JP2010229846A - Rotary expander and fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary expander with a simplified structure reducing energy loss due to sliding between members during operation. <P>SOLUTION: The rotary expander 2 includes: a rotor 13 being in contact with the inner peripheral surface 10a of a cylinder 10 and revolving in an expansion chamber 17; a blade 14 pushed and urged to abut on the outer peripheral surface of the rotor 13, reciprocating corresponding to the revolution of the rotor 13, and dividing the expansion chamber 17 into a section into which high pressure gas flows and a section discharging the expanded low pressure gas; a reciprocating member 15 pushed and urged to abut on the outer peripheral surface of the rotor 13 and reciprocating corresponding to the revolution of the rotor 13; and a regulating means 16 for causing the high pressure gas to flow intermittently into the expansion chamber 17 by the reciprocating motion of the reciprocating member 15. Thus, the structure of the rotary expander 2 is made simple, and energy loss due to sliding between members during operation is reduced. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a rotary expander and a fluid machine, and more particularly to a rotary expander having a simple structure and less energy loss due to sliding between members, and a fluid machine using the rotary expander.

  Conventionally, as inventions of a rotary expander and a fluid machine using the rotary expander, for example, those described in the following Patent Documents 1 to 3 are known.

  The rotary type expander described in Patent Document 1 is fitted into a cylinder whose both end faces are closed by a closing member, a rotating shaft that penetrates the cylinder, and an eccentric portion of the rotating shaft, and is accommodated in the cylinder. The rotor which forms an expansion chamber in a cylinder by this, and the revolution member fitted by the sub-eccentric part of the rotating shaft are provided. An opening formed in the revolution member at a specific timing when the revolution member revolves with the rotation of the rotation shaft. And a suction port formed in the closing member communicate with each other, and a high-pressure refrigerant is supplied into the expansion chamber. The high-pressure refrigerant supplied into the expansion chamber expands in the expansion chamber, and is discharged after being expanded to a low pressure.

  The rotary expander described in Patent Document 2 is fitted into a cylinder whose both end faces are closed by a closing member, a rotating shaft that passes through the cylinder, and an eccentric portion of the rotating shaft, and is accommodated in the cylinder. Thus, a rotor (piston) that forms an expansion chamber in the cylinder and a communication path formed in the eccentric portion are provided. The eccentric portion is arranged such that the surface on which the communication passage is formed slides in contact with the surface of the one closing member, and the introduction passage is formed in the closing member only while the rotation angle of the rotation shaft is within a predetermined range. In addition, high-pressure refrigerant is supplied into the expansion chamber via the communication path of the rotor. The high-pressure refrigerant supplied into the expansion chamber expands in the expansion chamber, and is discharged after being expanded to a low pressure.

  The rotary expander described in Patent Document 3 is fitted into a cylinder whose end faces are changed by a closing member, a rotating shaft that penetrates the cylinder, and an eccentric portion of the rotating shaft, and is accommodated in the cylinder. A rotor (piston) that forms an expansion chamber in the cylinder, a slidable partition vane, a slidable closing vane, and a cam that is connected to the rotating shaft and regulates the sliding movement of the closing vane. It has. The refrigerant suction hole formed in the closing member is opened and closed depending on the rotational position of the rotor, and the high-pressure refrigerant is supplied into the expansion chamber at the timing when the suction hole is opened. The refrigerant supplied into the expansion chamber expands in the expansion chamber and is discharged after reaching a low pressure.

JP 2001-153077 A JP 2004-44569 A JP 2007-138728 A

  However, the following points are not considered in the rotary expander described above.

  In the rotary expander described in Patent Document 1, it is necessary to provide a sub-eccentric part on the rotating shaft, and it is also necessary to provide an Oldham mechanism for preventing the rotation of the revolving member fitted to the sub-eccentric part. In addition, the structure becomes complicated and it is difficult to reduce the cost. Further, since the revolving member revolves in a state where it is in surface contact with the closing member, energy loss at the sliding portion is increased.

  In the rotary type expander described in Patent Document 2, since the eccentric portion rotates in a state where the end surface thereof is in surface contact with the closing member, energy loss at the sliding portion is large. Furthermore, in order to form the communication path in the eccentric portion, it is necessary to increase the amount of eccentricity of the eccentric portion, and the design is greatly restricted.

  In the rotary type expander described in Patent Document 3, a cam for sliding the closing vane is necessary, and the structure becomes complicated and it is difficult to reduce the cost. In addition, since the closed vane repeats contact and non-contact with the rotor, there are problems that noise is generated, and that the reliability of the rotor and the closed vane is damaged and reliability is lowered.

  The present invention has been made in order to solve the above-described problems, and an object of the present invention is to provide a rotary type expander capable of simplifying the structure and reducing energy loss due to sliding between members during operation. And providing a fluid machine.

  A first feature according to an embodiment of the present invention is that in a rotary expander, a cylinder having an inner peripheral surface, a rotating shaft provided through the cylinder, and both end surfaces of the cylinder are closed. A closing member that forms an expansion chamber in the cylinder, a rotor that is fitted to an eccentric portion of the rotating shaft, revolves in the expansion chamber in contact with an inner peripheral surface of the cylinder, and an outer periphery of the rotor A blade that is pressed and urged to abut against the surface, reciprocates in response to the revolution of the rotor, and divides the expansion chamber into a side into which high-pressure gas flows and a side from which low-pressure gas after expansion is discharged A reciprocating member that is pressed and urged to contact the outer peripheral surface of the rotor and reciprocates in response to the revolution of the rotor, and a reciprocating operation of the reciprocating member causes the high-pressure gas to enter the expansion chamber. Regulators that interrupt the inflow And, it is by providing the.

  A second feature according to an embodiment of the present invention is that in a fluid machine, the rotary expander according to the first feature, an electric motor that rotationally drives the rotating shaft, the rotary expander, and the electric motor. And a compression mechanism portion to which a driving force is transmitted, and a case for housing the rotary expander, the electric motor, and the compression mechanism portion.

  ADVANTAGE OF THE INVENTION According to this invention, the structure can be simplified and the rotary type expander and fluid machine which can reduce the energy loss by sliding between the members at the time of a driving | operation can be provided.

It is a vertical side view which shows the fluid machine of one embodiment of this invention. It is the vertical side view which made the cross section the part of the rotary type expander in a fluid machine in the position different from FIG. It is an expansion operation | movement figure in case the rotation angle of the rotating shaft of a rotary type expander is 0 degree (360 degrees) and 45 degrees. It is an expansion operation | movement figure in case the rotation angle of the rotating shaft of a rotary type expander is 90 degrees and 135 degrees. It is an expansion operation | movement figure in case the rotation angle of the rotating shaft of a rotary type expander is 180 degrees and 225 degrees. It is an expansion operation | movement figure in case the rotation angle of the rotating shaft of a rotary type expander is 270 degrees and 315 degrees.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  A fluid machine 1 shown in FIG. 1 is used as a part of a refrigeration apparatus, and includes a rotary type expander 2, an electric motor 3, a compressor 4 as a compression mechanism, and these rotary type expander 2 and an electric motor. 3 and a case 5 for housing the compressor 4. The case 5 includes a discharge pipe 6 through which high-temperature and high-pressure refrigerant compressed by the compressor 4 is discharged toward a radiator (not shown), and the refrigerant radiated by the radiator etc. is a rotary expander. 2, an inflow pipe 7 that flows into the rotary expander 2, a low-temperature / low-pressure refrigerant expanded by the rotary expander 2 is discharged toward the evaporator (not shown), and the evaporator absorbs heat. An inflow pipe 9 through which the refrigerant flows toward the compressor 4 is provided.

  The rotary expander 2 includes a cylinder 10, closing members 11 a and 11 b, a rotating shaft 12, a rotor 13, a blade 14 (see FIGS. 3 to 6), a reciprocating member 15, and a regulating means 16. Have.

  The cylinder 10 is formed in a substantially cylindrical shape and has an inner peripheral surface 10a. One end face of the cylinder 10 is closed by a closing member 11a, and the other end face of the cylinder 10 is closed by a closing member 11b. An area closed by the closing members 11 a and 11 b in FIG.

  The rotary shaft 12 is provided through the cylinder 10 and the closing members 11a and 11b in the direction of the central axis of the cylinder 10, and an eccentric portion 12a is formed in a portion of the rotary shaft 12 located in the expansion chamber 17, The rotor 13 is rotatably fitted to the eccentric portion 12a. The rotor 13 revolves in the expansion chamber 17 while being in contact with the inner peripheral surface 10 a of the cylinder 10 as the rotary shaft 12 rotates.

  The blade 14 is slidably accommodated in a groove 18 formed in the cylinder 10 as shown in FIGS. 3 to 6, and is moved by a spring 19 so that one end in the sliding direction abuts on the outer peripheral surface of the rotor 13. It is pressed and urged to reciprocate in the groove 18 in response to the revolution of the rotor 13. When the blade 14 is brought into contact with the outer peripheral surface of the rotor 13, the expansion chamber 17 is divided into two parts by the rotor 13 and the blade 14, one of which is the inflow passage 7 a formed in the inflow pipe 7 and the cylinder 10 and the inflow gas introduction. The other side is an inflow side expansion chamber 17a into which high-pressure refrigerant flows via the passage 23, and the other is expanded low-pressure refrigerant discharged via the discharge passage 20 and the discharge pipe 8 formed in the cylinder 10. The discharge side expansion chamber 17b.

  The reciprocating member 15 is slidably accommodated in a groove 21 formed in the cylinder 10 as shown in FIGS. 3 to 6, and is a spring so that one end in the sliding direction abuts the outer peripheral surface of the rotor 13. It is urged by 22 and reciprocates in the groove 21 in response to the revolution of the rotor 13.

  The restricting means 16 is a mechanism that interrupts the flow of the high-pressure refrigerant into the inflow side expansion chamber 17 a by the reciprocating movement of the reciprocating member 15, and flows into the inflow gas introduction passage 23 formed in the cylinder 10 and the cylinder 10. A groove 21 that intersects with the gas introduction passage 23 and slidably accommodates the reciprocating member 15 and a reciprocating member 15 that is provided in the reciprocating member 15 slides within a predetermined sliding range. In this case, a communication passage portion 24 is provided for bringing the inflow gas introduction passage 23 into a communication state. When the reciprocating member 15 is located outside a predetermined sliding range, the inflow gas introduction passage 23 is blocked by the reciprocating member 15. Further, the communication passage portion 24 is formed at a position that does not communicate with the expansion chamber 17 even when the reciprocating member 15 enters the expansion chamber 17 most.

  The inflow gas introduction passage 23 is formed by covering a concave groove 25 formed on the end surface of the cylinder 10 with a closing member 11a which is a covering member.

  The electric motor 3 includes a rotor 26 fixed to the outer peripheral surface of the rotary shaft 12 and a stator 27 fixed to the inner peripheral portion of the case 5 and disposed at a position surrounding the outer periphery of the rotor 26. A winding is wound around the stator 27, and the rotating shaft 12 rotates around the axis by controlling energization of the winding.

  The compressor 4 is fitted into a cylinder 29 having a compression chamber 28 formed therein, a rotary shaft 12 provided through the cylinder 29 in the direction of its central axis, and an eccentric portion 12b of the rotary shaft 12 so as to be compressed. It is comprised by the roller 30 etc. which revolve inside. The inflow pipe 9 is connected to the inflow side of the compression chamber 28, and the refrigerant compressed in the compression chamber 28 and having a high temperature and high pressure is discharged from the discharge muffler 31 into the case 5. The high-temperature and high-pressure refrigerant discharged into the case 5 is discharged toward the radiator via the discharge pipe 6.

  In such a configuration, the expansion operation of the rotary expander 2 will be described with reference to FIGS. The rotary shaft 12 rotates in the arrow direction (counterclockwise direction), and the rotor 13 revolves in the same direction (counterclockwise direction) as the rotation direction.

  As shown in FIG. 3A, when the rotation angle of the rotary shaft 12 becomes approximately 0 ° (360 °), the reciprocating member 15 moves in the direction of being pushed out of the expansion chamber 17, and the reciprocating member 15 The inflow gas introduction passage 23 that has been blocked by the communication state is brought into a communication state via the communication passage portion 24, and high-pressure refrigerant can flow into the expansion chamber 17 through the inflow gas introduction passage 23. In this case, the discharge-side expansion chamber 17b in which the low-pressure refrigerant after expansion is accommodated communicates with the discharge passage 20 and passes through the discharge passage 20 and the discharge pipe 8 in the discharge-side expansion chamber 17b. The discharge of the low-pressure refrigerant is started.

  As shown in FIG. 3 (b), when the rotation angle of the rotary shaft 12 becomes approximately 45 °, the inflow gas introduction passage 23 is maintained in the communication state via the communication passage portion 24, and the rotor 13 With this revolution, the inflow side expansion chamber 17a is generated in the expansion chamber 17, and the high-pressure refrigerant starts to flow into the inflow side expansion chamber 17a. In addition, the inflow of the high-pressure refrigerant into the inflow side expansion chamber 17a is continued until the rotation angle of the rotating shaft 12 becomes approximately 90 ° as shown in FIG.

  When the rotation angle of the rotary shaft 12 exceeds 90 °, for example, 135 ° as shown in FIG. 4B, the inflow gas introduction passage 23 is blocked by the reciprocating member 15, and the high-pressure to the inflow side expansion chamber 17a. Inflow of the refrigerant ends. After the inflow of the high-pressure refrigerant into the inflow side expansion chamber 17a is completed as shown in FIG. 4B, the inflow side expansion chamber 17a is accompanied with the rotation of the rotary shaft 12 as shown in FIGS. Gradually increases, the refrigerant in the inflow side expansion chamber 17a expands, and gradually becomes a low pressure. 3 to FIG. 6, the discharge side expansion chamber 17 b is maintained in communication with the discharge passage 20, and the low-pressure refrigerant in the discharge side expansion chamber 17 b passes through the discharge passage 20 and the discharge pipe 8. It is discharged via.

  Then, during the transition from the state of FIG. 6B to the state of FIG. 3A, the portion that has been the inflow side expansion chamber 17a until then communicates with the discharge passage 20 and switches to the discharge side expansion chamber 17b. Then, the refrigerant that has flowed into the inflow side expansion chamber 17 a and expanded is discharged through the discharge passage 20 and the discharge pipe 8.

  Here, in the rotary expander 2, the one end of the blade 14 and one end of the reciprocating member 15 are brought into contact with the outer peripheral surface of the rotor 13, and the blade 14 and the reciprocating member 15 are Further, the flow of the high-pressure refrigerant into the inflow side expansion chamber 17a is intermittently interrupted by the restricting means 16 by the reciprocating motion of the reciprocating member 15. Then, the regulating means 16 forms the communication passage portion 24 in the reciprocating member 15, and communicates the inflow gas introduction passage 23 via the communication passage portion 24 when the reciprocating member 15 slides within a predetermined sliding range. The inflow gas introduction passage 23 is blocked when the reciprocating member 15 is located in another sliding range. Therefore, the structure of the rotary expander 2 can be simplified. Further, when the rotary expander 2 is operated, there is no portion that rotates while contacting a large area, and energy loss due to sliding between members can be reduced.

  The inflow gas introduction passage 23 is formed by forming a concave groove 25 on the end face of the cylinder 10 and covering the concave groove 25 with a closing member 11a as a cover member. Can be done easily.

  In addition, the member which covers the concave groove | channel 25 is not limited to the obstruction | occlusion member 11a, You may use another member.

  The position where the communication passage portion 24 is formed is a position where the reciprocating member 15 does not communicate with the expansion chamber 17 even when the reciprocating member 15 enters the expansion chamber 17 most. Therefore, when the reciprocating member 15 that shuts off the inflow gas introduction passage 23 enters the expansion chamber 17 most, for example, in the case of FIG. 5B, the communication passage portion 24 in which the high-pressure refrigerant remains. Does not communicate with the inflow-side expansion chamber 17a in the expansion process, and the high-pressure refrigerant remaining in the communication passage portion 24 flows into the inflow-side expansion chamber 17a, and the low-pressure refrigerant enters the communication passage portion 24. This is prevented. For this reason, it can prevent that the quantity of the refrigerant | coolant which flows in into the inflow side expansion chamber 17a at the next process decreases, and expansion efficiency falls. This point becomes important as the volume of the communication path portion 24 increases.

  In the fluid machine 1, the rotary type expander 2 and the compressor 4 are accommodated in the same case 5, and the rotary type expander 2 and the compressor 4 commonly use the rotary shaft 12. For this reason, in the rotary expander 2, the pressure difference between the inflow side expansion chamber 17 a and the discharge side expansion chamber 17 b acts on the rotation shaft 12 as a driving force for rotating the rotation shaft 12. The electric motor 3 to be made can be downsized.

  In the present embodiment, the case where the inflow gas introduction passage 23 and the groove 21 in which the reciprocating member 15 is slidably accommodated is described as an example, but the inflow gas introduction is described. The fact that the passage 23 and the groove 21 intersect with each other is not limited to the case of intersecting with a substantially cross shape, but includes the case of intersecting with a V shape.

  In the present embodiment, the fluid machine 1 using the compressor 4 as the compression mechanism is described as an example. However, the rotary expander 2 of the present invention is also used in a fluid machine using a pump as the compression mechanism. Can be used.

  DESCRIPTION OF SYMBOLS 1 ... Fluid machine, 2 ... Rotary type expander, 3 ... Electric motor, 4 ... Compressor (compression mechanism part), 5 ... Case, 10 ... Cylinder, 10a ... Inner peripheral surface, 11a, 11b ... Closure member, 11a ... Blockage Member (cover member), 12 ... rotating shaft, 12a ... eccentric part, 13 ... rotor, 14 ... blade, 15 ... reciprocating member, 16 ... restricting means, 20 ... communication path part, 21 ... groove, 23 ... inflow gas introduction Passage, 25 ... concave groove

Claims (5)

A cylinder having an inner peripheral surface;
A rotating shaft provided penetrating through the cylinder;
A closing member provided by closing both end faces of the cylinder, and forming an expansion chamber in the cylinder;
A rotor that is fitted to an eccentric portion of the rotating shaft and revolves in the expansion chamber in contact with an inner peripheral surface of the cylinder;
Pressed and urged to contact the outer peripheral surface of the rotor, reciprocates in response to the revolution of the rotor, and into the side where the high-pressure gas flows into the expansion chamber and the side where the low-pressure gas after expansion is discharged A blade that bisects,
A reciprocating member that is pressed and urged to contact the outer peripheral surface of the rotor and reciprocates in response to the revolution of the rotor;
Restricting means for intermittently inflow of high-pressure gas into the expansion chamber by the reciprocating movement of the reciprocating member;
A rotary type expander comprising:   The restricting means includes an inflow gas introduction passage provided in the cylinder, a groove provided in the cylinder so as to cross the inflow gas introduction passage and in which the reciprocating member is slidably received, and the reciprocation The rotary expansion according to claim 1, further comprising a communication passage portion provided on the member and configured to communicate with the inflowing gas introduction passage when the reciprocating member slides within a predetermined sliding range. Machine.   3. The rotary expander according to claim 1, wherein the inflow gas introduction passage is formed by covering a concave groove formed on an end surface of the cylinder with a covering member. 4.   The said communicating path part is provided in the position which is not connected in the said expansion chamber when the said reciprocating member enters the said expansion chamber most, The Claim 1 thru | or 3 characterized by the above-mentioned. Rotary type expander. A rotary expander according to any one of claims 1 to 4;
An electric motor for rotating the rotating shaft;
A compression mechanism that transmits driving force from the rotary expander and the electric motor;
A case that houses the rotary expander, the electric motor, and the compression mechanism;
A fluid machine comprising:

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