EP2241719A1 - Expander-integrated compressor and refrigeration cycle device using the same - Google Patents
Expander-integrated compressor and refrigeration cycle device using the same Download PDFInfo
- Publication number
- EP2241719A1 EP2241719A1 EP09705176A EP09705176A EP2241719A1 EP 2241719 A1 EP2241719 A1 EP 2241719A1 EP 09705176 A EP09705176 A EP 09705176A EP 09705176 A EP09705176 A EP 09705176A EP 2241719 A1 EP2241719 A1 EP 2241719A1
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- EP
- European Patent Office
- Prior art keywords
- oil
- shaft
- oil supply
- expander
- expansion mechanism
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- 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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
- F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
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- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
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- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
Definitions
- the present invention relates to an expander-integrated compressor and a refrigeration cycle apparatus using the same.
- FIG. 11 is a vertical cross-sectional view illustrating a typical expander-integrated compressor.
- An expander-integrated compressor 200 has a two-stage rotary type compression mechanism 121, a motor 122, a two-stage rotary type expansion mechanism 123, and a closed casing 120 that accommodates them.
- the compression mechanism 121, the motor 122, and the expansion mechanism 123 are coupled to each other by a shaft 124.
- a bottom part of the closed casing 120 forms an oil reservoir 125 for holding oil (refrigeration oil).
- An oil pump 126 is fitted to a lower end portion of the shaft 124 in order to pump up the oil held in the oil reservoir 125.
- the oil pumped up by the oil pump 126 is supplied to the compression mechanism 121 and the expansion mechanism 123 via an oil supply passage 127 formed in the shaft 124. Thereby, lubricity and sealing of the sliding parts of the compression mechanism 121 and the expansion mechanism 123 are ensured.
- An oil return pipe 128 is disposed in an upper part of the expansion mechanism 123.
- One end of the oil return pipe 128 communicates with the oil supply passage 127 formed in the shaft 124, while the other end opens below the expansion mechanism 123.
- the oil is supplied excessively in order to ensure the reliability of the expansion mechanism 123.
- the excess oil is returned via the oil return pipe 128 to the oil reservoir 125.
- the oil pumped up from the oil reservoir 125 is heated by the compression mechanism 121 because it passes through the compression mechanism 121 that is at a high temperature.
- the oil heated by the compression mechanism 121 is heated further by the motor 122, and it reaches the expansion mechanism 123.
- the oil having reached the expansion mechanism 123 is cooled by the expansion mechanism 123 that is at a low temperature, and is thereafter discharged below the expansion mechanism 123 via the oil return pipe 128.
- the oil discharged from the expansion mechanism 123 and the oil return pipe 128 is heated again when passing along a side face of the motor 122 and is also heated when passing along a side face of the compression mechanism 121.
- the oil then returns to the oil reservoir 125 of the closed casing 120.
- the oil circulation between the compression mechanism 121 and the expansion mechanism 123 causes heat transfer from the compression mechanism 121 to the expansion mechanism 123.
- Such heat transfer lowers the temperature of the refrigerant discharged from the compression mechanism 121, and elevates the temperature of the refrigerant discharged from the expansion mechanism 123.
- this means a decrease of indoor heating capacity during heating, or a decrease of indoor cooling capacity during cooling.
- the present invention has been accomplished in view of the foregoing circumstances, and it is an object of the invention to reduce the heat transfer from the compression mechanism to the expansion mechanism.
- an expander-integrated compressor including:
- the present invention provides a refrigeration cycle apparatus including:
- the present invention provides an expander-integrated compressor including:
- the above-described expander-integrated compressor of the present invention is provided with the oil supply amount regulating mechanism. Therefore, an appropriate amount of oil can be supplied to the compression mechanism or the expansion mechanism regardless of the rotation speed of the shaft. As a result, it is possible to reduce the heat transfer from the compression mechanism to the expansion mechanism that results from the oil circulation.
- FIG. 1 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a first embodiment of the present invention.
- An expander-integrated compressor 100A has a closed casing 1, a compression mechanism 2, an expansion mechanism 3, a motor 4, a shaft 5, an oil pump 6, and an oil supply amount regulating mechanism 30.
- the compression mechanism 2 is disposed in a lower part of the closed casing 1.
- the expansion mechanism 3 is disposed in an upper part of the closed casing 1.
- the motor 4 is disposed between the compression mechanism 2 and the expansion mechanism 3.
- the compression mechanism 2, the motor 4, and the expansion mechanism 3 are coupled to each other by the shaft 5 so that mechanical power can be transmitted.
- the oil pump 6 is provided at a lower portion of the shaft 5.
- the oil supply amount regulating mechanism 30 is for regulating the amount of the oil to be supplied to the expansion mechanism 3.
- a regulating valve typically a needle valve
- the motor 4 drives the shaft 5 to operate the compression mechanism 2.
- the expansion mechanism 3 recovers mechanical power from the expanding working fluid, and supplies the mechanical power to the shaft 5 to assist the motor 4 to drive the shaft 5.
- the working fluid is, for example, a refrigerant such as carbon dioxide and hydrofluorocarbon.
- the arrangement of the compression mechanism 2, the motor 4, and the expansion mechanism 3 is determined in such a manner that the axis direction of the shaft 5 is in agreement with the vertical direction.
- the positional relationship between the compression mechanism 2 and the expansion mechanism 3 may be opposite of that in the present embodiment.
- the compression mechanism 2 may be disposed in an upper part of the closed casing 1
- the expansion mechanism 3 may be disposed in a lower part of the closed casing 1.
- the closed casing 1 has an interior space 24 for accommodating various components.
- the interior space 24 of the closed casing 1 is filled with the refrigerant compressed by the compression mechanism 2.
- a bottom portion of the closed casing 1 is utilized as an oil reservoir 25.
- the oil is used for ensuring lubrication and sealing on the sliding parts of the compression mechanism 2 and the expansion mechanism 3.
- the amount of the oil in the oil reservoir 25 is controlled so that the oil level is below the motor 4. This prevents a decrease of the efficiency of the motor and an increase of the oil discharge amount to the refrigerant circuit, which result from the agitation of the oil by the rotor of the motor 4. Since the temperature of the compression mechanism 2 becomes high during operation of the expander-integrated compressor 100A, the temperature of the oil held in the oil reservoir 25 becomes accordingly high.
- the compression mechanism 2 has cylinders 17 and 18, pistons 7 and 8, and bearing members 10 and 11, and it has the same structure as that of the conventional two-stage rotary compressor.
- a suction pipe 13 is connected to the cylinder 17, and a suction pipe 14 is connected to the cylinder 18.
- the refrigerant is guided to compression chambers 19 and 20, formed in the respective cylinders 17 and 18, through the suction pipes 13 and 14.
- the refrigerant compressed in the compression chambers 19 and 20 is discharged to the interior space 24 of the closed casing 19.
- a discharge pipe 15 is connected to the closed casing 1 so that an opening thereof is located between the motor 4 and the expansion mechanism 3.
- the refrigerant discharged to the interior space 24 flows upward through a region surrounding the motor 4.
- the refrigerant is then guided through the discharge pipe 15 to a flow passage outside the closed casing 1. At that time, the refrigerant and the oil can be separated from each other by a gravitational force or a centrifugal force.
- a rotary-type fluid mechanism is employed as the compression mechanism 2.
- the "rotary type” includes not only a rolling piston type, in which a vane slides along the outer circumferential surface of a piston, and a sliding vane type, in which a vane slides along the inner circumferential surface of a cylinder, but also a swing piston type, in which a piston and a vane are integrally formed.
- the type of the compression mechanism 2 is not limited to the rotary type. It is also possible to employ other types of fluid mechanisms, such as a scroll type, a reciprocating type, and a screw type, as the compression mechanism 2. The same applies to the later-described expansion mechanism 3.
- the motor 4 has a stator 21 fixed to the closed casing 1 and a rotor 22 fixed to the shaft 5. Electric power is supplied to the motor 4 through a terminal (not shown) disposed at the top of the closed casing 1.
- An oil supply passage 29 communicating with sliding parts of the expansion mechanism 3 is formed in the shaft 5 so as to extend in the axis direction. This is desirable because, when forming the oil supply passage 29 inside the shaft 5, the problems associated with an increase in the parts count and parts layout do not arise.
- the oil is supplied to sliding parts of the expansion mechanism 3 through the oil supply passage 29.
- the oil supply passage 29 does not open in the upper end face of the shaft 5. In this way, the oil does not flow out over the expansion mechanism 3, unlike the conventional example described with reference to Fig. 11 . Thereby, the oil is less easily cooled by the expansion mechanism 3. In other words, the heat transfer from the compression mechanism 2 to the expansion mechanism 3 can be reduced more effectively.
- the oil supply passage 29 may open in the upper end face of the shaft 5.
- the shaft 5 may be made of a single component, or may be made by combining (coupling) a plurality of components together.
- the shaft 5 may include a first shaft on the compression mechanism 2 side and a second shaft on the expansion mechanism 3 side.
- the first shaft and the second shaft may be coupled directly by fitting them onto each other, or may be coupled to each other via another component (coupler).
- the expansion mechanism 3 has a first cylinder 42, a second cylinder 44 having an inner diameter larger than the inner diameter of the first cylinder 42, an intermediate plate 43 partitioning the first cylinder 42 and the second cylinder 44.
- the first cylinder 42 and the second cylinder 44 are disposed concentrically with each other.
- the expansion mechanism 3 further has a first piston 46, a first vane 48, a first spring 50, a second piston 47, a second vane 49, and a second spring 51.
- the first piston 46 is fitted with an eccentric portion 5c of the shaft 5, and it performs eccentric rotational motion in the first cylinder 42.
- the first vane 48 is retained reciprocably in a vane groove 42a formed in the first cylinder 42.
- One end of the first vane 48 is in contact with the first piston 46.
- the first spring 50 is in contact with the other end of the first vane 48, and biases the first vane 48 toward the first piston 46.
- the second piston 47 is fitted with an eccentric portion 5d of the shaft 5, and it performs eccentric rotational motion in the second cylinder 44.
- the second vane 49 is retained reciprocably in a vane groove 44a formed in the second cylinder 44.
- One end of the second vane 49 is in contact with the second piston 47.
- the second spring 51 is in contact with the other end of the second vane 49, and biases the second vane 49 toward the second piston 47.
- the expansion mechanism 3 further has a bearing member 45 and a bearing member 41.
- the bearing member 41 is fitted to the closed casing 1 with no clearance between them.
- the components such as the cylinders and the intermediate plate are fixed to the closed casing 1 via the bearing member 41.
- the bearing member 41 and the intermediate plate 43 sandwiches the first cylinder 42 from the top and bottom, and the intermediate plate 43 and the bearing member 45 sandwiches the second cylinder 44 from the top and bottom. Sandwiching the bearing member 45, the intermediate plate 43, and the bearing member 41 forms working chambers 55 and 56 in the first cylinder 42 and the second cylinder 44, respectively.
- a suction-side working chamber 55a (first suction-side space) and a discharge-side working chamber 55b (first discharge-side space) are formed inside the first cylinder 42.
- the working chamber 55a and the working chamber 55b are partitioned by the first piston 46 and the first vane 48.
- a suction-side working chamber 56a (second suction-side space) and a discharge-side working chamber 56b (second discharge-side space) are formed inside the second cylinder 44.
- the working chamber 56a and the working chamber 56b are partitioned by the second piston 47 and the second vane 49.
- the total volumetric capacity of the two working chambers 56a and 56b in the second cylinder 44 is greater than the total volumetric capacity of the two working chambers 55a and 55b in the first cylinder 42.
- the discharge-side working chamber 55b of the first cylinder 42 and the suction-side working chamber 56a of the second cylinder 44 are brought into communication with each other through a through hole 43a formed in the intermediate plate 43, so that they can function as a single working chamber (an expansion chamber).
- the method for making the total volumetric capacity of the working chambers 56a and 56b greater than the total volumetric capacity of the working chambers 55a and 55b is not limited to the method of varying the inner diameters of the first cylinder 42 and the second cylinder 44. It is also possible to employ the method of appropriately setting the thicknesses of the cylinders 42 and 44 or the outer diameters of the pistons 46 and 47.
- the expansion mechanism 3 further has a suction pipe 52 serving as a suction passage for directly drawing the refrigerant that has not yet been expanded from a flow passage external to the closed casing 1, and a discharge pipe 53 serving as a discharge passage for directly discharging the refrigerant that has been expanded to a flow passage external to the closed casing 1.
- the suction pipe 52 is directly inserted in the first cylinder 42 so that the refrigerant can be guided from the flow passage external to the closed casing 1 to the working chamber 55 of the first cylinder 42.
- the discharge pipe 53 is directly inserted in the second cylinder 44 so that the refrigerant can be guided from the working chamber 56 of the second cylinder 44 to the flow passage external to the closed casing 1.
- the suction pipe 52 may be inserted in the bearing member 41, and the discharge pipe 53 may be inserted in the bearing member 45.
- the refrigerant that has not yet been expanded passes through the suction pipe 52 and flows into the working chamber 55a of the first cylinder 42.
- the working fluid having flowed into the working chamber 55a of the first cylinder 42 moves to the working chamber 55b in association with rotation of the shaft 5, and it expands and reduces its pressure in the expansion chamber formed by the working chamber 55b, the through hole 43a, and the working chamber 56a, while rotating the shaft 5.
- the refrigerant having expanded is guided to the outside of the closed casing 1 through the working chamber 56b and the discharge pipe 53.
- the location at which the oil pump 6 is provided is a lower portion of the shaft 5. Specifically, the oil pump 6 is disposed in the oil supply passage 29 in a lower portion of the shaft 5. Disposing the oil pump 6 in the oil supply passage 29 eliminates the need to provide an oil supply pipe separately.
- the oil pump 6 is operated by the mechanical power supplied from the shaft 5.
- a velocity type pump turbine pump
- the oil pump 6 has a pump blade 6a and a blade stopper 6b.
- the pump blade 6a is fixed to the shaft 5 by the blade stopper 6b.
- Rotation of the pump blade 6a together with the shaft 5 causes the oil to be pumped upward.
- the rotation speed of the oil pump 6 is equal to the rotation speed of the shaft 5. Therefore, as the rotation speed of the shaft 5 increases, the delivery capacity and delivery pressure of the oil pump 6 increases accordingly.
- the effectiveness of the oil supply amount regulating mechanism 30 increases as the delivery pressure of the oil pump 6 increases, the amount of the oil to be supplied to the expansion mechanism 3 is not proportional to the rotation speed of the shaft 5.
- the type of the oil pump is not limited to the velocity type pump, and a positive displacement pump may be used.
- the positive displacement pump include a rotary type oil pump and a TROCHOID pump (registered trademark of Nippon Oil Pump Co., Ltd.).
- the velocity type pump is better suited for the oil supply amount regulating mechanism 30 in the present embodiment than the positive displacement pump. The reason is that no oil escape route is provided in the present embodiment, as it is provided in the later-described second and third embodiments.
- the oil supply amount regulating mechanism 30 includes a structure for preventing the amount of the oil to be supplied to the expansion mechanism 3 through the oil supply passage 29 from increasing correspondingly to an increase of the rotation speed of the shaft 5. As described previously, it is important to reduce the heat transfer from the compression mechanism 2 to the expansion mechanism 3 resulting from the oil circulation as much as possible, in order to improve the efficiency of a refrigeration cycle apparatus (see Fig. 10 ) using the expander-integrated compressor 100A. When the rotation speed of the shaft 5 increases, the delivery capacity and delivery pressure of the oil pump 6 tend to increase. However, excessive supply of the oil is prevented by the workings of the oil supply amount regulating mechanism 30. In some cases, the oil supply amount to the expansion mechanism 3 can be maintained at almost a constant level regardless of the rotation speed of the shaft 5. As a result, it is possible to reduce the heat transfer from the compression mechanism 2 to the expansion mechanism 3 that results from the oil circulation.
- the oil supply amount regulating mechanism 30 is provided in the oil supply passage 29. For this reason, it is unnecessary to provide a dedicated space for the oil supply amount regulating mechanism 30.
- the location at which the oil supply amount regulating mechanism 30 should be provided may be below the expansion mechanism 3, which is located in the upper part of the closed casing 1.
- the oil supply amount regulating mechanism 30 is provided between the working chamber 20 of the compression mechanism 2 and the motor 4 with respect to the axis direction of the shaft 5.
- Fig. 3 is a partially enlarged view of Fig. 1 .
- the oil supply amount regulating mechanism 30 has a valve seat 31, a needle 32 (valve body), a spring 33, and a needle stopper 34.
- the valve seat 31 has an orifice shape whose inner diameter decreases toward the expansion mechanism 3.
- the needle 32 is disposed so as to face the valve seat 31.
- the needle 32 has a leading end portion in a circular conic shape.
- the spring 33 is disposed between the valve seat 31 and the needle 32 so that a gap through which the oil can flow is formed between the valve seat 31 and the needle 32.
- the spring 33 expands and contracts according to a pressure change of the oil in the oil supply passage 29, so that the gap between the valve seat 31 and the needle 32 can be adjusted.
- the needle stopper 34 for defining the range of motion of the needle 32 is disposed opposite the valve seat 31 across the needle 32.
- the valve seat 31 or the needle stopper 34 may be formed by a portion of the shaft 5.
- the oil to be supplied to the expansion mechanism 3 flows through the oil supply passage 29 and hits the back face of the needle 32. Thereafter, the oil passes through the surrounding region of the needle 32 and flows toward the valve seat 31. The oil hitting the back face of the needle 32 presses the needle 32 toward the valve seat 31 with a force corresponding to the flow rate of the oil. The needle 32 is pushed back with a force in proportion to the displacement of the spring 33. Specifically, the area of the gap between the valve seat 31 and the needle 32 (the cross-sectional area of the gap) changes according to the flow rate of the oil.
- the effect of optimizing the oil supply amount can be obtained by providing only the valve seat 31 in the oil supply passage 29. That is, by merely providing an orifice in the oil supply passage 29, the oil can be prevented from being excessively supplied to the expansion mechanism 3 because the pressure loss at the orifice increases proportionally to an increase of the oil flow rate.
- the oil of the oil supply passage 29 is supplied only to the expansion mechanism 3.
- the oil of the oil supply passage 29 may also be supplied to the compression mechanism 2.
- Fig. 5 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a second embodiment of the present invention. As illustrated in Fig. 5 , a main difference between an expander-integrated compressor 100B of the present embodiment and the expander-integrated compressor 100A of the first embodiment is in the oil supply amount regulating mechanism.
- the same parts as those in the embodiment shown in Fig. 1 will be designated by the same reference numerals, and the descriptions thereof will be omitted.
- Fig. 6 is a partially enlarged view of Fig. 5 .
- a branch passage 29s branching in a radial direction from the oil supply passage 29 and opening in an outer circumferential surface of the shaft5 is formed in the shaft 5.
- An oil supply amount regulating mechanism 60 is provided in the branch passage 29s. In this way, mounting of the oil supply amount regulating mechanism 60 is possible from the outside of the shaft 5, so assembling is easier than that in the first embodiment.
- this is suitable also in the case where the oil pump is a positive displacement pump because the branch passage 29s behaves as an oil escape route.
- the oil supply amount regulating mechanism 60 has a valve seat 61, a needle 62, a spring 63, and a needle stopper 64.
- the valve seat 61 has an orifice shape whose inner diameter decreases toward the oil supply passage 29.
- the valve seat 61 is disposed at a portion of the branch passage 29s that faces the oil supply passage 29.
- the needle 62 in a circular conic shape is disposed so as to face the valve seat 61.
- the needle 62 is displaceable in a direction toward the valve seat 61 and a direction away from the valve seat 61 (radial directions of the shaft 5).
- the needle stopper 64 is disposed at a portion of the branch passage 29s that faces an outside of the shaft 5.
- the needle stopper 64 defines the range of motion of the needle 62.
- the spring 63 is disposed between the needle 62 and the needle stopper 64.
- a bearing member 10 has a bearing portion 10a that supports the shaft 5.
- the bearing portion 10a covers an outer circumferential surface of the shaft 5 at a location where the branch passage 29s is formed.
- a circular chamber 67 is formed in an inner circumferential surface of the bearing portion 10a.
- the branch passage 29s opens toward the chamber 67.
- An oil discharge passage 66 for connecting the chamber 67 and the interior space 24 of the closed casing 1 is further formed in the bearing portion 10a so as to penetrate through the bearing portion 10a in a radial direction.
- the closed state refers to a state in which the branch passage 29s is closed by the needle 62 being fitted into the valve seat 61. In the closed state, the oil cannot flow through the branch passage 29s.
- the oil supply amount regulating mechanism 60 is brought to an open state.
- the open state refers to a state in which the needle 62 is detached from the valve seat 61 so that a gap is formed between the valve seat 61 and the needle 62. In the open state, the oil can flow through the branch passage 29s.
- the oil supply amount regulating mechanism 60 switches from the closed state to the open state.
- the oil supply amount regulating mechanism 60 is constructed by a relief valve.
- the oil is allowed to escape to the outside of the shaft 5 through the branch passage 29s.
- the oil supply amount regulating mechanism 60 is brought into the open state, a difference in the flow rate of the oil in the oil supply passage 29 arises between the positions before and after the oil supply amount regulating mechanism 60.
- the flow rate is high between the oil supply amount regulating mechanism 60 and the oil pump 6, and the flow rate is low between the expansion mechanism 3 and the oil supply amount regulating mechanism 60.
- the portion at which the flow rate of the oil is high be farther away from the expansion mechanism 3, from the view point of reducing the heat transfer from the compression mechanism 2 to the expansion mechanism 3 that results from the oil circulation. Therefore, it is desirable that the branch passage 29s be formed in a portion of the shaft 5 that is between the motor 4 and the compression mechanism 2.
- Fig. 7 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a third embodiment of the present invention. As illustrated in Fig. 7 , a main difference between an expander-integrated compressor 100C of the present embodiment and the expander-integrated compressor 100A of the first embodiment is in the oil supply amount regulating mechanism.
- Fig. 8 is a partially enlarged view of Fig. 7 .
- a branch passage 29t branching in a radial direction from the oil supply passage 29 and opening in an outer circumferential surface of the shaft 5 is formed in the shaft 5.
- An oil supply amount regulating mechanism 70 is provided exteriorly of the shaft so that the oil is guided to the interior space 24 of the closed casing 1 through the branch passage 29t. Since the oil supply amount regulating mechanism 70 is provided exteriorly of the shaft 5, a larger space than is available in the preceding two embodiments can be ensured for the oil supply amount regulating mechanism 70.
- the present embodiment is similar to the second embodiment in the respect that the branch passage 29t is formed in the shaft 5 as an oil escape route.
- the present embodiment is different from the second embodiment in the respect that the oil supply amount regulating mechanism 70 does not rotate together with the shaft 5. This is suitable also in the case where the oil pump is a positive displacement pump because the branch passage 29t behaves as an oil escape route.
- the oil supply amount regulating mechanism 70 is provided inside the bearing member 10.
- the bearing member 10 has the bearing portion 10a that supports the shaft 5.
- the bearing portion 10a covers an outer circumferential surface of the shaft 5 at a location where the branch passage 29t is formed.
- a circular chamber 77 is formed in an inner circumferential surface of the bearing portion 10a.
- the branch passage 29t opens toward the chamber 77.
- An oil discharge passage 76 is further formed in the bearing portion 10a, as a passage for connecting the chamber 77 and the interior space 24 of the closed casing 1.
- the oil supply amount regulating mechanism 70 is provided in the oil discharge passage 76.
- the oil supply amount regulating mechanism 70 has a valve seat 71, a valve body 72, a spring 73, and a valve body stopper 74.
- the oil discharge passage 76 includes a portion having a T-shaped cross-sectional shape along the flow direction of the oil.
- the valve seat 71 is disposed in the T-shaped portion.
- the valve body 72 in a spherical shape is disposed so as to face the valve seat 71.
- the valve body stopper 74 is disposed opposite the valve seat 71 across the valve body 72.
- the valve body stopper 74 defines the range of motion of the valve body 72.
- the spring 73 is disposed between the valve body 72 and the valve body stopper 74. It should be noted that the structure of the oil supply amount regulating mechanism 70 may be the same as that in the second embodiment.
- the closed state refers to a state in which the oil discharge passage 76 is closed by the valve body 72 being fitted into the valve seat 71. In the closed state, the oil cannot flow through the oil discharge passage 76.
- the oil supply amount regulating mechanism 70 is brought to an open state.
- the open state refers to a state in which the valve body 72 is detached from the valve seat 71 so that a gap is formed between the valve seat 71 and the valve body 72. In the open state, the oil can flow through the oil discharge passage 76.
- the oil displaces the valve body 72, causing the oil discharge passage 76 to open.
- the force of the oil that displaces the valve body 72 is proportional to the internal pressure of the oil supply passage 29.
- the oil supply amount regulating mechanism 70 is constructed by a relief valve.
- the oil supply amount regulating mechanism 70 may be disposed at an outlet of the oil discharge passage 76, or may be disposed in the chamber 77.
- the oil is allowed to escape to the outside of the shaft 5 through the branch passage 29t. Therefore, it is desirable that the branch passage 29t be formed in a portion of the shaft 5 that is between the motor 4 and the compression mechanism 2, which is located in the lower part of the closed casing 1.
- the axis direction of the shaft 5 is parallel to the horizontal direction, as illustrated in Fig. 9 .
- the oil reservoir 25 is formed along the longitudinal direction of the closed casing 1.
- a partition wall 27 is provided between the expansion mechanism 3 and the motor 4.
- the partition wall 27 divides the interior space 24 into a space on the expansion mechanism 3 side and a space on the compression mechanism 2 side.
- the motor 4 is disposed also in the space on the compression mechanism 2 side.
- This partition wall 27 also has the function to reduce the heat transfer from the compression mechanism 2 and the motor 4 to the expansion mechanism 3.
- the partition wall 27 has a passage 27h allowing the oil to flow therethrough.
- a positive displacement-type the oil pump 26 is provided at an end portion of the shaft 5.
- the oil pump 26, the expansion mechanism 3, the motor 4, and the compression mechanism 2 are arrayed in that order along the axis direction of the shaft 5.
- the oil supply amount regulating mechanism 60 is the same one as described with reference to Fig. 6 in the third embodiment.
- a nozzle 26k of the oil pump 26 extends toward the oil reservoir 25 so that it can draw the oil in the oil reservoir 25.
- the oil drawn by the oil pump 26 is supplied through the oil supply passage 29 to the compression mechanism 2 located in the far side, viewed from the oil pump 26, with respect to the axis direction the shaft 5.
- the oil from the oil pump 26 is also supplied to the expansion mechanism 3, which is located on the near side, viewed from the oil pump 26.
- the oil discharged from the oil supply passage 29 through the oil supply amount regulating mechanism 60 returns to the space on the expansion mechanism 3 side.
- the oil supply amount regulating mechanism 60 prevents excessive supply of the oil. Thereby, the heat transfer from the compression mechanism 2 to the expansion mechanism 3 is suppressed.
- the oil pump 26 is provided in the expansion mechanism 3 side. However, it is possible to provide the oil pump 26 in the compression mechanism 2 side. It is also possible to provide the oil supply amount regulating mechanism 30 (first embodiment) or the oil supply amount regulating mechanism 70 (third embodiment), in place of the oil supply amount regulating mechanism 60.
- a refrigeration cycle apparatus 110 includes: an expander-integrated compressor 100A (, 100B, 100C, or 100D); a radiator 101 for cooling the refrigerant compressed by the compression mechanism 2; and an evaporator 114 for evaporating the refrigerant expanded by the expansion mechanism 3.
- the compression mechanism 2, the radiator 101, the expansion mechanism 3, and the evaporator 102 are connected by pipes, to form a refrigerant circuit.
- refrigeration cycle apparatus 110 when refrigeration cycle apparatus 110 is applied to an air conditioner, it is possible to prevent a decrease in heating capacity caused by a decreased discharge temperature of the compression mechanism 2 during heating operation, and a decrease in cooling capacity caused by an increased discharge temperature of the expansion mechanism 3 during cooling operation, by reducing the heat transfer from the compression mechanism 2 to the expansion mechanism 3. As a result, the coefficient of performance of the air conditioner is improved.
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Abstract
An expander-integrated compressor (100A) has a compression mechanism (2), an expansion mechanism (3), a shaft (5), an oil pump (6), and an oil supply amount regulating mechanism (30). The compression mechanism (2) and the expansion mechanism (3) are coupled to each other by the shaft (5) so that mechanical power can be transmitted. The compression mechanism (2) and the expansion mechanism (3) are arrayed vertically in the closed casing (1). The oil pump (6) is provided at a lower portion of the shaft (5). An oil supply passage (29) is formed in the shaft (5) so as to extend in the axis direction. The oil supply amount regulating mechanism 30 controls the amount of the oil to be supplied by the oil pump (6) to the expansion mechanism (3).
Description
- The present invention relates to an expander-integrated compressor and a refrigeration cycle apparatus using the same.
- Recently, as natural resource issues and global warming issues have become ever more serious, much research and development efforts have been invested in reducing energy consumption of refrigeration cycle apparatuses, which are used for water heaters and air conditioners. For example, conventional refrigeration cycle apparatuses have a mechanism of expanding the refrigerant using an expansion valve, but there is an attempt to employ a positive displacement expander in place of the expansion valve in order to recover the energy of expansion of the refrigerant and utilize it as auxiliary power for the compressor. By the recovery and utilization of the expansion energy of the refrigerant, it can be expected to achieve about a 20% reduction in power usage theoretically, or about a 10% reduction even with an actual apparatus. As a fluid machine that achieves such an attempt, development of a fluid machine (expander-integrated compressor), such as disclosed in
JP 2005-299632 A -
Fig. 11 is a vertical cross-sectional view illustrating a typical expander-integrated compressor. An expander-integratedcompressor 200 has a two-stage rotarytype compression mechanism 121, amotor 122, a two-stage rotarytype expansion mechanism 123, and a closedcasing 120 that accommodates them. Thecompression mechanism 121, themotor 122, and theexpansion mechanism 123 are coupled to each other by ashaft 124. - A bottom part of the closed
casing 120 forms anoil reservoir 125 for holding oil (refrigeration oil). Anoil pump 126 is fitted to a lower end portion of theshaft 124 in order to pump up the oil held in theoil reservoir 125. The oil pumped up by theoil pump 126 is supplied to thecompression mechanism 121 and theexpansion mechanism 123 via anoil supply passage 127 formed in theshaft 124. Thereby, lubricity and sealing of the sliding parts of thecompression mechanism 121 and theexpansion mechanism 123 are ensured. - An
oil return pipe 128 is disposed in an upper part of theexpansion mechanism 123. One end of theoil return pipe 128 communicates with theoil supply passage 127 formed in theshaft 124, while the other end opens below theexpansion mechanism 123. Generally, the oil is supplied excessively in order to ensure the reliability of theexpansion mechanism 123. The excess oil is returned via theoil return pipe 128 to theoil reservoir 125. - By disposing both the
compression mechanism 121 and theexpansion mechanism 123 in the closedcasing 120, there is an advantage in being able to lubricate both thecompression mechanism 121 and theexpansion mechanism 123 by the oil held in theoil reservoir 125. - In the expander-integrated
compressor 200 shown inFig. 11 , the oil pumped up from theoil reservoir 125 is heated by thecompression mechanism 121 because it passes through thecompression mechanism 121 that is at a high temperature. The oil heated by thecompression mechanism 121 is heated further by themotor 122, and it reaches theexpansion mechanism 123. The oil having reached theexpansion mechanism 123 is cooled by theexpansion mechanism 123 that is at a low temperature, and is thereafter discharged below theexpansion mechanism 123 via theoil return pipe 128. The oil discharged from theexpansion mechanism 123 and theoil return pipe 128 is heated again when passing along a side face of themotor 122 and is also heated when passing along a side face of thecompression mechanism 121. The oil then returns to theoil reservoir 125 of the closedcasing 120. - As described above, the oil circulation between the
compression mechanism 121 and theexpansion mechanism 123 causes heat transfer from thecompression mechanism 121 to theexpansion mechanism 123. Such heat transfer lowers the temperature of the refrigerant discharged from thecompression mechanism 121, and elevates the temperature of the refrigerant discharged from theexpansion mechanism 123. In terms of air conditioners, this means a decrease of indoor heating capacity during heating, or a decrease of indoor cooling capacity during cooling. - It is important to reduce the above-described heat transfer as much as possible in order to improve cycle efficiency. In particular, when the system operates at high output power and the rotation speed of the expander-integrated compressor is correspondingly high, the amount of the oil supplied by the
oil pump 126, and accordingly the quantity of heat transferred by the oil, is great. - The present invention has been accomplished in view of the foregoing circumstances, and it is an object of the invention to reduce the heat transfer from the compression mechanism to the expansion mechanism.
- Accordingly, the present invention provides an expander-integrated compressor including:
- a compression mechanism for compressing a working fluid;
- an expansion mechanism for recovering mechanical power from the working fluid;
- a shaft coupling the compression mechanism and the expansion mechanism so as to transmit the mechanical power recovered by the expansion mechanism to the compression mechanism;
- a closed casing accommodating the compression mechanism, the expansion mechanism, and the shaft in such a manner that the compression mechanism and the expansion mechanism are arrayed vertically, the closed casing having a bottom portion utilized as an oil reservoir and an interior space to be filled with the working fluid having been compressed;
- an oil pump provided at a lower portion of the shaft; and
- an oil supply passage for supplying oil in the oil reservoir to the compression mechanism or the expansion mechanism located in an upper part of the closed casing by the oil pump, the oil supply passage being formed in the shaft so as to extend in an axis direction; and
- an oil supply amount regulating mechanism, disposed below the compression mechanism or the expansion mechanism located in the upper part of the closed casing, for regulating the amount of the oil to be supplied to the compression mechanism or the expansion mechanism located in the upper part of the closed casing through the oil supply passage.
- In another aspect, the present invention provides a refrigeration cycle apparatus including:
- an expander-integrated compressor according to the present invention;
- a radiator for cooling the refrigerant compressed by the compression mechanism of the expander-integrated compressor; and
- an evaporator for evaporating refrigerant expanded by the expansion mechanism of the expander-integrated compressor.
- In yet another aspect, the present invention provides an expander-integrated compressor including:
- a compression mechanism for compressing a working fluid;
- an expansion mechanism for recovering mechanical power from the working fluid;
- a shaft coupling the compression mechanism and the expansion mechanism so as to transmit the mechanical power recovered by the expansion mechanism to the compression mechanism;
- a closed casing accommodating the compression mechanism, the expansion mechanism, and the shaft, the closed casing having a bottom portion utilized as an oil reservoir and an interior space to be filled with the working fluid having been compressed;
- an oil pump provided at an end portion of the shaft;
- an oil supply passage for supplying oil in the oil reservoir by the oil pump to the compression mechanism or the expansion mechanism that is located in a far side, viewed from the oil pump, with respect to an axis direction of the shaft, the oil supply passage being formed in the shaft so as to extend in the axis direction; and
- an oil supply amount regulating mechanism for regulating the amount of the oil to be supplied to the compression mechanism or the expansion mechanism through the oil supply passage.
- The above-described expander-integrated compressor of the present invention is provided with the oil supply amount regulating mechanism. Therefore, an appropriate amount of oil can be supplied to the compression mechanism or the expansion mechanism regardless of the rotation speed of the shaft. As a result, it is possible to reduce the heat transfer from the compression mechanism to the expansion mechanism that results from the oil circulation.
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Fig. 1 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a first embodiment of the present invention. -
Fig. 2A is a horizontal cross-sectional view taken along line IIA-IIA of the expansion mechanism. -
Fig. 2B is a horizontal cross-sectional view taken along line IIB-IIB of an expansion mechanism. -
Fig. 3 is a partially enlarged view ofFig. 1 . -
Fig. 4 is a view illustrating a modified embodiment of an oil supply amount regulating mechanism. -
Fig. 5 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a second embodiment of the present invention. -
Fig. 6 is a partially enlarged view ofFig. 5 . -
Fig. 7 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a third embodiment of the present invention. -
Fig. 8 is a partially enlarged view ofFig. 7 . -
Fig. 9 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a fourth embodiment of the present invention. -
Fig. 10 is a configuration diagram of a refrigeration cycle apparatus using the expander-integrated compressor. -
Fig. 11 is a vertical cross-sectional view illustrating a conventional expander-integrated compressor. -
Fig. 1 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a first embodiment of the present invention. An expander-integratedcompressor 100A has a closedcasing 1, acompression mechanism 2, anexpansion mechanism 3, amotor 4, ashaft 5, anoil pump 6, and an oil supplyamount regulating mechanism 30. Thecompression mechanism 2 is disposed in a lower part of theclosed casing 1. Theexpansion mechanism 3 is disposed in an upper part of theclosed casing 1. Themotor 4 is disposed between thecompression mechanism 2 and theexpansion mechanism 3. Thecompression mechanism 2, themotor 4, and theexpansion mechanism 3 are coupled to each other by theshaft 5 so that mechanical power can be transmitted. Theoil pump 6 is provided at a lower portion of theshaft 5. The oil supplyamount regulating mechanism 30 is for regulating the amount of the oil to be supplied to theexpansion mechanism 3. In the present embodiment, a regulating valve (typically a needle valve) is employed as the oil supplyamount regulating mechanism 30. - The
motor 4 drives theshaft 5 to operate thecompression mechanism 2. Theexpansion mechanism 3 recovers mechanical power from the expanding working fluid, and supplies the mechanical power to theshaft 5 to assist themotor 4 to drive theshaft 5. The working fluid is, for example, a refrigerant such as carbon dioxide and hydrofluorocarbon. - In the present embodiment, the arrangement of the
compression mechanism 2, themotor 4, and theexpansion mechanism 3 is determined in such a manner that the axis direction of theshaft 5 is in agreement with the vertical direction. However, the positional relationship between thecompression mechanism 2 and theexpansion mechanism 3 may be opposite of that in the present embodiment. In other words, thecompression mechanism 2 may be disposed in an upper part of theclosed casing 1, and theexpansion mechanism 3 may be disposed in a lower part of theclosed casing 1. - The
closed casing 1 has aninterior space 24 for accommodating various components. Theinterior space 24 of theclosed casing 1 is filled with the refrigerant compressed by thecompression mechanism 2. A bottom portion of theclosed casing 1 is utilized as anoil reservoir 25. The oil is used for ensuring lubrication and sealing on the sliding parts of thecompression mechanism 2 and theexpansion mechanism 3. The amount of the oil in theoil reservoir 25 is controlled so that the oil level is below themotor 4. This prevents a decrease of the efficiency of the motor and an increase of the oil discharge amount to the refrigerant circuit, which result from the agitation of the oil by the rotor of themotor 4. Since the temperature of thecompression mechanism 2 becomes high during operation of the expander-integratedcompressor 100A, the temperature of the oil held in theoil reservoir 25 becomes accordingly high. - The
compression mechanism 2 hascylinders pistons members suction pipe 13 is connected to thecylinder 17, and asuction pipe 14 is connected to thecylinder 18. The refrigerant is guided tocompression chambers respective cylinders suction pipes compression chambers interior space 24 of theclosed casing 19. Adischarge pipe 15 is connected to theclosed casing 1 so that an opening thereof is located between themotor 4 and theexpansion mechanism 3. The refrigerant discharged to theinterior space 24 flows upward through a region surrounding themotor 4. The refrigerant is then guided through thedischarge pipe 15 to a flow passage outside theclosed casing 1. At that time, the refrigerant and the oil can be separated from each other by a gravitational force or a centrifugal force. - In the present embodiment, a rotary-type fluid mechanism is employed as the
compression mechanism 2. The "rotary type" includes not only a rolling piston type, in which a vane slides along the outer circumferential surface of a piston, and a sliding vane type, in which a vane slides along the inner circumferential surface of a cylinder, but also a swing piston type, in which a piston and a vane are integrally formed. In addition, the type of thecompression mechanism 2 is not limited to the rotary type. It is also possible to employ other types of fluid mechanisms, such as a scroll type, a reciprocating type, and a screw type, as thecompression mechanism 2. The same applies to the later-describedexpansion mechanism 3. - The
motor 4 has astator 21 fixed to theclosed casing 1 and arotor 22 fixed to theshaft 5. Electric power is supplied to themotor 4 through a terminal (not shown) disposed at the top of theclosed casing 1. - An
oil supply passage 29 communicating with sliding parts of theexpansion mechanism 3 is formed in theshaft 5 so as to extend in the axis direction. This is desirable because, when forming theoil supply passage 29 inside theshaft 5, the problems associated with an increase in the parts count and parts layout do not arise. The oil is supplied to sliding parts of theexpansion mechanism 3 through theoil supply passage 29. - In the present embodiment, the
oil supply passage 29 does not open in the upper end face of theshaft 5. In this way, the oil does not flow out over theexpansion mechanism 3, unlike the conventional example described with reference toFig. 11 . Thereby, the oil is less easily cooled by theexpansion mechanism 3.
In other words, the heat transfer from thecompression mechanism 2 to theexpansion mechanism 3 can be reduced more effectively. However, theoil supply passage 29 may open in the upper end face of theshaft 5. - The
shaft 5 may be made of a single component, or may be made by combining (coupling) a plurality of components together. Specifically, theshaft 5 may include a first shaft on thecompression mechanism 2 side and a second shaft on theexpansion mechanism 3 side. The first shaft and the second shaft may be coupled directly by fitting them onto each other, or may be coupled to each other via another component (coupler). When theshaft 5 is made of a combination of a plurality of components, assembling, especially alignment between thecompression mechanism 2 and theexpansion mechanism 3, becomes easy. - The
expansion mechanism 3 has afirst cylinder 42, asecond cylinder 44 having an inner diameter larger than the inner diameter of thefirst cylinder 42, anintermediate plate 43 partitioning thefirst cylinder 42 and thesecond cylinder 44. Thefirst cylinder 42 and thesecond cylinder 44 are disposed concentrically with each other. As illustrated inFigs. 2A and 2B , theexpansion mechanism 3 further has afirst piston 46, afirst vane 48, afirst spring 50, asecond piston 47, asecond vane 49, and asecond spring 51. - As illustrated in
Fig. 2A , thefirst piston 46 is fitted with aneccentric portion 5c of theshaft 5, and it performs eccentric rotational motion in thefirst cylinder 42. Thefirst vane 48 is retained reciprocably in avane groove 42a formed in thefirst cylinder 42. One end of thefirst vane 48 is in contact with thefirst piston 46. Thefirst spring 50 is in contact with the other end of thefirst vane 48, and biases thefirst vane 48 toward thefirst piston 46. - As illustrated in
Fig. 2B , thesecond piston 47 is fitted with aneccentric portion 5d of theshaft 5, and it performs eccentric rotational motion in thesecond cylinder 44. Thesecond vane 49 is retained reciprocably in avane groove 44a formed in thesecond cylinder 44. One end of thesecond vane 49 is in contact with thesecond piston 47. Thesecond spring 51 is in contact with the other end of thesecond vane 49, and biases thesecond vane 49 toward thesecond piston 47. - The
expansion mechanism 3 further has a bearingmember 45 and a bearingmember 41. The bearingmember 41 is fitted to theclosed casing 1 with no clearance between them. The components such as the cylinders and the intermediate plate are fixed to theclosed casing 1 via the bearingmember 41. The bearingmember 41 and theintermediate plate 43 sandwiches thefirst cylinder 42 from the top and bottom, and theintermediate plate 43 and the bearingmember 45 sandwiches thesecond cylinder 44 from the top and bottom. Sandwiching the bearingmember 45, theintermediate plate 43, and the bearingmember 41forms working chambers first cylinder 42 and thesecond cylinder 44, respectively. - As illustrated in
Fig. 2A , a suction-side working chamber 55a (first suction-side space) and a discharge-side working chamber 55b (first discharge-side space) are formed inside thefirst cylinder 42. The workingchamber 55a and the workingchamber 55b are partitioned by thefirst piston 46 and thefirst vane 48. As illustrated inFig. 2B , a suction-side working chamber 56a (second suction-side space) and a discharge-side working chamber 56b (second discharge-side space) are formed inside thesecond cylinder 44. The workingchamber 56a and the workingchamber 56b are partitioned by thesecond piston 47 and thesecond vane 49. The total volumetric capacity of the two workingchambers second cylinder 44 is greater than the total volumetric capacity of the two workingchambers first cylinder 42. The discharge-side working chamber 55b of thefirst cylinder 42 and the suction-side working chamber 56a of thesecond cylinder 44 are brought into communication with each other through a throughhole 43a formed in theintermediate plate 43, so that they can function as a single working chamber (an expansion chamber). - The method for making the total volumetric capacity of the working
chambers chambers first cylinder 42 and thesecond cylinder 44. It is also possible to employ the method of appropriately setting the thicknesses of thecylinders pistons - The
expansion mechanism 3 further has asuction pipe 52 serving as a suction passage for directly drawing the refrigerant that has not yet been expanded from a flow passage external to theclosed casing 1, and adischarge pipe 53 serving as a discharge passage for directly discharging the refrigerant that has been expanded to a flow passage external to theclosed casing 1. Specifically, thesuction pipe 52 is directly inserted in thefirst cylinder 42 so that the refrigerant can be guided from the flow passage external to theclosed casing 1 to the workingchamber 55 of thefirst cylinder 42. Thedischarge pipe 53 is directly inserted in thesecond cylinder 44 so that the refrigerant can be guided from the workingchamber 56 of thesecond cylinder 44 to the flow passage external to theclosed casing 1. Thesuction pipe 52 may be inserted in the bearingmember 41, and thedischarge pipe 53 may be inserted in the bearingmember 45. - The refrigerant that has not yet been expanded passes through the
suction pipe 52 and flows into the workingchamber 55a of thefirst cylinder 42. The working fluid having flowed into the workingchamber 55a of thefirst cylinder 42 moves to the workingchamber 55b in association with rotation of theshaft 5, and it expands and reduces its pressure in the expansion chamber formed by the workingchamber 55b, the throughhole 43a, and the workingchamber 56a, while rotating theshaft 5. The refrigerant having expanded is guided to the outside of theclosed casing 1 through the workingchamber 56b and thedischarge pipe 53. - The location at which the
oil pump 6 is provided is a lower portion of theshaft 5. Specifically, theoil pump 6 is disposed in theoil supply passage 29 in a lower portion of theshaft 5. Disposing theoil pump 6 in theoil supply passage 29 eliminates the need to provide an oil supply pipe separately. - The
oil pump 6 is operated by the mechanical power supplied from theshaft 5. In the present embodiment, a velocity type pump (turbine pump) is employed as theoil pump 6. Specifically, theoil pump 6 has apump blade 6a and ablade stopper 6b. Thepump blade 6a is fixed to theshaft 5 by theblade stopper 6b. Rotation of thepump blade 6a together with theshaft 5 causes the oil to be pumped upward. Generally, the rotation speed of theoil pump 6 is equal to the rotation speed of theshaft 5. Therefore, as the rotation speed of theshaft 5 increases, the delivery capacity and delivery pressure of theoil pump 6 increases accordingly. However, since the effectiveness of the oil supplyamount regulating mechanism 30 increases as the delivery pressure of theoil pump 6 increases, the amount of the oil to be supplied to theexpansion mechanism 3 is not proportional to the rotation speed of theshaft 5. - The type of the oil pump is not limited to the velocity type pump, and a positive displacement pump may be used. Examples of the positive displacement pump include a rotary type oil pump and a TROCHOID pump (registered trademark of Nippon Oil Pump Co., Ltd.). However, the velocity type pump is better suited for the oil supply
amount regulating mechanism 30 in the present embodiment than the positive displacement pump. The reason is that no oil escape route is provided in the present embodiment, as it is provided in the later-described second and third embodiments. - The oil supply
amount regulating mechanism 30 includes a structure for preventing the amount of the oil to be supplied to theexpansion mechanism 3 through theoil supply passage 29 from increasing correspondingly to an increase of the rotation speed of theshaft 5. As described previously, it is important to reduce the heat transfer from thecompression mechanism 2 to theexpansion mechanism 3 resulting from the oil circulation as much as possible, in order to improve the efficiency of a refrigeration cycle apparatus (seeFig. 10 ) using the expander-integratedcompressor 100A. When the rotation speed of theshaft 5 increases, the delivery capacity and delivery pressure of theoil pump 6 tend to increase. However, excessive supply of the oil is prevented by the workings of the oil supplyamount regulating mechanism 30. In some cases, the oil supply amount to theexpansion mechanism 3 can be maintained at almost a constant level regardless of the rotation speed of theshaft 5. As a result, it is possible to reduce the heat transfer from thecompression mechanism 2 to theexpansion mechanism 3 that results from the oil circulation. - In the present embodiment, the oil supply
amount regulating mechanism 30 is provided in theoil supply passage 29. For this reason, it is unnecessary to provide a dedicated space for the oil supplyamount regulating mechanism 30. The location at which the oil supplyamount regulating mechanism 30 should be provided may be below theexpansion mechanism 3, which is located in the upper part of theclosed casing 1. Typically, the oil supplyamount regulating mechanism 30 is provided between the workingchamber 20 of thecompression mechanism 2 and themotor 4 with respect to the axis direction of theshaft 5. -
Fig. 3 is a partially enlarged view ofFig. 1 . As illustrated inFig. 3 , the oil supplyamount regulating mechanism 30 has avalve seat 31, a needle 32 (valve body), aspring 33, and aneedle stopper 34. Thevalve seat 31 has an orifice shape whose inner diameter decreases toward theexpansion mechanism 3. Theneedle 32 is disposed so as to face thevalve seat 31. Theneedle 32 has a leading end portion in a circular conic shape. Thespring 33 is disposed between thevalve seat 31 and theneedle 32 so that a gap through which the oil can flow is formed between thevalve seat 31 and theneedle 32. Thespring 33 expands and contracts according to a pressure change of the oil in theoil supply passage 29, so that the gap between thevalve seat 31 and theneedle 32 can be adjusted. Theneedle stopper 34 for defining the range of motion of theneedle 32 is disposed opposite thevalve seat 31 across theneedle 32. Thevalve seat 31 or theneedle stopper 34 may be formed by a portion of theshaft 5. - With the oil supply
amount regulating mechanism 30, the oil to be supplied to theexpansion mechanism 3 flows through theoil supply passage 29 and hits the back face of theneedle 32. Thereafter, the oil passes through the surrounding region of theneedle 32 and flows toward thevalve seat 31. The oil hitting the back face of theneedle 32 presses theneedle 32 toward thevalve seat 31 with a force corresponding to the flow rate of the oil. Theneedle 32 is pushed back with a force in proportion to the displacement of thespring 33. Specifically, the area of the gap between thevalve seat 31 and the needle 32 (the cross-sectional area of the gap) changes according to the flow rate of the oil. While the oil feeding capability of theoil pump 6 becomes higher in proportional to an increase of the rotation speed of theshaft 5, the resistance to the oil flow increases because the gap between thevalve seat 31 and theneedle 32 narrows. As a result, the amount of the oil to be supplied is restricted (optimized). - Even when the
shaft 5 revolves at a high speed, an unnecessarily great amount of the oil is not supplied to theexpansion mechanism 3 because of the workings of the oil supplyamount regulating mechanism 30. In other words, an appropriate amount of the oil can be supplied to theexpansion mechanism 3. As a result, it is possible to reduce the heat transfer from thecompression mechanism 2 to theexpansion mechanism 3 that results from the oil circulation. Moreover, since excess oil is not supplied to theexpansion mechanism 3, it is possible to prevent the working fluid from mixing with a large amount of the oil in theexpansion mechanism 3. Thus, it is possible to prevent a considerable decrease in heat exchange efficiency resulting from the excess oil flowing into an evaporator 102 (seeFig. 10 ). As illustrated inFig. 4 , the effect of optimizing the oil supply amount can be obtained by providing only thevalve seat 31 in theoil supply passage 29. That is, by merely providing an orifice in theoil supply passage 29, the oil can be prevented from being excessively supplied to theexpansion mechanism 3 because the pressure loss at the orifice increases proportionally to an increase of the oil flow rate. - In the present embodiment, the oil of the
oil supply passage 29 is supplied only to theexpansion mechanism 3. However, the oil of theoil supply passage 29 may also be supplied to thecompression mechanism 2. -
Fig. 5 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a second embodiment of the present invention. As illustrated inFig. 5 , a main difference between an expander-integratedcompressor 100B of the present embodiment and the expander-integratedcompressor 100A of the first embodiment is in the oil supply amount regulating mechanism. The same parts as those in the embodiment shown inFig. 1 will be designated by the same reference numerals, and the descriptions thereof will be omitted. -
Fig. 6 is a partially enlarged view ofFig. 5 . In the present embodiment, abranch passage 29s branching in a radial direction from theoil supply passage 29 and opening in an outer circumferential surface of the shaft5 is formed in theshaft 5. An oil supplyamount regulating mechanism 60 is provided in thebranch passage 29s. In this way, mounting of the oil supplyamount regulating mechanism 60 is possible from the outside of theshaft 5, so assembling is easier than that in the first embodiment. Moreover, this is suitable also in the case where the oil pump is a positive displacement pump because thebranch passage 29s behaves as an oil escape route. - As illustrated in
Fig. 6 , the oil supplyamount regulating mechanism 60 has avalve seat 61, aneedle 62, aspring 63, and aneedle stopper 64. Thevalve seat 61 has an orifice shape whose inner diameter decreases toward theoil supply passage 29. Thevalve seat 61 is disposed at a portion of thebranch passage 29s that faces theoil supply passage 29. Theneedle 62 in a circular conic shape is disposed so as to face thevalve seat 61. Theneedle 62 is displaceable in a direction toward thevalve seat 61 and a direction away from the valve seat 61 (radial directions of the shaft 5). Theneedle stopper 64 is disposed at a portion of thebranch passage 29s that faces an outside of theshaft 5. Theneedle stopper 64 defines the range of motion of theneedle 62. Thespring 63 is disposed between theneedle 62 and theneedle stopper 64. - A bearing
member 10 has a bearingportion 10a that supports theshaft 5. The bearingportion 10a covers an outer circumferential surface of theshaft 5 at a location where thebranch passage 29s is formed. Acircular chamber 67 is formed in an inner circumferential surface of the bearingportion 10a. Thebranch passage 29s opens toward thechamber 67. Anoil discharge passage 66 for connecting thechamber 67 and theinterior space 24 of theclosed casing 1 is further formed in the bearingportion 10a so as to penetrate through the bearingportion 10a in a radial direction. By thebranch passage 29s, thechamber 67, and theoil discharge passage 66, the oil can flow from theoil supply passage 29 to theinterior space 24 of theclosed casing 1. - When the internal pressure of the
oil supply passage 29 is lower than a predetermined pressure, the oil supplyamount regulating mechanism 60 is brought to a closed state. The closed state refers to a state in which thebranch passage 29s is closed by theneedle 62 being fitted into thevalve seat 61. In the closed state, the oil cannot flow through thebranch passage 29s. On the other hand, when the rotation speed of theshaft 5 increases and the internal pressure of theoil supply passage 29 thereby becomes higher than a predetermined pressure, the oil supplyamount regulating mechanism 60 is brought to an open state. The open state refers to a state in which theneedle 62 is detached from thevalve seat 61 so that a gap is formed between thevalve seat 61 and theneedle 62. In the open state, the oil can flow through thebranch passage 29s. - When the internal pressure of the
oil supply passage 29 becomes higher than the predetermined pressure, the oil enters thebranch passage 29s through thevalve seat 61 while displacing theneedle 62. The force of the oil that displaces theneedle 62 is proportional to the internal pressure of theoil supply passage 29. On the condition that the outward load that is applied to theneedle 62 by the oil in theoil supply passage 29 and the like (more specifically, the pressure of the oil and the centrifugal force) exceeds the force by which thespring 63 pushes theneedle 62 when the oil supplyamount regulating mechanism 60 is in the closed state, the oil supplyamount regulating mechanism 60 switches from the closed state to the open state. - In other words, when the rotation speed of the
shaft 5 increases and the oil is fed into theoil supply passage 29 in an amount greater than is necessary, the increase of the internal pressure of theoil supply passage 29 brings the oil supplyamount regulating mechanism 60 into the open state. When the oil supplyamount regulating mechanism 60 is brought into the open state, part of the oil flowing through theoil supply passage 29 is guided to the outside of theshaft 5 through thebranch passage 29s. The oil having flowed out of theshaft 5 is discharged to theinterior space 24 of theclosed casing 1 through thechamber 67 and theoil discharge passage 66 formed in the bearingportion 10a of the bearingmember 10. As a result, the amount of the oil to be supplied to theexpansion mechanism 3 is optimized. Thus, in the present embodiment, the oil supplyamount regulating mechanism 60 is constructed by a relief valve. - In addition, in the present embodiment, the oil is allowed to escape to the outside of the
shaft 5 through thebranch passage 29s. For this reason, when the oil supplyamount regulating mechanism 60 is brought into the open state, a difference in the flow rate of the oil in theoil supply passage 29 arises between the positions before and after the oil supplyamount regulating mechanism 60. Specifically, the flow rate is high between the oil supplyamount regulating mechanism 60 and theoil pump 6, and the flow rate is low between theexpansion mechanism 3 and the oil supplyamount regulating mechanism 60. It is preferable that the portion at which the flow rate of the oil is high be farther away from theexpansion mechanism 3, from the view point of reducing the heat transfer from thecompression mechanism 2 to theexpansion mechanism 3 that results from the oil circulation. Therefore, it is desirable that thebranch passage 29s be formed in a portion of theshaft 5 that is between themotor 4 and thecompression mechanism 2. -
Fig. 7 is a vertical cross-sectional view illustrating an expander-integrated compressor according to a third embodiment of the present invention. As illustrated inFig. 7 , a main difference between an expander-integrated compressor 100C of the present embodiment and the expander-integratedcompressor 100A of the first embodiment is in the oil supply amount regulating mechanism. -
Fig. 8 is a partially enlarged view ofFig. 7 . In the present embodiment, abranch passage 29t branching in a radial direction from theoil supply passage 29 and opening in an outer circumferential surface of theshaft 5 is formed in theshaft 5. An oil supplyamount regulating mechanism 70 is provided exteriorly of the shaft so that the oil is guided to theinterior space 24 of theclosed casing 1 through thebranch passage 29t. Since the oil supplyamount regulating mechanism 70 is provided exteriorly of theshaft 5, a larger space than is available in the preceding two embodiments can be ensured for the oil supplyamount regulating mechanism 70. - The present embodiment is similar to the second embodiment in the respect that the
branch passage 29t is formed in theshaft 5 as an oil escape route. On the other hand, the present embodiment is different from the second embodiment in the respect that the oil supplyamount regulating mechanism 70 does not rotate together with theshaft 5. This is suitable also in the case where the oil pump is a positive displacement pump because thebranch passage 29t behaves as an oil escape route. - As illustrated in
Fig. 8 , in the present embodiment, the oil supplyamount regulating mechanism 70 is provided inside the bearingmember 10. The bearingmember 10 has the bearingportion 10a that supports theshaft 5. The bearingportion 10a covers an outer circumferential surface of theshaft 5 at a location where thebranch passage 29t is formed. Acircular chamber 77 is formed in an inner circumferential surface of the bearingportion 10a. Thebranch passage 29t opens toward thechamber 77. Anoil discharge passage 76 is further formed in the bearingportion 10a, as a passage for connecting thechamber 77 and theinterior space 24 of theclosed casing 1. The oil supplyamount regulating mechanism 70 is provided in theoil discharge passage 76. - The oil supply
amount regulating mechanism 70 has avalve seat 71, avalve body 72, aspring 73, and avalve body stopper 74. Theoil discharge passage 76 includes a portion having a T-shaped cross-sectional shape along the flow direction of the oil. Thevalve seat 71 is disposed in the T-shaped portion. Thevalve body 72 in a spherical shape is disposed so as to face thevalve seat 71. Thevalve body stopper 74 is disposed opposite thevalve seat 71 across thevalve body 72. Thevalve body stopper 74 defines the range of motion of thevalve body 72. Thespring 73 is disposed between thevalve body 72 and thevalve body stopper 74. It should be noted that the structure of the oil supplyamount regulating mechanism 70 may be the same as that in the second embodiment. - When the internal pressure of the
oil supply passage 29 is lower than a predetermined pressure, the oil supplyamount regulating mechanism 70 is brought to a closed state. The closed state refers to a state in which theoil discharge passage 76 is closed by thevalve body 72 being fitted into thevalve seat 71. In the closed state, the oil cannot flow through theoil discharge passage 76. On the other hand, when the rotation speed of theshaft 5 increases and the internal pressure of theoil supply passage 29 thereby becomes higher than the predetermined pressure, the oil supplyamount regulating mechanism 70 is brought to an open state. The open state refers to a state in which thevalve body 72 is detached from thevalve seat 71 so that a gap is formed between thevalve seat 71 and thevalve body 72. In the open state, the oil can flow through theoil discharge passage 76. - When the internal pressure of the
oil supply passage 29 becomes higher than the predetermined pressure, the oil displaces thevalve body 72, causing theoil discharge passage 76 to open. The force of the oil that displaces thevalve body 72 is proportional to the internal pressure of theoil supply passage 29. On the condition that the load that is applied to thevalve body 72 by the oil in theoil supply passage 29 exceeds the force by which thespring 73 pushes theneedle 72 when the oil supplyamount regulating mechanism 70 is in the closed state, the oil supplyamount regulating mechanism 70 switches from the closed state to the open state. - In other words, when the rotation speed of the
shaft 5 increases and the oil is fed into theoil supply passage 29 in an amount greater than is necessary, the increase of the internal pressure of theoil supply passage 29 brings the oil supplyamount regulating mechanism 70 into the open state. When the oil supplyamount regulating mechanism 70 is brought into the open state, part of the oil flowing through theoil supply passage 29 is guided to the outside of theshaft 5 through thebranch passage 29t. The oil having flowed out of theshaft 5 is discharged to theinterior space 24 of theclosed casing 1 through thechamber 77 and theoil discharge passage 76 each formed in the bearingportion 10a of the bearingmember 10. As a result, the amount of the oil to be supplied to theexpansion mechanism 3 is optimized. Thus, in the present embodiment as well, the oil supplyamount regulating mechanism 70 is constructed by a relief valve. - It should be noted that the oil supply
amount regulating mechanism 70 may be disposed at an outlet of theoil discharge passage 76, or may be disposed in thechamber 77. - In the present embodiment as well, the oil is allowed to escape to the outside of the
shaft 5 through thebranch passage 29t. Therefore, it is desirable that thebranch passage 29t be formed in a portion of theshaft 5 that is between themotor 4 and thecompression mechanism 2, which is located in the lower part of theclosed casing 1. - In an expander-integrated
compressor 100D of the present embodiment, the axis direction of theshaft 5 is parallel to the horizontal direction, as illustrated inFig. 9 . Theoil reservoir 25 is formed along the longitudinal direction of theclosed casing 1. Apartition wall 27 is provided between theexpansion mechanism 3 and themotor 4. Thepartition wall 27 divides theinterior space 24 into a space on theexpansion mechanism 3 side and a space on thecompression mechanism 2 side. Themotor 4 is disposed also in the space on thecompression mechanism 2 side. Thispartition wall 27 also has the function to reduce the heat transfer from thecompression mechanism 2 and themotor 4 to theexpansion mechanism 3. Thepartition wall 27 has apassage 27h allowing the oil to flow therethrough. - A positive displacement-type the
oil pump 26 is provided at an end portion of theshaft 5. Theoil pump 26, theexpansion mechanism 3, themotor 4, and thecompression mechanism 2 are arrayed in that order along the axis direction of theshaft 5. The oil supplyamount regulating mechanism 60 is the same one as described with reference toFig. 6 in the third embodiment. Anozzle 26k of theoil pump 26 extends toward theoil reservoir 25 so that it can draw the oil in theoil reservoir 25. The oil drawn by theoil pump 26 is supplied through theoil supply passage 29 to thecompression mechanism 2 located in the far side, viewed from theoil pump 26, with respect to the axis direction theshaft 5. In the present embodiment, the oil from theoil pump 26 is also supplied to theexpansion mechanism 3, which is located on the near side, viewed from theoil pump 26. The oil discharged from theoil supply passage 29 through the oil supplyamount regulating mechanism 60 returns to the space on theexpansion mechanism 3 side. - As in the foregoing embodiments, the oil supply
amount regulating mechanism 60 prevents excessive supply of the oil. Thereby, the heat transfer from thecompression mechanism 2 to theexpansion mechanism 3 is suppressed. In the embodiment shown inFig. 9 , theoil pump 26 is provided in theexpansion mechanism 3 side. However, it is possible to provide theoil pump 26 in thecompression mechanism 2 side. It is also possible to provide the oil supply amount regulating mechanism 30 (first embodiment) or the oil supply amount regulating mechanism 70 (third embodiment), in place of the oil supplyamount regulating mechanism 60. - The expander-integrated compressor according to the present invention may be suitably applied to, for example, refrigeration cycle apparatuses (heat pumps) for air conditioners, water heaters, driers, or refrigerator-freezers. As illustrated in
Fig. 10 , arefrigeration cycle apparatus 110 includes: an expander-integratedcompressor 100A (, 100B, 100C, or 100D); aradiator 101 for cooling the refrigerant compressed by thecompression mechanism 2; and an evaporator 114 for evaporating the refrigerant expanded by theexpansion mechanism 3. Thecompression mechanism 2, theradiator 101, theexpansion mechanism 3, and theevaporator 102 are connected by pipes, to form a refrigerant circuit. - For example, when
refrigeration cycle apparatus 110 is applied to an air conditioner, it is possible to prevent a decrease in heating capacity caused by a decreased discharge temperature of thecompression mechanism 2 during heating operation, and a decrease in cooling capacity caused by an increased discharge temperature of theexpansion mechanism 3 during cooling operation, by reducing the heat transfer from thecompression mechanism 2 to theexpansion mechanism 3. As a result, the coefficient of performance of the air conditioner is improved.
Claims (13)
- An expander-integrated compressor comprising:a compression mechanism for compressing a working fluid;an expansion mechanism for recovering mechanical power from the working fluid;a shaft coupling the compression mechanism and the expansion mechanism so as to transmit the mechanical power recovered by the expansion mechanism to the compression mechanism;a closed casing accommodating the compression mechanism, the expansion mechanism, and the shaft in such a manner that the compression mechanism and the expansion mechanism are arrayed vertically, the closed casing having a bottom portion utilized as an oil reservoir and an interior space to be filled with the working fluid having been compressed;an oil pump provided at a lower portion of the shaft;an oil supply passage for supplying oil in the oil reservoir to the compression mechanism or the expansion mechanism located in an upper part of the closed casing by the oil pump, the oil supply passage being formed in the shaft so as to extend in an axis direction; andan oil supply amount regulating mechanism, disposed below the compression mechanism or the expansion mechanism located in the upper part of the closed casing, for regulating the amount of the oil to be supplied to the compression mechanism or the expansion mechanism located in the upper part of the closed casing through the oil supply passage.
- The expander-integrated compressor according to claim 1, wherein:a branch passage is formed in the shaft, the branch passage branching in a radial direction from the oil supply passage and opening in an outer circumferential surface of the shaft; andthe oil supply amount regulating mechanism is provided in the branch passage.
- The expander-integrated compressor according to claim 2, further comprising:a motor, disposed between the compression mechanism and the expansion mechanism, for driving the shaft; and whereinthe branch passage is formed in a portion of the shaft that is between the motor and the compression mechanism or the expansion mechanism located in a lower part of the closed casing.
- The expander-integrated compressor according to claim 1, wherein the oil supply amount regulating mechanism includes a structure for preventing the amount of the oil to be supplied to the compression mechanism or the expansion mechanism through the oil supply passage, from increasing correspondingly to an increase of a rotation speed of the shaft.
- The expander-integrated compressor according to claim 1, wherein the oil supply amount regulating mechanism includes an orifice, a needle valve, or a relief valve.
- The expander-integrated compressor according to claim 1, wherein the oil supply amount regulating mechanism is provided in the oil supply passage.
- The expander-integrated compressor according to claim 1, wherein:a branch passage is formed in the shaft, the branch passage branching in a radial direction from the oil supply passage and opening in an outer circumferential surface of the shaft; andthe oil supply amount regulating mechanism is provided exteriorly of the shaft so that the oil is guided to the interior space of the closed casing through the branch passage.
- The expander-integrated compressor according to claim 1, wherein the oil supply amount regulating mechanism includes a valve seat, a valve body disposed so as to face the valve seat, and a spring for regulating a gap between the valve seat and the valve body by expanding and contracting according to a pressure change of the oil in the oil supply passage.
- The expander-integrated compressor according to claim 8, wherein the shape of the valve body is spherical.
- The expander-integrated compressor according to claim 7, further comprising:a chamber provided so as to face the shaft at a location at which the branch passage is formed; and whereinthe oil supply amount regulating mechanism is disposed in the chamber or on a path connecting the chamber and the interior space of the closed casing.
- The expander-integrated compressor according to claim 1, wherein the oil pump is a velocity type pump.
- A refrigeration cycle apparatus comprising:an expander-integrated compressor according to claim 1;a radiator for cooling the refrigerant compressed by the compression mechanism of the expander-integrated compressor; andan evaporator for evaporating the refrigerant expanded by the expansion mechanism of the expander-integrated compressor.
- An expander-integrated compressor comprising:a compression mechanism for compressing a working fluid;an expansion mechanism for recovering mechanical power from the working fluid;a shaft coupling the compression mechanism and the expansion mechanism so as to transmit the mechanical power recovered by the expansion mechanism to the compression mechanism;a closed casing accommodating the compression mechanism, the expansion mechanism, and the shaft, the closed casing having a bottom portion utilized as an oil reservoir and an interior space to be filled with the working fluid having been compressed;an oil pump provided at an end portion of the shaft;an oil supply passage for supplying oil in the oil reservoir by the oil pump to the compression mechanism or the expansion mechanism that is located in a far side, viewed from the oil pump, with respect to an axis direction of the shaft, the oil supply passage being formed in the shaft so as to extend in the axis direction; and an oil supply amount regulating mechanism for regulating the amount of the oil to be supplied to the compression mechanism or the expansion mechanism through the oil supply passage.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2008018354 | 2008-01-29 | ||
PCT/JP2009/000295 WO2009096167A1 (en) | 2008-01-29 | 2009-01-27 | Expander-integrated compressor and refrigeration cycle device using the same |
Publications (1)
Publication Number | Publication Date |
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EP2241719A1 true EP2241719A1 (en) | 2010-10-20 |
Family
ID=40912523
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP09705176A Withdrawn EP2241719A1 (en) | 2008-01-29 | 2009-01-27 | Expander-integrated compressor and refrigeration cycle device using the same |
Country Status (5)
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US (1) | US20100326124A1 (en) |
EP (1) | EP2241719A1 (en) |
JP (1) | JPWO2009096167A1 (en) |
CN (1) | CN101910563A (en) |
WO (1) | WO2009096167A1 (en) |
Families Citing this family (14)
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EP2177760A1 (en) * | 2008-05-23 | 2010-04-21 | Panasonic Corporation | Fluid machine and refrigeration cycle device |
KR101409876B1 (en) * | 2008-08-22 | 2014-06-20 | 엘지전자 주식회사 | Variable capacity type rotary compressor and refrigerator having the same and method for driving thereof |
JP5515558B2 (en) | 2009-09-25 | 2014-06-11 | ソニー株式会社 | COMMUNICATION SYSTEM, RELAY DEVICE, AND COMMUNICATION DEVICE |
TWI463073B (en) * | 2011-12-22 | 2014-12-01 | Fu Sheng Ind Co Ltd | Multi-stage heat-pump compressor |
CN103452847B (en) * | 2013-08-19 | 2015-11-18 | 广东美芝制冷设备有限公司 | Rotary compressor and there is the freezing cycle device of this rotary compressor |
ES2612232T3 (en) * | 2014-06-05 | 2017-05-12 | Wabco Europe Bvba | Vacuum pump and system of a vacuum pump and an engine |
CN106247657A (en) * | 2016-07-22 | 2016-12-21 | 西安交通大学 | A kind of carbon dioxide refrigerator refrigeration system |
CN106196685A (en) * | 2016-07-22 | 2016-12-07 | 西安交通大学 | A kind of critical-cross carbon dioxide refrigeration system |
CN107387419B (en) * | 2017-08-22 | 2020-12-22 | 广东美芝制冷设备有限公司 | Oil control assembly, pump and rotary compressor |
CN108050066A (en) * | 2017-12-22 | 2018-05-18 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor and refrigerating circulatory device |
CN108518276A (en) * | 2018-03-26 | 2018-09-11 | 陈平武 | External internal combustion engine |
CN111946621A (en) * | 2020-09-14 | 2020-11-17 | 松下压缩机(大连)有限公司 | Oil supply mechanism of variable frequency compressor |
CN112343797B (en) * | 2020-10-09 | 2023-06-13 | 珠海格力节能环保制冷技术研究中心有限公司 | Crankshaft oil pumping assembly, crankshaft assembly and compressor |
WO2024091965A1 (en) * | 2022-10-24 | 2024-05-02 | Thermolift, Inc. | Unidirectional heat pump system |
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JPH0799151B2 (en) * | 1988-06-22 | 1995-10-25 | 三菱電機株式会社 | Scroll compressor |
JP2616094B2 (en) * | 1990-02-14 | 1997-06-04 | ダイキン工業株式会社 | Scroll compressor |
KR100315791B1 (en) * | 1999-01-19 | 2001-12-12 | 구자홍 | Scroll Compressor |
JP4561326B2 (en) * | 2004-03-17 | 2010-10-13 | ダイキン工業株式会社 | Fluid machinery |
DE602006020880D1 (en) * | 2005-06-29 | 2011-05-05 | Panasonic Corp | FLOW MACHINE AND COOLING CYCLE DEVICE |
WO2007132649A1 (en) * | 2006-05-17 | 2007-11-22 | Panasonic Corporation | Compressor with built-in expander |
CN101506597B (en) * | 2006-10-25 | 2013-01-02 | 松下电器产业株式会社 | Refrigeration cycle device and fluid machine used for the same |
WO2008142822A1 (en) * | 2007-05-16 | 2008-11-27 | Panasonic Corporation | Expander-integrated compressor and refrigeration cycle device with the same |
JP4837094B2 (en) * | 2007-05-16 | 2011-12-14 | パナソニック株式会社 | Refrigeration cycle apparatus and fluid machine used therefor |
JP4423348B2 (en) * | 2007-11-21 | 2010-03-03 | パナソニック株式会社 | Expander integrated compressor |
CN101868597B (en) * | 2007-11-21 | 2012-05-30 | 松下电器产业株式会社 | Compressor integral with expander |
-
2009
- 2009-01-27 US US12/865,085 patent/US20100326124A1/en not_active Abandoned
- 2009-01-27 EP EP09705176A patent/EP2241719A1/en not_active Withdrawn
- 2009-01-27 CN CN2009801020298A patent/CN101910563A/en active Pending
- 2009-01-27 WO PCT/JP2009/000295 patent/WO2009096167A1/en active Application Filing
- 2009-01-27 JP JP2009551430A patent/JPWO2009096167A1/en active Pending
Non-Patent Citations (1)
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JPWO2009096167A1 (en) | 2011-05-26 |
CN101910563A (en) | 2010-12-08 |
US20100326124A1 (en) | 2010-12-30 |
WO2009096167A1 (en) | 2009-08-06 |
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