machine according to claim 1, wherein the number of drive pins (n) and the number of guide rings (m) is an even number.
[3]
The scroll fluid machine according to claims 1 or 2, wherein the number of drive pins (n) and the number of guide rings (m) is six (n = m = 6).

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引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

US20130309116A1|2012-04-25|2013-11-21|Anest Iwata Corporation|Double rotation type scroll expander and power generation apparatus including same|

US20130315767A1|2012-04-25|2013-11-28|Anest Iwata Corporation|Scroll expander|

DE58906623D1|1988-08-03|1994-02-17|Aginfor Ag|Displacement machine based on the spiral principle.|

EP0478795B1|1990-04-19|1995-11-02|Sanyo Electric Co., Ltd|Scroll compressor|

JP3066171B2|1992-03-05|2000-07-17|三洋電機株式会社|Scroll compressor|

JP2002357188A|2001-05-30|2002-12-13|Toyota Industries Corp|Scroll compressor and gas compressing method for scroll compressor|

US6758659B2|2002-04-11|2004-07-06|Shimao Ni|Scroll type fluid displacement apparatus with fully compliant floating scrolls|

US7467933B2|2006-01-26|2008-12-23|Scroll Laboratories, Inc.|Scroll-type fluid displacement apparatus with fully compliant floating scrolls|

JP5769332B2|2010-06-02|2015-08-26|アネスト岩田株式会社|Scroll expander|

JP2013241869A|2012-05-18|2013-12-05|Toyota Industries Corp|Driven crank type scroll expander|

JP5613912B2|2013-04-10|2014-10-29|株式会社リッチストーン|Scroll fluid machinery|JP6345081B2|2014-10-31|2018-06-20|アネスト岩田株式会社|Scroll expander|

CN106014981B|2016-07-28|2018-01-05|陆亚明|Scroll type air compressor assembly|

CN109563832B|2016-08-01|2020-12-04|三菱重工业株式会社|Double-rotation scroll compressor|

JP6727978B2|2016-08-01|2020-07-22|三菱重工業株式会社|Double rotary scroll compressor|

JP6710628B2|2016-12-21|2020-06-17|三菱重工業株式会社|Double rotary scroll compressor|

DE102017111778B4|2017-05-30|2019-09-19|Hanon Systems|Apparatus for compressing a gaseous fluid|

CN107620704A|2017-08-23|2018-01-23|南昌大学|A kind of mechanical motor integration bilateral oil-free turbo-compressor|

法律状态:
2021-08-11| MM| Lapsed because of non-payment of the annual fee|Effective date: 20201130 |

优先权:

申请号 | 申请日 | 专利标题

JP2014-227360|2014-11-07|

JP2014227360A|JP6441645B2|2014-11-07|2014-11-07|Scroll fluid machinery|

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