WO2008044456A1 - Rotary expander - Google Patents
Rotary expander Download PDFInfo
- Publication number
- WO2008044456A1 WO2008044456A1 PCT/JP2007/068441 JP2007068441W WO2008044456A1 WO 2008044456 A1 WO2008044456 A1 WO 2008044456A1 JP 2007068441 W JP2007068441 W JP 2007068441W WO 2008044456 A1 WO2008044456 A1 WO 2008044456A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cylinder
- working chamber
- rotary expander
- path
- working fluid
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 59
- 238000002347 injection Methods 0.000 claims abstract description 58
- 239000007924 injection Substances 0.000 claims abstract description 58
- 230000002093 peripheral effect Effects 0.000 claims abstract description 48
- 238000000034 method Methods 0.000 claims abstract description 7
- 238000005192 partition Methods 0.000 claims description 40
- 238000004891 communication Methods 0.000 claims description 7
- 230000006835 compression Effects 0.000 claims description 7
- 238000007906 compression Methods 0.000 claims description 7
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 6
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 3
- 239000001569 carbon dioxide Substances 0.000 claims description 3
- 230000006698 induction Effects 0.000 claims description 3
- 230000000903 blocking effect Effects 0.000 claims 2
- 238000005057 refrigeration Methods 0.000 description 15
- 239000003507 refrigerant Substances 0.000 description 13
- 238000011084 recovery Methods 0.000 description 12
- 239000003921 oil Substances 0.000 description 9
- 230000001105 regulatory effect Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 3
- 230000002265 prevention Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/32—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members
- F01C1/322—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F01C1/3562—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F01C1/3564—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
- F01C11/006—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle
- F01C11/008—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of dissimilar working principle and of complementary function, e.g. internal combustion engine with supercharger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
Definitions
- the present invention relates to a rotary expander that can be used in an air conditioner or a hot water heater and can be used in a power recovery type refrigeration cycle apparatus.
- An expander is known as a fluid machine used for the purpose of recovering internal energy when a refrigerant in a refrigeration cycle drops in pressure from high pressure to low pressure with expansion.
- a power recovery type refrigeration cycle apparatus using a conventional expander will be described.
- FIG. 7A shows a conventional power recovery type refrigeration cycle apparatus.
- This refrigeration cycle apparatus is composed of a compressor 1, a gas cooler 2, an expander 3, an evaporator 4, a rotary motor 5, and a shaft 6 directly connecting the compressor 1, the expander 3, and the rotary motor 5.
- Carbon dioxide is used as the working fluid refrigerant.
- the refrigerant is compressed to high temperature and high pressure in the compressor 1 and then cooled in the gas cooler 2. Furthermore, the refrigerant is heated by the evaporator 4 after being dropped to a low temperature and a low pressure in the expander 3.
- the expander 3 collects internal energy when the refrigerant is reduced in pressure from high pressure to low pressure and converts it into the rotational energy of the shaft 6 to be part of the energy that drives the compressor 1. As a result, the dynamic power of the rotary motor 5 is reduced.
- the compressor 1 and the expander 3 are connected by the shaft 6, and the rotation speed of the compressor 1 and the rotation speed of the expander 3 are equal.
- the ratio of the specific volume of the suction refrigerant and the specific volume of the refrigerant sucked by the expander 3 or the ratio of the density of the refrigerant sucked by the compressor 1 and the density of the refrigerant sucked by the expander 3 is the ratio of the respective suction volumes.
- the so-called density ratio is restricted. For this reason, optimal pressure-temperature control cannot be performed, and a reduction in the COP (Coefficient of Performance) of the refrigeration cycle is an issue.
- a power recovery refrigeration cycle apparatus in which injection is performed is disclosed in Japanese Patent Application Laid-Open No. 2004-150748, and its configuration Is shown in Figure 7B.
- the refrigerant path is branched into two at the outlet of the gas cooler 2, and the suction path 9A and the injection path 9B are formed!
- the refrigerant passing through the suction passage 9A passes through the pre-expansion valve 7 and then is sucked into the expander 3.
- the refrigerant passing through the injection passage 9B passes through the regulating valve 8 and then passes through the regulating valve 8 and the expansion chamber working chamber (not shown). ).
- control the opening of the pre-expansion valve 7 and the regulating valve 8 to change the specific volume of the refrigerant sucked into the expander 3 and avoid the restriction of the constant density ratio. It is.
- Japanese Unexamined Patent Application Publication No. 2006-46222 discloses a first-stage rotary expander and a two-stage rotary expander for use in a power recovery refrigeration site apparatus designed to perform injection. It is shown in 8A and Fig. 8B.
- a throttle valve 13 whose opening degree can be adjusted is provided in the injection path 12 branched from the suction path 11, and the introduction port 15 for the working chamber 16 of the injection path 12 is a cylinder. Is provided on the inner peripheral surface 14.
- the throttle valve 23 whose opening degree can be adjusted is provided in the injection path 22 branched from the suction path 21, and the working chamber 28 of the injection path 22 is provided.
- the introduction port 27 is provided at a position in contact with the inner peripheral surface 24a of the first cylinder 24 in a closing member (not shown) that closes the working chamber 28 on the first cylinder 24 side.
- the piston is When located near the top dead center, the injection passages 12, 22 communicate with the discharge passages 17, 30 via the working chamber 16, or the working chambers 28, 29 and the communication passage 26, and the induction passages 12, 22 The working fluid is blown from the discharge path 17, 30 to the low pressure. Since the expansion energy of the blown working fluid cannot be recovered by the expander, the conventional rotary expander has a problem that efficiency is lowered.
- the present invention has been made in view of the force and the problem, and an object thereof is to provide a highly efficient expander that prevents blow-through from the injection path to the discharge path.
- the rotary expander of the present invention forms a cylindrical surface.
- An operation chamber is formed between a cylinder having an inner peripheral surface and an inner peripheral surface disposed inside the cylinder, and a piston that moves along the inner peripheral surface, and the operation sandwiching the cylinder
- a closing member that closes the chamber; a suction passage through which the working fluid flows into the working chamber; and an eccentric portion to which the piston is mounted.
- the working fluid that flows into the working chamber expands to receive a rotational force.
- a shaft for allowing the working fluid expanded from the working chamber to flow out, and an induction passage for further introducing the working fluid into the working chamber during the expansion process of the working fluid, and the injection passage with respect to the working chamber
- the introduction port is provided at a position closer to the inner side than the inner circumferential surface of the cylinder in the closing member so that the injection path and the discharge path do not communicate with each other. And said that you are.
- the working fluid introduced from the injection path into the working chamber is prevented from being blown through to the discharge path having a low pressure. Therefore, according to the present invention, a highly efficient expander can be obtained.
- FIG. 1 is a longitudinal sectional view of an expander-integrated compressor using a one-stage rotary expander according to Embodiment 1 of the present invention.
- FIG. 4 is a longitudinal sectional view of an expander-integrated compressor using a two-stage rotary expander according to Embodiment 2 of the present invention.
- FIG. 5A Cross section along VA-VA section line in Fig. 4
- FIG. 7A is a diagram showing a conventional power recovery refrigeration cycle apparatus.
- FIG. 7B A diagram showing a power recovery type refrigeration cycle apparatus configured to perform conventional injection.
- FIG. 8B Cross section of conventional two-stage rotary expander
- Embodiment 1 of the present invention will be described below with reference to the drawings.
- FIG. 1 is a longitudinal sectional view of an expander-integrated compressor using a one-stage rotary expander according to Embodiment 1 of the present invention
- FIG. 2 is a transverse section taken along the line II-II in FIG. FIG.
- the expander-integrated compressor includes a vertically long sealed container 31. Inside the hermetic container 31, a scroll-type compression mechanism 40 is disposed at the upper position, a rotary-type expansion mechanism 60 is disposed at the lower position, and a rotary motor 32 including a rotor 32a and a stator 32b is disposed therebetween. These are linked by shaft 33.
- the expansion mechanism 60, the shaft 33, and pipes 67A to 67C to be described later constitute a one-stage rotary expander according to Embodiment 1 of the present invention.
- the compression mechanism 40 and the expansion mechanism 60 are configured separately and are connected by the shaft 33 at the time of assembly.
- Carbon dioxide is used as a working fluid described later.
- Oil for lubrication is stored at the bottom of the hermetic container 31, and an oil pump 34 is provided at the lower end of the shaft 33.
- An oil supply passage 35 for supplying oil to the sliding portions of the expansion mechanism 60 and the compression mechanism 40 is formed inside the shaft 33.
- the shaft 33 rotates clockwise in FIG. 2. When the shaft 33 rotates, the oil is pumped up by the oil pump 34 and is supplied to each sliding portion via the oil supply path 35. Used for lubrication and sealing and compression mechanism 40 lubrication and sealing.
- the scroll-type compression mechanism 40 includes a fixed scroll 41, an orbiting scroll 42, an old ring 43, a vehicle bearing 44, a muffler 45, a suction pipe 46, a discharge pipe 47, a force, It is composed of.
- the orbiting scroll 42 fitted to the eccentric portion 33a provided at the upper end of the shaft 33 and restrained by the Oldham's ring 43 has a spiral wrap 42a mating with the wrap 41a of the fixed scroll 41. However, as the shaft 33 rotates, it turns.
- the crescent-shaped working chamber 48 1S formed between the wraps 41a and 42a reduces the volume while moving from the outside to the inside, thereby compressing the working fluid sucked from the suction pipe 46 and fixing the fixed scroll 41
- the air is discharged into the inner space 31a of the sealed container 31 through the inner space 45a of the muffler 45, the flow path 49 provided in the fixed scroll 41 and the bearing member 44 in this order.
- the discharged working fluid is While staying in the internal space 31a, it is separated from the mixed lubricating oil by gravity or centrifugal force, and then discharged from the discharge pipe 47 to the outside of the sealed container 31.
- the rotary type expansion mechanism 60 is provided with a cylinder 61, a piston 62 disposed inside the cylinder 61, an upper bearing member 65 disposed above the cylinder 61, and a lower portion of the cylinder 61.
- a lower bearing member 66 is provided.
- a disc-shaped eccentric portion 33b that is eccentric by a predetermined amount from the axis of the shaft 33 is provided at the lower portion of the shaft 33.
- the upper bearing member 65 is fixed to the sealed container 31 and rotatably supports a portion of the shaft 33 in the vicinity of the upper side of the eccentric portion 33b.
- the lower bearing member 66 is fixed to the upper bearing member 65 via the cylinder 61.
- the upper bearing member 65 has a flat disk-like shape that has a flat lower surface and partitions the inside of the sealed container 31 up and down, and has a through hole through which the shaft 33 is passed in the center.
- the upper bearing member 65 is provided with a flow passage at a suitable position for allowing oil separated from the working fluid to flow downward.
- the lower bearing member 66 has a plate shape having a flat upper surface and lower surface.
- the cylinder 61 has a cylindrical shape having an inner peripheral surface 61b forming a cylindrical surface, an outer peripheral surface in which a part of the cylindrical surface projects outward, and upper and lower end surfaces parallel to each other.
- the cylinder 61 is interposed between the upper bearing member 65 and the lower bearing member 66 so that the center of the inner peripheral surface 61b coincides with the axis of the shaft 33, and the upper end surface of the upper bearing member 65 is The lower end surface is in contact with the upper surface of the lower bearing member 66.
- the piston 62 has a circular ring shape, and is fitted to the eccentric portion 33b of the shaft 33 by fitting so that the piston 62 comes into line contact with the inner peripheral surface 61b of the cylinder 61 and contacts the inner peripheral surface 61b.
- An arcuate working chamber 69 is formed between them, and it can move along the inner peripheral surface 61b while sliding on the inner peripheral surface 61b while rotating eccentrically inside the cylinder 61.
- the thickness of the piston 62 is set to be approximately the same as the thickness of the cylinder 61, the upper end surface of the piston 62 slides on the lower surface of the upper bearing member 65, and the lower end surface of the piston 62 is the lower bearing member 66. It is designed to slide on the top surface.
- the working chamber 69 is closed by the upper bearing member 65 and the lower bearing member 66, and these bearing members 65, 66 are It also serves as a closing member that closes the working chamber 69 with the da 61 interposed therebetween.
- the thickness of the eccentric portion 33b of the shaft 33 is also set to be approximately the same as the thickness of the cylinder 61, the upper surface of the eccentric portion 33b slides on the lower surface of the upper bearing member 65, and the lower surface of the eccentric portion 33b. Slides on the upper surface of the lower bearing member 66.
- the cylinder 61 is provided with a groove 61a extending radially outward from the inner peripheral surface 61b at a position where the outer peripheral surface projects outward.
- a partition member 63 that is fitted in the groove 61a so as to be reciprocally held by the cylinder 61, and a spring 64 that biases the partition member 63.
- the partition member 63 is brought into contact with the piston 62 by being urged by the spring 64, whereby the working chamber 69 is partitioned into the suction side working chamber 69a and the discharge side working chamber 69b! /,
- the partition member 63 is brought into contact with the piston 62 by being urged by the spring 64, whereby the working chamber 69 is partitioned into the suction side working chamber 69a and the discharge side working chamber 69b! /,
- a suction pipe 67A is connected to the upper bearing member 65, and a first passage 65a and a second passage 65b are formed.
- a 180 ° arc-shaped groove 33c is formed on the upper surface of the eccentric portion 33b.
- the first passage 65a, the groove 33c and the second passage 65b form an inflow timing mechanism, and the groove 33c communicates with both the first passage 65a and the second passage 65b as the groove 33c rotates together with the shaft 33.
- the working fluid flows into the suction side working chamber 69a.
- the opening of the first passage 65a is provided at a position forming 90 ° with the partition member 63 with respect to the shaft center of the shaft 33 on the lower surface of the upper bearing member 65
- the second passage 65b is A groove shape extending in the reciprocating direction of the partition member 63 is formed at a position near the partition member 63 on the lower surface of the bearing member 65.
- the groove portion 33c is symmetrical from the axial center of the shaft 33 toward the eccentric direction of the eccentric portion 33c.
- a discharge pipe 67B is connected to the cylinder 61, and a discharge port 61c is formed. These 67B and 61c constitute a discharge path through which the working fluid flows out from the discharge side working chamber 69b.
- the opening of the discharge port 61c is on the inner peripheral surface 61b of the cylinder 61. It is provided in the vicinity of the partition member 63.
- FIG. 3 shows an operation principle diagram of the expansion mechanism 60 at every 90 ° with respect to the rotation angle of the shaft 33. 0.
- the suction stroke in which the groove 33c communicates simultaneously with the first passage 65a and the second passage 65b starts It flows into the suction side working chamber 69a.
- the communication between the groove 33c and the second passage 65b is cut off, and the suction stroke ends.
- the working fluid in the suction side working chamber 69a expands while being depressurized, and the volume of the suction side working chamber 69a increases by 180 ° and 270 °.
- the shaft 33 receives a rotational force as the working fluid expands.
- the suction side working chamber 69a communicates with the discharge port 61c, and the expansion stroke ends.
- the contact point of the piston 62 with respect to the inner peripheral surface 61b of the cylinder 61 passes through the partition member 63, so that the suction side working chamber so far is switched to the discharge side working chamber 69b.
- a suction side working chamber 69a is newly formed.
- the expanded working fluid flows out from the discharge port 61c and the discharge stroke is performed.
- an injection pipe 67C is connected to the upper bearing member 65, and an injection port 65d is formed.
- These 67C and 65d constitute an injection path for further introducing the working fluid into the suction side working chamber 69a during the expansion process of the working fluid (in the middle of the expansion stroke).
- the injection pipe 67C is branched from an unillustrated working fluid supply pipe and a suction pipe 67A, and the injection pipe 67C is provided with a throttle valve 68 whose opening degree can be adjusted.
- the injection port 65d is provided with a backflow prevention valve.
- the opening of the injection port 65d that is, the introduction port 65c with respect to the suction side working chamber 69a of the injection path is closer to the inside (offset) than the inner peripheral surface 61b of the cylinder 61 on the lower surface of the upper bearing member 65.
- the introduction port 65c is provided at a position that forms about 55 ° with the partition member 63 with respect to the axis of the shaft 33. For this reason, in the injection path, the introduction port 65c is opened and closed by the moving piston 62. As a result, only the suction side working chamber 69a can be opened. This prevents communication between the injection path and the discharge path.
- the introduction port 65c is provided immediately before the contact of the piston 62 with the inner peripheral surface 61b of the cylinder 61 is applied to the discharge port 61c (that is, the contact is in the vicinity of the discharge port 61c).
- the piston 62 is completely closed by the upper end surface of the piston 62, and the contact of the piston 62 with respect to the inner peripheral surface 6 lb is gradually opened after rotating about 90 ° from the partition member 63.
- the introduction port 65c is closed by the upper end surface of the piston 62 at least from the start to the end of the discharge stroke, and is opened from the end of the intake stroke to the expansion stroke.
- the injection path is the force that causes the working fluid to flow into the suction-side working chamber 69a via the control valve 8 (throttle valve 68) and the inlet port 65c in the discharge stroke at least in the discharge stroke in this embodiment. Since it is closed, the injection port 65d force, the working fluid force S flowing into the suction side working chamber 69a, and the force that prevents the blowout from the discharge port 61c with a low pressure as it is are controlled.
- the introduction port 65c is provided at a position slightly shifted in the rotational direction of the shaft 33 from the position of Fig. 3, the flow of the working fluid from the suction passage of the suction side working chamber 69a ⁇ is completed.
- the inlet 65c can be opened. In this way, it is possible to prevent high-pressure working fluid from entering the dead space of the injection port 65d (the space to the inlet port 65c and the backflow prevention valve).
- the position of the introduction port 65c need only be within an angle range of 90 ° from the partition member 63 in the rotation direction of the shaft 33 which is not necessarily the position shown in the present embodiment. In such a position, the introduction port 65c can be kept open for a relatively long period in the expansion stroke. A more preferable position of the introduction port 65c is within an angle range of 30 ° or more and 70 ° or less from the partition member 63 in the rotation direction of the shaft 33.
- an injection port 65d is provided in the lower bearing member 66, and the injection port It is also possible to provide the inlet 65c of the channel in a position closer to the inner side than the inner peripheral surface 61b of the cylinder 61 on the upper surface of the lower bearing member 66.
- FIG. 4 is a longitudinal sectional view of an expander-integrated compressor using a two-stage rotary expander according to Embodiment 2 of the present invention
- FIG. 5A is a cross-sectional view taken along the VA—VA sectional line of FIG.
- FIG. 5B is a cross-sectional view taken along the line VB—VB in FIG.
- the expander-integrated compressor according to the second embodiment is the same as the expander-integrated compressor according to the first embodiment except that the expander-compressor is a three-stage rotary type. Are given the same reference numerals and their explanation is omitted.
- the two-stage rotary expansion mechanism 80 includes a first cylinder 81 and a second cylinder 82 that are arranged vertically, a first piston 84 disposed inside the first cylinder 81, and an inner side of the second cylinder 82.
- the second piston 85 disposed, the intermediate plate 83 disposed between the first cylinder 81 and the second cylinder 82, the upper bearing member 90 disposed above the first cylinder 81, and the second cylinder 82 And a lower bearing member 91 disposed below.
- a disc-shaped first eccentric portion 33d and a second eccentric portion 33e that are eccentric by a predetermined amount in the same direction from the axis of the shaft 33 are provided at the lower portion of the shaft 33.
- the upper bearing member 90 is fixed to the sealed container 31 and rotatably supports a portion near the upper side of the first eccentric portion 33d of the shaft 33.
- the lower bearing member 91 includes the first cylinder 81, the middle plate 83, and the like.
- a second cylinder 82 to be fixed to the upper bearing member 90 to rotatably support the lower vicinity of the second eccentric portion 33b of the shaft 33.
- the upper bearing member 90 has a flat disk-like shape that has a flat lower surface and partitions the inside of the sealed container 31 up and down, and has a through hole through which the shaft 33 is passed in the center. Have. Although not shown in the drawing, the upper bearing member 90 is provided with a flow path for flowing down the oil separated from the working fluid in the upper part at an appropriate position.
- the lower bearing member 91 has a plate shape having a flat upper surface and lower surface.
- the middle plate 83 has a plate shape having a flat upper surface and a lower surface, and its thickness is set to be approximately the same as the distance between the first eccentric portion 33d and the second eccentric portion 33e. In the center of the middle plate 83, the second eccentric part 33e is passed during assembly. Through-holes are provided.
- the first cylinder 81 and the second cylinder 82 have inner peripheral surfaces 81b, 82b forming a cylindrical surface, an outer peripheral surface in which a part of the cylindrical surface projects outward, and upper and lower end surfaces parallel to each other. It has a cylindrical shape.
- the thickness of the second cylinder 82 is set larger than the thickness of the first cylinder 81.
- the first cylinder 81 is interposed between the upper bearing member 90 and the middle plate 83 so that the center of the inner peripheral surface 81b coincides with the axis of the shaft 33, and the upper end surface is below the upper bearing member 90.
- the lower end surface is in contact with the upper surface of the intermediate plate 83.
- the second cylinder 82 is interposed between the intermediate plate 83 and the lower bearing member 91 in a state where the center of the inner peripheral surface 82 b coincides with the axis of the shaft 33, and the upper end surface is the lower surface of the intermediate plate 83. The lower end surface is in contact with the upper surface of the lower bearing member 91.
- the first piston 84 and the second piston 85 have a circular ring shape, and are fitted to the eccentric portions 33d and 33e of the shaft 33 by fitting, whereby the inner peripheral surface 81b of the first cylinder 81 is obtained. Or, it makes line contact with the inner peripheral surface 82b of the second cylinder 82 to form arcuate working chambers 94, 95 between the inner peripheral surfaces 81b, 82b, and eccentric rotation inside the cylinders 81, 82. Movement, that is, movement along the inner peripheral surface 8 lb, 82b is possible while sliding on the inner peripheral surface 8 lb, 82b.
- the thicknesses of these pistons 84 and 85 are set to be approximately the same as the thicknesses of the cylinders 81 and 82, and the upper end surfaces of the pistons 84 and 85 slide on the lower surface of the upper bearing member 90 or the middle plate 83, and The lower end surface of the piston 62 slides on the upper surface of the intermediate plate 83 or the lower bearing member 91. That is, the working chamber 94 on the first cylinder 81 side is closed by the upper bearing member 90 and the middle plate 83, and the working chamber 95 on the second cylinder 82 side is closed by the middle plate 83 and the lower bearing member 91.
- the thickness of the eccentric portions 33d and 33e of the shaft 33 is also set to be approximately the same as the thickness of the cylinders 81 and 82, and the upper surface of the eccentric portions 33d and 33e slides on the lower surface of the upper bearing member 90 or the middle plate 83.
- the lower surfaces of the eccentric parts 33d and 33e slide on the upper surface of the intermediate plate 83 or the lower bearing member 91.
- the inner peripheral surfaces 81b and 82b of the first cylinder 81 and the second cylinder 82 have the same diameter, and the first piston 84 and the second piston 85 have the same outer diameter.
- the second By making the thickness of the Linda 82 larger than the thickness of the first cylinder 81, the volume of the working chamber 95 on the second cylinder 82 side is set larger than the volume of the working chamber 94 on the first cylinder 81 side.
- the first cylinder 81 and the second cylinder 82 have the same thickness, and the diameter of the inner peripheral surface 82b of the second cylinder 82 is larger than the diameter of the inner peripheral surface 81b of the first cylinder 81.
- the outer diameter of the second piston 85 may be made smaller than the outer diameter of the first piston 84.
- the first cylinder 81 and the second cylinder 82 are provided with grooves 81a and 82a extending radially outward from the inner peripheral surfaces 81b and 82b at positions where the outer peripheral surfaces protrude outward.
- a first partition member 86 and a second partition member 87 which are held in a reciprocating manner by the cylinders 81 and 82 by being fitted in the cylinders 81a and 82a, and a partition member 86 , 87 and springs 88, 89 for urging.
- An intermediate plate (intermediate closing member) 83 includes a portion near the first partition member 86 of the discharge side working chamber 94b on the first cylinder 81 side and a second partition member 87 of the suction side working chamber 95a on the second cylinder 82 side.
- a communication passage 83a that communicates with the vicinity is provided, and an expansion chamber is configured by these 94b, 83a, and 95a.
- a suction pipe 92 is connected to the upper bearing member 90, and a suction port 90a is formed. These 92 and 90a constitute a suction passage through which the working fluid flows into the discharge side working chamber 94a.
- the opening of the suction port 90a is provided in the vicinity of the first partition member 86 on the lower surface of the upper bearing member 90! /.
- a discharge pipe 93 is connected to the second cylinder 82, and a discharge port 82c is formed. These 93 and 82c constitute a discharge path through which the working fluid flows out from the discharge side working chamber 95b.
- the opening of the discharge port 82 c is provided in the vicinity of the second partition member 87 on the inner peripheral surface 82 b of the second cylinder 82.
- FIG. 6 shows an operation principle diagram of the expansion mechanism 80 at every 90 ° with respect to the rotation angle of the shaft 33. 0 ° (The contact point of the first piston 84 with respect to the inner peripheral surface 81b of the first cylinder 81 is the first partition member. 86), the suction stroke is started, and the working fluid flows from the suction port 90a of the first cylinder 81 into the suction side working chamber 94a. When shaft 33 rotates to 360 °, the suction stroke is completed.
- the shaft 33 receives rotational force due to expansion of the working fluid.
- the contact point of the second piston 85 with the inner circumferential surface 82b of the second cylinder 82 passes through the second partition member 87, so that the suction side working chamber on the second cylinder 82 side is operated on the discharge side.
- the chamber 95b is switched to, and a suction side working chamber 95a is newly formed between the contact point and the second partition member 87.
- the expanded working fluid is caused to flow out of the discharge port 82c, and a discharge stroke is performed.
- the lower bearing member 91 is connected to the injection pipe 96 and is formed with an injection port 91b.
- These 96 and 91b constitute an injection path for further introducing the working fluid into the suction side working chamber 95a on the second cylinder 82 side during the expansion process of the working fluid.
- the injection pipe 96 is branched from an unillustrated working fluid supply pipe and a suction pipe 92, and the injection pipe 96 is provided with a throttle valve 68 whose opening degree can be adjusted.
- the injection port 91b is provided with a backflow prevention valve.
- the opening of the injection port 91b that is, the introduction port 91a with respect to the suction side working chamber 95a of the injection path is closer to the inner side than the inner peripheral surface 82b of the second cylinder 82 on the upper surface of the lower bearing member 91 ( (Offset) position. More specifically, the introduction port 91a is provided at a position that forms about 50 ° with the second partition member 87 with respect to the axis of the shaft 33. For this reason, the injection path can be opened only to the suction side working chamber 95a by opening and closing the introduction port 91a by the moving second piston 85. This Communication between the injection path and the discharge path is prevented.
- the introduction port 91a is provided immediately before the contact point of the second piston 85 with respect to the inner peripheral surface 82b of the second cylinder 82 is applied to the discharge port 82c (that is, the contact point) Was completely closed by the lower end surface of the second piston 85 when the nozzle reached the vicinity of the discharge port 82c), and the contact point of the second piston 85 with respect to the inner peripheral surface 82b was rotated about 90 ° from the second partition member 87. It will be gradually opened later.
- the introduction port 91a is closed by the lower end surface of the second piston 85 at least from the start to the end of the discharge stroke, and is opened shortly after the start of the expansion stroke and just before the end. As in FIG.
- the injection path allows the working fluid to flow into the suction-side working chamber 95a on the second cylinder 82 side via the control valve 8 (throttle valve 68), even though V in this embodiment. Is closed by the second piston 85 at least in the discharge stroke, so that it is possible to prevent the working fluid flowing into the suction side working chamber 95a from the injection port 91b from being blown into the discharge port 82c having a low pressure. S can.
- the position of the introduction port 91a need only be within an angle range of 90 ° from the second partition member 87 in the rotational direction of the shaft 33 which is not necessarily the position shown in the present embodiment. In such a position, the inlet 91a can be kept open for a relatively long period in the expansion stroke.
- a more preferable position of the introduction port 91a is within an angle range of 30 ° or more and 70 ° or less from the second partition member 87 in the rotation direction of the shaft 33.
- the injection path 91a is opened and closed by the moving second piston 85 or the first piston 84 so that the injection path is opened. It suffices if it is provided at a position where it can be opened only in the expansion chamber.
- the injection port 91b may be provided in the upper closing member 90.
- the inlet 91 a is provided at a position within an angle range of 90 ° from the first partition member 86 in the rotational direction of the shaft 33 on the lower surface of the upper closing member 90, and is formed by the upper end surface of the first piston 84. To be opened and closed.
- the injection port 91 b is provided in the lower bearing member 91 as in the present embodiment, the working fluid can be introduced in the latter half of the expansion stroke. Further, since the pressure in the suction side working chamber 95a on the second cylinder 82 side is smaller than the pressure in the discharge side working chamber 94b on the first cylinder 81 side, the introduction port 91a is provided in the upper bearing member 90. However, if the lower bearing member 91 is provided, more working fluid can be introduced into the expansion chamber. Therefore, according to the two-stage rotary expander of the present embodiment, it is possible to secure a wide adjustment range of the injection amount and increase the variable range of the density ratio, and to perform optimum pressure temperature control over a wide range of environmental temperatures. It becomes like this.
- the adjustment valve 8 is a valve that cannot be controlled in accordance with the rotation cycle of the shaft 33, for example, a throttle valve 68 that only adjusts the opening degree to control the flow rate of the working fluid
- the adjustment valve 8 Since the valve 8 is always maintained at a constant opening, it was not possible to prevent the working fluid from being blown from the injection ports 65d, 91b to the discharge ports 61c, 82c, but the rotary expander of the present invention If is used, the effect of preventing the working fluid from blowing through is remarkable.
- the regulating valve 8 is an electromagnetic valve that can be controlled to open and close in accordance with the rotation cycle of the shaft 33, the regulating valve 8 is opened during the suction process or the expansion process, and the regulating valve 8 is closed immediately before the discharge stroke. By performing the control, it is possible to prevent the working fluid from being blown from the injection ports 65d and 91b of the present invention to the discharge ports 61c and 82c.
- the main object of the present invention is to be applied to an expander of an expander-integrated compressor in which injection is performed in order to avoid the restriction of a constant density ratio, but injection is performed.
- the present invention can also be applied to a single expander.
- Embodiments 1 and 2 the description has been given using the expansion mechanism 60, 80 of the rotor piston type, but the expansion mechanism is a one-stage or two-stage structure in which the partition member and the piston are integrally formed. It goes without saying that the same effect can be obtained by replacing the swing type.
- the expander of the present invention is useful as power recovery means for recovering the expansion energy of the working fluid in the refrigeration cycle.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07807772.4A EP2072753B1 (en) | 2006-10-11 | 2007-09-21 | Rotary expander |
CN2007800309193A CN101506471B (zh) | 2006-10-11 | 2007-09-21 | 旋转式膨胀机 |
JP2008538619A JP4806027B2 (ja) | 2006-10-11 | 2007-09-21 | ロータリ式膨張機 |
US12/376,349 US8172558B2 (en) | 2006-10-11 | 2007-09-21 | Rotary expander with discharge and introduction passages for working fluid |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006277531 | 2006-10-11 | ||
JP2006-277531 | 2006-10-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008044456A1 true WO2008044456A1 (en) | 2008-04-17 |
Family
ID=39282661
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/068441 WO2008044456A1 (en) | 2006-10-11 | 2007-09-21 | Rotary expander |
Country Status (5)
Country | Link |
---|---|
US (1) | US8172558B2 (ja) |
EP (2) | EP3176364A1 (ja) |
JP (1) | JP4806027B2 (ja) |
CN (1) | CN101506471B (ja) |
WO (1) | WO2008044456A1 (ja) |
Cited By (3)
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JP2016118212A (ja) * | 2016-03-28 | 2016-06-30 | 三菱重工業株式会社 | 流体機械 |
JP2016538455A (ja) * | 2013-10-28 | 2016-12-08 | グリー グリーン リフリジレーション テクノロジー センター カンパニー リミテッド オブ ズーハイGree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | 膨張圧縮機装置及びそれを備えるエアコン |
CN112551473A (zh) * | 2020-12-28 | 2021-03-26 | 牡丹江师范学院 | 卸油扫仓抽送装置 |
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CN112554957B (zh) * | 2020-11-13 | 2022-01-28 | 珠海格力节能环保制冷技术研究中心有限公司 | 一种铰接式膨胀机吸气装置 |
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- 2007-09-21 WO PCT/JP2007/068441 patent/WO2008044456A1/ja active Application Filing
- 2007-09-21 CN CN2007800309193A patent/CN101506471B/zh not_active Expired - Fee Related
- 2007-09-21 EP EP16198574.2A patent/EP3176364A1/en not_active Withdrawn
- 2007-09-21 EP EP07807772.4A patent/EP2072753B1/en not_active Expired - Fee Related
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JP2016538455A (ja) * | 2013-10-28 | 2016-12-08 | グリー グリーン リフリジレーション テクノロジー センター カンパニー リミテッド オブ ズーハイGree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | 膨張圧縮機装置及びそれを備えるエアコン |
JP2016118212A (ja) * | 2016-03-28 | 2016-06-30 | 三菱重工業株式会社 | 流体機械 |
CN112551473A (zh) * | 2020-12-28 | 2021-03-26 | 牡丹江师范学院 | 卸油扫仓抽送装置 |
CN112551473B (zh) * | 2020-12-28 | 2023-05-09 | 牡丹江师范学院 | 卸油扫仓抽送装置 |
Also Published As
Publication number | Publication date |
---|---|
CN101506471A (zh) | 2009-08-12 |
JP4806027B2 (ja) | 2011-11-02 |
JPWO2008044456A1 (ja) | 2010-02-04 |
EP3176364A1 (en) | 2017-06-07 |
EP2072753B1 (en) | 2018-02-14 |
EP2072753A1 (en) | 2009-06-24 |
US20100158729A1 (en) | 2010-06-24 |
US8172558B2 (en) | 2012-05-08 |
EP2072753A4 (en) | 2010-10-27 |
CN101506471B (zh) | 2011-06-15 |
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