JP2006329140A - Expander - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an expander as a motor for generating rotation power by operating by compressive fluid having high pressure to prevent vane jumping phenomenon securely, improve performance, suppress occurrence of noise, and achieve high reliability. <P>SOLUTION: In this expander, a roller and a vane for partitioning a space formed by a cylinder, the roller, and a blocking member into a plurality of operation chambers are mutually connected. Consequently, the vane jumping phenomenon is securely prevented to improve performance by preventing leakage of refrigerant caused by the vane jumping phenomenon, occurrence of noise is suppressed, and reliability is improved. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an expander as a prime mover that generates rotational power by operating with a high-pressure compressive fluid.

  Conventionally, as a general expander used in a heat pump cycle, there is a rotary type expander as disclosed in Patent Document 1.

  The configuration of this expander will be described. FIG. 14 is a longitudinal sectional view of a conventional expander, and FIG. 15 is a transverse sectional view of the conventional expander. FIG. 15 corresponds to a cross-sectional view taken along the line ZZ in FIG. For the sake of explanation, in FIG. 15, the axial path 3b and radial path 3c of the shaft 3 and the suction path 4a of the roller 4 are indicated by broken lines.

  The expander includes a sealed container 1, a suction space 20, a cylinder 2, a shaft 3 having an eccentric portion 3a, a roller 4 that rotates eccentrically inside the cylinder 2, a groove 4h provided in the roller 4, A vane 5 that reciprocates inside the vane groove 2a, a vane spring 6 that is installed in a vane back space 6a that is configured by the vane 5 and the vane groove 2a and contacts the vane back surface 5c, and a first closing member that supports the shaft 3. 7 and the lower bearing member 8, a suction pipe 9 for sucking the working fluid, and a discharge pipe 10 for discharging the working fluid.

  A working chamber 12 partitioned by a vane 5 is formed between the cylinder 2, the roller 4, the first closing member 7 and the lower bearing member 8. The roller 4 includes a suction path 4a that guides the working fluid to the working chamber 12 side. The shaft 3 includes an axial path 3b and a radial path 3c. Further, the cylinder 2 is provided with a discharge hole 2 b for discharging the working fluid from the working chamber 12 to the discharge pipe 10.

  Next, the operation of the expander will be described. 16 (a) to 16 (d) are operation diagrams of the expander, and correspond to those obtained by omitting the cross-sectional view of the sealed container 1 along the line ZZ in FIG.

  As shown in FIG. 14, the high-pressure working fluid flows from the suction pipe 9 through the suction space 20, passes through the axial path 3 b of the shaft 3, and flows into the radial path 3 c of the shaft 3. As shown in FIG. 16, the shape of the radial path 3 c of the shaft 3 is open only in a certain angular range on the outer peripheral surface of the shaft 3, and between the suction path 4 a of the roller 4 with the rotation of the shaft 3. Inflow timing control means for repeating communication and non-communication is formed.

  When the radial path 3c and the suction path 4a communicate with each other, the working fluid is sucked into the working chamber 12 from the radial path 3c through the suction path 4a.

  Hereinafter, the operation of the expander will be described focusing on the working chamber 12. FIG. 16A shows a state immediately before the start of the intake stroke. When the shaft 3 rotates counterclockwise from this state, the radial path 3c of the shaft 3 and the suction path 4a of the roller 4 communicate with each other, so that the inflow timing control means is opened and high-pressure working fluid flows into the working chamber 12. The inhalation stroke is started. At this time, since the tip of the vane 5 is fitted into the groove 4 h of the roller 4, the position of the suction path 4 a is not changed by the rotation of the roller 4.

  16B after the shaft 3 rotates counterclockwise, the communication between the radial path 3c of the shaft 3 and the suction path 4a of the roller 4 is cut off, and the inflow timing control means is closed. Immediately after that, that is, the state of the end of the intake stroke is shown.

  The volume of the working chamber 12 at this time becomes the suction volume Vs of the expander. Thereafter, the high-pressure working fluid sucked into the working chamber 12 enters an expansion stroke in which the shaft 3 is rotated in the direction in which the volume of the working chamber 12 is increased, and the state of FIG. It will be in the state of d).

  This state is a state immediately before the working chamber 12 communicates with the discharge hole 2b, and the volume of the working chamber 12 at this time becomes the discharge volume Vd of the expander. Thereafter, when the shaft 3 rotates slightly, the working chamber 12 communicates with the discharge hole 2b, and a discharge stroke is started.

  As the volume of the working chamber 12 decreases, the working fluid is discharged from the discharge hole 2b through the discharge pipe 10 to the outside of the expander.

  As is clear from the above description, in the expander of this configuration, the transition from the suction stroke to the expansion stroke depends on the opening / closing of the inflow timing control means, and therefore the inflow timing control means is an essential component. I understand that. Note that examples of the inflow timing control means other than the above configuration are shown in Patent Documents 2 and 3. The rotary expander repeats the states shown in FIGS. 16A to 16D, and the rotational power is taken out by rotating the shaft 3 in the direction in which the successively generated working chamber 12 increases in volume during the expansion stroke.

  Next, a case where a rotary compressor using a plurality of cylinders as disclosed in Patent Document 4 is used as an expander by reversing the flow direction of the working fluid will be described. 17 is a longitudinal sectional view of the expander, FIG. 18A is a transverse sectional view taken along the line Z1-Z1 in FIG. 17, and FIG. 18B is a transverse sectional view taken along the line Z2-Z2 in FIG.

  The expander includes an airtight container 31, a suction space 50, an upper cylinder 32 and a lower cylinder 33, a shaft 34 having an upper eccentric portion 34 a and a lower eccentric portion 34 b, and eccentricity inside each of the upper cylinder 32 and the lower cylinder 33. The upper roller 35 and the lower roller 36 that rotate, the upper vane 37 and the lower vane 38 that reciprocate inside the upper vane groove 32a and the lower vane groove 33a, the upper vane 37, the lower vane 38, and the upper vane groove 32a An upper vane spring 39 and a lower vane spring 40 installed in the upper vane back space, the lower vane back space, and the first closing member 41 and the lower bearing member 42 that support the shaft 34; An intermediate closing member 51 that partitions the upper cylinder 32 and the lower cylinder 33, a suction pipe 43 that sucks the working fluid, and a discharge pipe 44 that discharges the working fluid. That.

  An upper space and a lower space constituted by the upper cylinder 32 and the lower cylinder 33, the upper roller 35 and the lower roller 36, the first closing member 41, the lower bearing member 42, and the intermediate closing member 51 are defined as the upper vane 37. An upper working chamber 45 and a lower working chamber 46 are formed by partitioning with the lower vane 38. The first closing member 41 includes a suction hole 41a serving as an opening on the upper working chamber 45 side. The intermediate closing member 51 is provided with a communication hole 47 that allows the upper working chamber 45 and the lower working chamber 46 to communicate with each other. Further, the lower cylinder 33 is provided with a discharge hole 33 b for discharging the working fluid from the lower working chamber 46 to the discharge pipe 44.

  Next, the operation of the expander will be described. 19A to 19D are operation diagrams of the expander, and correspond to cross-sectional views taken along lines Z1-Z1 and Z2-Z2 in FIG. As shown in FIG. 17, the high-pressure working fluid is sucked into the upper working chamber 45 from the suction pipe 43 through the suction space 50 and the suction hole 41a.

  Hereinafter, the operation of the expander will be described focusing on the working fluid in the upper working chamber 45 and the lower working chamber 46.

  The working fluid is guided to the upper working chamber 45 from the suction hole 41a. The inhalation start state is shown in FIG. Then, the working fluid is sucked in as shown by the hatched portion as it proceeds to FIGS. 19B and 19C, and the suction process is completed in the state of FIG. 19D.

  Next, the working fluid that has been sucked into the upper working chamber 45 moves to the lower working chamber 46 through the communication hole 47. This is indicated by the horizontal line in FIG. Then, the working fluid moves to the lower working chamber 46 as shown by the horizontal line portion as it proceeds to FIGS. 19B and 19C, and the movement is completed in the state of FIG. The expansion occurs while moving from the upper working chamber 45 to the lower working chamber 46, and the volume ratio between the upper working chamber 45 and the lower working chamber 46 becomes the expansion ratio.

  Next, the working fluid that has been moved to the lower working chamber 46 is discharged to the discharge pipe 44 through the discharge hole 33b. The discharge start state is indicated by the vertical line portion in FIG. Then, the working fluid is discharged as shown by the vertical line as it proceeds to FIGS. 19B and 19C, and the discharge is completed in the state of FIG. 19D.

  That is, in this configuration, the upper working chamber 45 functions as a kind of inflow timing control means, and the expansion phenomenon occurs in the process of moving the working fluid from the upper working chamber 45 having a small volume to the lower working chamber 46 having a large volume. The rotating power is taken out by rotating the shaft 34 with the expanding force at this time. Further, it is not necessary to intermittently suck the working fluid while the shaft 34 rotates, and the suction can be continuously performed and the expansion process can be performed continuously, so that the pulsation is small and the noise caused thereby. Is also small.

  Below, the example which uses an expander for a heat pump cycle is demonstrated. FIG. 20 shows a conceptual diagram and a Mollier diagram of a heat pump cycle using carbon dioxide as a working fluid. 20A is a normal heat pump cycle, FIG. 20B is a heat pump cycle using an expander, and FIG. 20C is a Mollier diagram.

  The normal heat pump cycle shown in FIG. 20A includes a compressor 13, a gas cooler 14, an expansion valve 15, and an evaporator 16. The compressor 13 is driven by a driving element 17 such as a motor. The Mollier diagram in this case corresponds to ABCD in FIG.

  On the other hand, in the heat pump cycle using the expander shown in FIG. 20 (b), the expander 18 is used instead of the expansion valve 15, and the shaft of the expander 18 is directly connected to the shaft of the compressor 13 via the drive element 17. is doing. The Mollier diagram in this case is ABCD ′ in FIG. 20C considering that the expansion stroke of the working fluid in the expander 18 is approximately adiabatic expansion.

By adopting such a heat pump configuration, the load of the driving element 17 can be reduced by assisting the driving of the compressor 13 using the rotational power recovered in the expansion stroke of the working fluid by the expander 18. At the same time, the enthalpy difference of the evaporator 16 increases at a portion corresponding to DD ′ on the Mollier diagram, and the refrigerating capacity can be improved.
JP-A-8-338356 JP 2001-153077 A JP 2003-172244 A JP 2003-343467 A

  However, in the conventional expander, the tip of the vane is in contact with the roller or only in contact with the groove provided in the roller. Therefore, in the rotary expander that intermittently controls the suction timing, the tip of the vane 5 is separated from the roller 4 due to the pressure fluctuation caused by the intermittent flow of the refrigerant and the vibration caused thereby. There was a vane jumping phenomenon. Further, in the rotary expander having a plurality of cylinders as shown in the conventional example, although the pressure fluctuation as described above is small, the pressure applied to the upper vane tip 37c of the upper vane 37 and the upper vane rear surface 37b particularly during the suction process. Therefore, the force that presses the upper vane 37 against the upper roller 35 is only the spring force of the upper vane spring 39, and the vane jump phenomenon frequently occurs. For this reason, there existed the subject that performance fell by the leakage of the working fluid of a vane front-end | tip part, and the subject that the noise and reliability which are caused by the vane jump phenomenon fall.

  Furthermore, when the working fluid used in the heat pump cycle is carbon dioxide, it has a higher density than the conventional working fluid, so the suction volume is smaller than when the conventional working fluid is used, and the working fluid There was a problem that the effect of leakage on performance degradation became significant. Therefore, for example, in the configuration in which the vane and the roller are integrally formed as shown in FIG. 7B of Patent Document 1, a member as indicated by reference numeral “35” in FIG. There was a problem that the performance deteriorated due to the expansion of the working fluid leakage path due to the increase in the flow rate. In addition, there is a problem that the suction path 4a of the roller 4 becomes a dead volume in the expansion process, and the influence on the performance degradation becomes remarkable.

  SUMMARY OF THE INVENTION The present invention solves the above-mentioned conventional problems, and aims to provide a highly reliable expander that reliably prevents the vane jump phenomenon with a simple configuration and improves performance, suppresses noise, and is highly reliable. And

  In the present invention, an intermediate closing member, an upper cylinder and a lower cylinder provided above and below the intermediate closing member, an upper roller and a lower roller that rotate eccentrically inside the upper cylinder and the lower cylinder, and the upper roller And a shaft fitted to the lower roller, an upper closing member and a lower closing member for closing each end face of the upper cylinder and the lower cylinder together with the intermediate closing member, the upper cylinder, the lower cylinder, and the upper roller An upper vane and a lower vane that divide an upper space and a lower space formed by the lower roller, the intermediate closing member, the upper closing member, and the lower closing member into a plurality of working chambers, and the intermediate closing member. A communication hole for communicating the upper space and the lower space, and a working fluid in either the upper space or the lower space. A suction hole for inflow, a discharge hole for discharging the working fluid from the other space to a discharge space, and a connecting means for slidably connecting at least one pair of the upper roller and the lower roller and the upper vane and the lower vane. It has the composition provided.

  As a result, dead volume can be kept extremely small without the need for a complicated inhalation timing mechanism, continuous inhalation and expansion are possible, and vane jumping is reliably prevented, thus suppressing pulsation during inhalation. On the other hand, the performance is improved by preventing the leakage of the refrigerant caused by the vane jump phenomenon, and the noise is suppressed and the reliability is improved.

  Further, as the connecting means, an upper concave portion is provided in one of the upper roller and the upper vane, and a lower concave portion is provided in either the lower roller or the lower vane, and the upper concave portion and the lower concave portion are provided. You may make it the structure which provided the upper convex part and the downward convex part which are fitted in each other.

  This ensures that the vane jump phenomenon is prevented by using only the vane and the roller, and the performance is improved by preventing the leakage of the refrigerant due to the vane jump phenomenon, and the noise is suppressed and the reliability is improved. There is an effect of letting.

  Further, as the connecting means, an upper roller cylindrical recess is provided in the outer diameter portion of the upper roller, and a lower roller cylindrical recess is provided in the outer diameter portion of the lower roller, and is fitted into the upper roller cylindrical recess. The upper vane cylindrical convex portion and the lower vane cylindrical convex portion that fits into the lower roller cylindrical concave portion may be provided on a part of the upper vane and the lower vane, respectively.

  As a result, the vane jump phenomenon can be reliably prevented by using only the vane and the roller, and the surface between the vane tip and the roller can be sealed by a cylindrical uneven surface, and the refrigerant caused by the vane jump phenomenon can be prevented. While preventing leakage, the performance is improved by improving the sealing performance by the face seal, the noise is suppressed, and the reliability is improved.

  The central angle of the upper roller cylindrical recess and the lower roller cylindrical recess may be at least 180 ° or more.

  As a result, when the upper vane cylindrical convex portion and the lower vane cylindrical convex portion are fitted to each other, the axial direction of the shaft can be removed by sliding in the radial direction of the upper roller and the lower roller. On the other hand, there is an effect that the vane jump phenomenon is surely prevented without being separated by the fitting of the cylindrical connecting portion.

  In addition, as the connecting means, the upper roller and the upper vane may be connected, and at least one connecting member for connecting the lower roller and the lower vane may be provided.

  This ensures that the vane jump phenomenon is prevented by providing the connecting member without requiring complicated processing, and the performance is improved by preventing the leakage of the refrigerant due to the vane jump phenomenon. It has the effect of suppressing and improving the reliability.

  Moreover, you may make it the structure which provided the leaf | plate spring as said connection member.

  This ensures that the vane jump phenomenon is prevented by simply providing a leaf spring, improves the performance by preventing leakage of the refrigerant due to the vane jump phenomenon, reduces noise, and improves reliability. There is an effect.

  The connecting member may be provided with a cylindrical fixing pin.

  This ensures that the vane jump phenomenon is prevented by simply providing a cylindrical fixing pin, improves the performance by preventing refrigerant leakage due to the vane jump phenomenon, reduces noise, and is reliable. There is an effect of improving.

  Further, an upper concave portion is provided on one of the upper roller and the upper vane, and a lower concave portion is provided on either the lower roller or the lower vane, and an upper convex portion and a lower convex portion are provided on the other. It is also possible to have a configuration in which at least one connecting sliding member that fits into the upper concave portion and the upper convex portion and fits into the lower concave portion and the lower convex portion is provided.

  As a result, the connecting sliding member is provided without requiring complicated processing, so that the vane jump phenomenon can be surely prevented, the refrigerant leakage due to the vane jump phenomenon is prevented, and the performance is improved. It has the effect of suppressing noise and improving reliability.

  Moreover, you may make it the structure which provided at least 1 or more bush as said connection sliding member.

  This makes it possible to select bushings with good sliding characteristics with the roller and vane material, and to reliably prevent the vane jump phenomenon, and to improve performance by preventing refrigerant leakage due to the vane jump phenomenon. In addition, there is an effect of suppressing noise and improving reliability.

  Moreover, you may make it the structure which provided the oil supply means which supplies lubricating oil to the said connection means.

  Thereby, it acts to selectively supply the lubricating oil to the connecting means portion, and there is an effect that the lubricity and sealing performance in the connecting means portion are improved.

  Further, as the oil supply means, a groove for communicating the inner diameter portions of the upper roller and the lower roller and the connecting means may be provided in the upper roller and the lower roller.

  Accordingly, it is possible to selectively supply lubricating oil to the connecting means simply by providing a groove on the roller, and the lubricity and sealing performance at the connecting means are improved.

  Further, the oil supply means may have a structure in which holes for communicating the inner diameter portions of the upper roller and the lower roller and the connecting means are provided in the upper roller and the lower roller.

  Accordingly, it is possible to selectively supply the lubricating oil to the connecting means simply by providing a hole in the roller, and there is an effect that lubricity and sealing performance in the connecting means are improved.

  Further, as the oil supply means, at least one of the upper closing member, the lower closing member, and the intermediate closing member is provided with a groove or hole for communicating the inner diameter portion of the upper roller and the lower roller with the communicating means. A configuration may be used.

  Accordingly, it is possible to selectively supply lubricating oil to the connecting means simply by providing a groove or a hole in at least one of the upper closing member and the lower closing member. There is an effect that the property is improved.

  Moreover, you may make it the structure by which the shaft of the compressor used for a heat pump cycle and the shaft of the said expander are directly connected.

  Thereby, it acts so that the recovery power in the expander can be directly used for the power of the compressor, and further has an effect of improving the efficiency.

  According to the present invention, an upper cylinder and a lower cylinder, which are in communication with each other, include an upper roller and a lower roller, an upper cylinder and a lower cylinder, an upper roller and a lower roller, an intermediate closing member, an upper closing member, and a lower closing member. By adopting a configuration in which at least a pair of upper and lower vanes that divide the formed space into a plurality of working chambers are slidably connected, dead volume can be suppressed to an extremely low level without requiring a complicated suction timing mechanism. In addition, continuous inhalation and expansion are possible, and the vane jump phenomenon is reliably prevented, so the performance is improved by preventing the leakage of the refrigerant due to the vane jump phenomenon while suppressing the pulsation during inhalation, Moreover, the effect of suppressing noise and improving reliability can be obtained.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

(Embodiment 1)
Hereinafter, an expander according to Embodiment 1 of the present invention will be described with reference to the drawings. The expander according to the first embodiment has the same configuration as the conventional expander described in detail with reference to FIGS. 17 to 19 except that a connecting means for slidably connecting the vane and the roller is provided. It is. Moreover, the same number is used about the same functional component, and description about the same structure is abbreviate | omitted.

  FIG. 1 is a longitudinal sectional view of an expander according to the first embodiment. FIG. 2 is a cross-sectional view of the expander according to the first embodiment. 2A corresponds to a cross-sectional view taken along line Z1-Z1 in FIG. 1, and FIG. 2B corresponds to a cross-sectional view taken along line Z2-Z2 in FIG.

  The expander in the first embodiment is different from the conventional expander described in FIGS. 17 to 19 in that an upper roller cylindrical recess 35a and a lower roller cylindrical recess 36a provided on the upper roller 35 and the lower roller 36, The upper vane cylindrical convex portion 37a and the lower vane cylindrical convex portion 38a are fitted and slidably connected.

  The shapes of the upper roller cylindrical recess 35a and the lower roller cylindrical recess 36a provided on the upper roller 35 and the lower roller 36 are the same as when the upper vane cylindrical projection 37a and the lower vane cylindrical projection 38a are fitted. Even if it is slidable and removable with respect to the axial direction of the shaft, the radial direction of the upper roller 35 and the lower roller 36 is not separated by the fitting of the cylindrical connecting portion by the above configuration. The fan-shaped central angles 35e and 36e of the upper roller cylindrical recess 35a and the lower roller cylindrical recess 36a are designed to be at least 180 ° or more (FIG. 3). The clearances between the upper roller cylindrical recess 35a and the lower roller cylindrical recess 36a and the upper vane cylindrical projection 37a and the lower vane cylindrical projection 38a are designed to be 50 μm or less.

  The operation of the expander configured as described above will be described by focusing on the working fluid in the upper working chamber 45 and the lower working chamber 46.

  The working fluid is guided to the upper working chamber 45 from the suction hole 41a. The inhalation start state is shown in FIG. Then, the working fluid is sucked in as shown by the hatched portion as it proceeds to FIGS. 4B and 4C, and the suction process is completed in the state of FIG. 4D.

  Next, the working fluid that has been sucked into the upper working chamber 45 moves to the lower working chamber 46 through the communication hole 47. This is indicated by the horizontal line in FIG. Then, the working fluid moves to the lower working chamber 46 as shown by the horizontal line portion as it proceeds to FIGS. 4B and 4C, and the movement is completed in the state of FIG. The expansion occurs while moving from the upper working chamber 45 to the lower working chamber 46, and the volume ratio between the upper working chamber 45 and the lower working chamber 46 becomes the expansion ratio.

  Next, the working fluid that has been moved to the lower working chamber 46 is discharged to the discharge pipe 44 through the discharge hole 33b. The discharge start state is indicated by the vertical line portion in FIG. Then, the working fluid is discharged as shown by the vertical line as it proceeds to FIGS. 4B and 4C, and the discharge is completed in the state of FIG. 4D.

  As described above, in this configuration, the upper working chamber 45 functions as a kind of inflow timing control means, and the expansion phenomenon occurs in the process in which the working fluid moves from the upper working chamber 45 having a small volume to the lower working chamber 46 having a larger volume. Occur. 4A and 4B, the upper vane 37 is slidably connected by the upper vane cylindrical convex portion 37a and the upper roller cylindrical concave portion 35a, so that a vane skip phenomenon occurs. However, since continuous inhalation can be performed and the expansion process can be performed continuously, the pulsation is small and the resulting noise is small.

  According to the first embodiment, the cylindrical connecting portion formed by connecting the vane and the roller has an effect of preventing the vane jumping phenomenon, preventing the leakage of the refrigerant due to the vane jumping phenomenon, and improving the performance. .

  In addition, there is an effect of preventing collision noise between the vane and the roller due to the vane jump phenomenon.

  In addition, since the vane and the roller are in contact with each other with a cylindrical surface, a wider sealing surface can be secured than when the tip of the conventional vane is in contact with the roller, and the gap between the vane and the roller can be secured. There is an effect of reducing the leakage.

  Further, since the vane and the roller are connected, the rotation of the roller can be prevented, and the effect of suppressing the sliding with the vane tip due to the rotation of the roller is exhibited.

  Further, since the vane and the roller are connected, it is not necessary to provide a vane spring, and the phenomenon that the vane spring is detached does not occur, so that the effect of improving the reliability is achieved.

  Further, by providing oil supply holes 35d and 36d (FIG. 5 (a)) in the upper roller 35 and the lower roller 36, the lubricating oil present in the inner diameter portions of the upper roller 35 and the lower roller 36 is supplied to the upper vane 37 and the lower vane 38. And can be supplied to the connecting portion of the upper roller 35 and the lower roller 36, and there is an effect of improving lubricity and sealing performance.

  The oil supply holes 35d and 36d provided in the upper roller 35 and the lower roller 36 are not necessarily holes provided in the upper roller 35 and the lower roller 36, and notches 35f and 36f as shown in FIG. It goes without saying that the same effect can be obtained by providing a cutout (not shown) for oil supply in the first closing member 41, the lower bearing member 42, or the intermediate closing member 51.

  Further, by providing an axial groove in at least one of the upper vane cylindrical convex portion 37a and the lower vane cylindrical convex portion 38a, or the upper roller cylindrical concave portion 35a and the lower roller cylindrical concave portion 36a (FIG. 6A). , (B)), the sliding area is reduced, the sliding loss is suppressed, and the lubricating oil is retained in the groove, thereby improving the lubricity.

  The connecting means for connecting the roller and the vane is more effective when provided in both the upper and lower working chambers 45 and 46, but the same effect can be obtained even if provided in either one of them. Needless to say.

  Further, by chamfering the communication hole 47 of the intermediate closing member 51 and reducing the hole diameter, it is possible to reduce the dead volume while suppressing the pressure loss when the working fluid is moved, and to further improve the performance. Play.

  The expander shown in the first embodiment is not related to the vertical type or horizontal type of the expander, and is related to the type in which the shaft of the expander is connected to the shaft of the compressor or the type not connected. Needless to say, the same effect can be obtained.

(Embodiment 2)
Hereinafter, an expander according to Embodiment 2 of the present invention will be described with reference to the drawings. In addition, since the expander in this Embodiment 2 takes the structure similar to the expander of Embodiment 1 except that the shape of a vane differs, only the working chamber figure containing a vane shape is described. In the second embodiment, the upper vane 37 and the upper roller 35 will be described as an example, but the same configuration is possible with the lower vane 38 and the lower roller 36.

  FIG. 7 is an operation chamber diagram of the expander according to the second embodiment. The upper vane 37 shown in FIG. 7 is provided with a groove 37g having a groove depth 37j so that the upper roller cylindrical recess tip 35b does not contact the upper vane 37 during the eccentric movement.

  According to the second embodiment, when the vane side surface 37h is polished by the above-described configuration, a degree of freedom of movement of the polishing member is generated by the distance of the groove length 37i of the groove 37g. The polishing step can be easily performed without damaging the vane cylindrical protrusion 37a.

  Further, at the time of the expansion operation, the groove 37g acts as a space for holding the lubricating oil, and improves the sealing performance between the upper vane 37 and the upper vane groove 32a provided in the upper cylinder 32, thereby improving the performance. .

  Further, as shown in FIG. 8, the upper vane cylindrical convex portion 37a and the upper vane neck portion 37p are fixed relative to each other in the direction of the communication hole 47 with respect to the upper vane center line L1 (the upper vane cylinder). The center line of the convex portion 37a and the upper vane neck portion 37p is L2), so that the upper roller cylindrical concave tip 35b does not contact the upper vane 37 during the eccentric motion, and the upper vane 37 and the upper vane groove 32a The space 37o close to the communication hole 47 can be made extremely small.

  Due to the above configuration, unlike the space 37n that is always exposed to the suction working fluid during the expansion operation and is not a dead volume, the space constituted by the upper vane 37 and the upper vane groove 32a that becomes a dead volume during the expansion operation. Since the space 37o close to the communication hole 47 can be made extremely small, it is possible to prevent performance degradation and to easily perform the polishing of the vane side surface 37h.

  In the lower working chamber space constituted by the lower vane 38, the lower roller 36, and the lower cylinder 33, the position of the communication hole 47 relative to the lower vane 38 is opposite to the positional relationship between the upper vane 37 and the communication hole 47. Therefore, the direction of shifting the lower vane cylindrical convex portion and the lower vane neck from the lower vane center line is opposite to that of the upper vane 37.

(Embodiment 3)
Hereinafter, an expander according to Embodiment 3 of the present invention will be described with reference to the drawings. In addition, since the expander in this Embodiment 3 takes the same structure as the expander of Embodiment 1 except the point from which the connection method of a vane and a roller differs, only the structure of a connection means is described. In the third embodiment, the upper vane 37 and the upper roller 35 will be described as an example, but the lower vane 38 and the lower roller 36 can have the same configuration.

  FIG. 9 is a diagram showing the connecting means of the expander according to the third embodiment. The connecting means shown in FIG. 9 includes an upper vane 37, an upper roller 35, and a leaf spring 22 a fitted into the notches of the upper vane 37 and the upper roller 35. A bulge is provided at both ends of the leaf spring, and a notch that fits into the bulge is provided in the upper vane 37 and the upper roller 35 to prevent the leaf spring 22a from being detached from the upper vane 37 and the upper roller 35.

  According to the third embodiment, with the above configuration, the connecting means can be configured only by a simple process of providing notches in the vane and the roller, and the vane and the roller can be connected by an inexpensive process and an inexpensive leaf spring. It becomes possible to connect so that sliding is possible.

(Embodiment 4)
Hereinafter, an expander according to Embodiment 4 of the present invention will be described with reference to the drawings. Since the expander in the fourth embodiment has the same configuration as that of the expander in the first embodiment except that the connection method between the vane and the roller is different, only the structure of the connecting means is described. In the fourth embodiment, the upper vane 37 and the upper roller 35 will be described as an example. However, the lower vane 38 and the lower roller 36 can have the same configuration.

  FIG. 10A is a view showing the connecting means of the expander according to the fourth embodiment, and FIG. 10B corresponds to a cross-sectional view taken along line XX of FIG.

  The connecting means shown in FIG. 10 includes an upper vane 37, an upper roller 35, and a pin 22b that connects the upper vane 37 and the upper roller 35. In addition, the upper vane 37 and the upper roller 35 are provided with staggered steps so that a part of the parts overlap each other, thereby enabling connection by the pins 22b. Further, the upper roller 35 is provided with a notch 35g so as not to collide with the upper vane 37 during the eccentric motion.

  According to the fourth embodiment, with the configuration described above, by using a pin for the connecting means, there is no repetition of deformation of the connecting member that occurs when a leaf spring or the like is used even when the rotor rotates eccentrically. There is little deterioration of the connecting member, and there is an effect of improving the reliability.

(Embodiment 5)
Hereinafter, an expander according to Embodiment 5 of the present invention will be described with reference to the drawings. The expander in the fifth embodiment has the same configuration as that of the expander in the first embodiment except that the connection method between the vane and the roller is different, so that only the structure of the connecting means is described. In the fifth embodiment, the upper vane 37 and the upper roller 35 will be described as an example. However, the lower vane 38 and the lower roller 36 can have the same configuration.

  11 (a) and 11 (b) are diagrams showing the connecting means of the expander according to the fifth embodiment. The connecting means shown in FIG. 11A includes an upper vane 37, an upper roller 35, and a bush 23 a that fits into a cylindrical concave portion of the upper roller 35 and a convex portion of the upper vane 37.

  According to the fifth embodiment, by using the bush 23a as the connecting means according to the above configuration, a material suitable for sliding can be selected, so that an effect of improving reliability can be achieved.

  In addition, by using a sintered material for the bush material, it becomes possible to perform precise processing, and it is possible to select a material that can be easily processed for the upper vane 37 and the upper roller 35. Therefore, the effect of improving reliability at low cost is achieved.

  Note that it is needless to say that the convex portion of the upper vane 37 does not need to be provided at two places as shown in FIG.

  Further, as shown in FIG. 11B, by connecting the bush 23a and the upper vane 37 with screws 22c, the processing of the upper vane 37 may be as simple as providing a screw hole. Since the screw hole provided in the hole acts as a space for holding the lubricating oil, the reliability is improved.

(Embodiment 6)
Hereinafter, an expander according to Embodiment 6 of the present invention will be described with reference to the drawings. Since the expander in the sixth embodiment has the same configuration as the expander in the first embodiment except that the connection method between the vane and the roller is different, only the structure of the connecting means is described. In the sixth embodiment, the upper vane 37 and the upper roller 35 will be described as an example. However, the lower vane 38 and the lower roller 36 can have the same configuration.

  12 (a) and 12 (c) are diagrams showing connecting means of the expander according to the sixth embodiment. FIG. 12B corresponds to a cross-sectional view taken along line XX in FIG.

  12 (a) and 12 (b) includes an upper vane 37, an upper roller 35, a bush 23b, and a fixing pin 22d that fixes the upper vane 37 and the bush 23b.

  According to the sixth embodiment, with the above configuration, the upper vane 37 and the bush 23b are provided with holes and fixed with the fixing pin 22d, and therefore the upper vane 37 and the bush 23b are formed by an extremely easy process without projections. can do.

  Further, the bush 23b to be fixed to the upper vane 37 may be either one of the left and right, and the positioning with either one of the bushes 23b may be performed, so that the processing becomes easier.

  Needless to say, the same effect can be obtained by fixing the upper vane 37 and the bush 23b with a plate-like fixing member 22e (not shown).

  Further, as shown in FIG. 12C, by providing a protrusion on the upper vane 37 and fitting with the bush 23b, a member such as a fixing pin becomes unnecessary.

(Embodiment 7)
Hereinafter, an expander according to Embodiment 7 of the present invention will be described with reference to the drawings. Since the expander in the seventh embodiment has the same configuration as that of the expander in the first embodiment except that the connection method between the vane and the roller is different, only the structure of the connecting means is described. In the seventh embodiment, the upper vane 37 and the upper roller 35 will be described as an example, but the lower vane 38 and the lower roller 36 can have the same configuration.

  13 (a) and 13 (b) are diagrams showing the connecting means of the expander according to the seventh embodiment. In the seventh embodiment shown in FIG. 13A, the upper vane 37 is provided with a cylindrical convex portion 37e having a thickness equal to or less than the vane thickness, and the upper roller 35 is provided with a cylindrical concave portion to be fitted to the upper vane 37. The upper roller 35 is configured to be slidably connected.

  According to the seventh embodiment, with the above configuration, the upper vane 37 and the upper roller 35 can be slidably connected without using a connecting member or a bush, and compared with the connecting means of the first embodiment. Since the cylindrical concave portion of the upper roller 35 is small, there is an effect that the radial length of the upper roller 35 can be increased.

  As shown in FIG. 13B, the upper vane 37 is provided with a cylindrical concave portion 37f, and the upper roller 35 is provided with a cylindrical convex portion to be fitted thereto, so that the vane and the roller are slidably connected. It goes without saying that the same effect can be obtained even with such a configuration.

  The expander of the present invention can be used as a prime mover or a generator that obtains rotational power from a compressible gas.

The longitudinal cross-sectional view of the expander in Embodiment 1 of this invention Cross section of expander in Embodiment 1 of the present invention The figure of the roller cylindrical recessed part shape in Embodiment 1 of this invention Operational diagram of working chamber of expander in Embodiment 1 of the present invention The perspective view of the roller with an oil supply hole in Embodiment 1 of this invention The perspective view of the grooved vane and roller in Embodiment 1 of this invention Working chamber diagram of expander in embodiment 2 of the present invention Working chamber diagram of expander in embodiment 2 of the present invention The figure of the connection means of the expander in Embodiment 3 of this invention The figure of the connection means of the expander in Embodiment 4 of this invention The figure of the connection means of the expander in Embodiment 5 of this invention The figure of the connection means of the expander in Embodiment 6 of this invention The figure of the connection means of the expander in Embodiment 7 of this invention Vertical section of a conventional expander Cross-sectional view of a conventional expander Operation diagram of the working chamber of a conventional expander Longitudinal sectional view of a conventional 2-cylinder expander Cross-sectional view of a conventional 2-cylinder expander Operation diagram of working chamber of conventional two-cylinder expander (A) Conceptual diagram of a conventional heat pump cycle (b) Conceptual diagram of a heat pump cycle using a conventional expander (c) Mollier diagram

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,31 Sealed container 2 Cylinder 2a Vane groove 2b, 33b Discharge hole 3,34 Shaft 3a Eccentric part 3b Axial direction path 3c Radial direction path 4 Roller 4a Suction path 4h, 37g Groove 5 Vane 5c Vane back surface 6 Vane spring 6a Back surface of vane Space 7, 41 First closing member 8, 42 Second closing member 9, 43 Suction pipe 10, 44 Discharge pipe 12 Working chamber 13 Compressor 14 Gas cooler 15 Expansion valve 16 Evaporator 17 Drive element 18 Expander 20, 50 Suction space 22a Leaf spring 22b Pin 22c Screw 22d Fixing pin 22e Plate-like fixing member 23a, 23b Bush 32 Upper cylinder 32a Upper vane groove 33 Lower cylinder 33a Lower vane groove 34a Upper eccentric part 34b Lower eccentric part 35 Upper roller 35a Upper roller cylindrical recess 35b Upper roller cylindrical recess tip 35d, 36 Lubricating hole 35e, 36e Center angle 35f, 35g, 36f Notch 36 Lower roller 36a Lower roller cylindrical recess 37 Upper vane 37a Upper vane cylindrical projection 37b Upper vane rear surface 37c Upper vane tip 37e Cylindrical projection 37f Cylindrical recess 37h Vane side surface 37i Groove length 37j Groove depth 37n, 37o Space 37p Upper vane neck 38 Lower vane 38a Lower vane cylindrical convex part 39 Upper vane spring 40 Lower vane spring 41a Suction hole 45 Upper working chamber 46 Lower working chamber 47 Communication Hole 51 Intermediate closing member

Claims (16)

(N-1) intermediate closing members (N is an integer equal to or greater than 2), N cylinders provided at positions sandwiching the (N-1) intermediate closing members in sequence, and the N N rollers that rotate eccentrically inside the cylinders, shafts fitted to the N rollers, and both end surfaces of the N cylinders are closed with the (N-1) intermediate closing members. A first closing member and a second closing member for closing the end surfaces of the remaining two surfaces, the N cylinders, the N rollers, the (N-1) intermediate closing members, and the first closing member. N spaces formed by the member and the second closing member are divided into a plurality of working chambers, and the (N-1) intermediate closing members are provided in the N spaces. And (N-1) or less communication holes, and a small number of the N spaces. A suction hole for allowing the working fluid to flow into any one or more, a discharge hole for discharging the working fluid from at least one of the N spaces to a discharge space, the N rollers, and the N An expander comprising a connecting means for slidably connecting at least a pair of vanes. An intermediate closing member, an upper cylinder and a lower cylinder provided above and below the intermediate closing member, an upper roller and a lower roller that rotate eccentrically inside the upper cylinder and the lower cylinder, and the upper roller and the lower roller. A fitted shaft, an upper closing member and a lower closing member for closing each end face of the upper cylinder and the lower cylinder together with the intermediate closing member, the upper cylinder, the lower cylinder, the upper roller, and the lower roller; An upper vane and a lower vane that divide an upper space and a lower space formed by the intermediate closing member, the upper closing member, and the lower closing member into a plurality of working chambers; the upper space provided in the intermediate closing member; A communication hole for communicating the lower space, and a suction hole for allowing the working fluid to flow into either the upper space or the lower space A discharge hole for discharging the working fluid from the other space to the discharge space; and a connecting means for slidably connecting at least one pair of the upper roller and the lower roller to the upper vane and the lower vane. Expansion machine. As the connecting means, an upper concave portion is provided on one of the upper roller and the upper vane, and a lower concave portion is provided on either the lower roller or the lower vane, and the upper concave portion and the lower concave portion are fitted. An upper convex portion and a lower convex portion are provided on each other,
The expander according to claim 2. As the connecting means, an upper roller cylindrical recess is provided in the outer diameter portion of the upper roller, and a lower roller cylindrical recess is provided in the outer diameter portion of the lower roller, and the upper vane is fitted into the upper roller cylindrical recess. A cylindrical convex portion, and a lower vane cylindrical convex portion that fits into the lower roller cylindrical concave portion are provided on a part of the upper vane and the lower vane, respectively.
The expander according to claim 2. The center angle of the upper roller cylindrical recess and the lower roller cylindrical recess is at least 180 ° or more,
The expander according to claim 4. As the connecting means, the upper roller and the upper vane are connected, and at least one connecting member for connecting the lower roller and the lower vane is provided,
The expander according to claim 2. As the connecting member, a leaf spring is provided,
The expander according to claim 6. As the connecting member, a cylindrical fixing pin is provided,
The expander according to claim 6. An upper concave portion is provided on one of the upper roller and the upper vane, a lower concave portion is provided on either the lower roller or the lower vane, and an upper convex portion and a lower convex portion are provided on the other, respectively. The at least one connecting sliding member that fits into the upper concave portion and the upper convex portion and that fits into the lower concave portion and the lower convex portion is provided.
The expander according to claim 2. As the connecting sliding member, at least one bush is provided,
The expander according to claim 9. The connecting means is provided with an oil supply means for supplying lubricating oil,
The expander in any one of Claims 1-10. As the oil supply means, a groove for communicating the inner diameter portions of the upper roller and the lower roller and the connecting means is provided in the upper roller and the lower roller,
The expander according to claim 11. As the oil supply means, holes are provided in the upper roller and the lower roller for communicating the inner diameter portions of the upper roller and the lower roller and the connecting means,
The expander according to claim 11. As the oil supply means, at least one of the upper closing member, the lower closing member, and the intermediate closing member is provided with a groove or hole for communicating the inner diameter portion of the upper roller and the lower roller with the communication means. Characterized by the
The expander according to claim 11. It is used for a heat pump cycle in which the working fluid is carbon dioxide,
The expander in any one of Claims 1-14. The shaft of the compressor used in the heat pump cycle and the shaft of the expander are directly connected,
The expander according to claim 15.

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