DE102006009211B4 - Fluid pump and fluid machine - Google Patents

Abstract

A fluid machine comprising: an expansion element (203) having a function of releasing mechanical energy by expansion of refrigerant, the expansion element having a low pressure port (203a) from which low pressure vapor phase refrigerant after decompression flows out and has a high pressure port (203b) from which high pressure refrigerant flows in before its decompression; an electric power generation element (204) having a function of generating electric power by using the mechanical energy; a refrigerant pressure supply member (205) for supplying refrigerant under pressure to the expansion element, the refrigerant pressure supply member having a refrigerant suction port (205a) from which liquid-phase refrigerant is drawn, and a refrigerant discharge port (205b), from which liquid phases Refrigerant is dispensed; and a communication part (206, 261, 262) for causing the low-pressure opening (203a) of the expansion element to communicate with the refrigerant suction port (205a) of the refrigerant pressure-feeding member (205), the communication part separating lubricating oil from the vapor-phase refrigerant and the lubricating oil to the refrigerant suction port (205a).

Description

BACKGROUND OF THE INVENTION

Field of the invention

The present invention relates to a fluid machine used for the Rankine cycle. The fluid pump and the fluid machine may be suitably used for a vapor compression type refrigerator combined with a Rankine cycle.

Description of the Related Art

An example in JP-A-7-12068 The disclosed fluid machine is conventionally known as a fluid machine such as a compressor used for a refrigeration cycle. That is, this fluid machine is a scroll-type machine and has a crankshaft for moving a circular scroll. The shaft portion of the crankshaft is rotatably supported by a bearing member and the crank member is connected to a circular spiral over the bearing member in a back pressure chamber.

The crankshaft has an oil supply passage which passes through its axial direction, and this oil supply passage has an oil supply port and an oil supply groove, which open to portions close to the bearing parts of the shaft part or the crank part. In a chamber of a housing of the fluid machine, the pressure of the refrigerant at high pressure on a side opposite to the spiral of the crankshaft is selected, and selected to a mean pressure in a back pressure chamber. Lubricating oil in the housing passes through the oil supply passage, the oil supply port and the oil supply groove to respective bearings by the pressure difference between the high pressure and the medium pressure, thereby lubricating the respective bearings.

However, in the above-described fluid machine, the oil supply passage, the oil supply port, and the oil supply groove must be formed into the crankshaft. In addition, in the housing, the high pressure portion and the medium pressure portion must be established with respect to the crankshaft. This makes the construction of the fluid machine complex.

Moreover, the technology of using a compressor for a refrigeration cycle, such as an expander, for a Rankine cycle in a vapor compression type refrigerator combined with a Rankine cycle is JP-A-63-96449A disclosed. Further describes US 2004/0231331 A1 a fluid machine capable of recovering heat energy with high efficiency in a vapor compression type refrigerator.

In US 2004/0231331 A1 the flow direction of refrigerant when a fluid machine is made to function as a compressor is reversed relative to that when the fluid machine is caused to function as an expander by using a refrigerant pump of refrigerant pressure supply means for supplying refrigerant under pressure to the fluid machine; and heat energy is converted into high efficiency electrical energy by providing a passageway for transmitting power from the expander to a generator having a speed change mechanism.

The flow direction of refrigerant in US 2004/0231331 A1 is referring to 22 and 23 described. When a fluid machine integrated with an expander 202 As a compressor is operated, power is applied to the compression and expansion part 203 the integrated with an expander fluid machine 202 Heat is not a heater 213 supplied, and an opening / closing valve 218 is opened and a refrigerant pump 205 not operated. Therefore flows as indicated by arrows in 22 the refrigerant is shown in the direction: the fluid machine integrated with an expander 202 → the heater 213 → the opening / closing valve 218 → a radiator 207 → a vapor / liquid separator 209 → an expansion valve 211 → an evaporator 212 → the fluid machine integrated with an expander 202 , This is equal to a known refrigeration cycle and by the refrigerant to the evaporator 212 absorbed heat is transferred to the radiator 207 radiated to effect a refrigeration capability.

Next is when the fluid machine integrated with an expander 202 is operated as an expander, an energy storage battery 222 (Storage battery) at a drive and electric power generation part 204 the integrated with an expander fluid machine 202 connected, it becomes heat to the heater 213 supplied, the opening / closing valve 218 closed and the refrigerant pump 205 operated. Therefore flows as indicated by arrows in 23 shown is the refrigerant in the direction: the refrigerant pump 205 → the heater 213 the integrated with an expander fluid machine 202 → a second bypass passage 220 → the radiator 207 → the vapor / liquid phase separator 209 → a first bypass passage 220 → the refrigerant pump 205 , In this circle generates when the volume of the heater 213 heated refrigerant is expanded, the fluid machine 202 which is integrated with an expander, mechanical energy and these Mechanical energy is converted into electrical energy, thereby recovering heat energy.

In general, the refrigerant for the vapor compression type refrigerator (for example, HFC-134a) in the state of a liquid phase has a lower viscosity than lubricating oil or water, and the oil has a property of easily dissolving into liquid phase refrigerant. For this reason, the lubrication tends to be insufficient in the mechanical sliding part in which only the liquid-phase refrigerant passes.

JP-A-63-96449 and US 2004/0231331 A1 reveal nothing about the lubrication in the sliding parts of the refrigerant pump. However, in this refrigerant pump, the liquid-phase refrigerant separated by the vapor-liquid separator is sucked and discharged. That is, only the liquid-phase refrigerant passes over the mechanically sliding parts of the refrigerant pump, and therefore mechanically sliding parts of the refrigerant pump tend to be insufficiently lubricated.

Furthermore, the JP-A-63-96449 and the US 2004/0231331 A1 Fluid machines applied to the vapor compression type refrigerator combined with a Rankine cycle, but also in a fluid machine specifically designed for a Rankine cycle, tend to mechanically slide the parts of the refrigerant pressure supply means for the same reason insufficiently lubricated.

The US Pat. No. 2,584,865 describes a pump in which a partial flow of a liquid to be pumped is fed to a bearing via a bore in an impeller or rolling piston in order to lubricate it.

The DE 1 403 854 A and the DE 102 02 620 C1 show pumps with lubricated by the fluid medium bearings.

The US 4 129 405 A describes a spiral pump with lubrication by the pumped medium.

The US 4,160,629 describes a spiral pump, which is designed as a submersible pump.

Furthermore, the US 4 129 405 A Reference to spiral pumps with lubrication by the pumped medium.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide a fluid machine that effectively lubricates mechanical sliding parts in a refrigerant pressure-feeding member.

According to one aspect of the present invention, a fluid machine includes: an expansion element having a function of discharging mechanical energy by expanding refrigerant, the expansion element having a low-pressure port from which low-pressure vapor-phase refrigerant after decompression flows out, and having a high-pressure port which high-pressure refrigerant flows in before its decompression; an electric power generation element having a function of generating electric power using the mechanical energy; a refrigerant pressure supply means for supplying under pressure of refrigerant to the expansion element, the refrigerant pressure supply member having a refrigerant suction port from which the liquid-phase refrigerant is sucked, and a refrigerant discharge port from which liquid-phase refrigerant is discharged; and a communication part for causing the low pressure opening of the expansion element to communicate with the refrigerant suction port of the refrigerant pressure supply element. Further, the communication part deposits lubricating oil from vapor-phase refrigerant, and supplies the lubricating oil to the refrigerant pressure port. In this case, the fluid machine can effectively lubricate mechanical sliding parts in a refrigerant pressure-feeding member.

A housing may be provided to receive all of the elements, expansion element, electric power generating element, and refrigerant pressure feeding element. Furthermore, the low-pressure opening may be arranged above the refrigerant suction opening. For example, the expansion member having the low pressure port is disposed above the electric power generating element, and the refrigerant pressure supplying member having the refrigerant suction port is disposed below the electric power generating element. Further, the communication part may deposit the oil from the vapor-phase refrigerant by gravity using a difference in specific gravity between the vapor-phase refrigerant and the oil, and includes an oil storage part for storing the separated oil, and the oil storage part is in the electric power generation means intended.

The communication part may be provided with a check valve for preventing the liquid-phase refrigerant from flowing back from the refrigerant suction port to the low-pressure port. In this case, the communication part has a throttle mechanism connected in series to the check valve is connected, and the throttle mechanism has a refrigerant passage area which is smaller than a refrigerant passage area of the check valve.

Further, a transmission part for transmitting drive power from the expansion element to the refrigerant pressure supply element may be provided. In this case, the refrigerant pressure supply member is operated by the driving power of the expansion element. For example, the transmission part is a one-way clutch that transmits the mechanical energy as the drive power from the expansion element only when the expansion element releases the mechanical energy.

The expansion member may be a compression and expansion member having a function of compressing refrigerant by driving power applied thereto, and the electric power generating means may be a driving and electric power generating member that supplies the driving power to the compression and power generating members Exercise expansion element. In this case, when the compression and expansion element compresses refrigerant, it sucks the low-pressure port of the low-pressure vapor-phase refrigerant after it has been decompressed, and the high-pressure port discharges high-pressure refrigerant before it is decompressed.

According to another aspect of the present invention, a fluid machine includes: an expansion element having a function of discharging mechanical energy by expansion of refrigerant; a refrigerant pressure supply member for supplying refrigerant under pressure to the expansion member, the expansion member having a low-pressure port from which low-pressure vapor-phase refrigerant after decompressing flows out, and a high-pressure port from which high-pressure refrigerant flows after decompression thereof, and a communication part which introduces oil contained in the refrigerant flowing from the low-pressure port to a sliding part of the refrigerant pressure-feeding member. Therefore, the fluid machine can effectively lubricate mechanical sliding parts in the refrigerant pressure-feeding member.

According to another aspect of the present invention, a vapor compression type refrigerator combined with a Rankine cycle includes: a compression and expansion element that has a function of compressing and discharging refrigerant by driving power applied thereto, and a function the release of mechanical energy by expansion of refrigerant, the compression and expansion element having a low-pressure port from which low-pressure refrigerant is sucked and discharged after decompression, and a high-pressure port from which high-pressure refrigerant is discharged and flows before it is decompressed; a driving and electric power generating element having a function of applying the driving power to the compression and expansion element and a function of generating electrical energy by the mechanical energy; and a refrigerant pressure supply member that supplies refrigerant under pressure to the compression and expansion member, the refrigerant pressure supply member having a refrigerant suction port from which liquid-phase refrigerant is sucked, and a refrigerant discharge port from which liquid-phase refrigerant is discharged ; and a communication part that causes the low-pressure port to communicate with the refrigerant suction port. Further, the communication part deposits lubricating oil from the vapor-phase refrigerant, and supplies the lubricating oil to the refrigerant suction port. Accordingly, mechanically sliding parts in the refrigerant pressure-feeding member can be effectively lubricated.

According to another aspect of the present invention, a vapor compression type refrigerator combined with a Rankine cycle includes: a compression and expansion element having a function of compressing and discharging refrigerant by driving power exerted thereon and a function of the Release of mechanical energy by expansion of refrigerant; a driving and electric power generating element having a function of applying the driving power to the compression and expansion element, and a function of generating electrical energy by the mechanical energy; a refrigerant pressure supply member that supplies refrigerant under pressure to the compression and expansion member under pressure; a first communication part through which a refrigerant suction side of the refrigerant pressure supply member is communicatively connected to a mechanically sliding portion of the refrigerant pressure supply member; and a second communication part that causes the low-pressure port to communicate with the mechanically sliding portion. In addition, the second communication part deposits lubricating oil from the vapor-phase refrigerant, and supplies the lubricating oil to the mechanically sliding portion. Accordingly, the mechanically sliding portion of the refrigerant pressure-feeding member can be effectively and satisfactorily lubricated.

There is also disclosed a vapor compression type refrigerator comprising a Rankine cycle which effectively lubricates mechanical sliding parts in a refrigerant pressure-feeding member.

According to one aspect of the present disclosure, a fluid pump includes a driving part, a movable part that is movable by power transmitted from the driving part, a transmitting part through which the power is transmitted from the driving part to the moving part, a fixed part, which is disposed on a side of the movable member opposite to the transfer member to form a working chamber having an outlet from which a fluid flowing into the working chamber is supplied under pressure to an outside in a liquid state through the movable member, and an introduction passage for introducing a part of the fluid in the working chamber to the transmission part. Therefore, fluid can be easily supplied to the transfer member including bearings, and foreign matter in the bearings can be discharged efficiently. Further, when the transmission part including the bearings can be lubricated effectively using the lubricating oil-containing liquid fluid.

The introduction passage may be provided in the movable part, and the introduction passage has an opening part which opens to the working chamber tapered. Alternatively, the movable part includes a passage part for limiting the introduction passage, and the passage part is a member separate from the moving part.

For example, the movable part is a movable scroll having a base plate portion and a first wall portion protruding from the base plate portion in a spiral shape, the fixed part being a fixed spiral having a spiral second wall portion engaging the first wall portion. In this case, the introduction passage has a diameter smaller than a predetermined value, and is provided in the base plate portion of the movable scroll to communicatively communicate the working chamber with the transmission part at a predetermined pressure loss. Furthermore, the transmission part can be accommodated in a closed space. In this case, the movable scroll receives a back pressure exerted thereon on one side of the fixed scroll through the fluid introduced into the closed space. In addition, the movable scroll may be provided with a plurality of openings, all of which have a diameter smaller than a predetermined value, for adjusting pressure between the working chamber and the closed space.

Alternatively, the movable member may be a rotor which is caused to rotate by the driving member disposed in a center of the movable member. In this case, the fixed part is a cylinder housing in which a rotor accommodating cylinder is disposed, and the introduction passage is a passage having a diameter smaller than a predetermined value, and is provided in the rotor to cause the working chamber to communicate with the Transmission member to be communicatively connected to a predetermined pressure loss. The introducing passage may be a groove provided on an end surface in an axial direction of the rotor, and causes the working chamber to be communicatively connected to the transmitting member with a predetermined pressure loss.

BRIEF DESCRIPTION OF THE DRAWINGS

Other objects and advantages of the present invention will become more readily apparent from the following detailed description of preferred embodiments when taken in conjunction with the accompanying drawings.

1 FIG. 10 is a cross-sectional view showing a refrigerant pump in a first embodiment which does not correspond to the claim language.

2 FIG. 12 is a cross-sectional view showing a refrigerant pump in a second embodiment, which does not correspond to the claims.

3 FIG. 12 is a cross-sectional view showing a small-diameter passage in a third embodiment, which does not correspond to the claim text.

4 FIG. 12 is a cross-sectional view showing a small-diameter passage in a fourth embodiment which does not correspond to the claim text. FIG.

5 FIG. 10 is a cross-sectional view showing a refrigerant pump in a fifth embodiment, which does not correspond to the claim text.

6 FIG. 12 is a cross-sectional view showing a refrigerant pump in a sixth embodiment that does not correspond to the claim language.

7 is a cross-sectional view taken on a line VII-VII in FIG 6 taken.

8th FIG. 15 is a cross-sectional view showing a refrigerant pump in a seventh embodiment that does not correspond to the claim language.

9 is a cross-sectional view taken on a line IX-IX in FIG 8th taken.

10 is a cross-sectional view taken on a line XX in FIG 9 taken.

11 Fig. 10 is a schematic diagram showing an entire circuit structure of the eighth embodiment.

12 Fig. 10 is a cross-sectional view of a fluid machine integrated with an expander of the eighth embodiment.

13 FIG. 12 is a schematic cross-sectional view showing a connection means of the eighth embodiment. FIG.

14 FIG. 10 is a cross-sectional view of a fluid machine integrated with an expander of a ninth embodiment. FIG.

15 FIG. 12 is a cross-sectional view of a fluid machine integrated with an expander of a tenth embodiment. FIG.

16 FIG. 12 is a schematic cross-sectional view showing a connection means of the tenth embodiment. FIG.

17 Fig. 10 is a schematic diagram showing an entire circuit structure of an eleventh embodiment.

18 Fig. 10 is a schematic diagram showing an entire circuit structure of a twelfth embodiment.

19 FIG. 10 is a cross-sectional view of a fluid machine of a thirteenth embodiment. FIG.

20 is a cross-sectional view taken on a line XX-XX in 19 taken.

21 is a cross-sectional view taken on a line XXI-XXI in 20 taken.

22 FIG. 12 is a schematic diagram showing the direction of flow of refrigerant in a refrigerant circuit of a conventional example. FIG.

23 FIG. 12 is a schematic diagram showing the direction of another flow of refrigerant in a refrigerant cycle of the conventional example. FIG.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

First Embodiment

In this embodiment, which does not correspond to the claims, a fluid pump typically becomes for a refrigerant pump 100 for supplying liquid refrigerant (corresponding to fluid in the present example) under pressure in a Rankine cycle. The basic structure of the refrigerant pump will be described below 100 under the use of 1 described. The Rankine cycle is a cycle that uses a refrigerant pump 100 , a heater, an expander and a condenser, which are connected together in the form of a circuit. The Rankine cycle carries liquid refrigerant from the refrigerant pump 100 to a heater and heats the liquid refrigerant by, for example, the waste heat of an internal combustion engine for a vehicle to produce superheated steam and leads the heated steam in the expander and recycles mechanical energy generated by the expansion of the refrigerant.

The refrigerant pump 100 In this embodiment, a scroll type electrically driven refrigerant pump is a scroll 112 . 113 in a pump section 110 used and its pump part 110 through a motor part 120 is driven. That under pressure by the refrigerant pump 100 supplied liquid refrigerant contains lubricating oil of the order of several percent for lubricating transmission parts such as a bearing to be described later 114d ,

The pump part 110 consists of a fixed spiral (corresponding to a solid part in the present invention) 112 attached to a pump housing 111 fixed, a movable scroll (corresponding to a moving part in the present example) 113 which revolves and is in position opposite the fixed roller 112 offset, a pump shaft (corresponding to a driving part in the present example) 114 for driving the movable spiral 113 and the same.

The solid spiral 112 is from a plate-shaped base plate section 112a and a spiral tooth portion (corresponding to a second wall part in the present invention) 112b built from the base plate sections 112a to the movable spiral 113 protrudes. During that is the moving spiral 113 from a spiral tooth portion (corresponding to a first wall part of the present example) 113b which is in contact with the tooth portion 112b stands and engages in this, and a base plate section 113a built, this tooth section 113b has trained on it. The moving spiral 113 revolves in a state in which both tooth sections 112b . 113b Contact each other to the position of one through both spirals 112 . 113 to move trained working chamber V. The solid spiral 112 has a discharge opening 112c which communicates with the working chamber V, and is connected to the heater (not shown) located in the center of the base plate portion 112a is trained.

The pump shaft 114 is a crankshaft with an eccentric section 114a which is eccentrically formed with respect to a rotation center axis at one end in a direction of the length, and is rotatable by the bearing 114b carried on the pump housing 111 is attached. A jack 114c is on this eccentric section 114a mounted in such a way, with respect to the eccentric section 114a to swing (powered crank mechanism). The socket 114c is at the movable spiral 113 via the bearing (corresponding to a transmission part in the present example) 114d coupled. One side opposite the eccentric section of the pump shaft 114 is at the motor shaft 121 of the engine part 120 connected. The warehouse 114d is a transmission member for transmitting a driving force on the pump mechanism and is a part including a portion to be lubricated, such as a sliding portion, a rolling portion or a rubbing portion.

A plate-shaped race 115a and a plate-shaped cage 115b are in layers on both a surface on one of the fixed spiral opposite side of the movable spiral 113 as well as a surface of the pump housing 111 attached, which is opposite to this surface, this by bolts 115d , roll 115e are interposed between tapered openings in each cage 115b are formed. This structure constitutes a rotation preventing mechanism 115 , The rotation prevention mechanism 115 prevents the moving spiral 113 rotates while the pump shaft 114 one turn rotates and the movable spiral 113 causes the rotation center of the pump shaft 114 to circle.

In this embodiment is a passage 113c small diameter (corresponding to an introducing passage in the present example) for causing the working chamber V, with the bearing 114d to communicate at a specified pressure loss, in the middle section of the movable scroll 113 educated. Here's in terms of the size of the passageway 113c of small diameter its inner diameter "d" and its length "L" (thickness of the movable spiral 113 ) are set to 0.1 mm and 6 mm, respectively, so as to prevent a large amount of liquid refrigerant from the working chamber V to the bearing 114d flows and in order to be able to be formed by actual machining (mechanical machining or electric discharge machining).

The amount of liquid refrigerant G passing through the refrigerant pump 100 is supplied under pressure, is selected at 230 kg / h and the validity of the flow rate .DELTA.G (kg / h) of the passage 113 small diameter flowing refrigerant is tested by the following mathematical equation 1 (Hagen-Poiseuille's equation). ΔG = (π / 8μ) × (ΔP / L) × (d / 2) ⁴ × ρ × 3600 (Mathematical Equation 1) where μ is the viscosity of liquid refrigerant (Pa), ΔP is a pressure difference (MPa) of liquid refrigerant passing on 113c small diameter acts, and ρ is the density of liquid refrigerant (kg / m ³ ).

Specifically, assuming that d = 0.1, L = 6, μ = 2 × 10 ^-4 , ΔP = 2 × 10 ⁶ and ρ = 1100, the liquid refrigerant flow rate ΔG becomes 16 kg / h and they is a level of 7% with respect to the amount of pressurized liquid refrigerant G (230 kg / h).

An open end on one side opposite the working chamber V of the passage 113c small diameter opens to the end surface of the eccentric section 114a , The cylindrical bush 114c is through the outer surface in the radial direction of the eccentric section 114a carried. The end surface of the eccentric section 114a and the end surface of the socket 114c are the base plate section 113a the movable spiral 113 opposite and a disc-shaped space is partitioned between them. The end portion of the side of the movable spiral 113 of the camp 114d is positioned so that it points directly to the exterior in the radial direction of this disk-shaped space. The moving spiral 113 has a cylindrical holding portion which is formed in a protruding manner and holds inside the bearing 114d , The disc-shaped space communicates with a space outside the radial direction of the holding portion through a space in the bearing 114d or a space between the eccentric section 114a and the socket 114b is divided. The rotation preventing mechanism 115 is disposed outside in the radial direction of this holding portion. In this structure is the passage 113c small diameter communicating with the disk-shaped space communicating and this space extends directly to the camp 114d , As a result, a passage is formed, which passes through the passage 113c small diameter passes through and the bearing 114d reached that on the back of the movable spiral 113 is arranged.

Next, the operation based on the above-described construction and the effect of the operation will be described. When the pump shaft 114 through the operation of the engine part 120 is rotated, the movable spiral 113 cause the spinning or spinning, the operating chamber V is displaced so that it is from the side of the outer diameter of the movable spiral 13 moved to the central side. The liquid refrigerant discharged from the condenser and flowing into a suction port (not shown) passes through the working chamber V and is discharged from a discharge port 112c discharged and supplied under pressure to the heater.

In this embodiment, the movable scroll 113 the passage 113c small diameter formed therein, and therefore a portion (corresponding to the above-described approximate 7%) of pressurized liquid refrigerant safely from the working chamber V to the side of the bearing 114d supplied according to a pressure difference. Therefore, by a simple structure, according to which only the passage 113c small diameter in the movable spiral 113 is formed, the camp 114d Cooled and lubricated by lubricating oil contained in the liquid refrigerant to the reliability of the refrigerant pump 100 to improve. If, on the other hand, the reliability of the refrigerant pump 100 held at the same level, the refrigerant pump 100 be produced at a lower cost. For example, it is possible to meet the need for choosing an expensive material for the bearing 114d or performing a surface treatment or heat treatment on the bearing 114 to eliminate. Here, since the fluid to be used is liquid (liquid refrigerant), unlike in the case of gas, the passage 113c small diameter in a size (in particular, the inner diameter d, which is related to the cross-sectional area of the passage), which can be actually machined without being significantly influenced by the amount of pressurized liquid refrigerant, and the above produce described effect.

Second Embodiment

The second embodiment, which does not correspond to the claim wording is in 2 shown. The second embodiment is compared with the first embodiment described above with a closed back pressure chamber 116 Mistake.

Here is a sealing element 116a between the movable spiral 113 and the pump housing 111 interposed and another sealing element (not shown) is between the pump shaft 114 (or a motor shaft 121 ) and the pump housing 111 interposed to the closed back pressure chamber 116 on one of the fixed spiral opposite side of the movable spiral 113 train.

Hereby can the warehouse 114 be lubricated by the liquid refrigerant, which from the working chamber V through the passage 113c small diameter is introduced and a back pressure (one on the fixed spiral 112 applied pressure) can on the movable spiral 113 be exercised. Therefore, the thrust or axial play between the movable spiral 113 and the solid spiral 112 be set, which results in making it possible to eliminate the need to provide a specifically designed adjustment function. As one on the front and the back of the movable spiral 113 applied pressure difference can be reduced, the selected strength (eg, the selected thickness) of the movable scroll 113 can be lowered, and therefore the movable spiral 113 be reduced in terms of weight and cost. In the second embodiment, the other parts can be manufactured similarly to the first embodiment described above.

Third Embodiment

The third embodiment, which does not correspond to the claim text, is in 3 shown. In the third embodiment, the shape of the passage 113 small diameter compared to the first embodiment described above. That is, an opening of the passage 113 small diameter on the side of the working chamber V has a tapered section 113d , This tapered section 113d provides the passage 113c small diameter with an opening. In the passage 113c its small diameter portion is formed as a circular main portion having a specified small diameter, and an opening is formed as the tapered portion in a tapered shape. In the tapered section 113d increases the inner diameter of the passage 113c small diameter gradually to the working chamber V. The tapered section 113d provides a circular opening with a diameter larger than the inside diameter of the passage 113c small diameter the wall surface on the side of the working chamber V of the base plate portion 113a the movable spiral 113 is. The tapered section 113d provides a wall surface shaped like a funnel which is uniform from the wall surface on the side of the working chamber V of the base plate portion 113a the movable spiral 113 to the main section of the passage 113c small diameter converges.

These shapes allow the liquid refrigerant to flow evenly and the flow into the bearing 114d to homogenize introduced liquid refrigerant. In the third embodiment, the other parts may be manufactured similarly to the above-described first embodiment or the second embodiment.

Fourth Embodiment

The fourth embodiment, which does not correspond to the claim wording is in 4 shown. In the fourth embodiment, a portion in which the passage is 113c is formed with a small diameter, formed on a member of the movable spiral compared with the first embodiment described above 113 is disconnected. That is, this separate element is previously considered an opening element 113e with the passage 113c small diameter formed and this opening element 113e becomes in the central portion of the base plate portion 113a the movable spiral 113 fastened by pressing or the like.

Accordingly, it is possible the passage 113c small diameter in the state of the movable spiral 113 separate opening element 113e train, and therefore the passage 113c small diameter easy to make. In the fourth embodiment, the other parts can be made similarly to the first embodiment described above.

Fifth Embodiment

The fifth embodiment, which does not correspond to the claim text, is in 5 shown. In the fifth embodiment, as compared with the first embodiment described above, an introduction passage is outside the refrigerant pump 100 educated. That is, a return passage 131 who with the camp 114d communicating, is in a delivery-side passage 130 formed by the discharge opening 112c connects to the heater and a throttle section 132 according to the passage 113c small diameter is in the middle of this return passage 131 educated.

Accordingly, it is possible to remove a portion of liquid refrigerant from the discharge port 112c is delivered to the warehouse 114d through the throttle section 132 to initiate and effect the same as in the first embodiment.

Sixth Embodiment

The sixth embodiment, which does not correspond to the claim wording, is in 6 and 7 shown. In the sixth embodiment, the present disclosure is a refrigerant pump 100A applied by rotary vane type.

A pump part 110A the refrigerant pump 100A of rotary vane type contains a pump housing 111A , a cylinder housing 117 , a pump housing 111B , a cylinder housing 117 , a cylinder 117a and a rotor 118 in an end housing 119 is formed, which are connected successively. Here is the pump part 110A a two-cylinder pump, with two cylinders 117a and two rotors 118 is provided. The end housing 119 has a suction opening 119a on, from which the liquid refrigerant is sucked, and a discharge port 119b from which the liquid refrigerant flows out of the working chamber V.

The cylinder 117a is with a circular cross section in the central portion of the cylinder housing 117 educated. The cylinder housing 117 corresponds to a fixed part of the present invention. The pump shaft 114A has a circular cam part 114e on which with respect to the pump shaft 114A is eccentric, on which it is formed, and a flat cylindrical rotor 118 is on the outer peripheral side of this cam part 114e about a camp 114D (corresponding to a transmission part in the present invention) attached. The rotor 118 corresponds to a movable part in the present invention. The rotor 118 has an outer diameter smaller than the inner diameter of the cylinder 117a is chosen and is in the cylinder 117a used in such a way that the rotor 118 in the cylinder 117a through the cam part 114e circles. A slider 118a which is in the radial direction of the rotor 118 can slide and is pressed towards the center, thereby to the rotor 118 abutting is in the outer peripheral portion of the rotor 118 used. A space through the rotor 118 and the slider 118a is enclosed in the working chamber V in the cylinder 117a educated.

In the cylinder housing 117 are a refrigerant inlet 117b and a refrigerant outlet 117c with the interior of the cylinder 117a communicating, near the slider 118a formed in such a way that it this slide 118a sandwich. The refrigerant inlet 117b is at the suction opening 119a connected by a passage (not shown) and the refrigerant outlet 117c is at the delivery port 119b connected by a passage (not shown).

In this embodiment, the (eg two) passages are 113c small diameter, all through the rotor 118 pass through, at a first position between the refrigerant outlet 117c of the rotor 118 and the slider 118a and a second position opposite to the first position. For example, the two passages 113c small diameter formed at positions, respectively, over the center of the rotor 113 opposite each other. An outer opening end in the radial direction of the passage 113 small diameter leads to the outer peripheral surface of the rotor 118 and an inner end of the opening in the radial direction of the passage 113c small diameter leads to the inner peripheral surface of the rotor 118 , The warehouse 114D is located in a space between the rotor 118 and the cam part 114e in the rotor 118 , The passage 113c small diameter communicates with the space between the rotor 118 and the cam part 114e ,

In this refrigerant pump 100A the liquid refrigerant flows from the suction port 119a and the refrigerant inlet 117b into the working chamber V and flows out of the refrigerant outlet 117c and the delivery port 119b by the circular operation of the rotor 118 out. A portion of liquid refrigerant in the working chamber V is from the passage 113c small diameter in the warehouse 114D initiated. Therefore, as in the first embodiment, it is possible to lubricate the bearing 114D to maintain and the reliability of the refrigerant pump 100A to improve.

In this embodiment, the refrigerant is introduced to the storage 114D to lubricate. If the refrigerant is mixed with lubricating oil, a larger lubricating effect may be expected. An open type bearing in which parts to be lubricated such as ball, roller, rolling surface, sliding surface are not included can be considered the bearing 114D be used. For example, when an open type sliding bearing is used, the liquid refrigerant may be in conformity with a pressure difference to the parts to be lubricated such as a sliding part, rolling part and friction part of the bearing 114D through the passages 113C small diameter lubricated in the rotor 118 are formed. To parts, such as balls, between the inner ring and the outer ring of the bearing 114D are received to lubricate securely, a through hole or a groove can be formed as a passage in bearing parts such as the inner ring, the outer ring and a cover. For example, one with one in the rotor 118 formed opening communicating passage in the outer ring are formed.

Seventh Embodiment

The seventh embodiment, which does not correspond to the claim text, is in 8th to 10 shown. In the seventh embodiment, the passages are as compared with the sixth embodiment 113c small diameter to grooves 113f changed.

The groove 113f is a groove (see 10 ) in the end surface in the axial direction of the rotor 118 (For example, the end surface on the right side of each rotor 118 ) is formed and is circular in cross section. The groove 113f is formed to be in a longitudinal direction from the outer circumferential surface of the rotor 118 to the inner peripheral surface is straight (see 9 ). Here are two grooves 113f formed at positions that extend beyond the center of the rotor 118 each opposed to each other, such that they face each other in the end surface in the axial direction of the rotor 118 are opposite.

The grooves described above 113f form inlet passages, all of which have a crescent-shaped cross-section between the rotor 118 and the pump housing 119 on the right in 8th and between the rotor 118 and the pump housing 111B on the left in 8th and cause the working chamber V with the bearing 114D is communicatively connected.

This inlet passage (the groove 113f ) having a crescent-shaped cross section (arc portion) can, as in the sixth embodiment described above, a part of liquid refrigerant from the working chamber V to the camp 114D initiate and therefore can lubricate the bearing 114D cause. Here, the introduction passage by forming the groove 113f in the rotor 118 can be formed and therefore can be compared with the case of forming the passage 113c small diameter, as described in the sixth embodiment, are easily formed.

Referring to the cross-sectional shape of the groove 113f is the groove 113f preferably in the 9 and 10 formed form, but the groove 113f is not necessarily circular, but may be formed in a polygonal shape. Further, referring to the longitudinal shape, the groove 113f be formed in a curved shape or in a circular shape. Further, referring to the number of grooves 113f a groove 113f in the end surface in the axial direction of the rotor 118 and three or more grooves 13f be educated. In addition, the groove 113f not only in a surface of end surfaces in the axial direction of the rotor 118 (the surface on the right in 8th ), but also in both surfaces. As a result, the lubricating effect can be further improved.

(Eighth Embodiment)

11 FIG. 15 is a diagram showing an entire circuit structure of a vapor compression type refrigerator for a vehicle in accordance with the eighth embodiment of the present invention. The vapor compression type refrigerator for a vehicle of this embodiment is a refrigerator combined with a Rankine cycle that generates cold and heat to condition a vehicle compartment and extracts heat energy in an engine 201 generated waste heat again.

First is a fluid machine 202 integrated with an expander, a fluid machine mounted in a vehicle engine compartment, and is composed of a compression and expansion part 203 , a drive and electric power generation part 204 , a refrigerant pump 205 and an oil feed passage 206 built up. The compression and expansion part 203 , the power and electric power generation part 204 and the refrigerant pump 205 are combined in an integral structure and the fluid machine 202 integrated with an expander is formed in its entirety in the shape of a cylinder.

The compression and expansion part 203 is a compression and expansion means having: both the function of a compressor for compressing and discharging refrigerant by a driving force applied thereto during the air conditioning of a vehicle compartment (hereinafter referred to as a compressor mode); and the function of discharging mechanical energy by expansion of the refrigerant during recovery of heat energy (hereinafter referred to as an expander mode). The compression and expansion part 203 has a low pressure opening 203a from which the low pressure vapor phase refrigerant is drawn, and a high pressure port 203b from which high-pressure refrigerant is released and flows.

The drive and electric power generation part 204 is a driving and electric power generating means with both the function of providing a driving force for the compression and expansion part 203 during the air conditioning of the vehicle compartment as well as the function of generating electrical energy by the mechanical energy passing through the compression and expansion part 203 is released during the recovery of heat energy.

The refrigerant pump 205 is a refrigerant pressure supply means for supplying under pressure of liquid-phase refrigerant to the compression and expansion part 203 during the recovery of heat energy. The refrigerant pump 205 has a refrigerant suction port 205a on, from which liquid phase refrigerant is drawn in and a refrigerant discharge port 205b from which the liquid-phase refrigerant is discharged.

The oil feed passage 206 is a means of communicating connection to the low pressure port 203a to induce with the refrigerant suction port 205a communicatively connected. The oil feed passage 206 is with an oil storage chamber 206a for separating lubricant from the vapor-phase refrigerant and for storing the lubricating oil, and with a check valve 206c to the oil flow from the low-pressure opening 203a only to the refrigerant suction port 205a to enable. The detailed descriptions of the other parts of the fluid machine 202 that is integrated with an expander are specified.

Next radiates a radiator 207 the heat of the refrigerant to cool the refrigerant, and is the refrigerant inlet of the radiator 207 at the high pressure port 203b the integrated with an expander fluid machine 202 through a refrigerant line 208 connected.

A vapor / liquid separator 209 is a transducer attached to the refrigerant outlet of the radiator 207 is connected and that from the radiator 207 outflowing gas separates into vapor-phase refrigerant and liquid-phase refrigerant. Further, the vapor / liquid separator 209 also at the refrigerant suction opening 205a through a first bypass passage 210 connected.

The first bypass passage 210 is a refrigerant line for supplying the through the vapor / liquid separator 209 deposited liquid phase refrigerant to the refrigerant pump 205 , The first bypass passage 210 is with a shut-off or check valve 210a provided to allow the refrigerant from the vapor / liquid separator 209 only to the refrigerant pump 205 flows. Further, this becomes the refrigerant pump 205 supplied refrigerant from the refrigerant discharge port 205b and is the refrigerant discharge port 205b on the refrigerant line 208 connected.

An expansion valve 211 is at the liquid phase refrigerant outlet of the vapor / liquid separator 209 connected and reduces the pressure of the separated liquid-phase refrigerant to expand the refrigerant. This embodiment employs a temperature-type expansion valve that isoenthalpically reduces the pressure of the refrigerant and controls a throttle opening such that the degree of overheating of the refrigerant flowing into the low-pressure port 203a the integrated with an expander fluid machine 202 is sucked in the compressor mode, approaches a specified value.

An evaporator 212 is a heat absorber attached to the expansion valve 211 is connected and the refrigerant vaporizes its pressure through the expansion valve 211 reduced to effect a heat absorption activity. The refrigerant outlet of the evaporator 212 is at the low pressure port 203a the integrated with an expander fluid machine 202 connected. A refrigerant line for connecting the evaporator 212 with the fluid machine integrated with an expander 202 is with a shut-off or check valve 212a provided, and the shut-off or check valve 212a allows the refrigerant from the refrigerant outlet of the evaporator 212 only to the low-pressure opening 203a to stream.

A heater 213 is a heat exchanger that is between the high pressure port 203b the refrigerant line 208 and the connecting portion of the refrigerant discharge port 205b is arranged and exchanges heat between the through the refrigerant line 208 flowing refrigerant and engine cooling water (hot water) to thereby heat the refrigerant.

Here, the engine cooling water through a hot water cycle 214 circulated by a broken line in 11 is shown, so the engine 201 to cool. A water pump 215 of the hot water circuit 214 is an electrically driven pump for circulating engine cooling water. A three-way valve 216 is an electromagnetic valve for switching between a circuit for introducing the engine cooling water coming out of the engine 201 in the heater 213 flows, and a circuit for not introducing the engine cooling water in the heater 213 but to cause the engine cooling water to be the heater 213 bypasses. In addition, a radiator 217 a heat exchanger that exchanges heat between the engine cooling water and the outside air to thereby cool the engine cooling water.

An opening / closing valve 218 is between the connecting portion of the refrigerant discharge port 205b the refrigerant line 208 and the radiator 207 provided, and is an electromagnetic valve, which controls the refrigerant pipe 208 opens and closes. A control valve 219 is between the high pressure port 203b the refrigerant line 208 and the heater 213 is disposed, and is an electromagnetic valve, which as a discharge valve, that is, a check valve, works, which allows the refrigerant, from the high-pressure opening 203b only to the heater 213 to flow in the compressor mode, and is brought in the expansion mode in a valve opening state.

A second bypass passage 220 is a refrigerant line for connecting the low pressure port 203a the integrated with an expander fluid machine 202 at the refrigerant inlet of the radiator 207 , The second bypass passage 220 is with a shut-off or check valve 220a provided to allow the refrigerant from the low-pressure opening 203a only to the radiator 207 to stream.

A control unit 221 performs according to the mode of operation of the fluid machine integrated with an expander 202 this control off: supply of electrical energy to a drive and electric power generation part 204 ; Connecting the drive and electric power generation part 204 to an electric energy storage battery 222 ; Switching the three-way valve 216 ; of the opening / closing valve 218 ; and the control valve 219 ,

Next, the detail of the fluid machine integrated with an expander 202 with reference to the cross-sectional view in FIG 12 described. Arrows shown in the drawing indicate an upward and downward direction (vertical direction) when the fluid machine integrated with an expander 202 is mounted in a vehicle engine room.

First, now the compression and expansion part 203 described. The compression and expansion part 203 is on the topmost portion of the fluid machine integrated with an expander 202 arranged and is provided with a mechanism for compressing and expanding the refrigerant. This compression and expansion mechanism can be manufactured with a structure similar to the publicly known spiral type compression mechanism.

In particular, the compression and expansion part contains 203 an upper case 301 ; a middle housing 302 ; a wave 303 ; a solid spiral (shell) 304 a fixed part integral with the upper housing 301 is trained; a circular spiral 305 a moving part that revolves and is in position in a room between the middle housing 302 and the solid spiral 304 shifts; a working chamber 306 a space which is between the fixed spiral 304 and the orbiting spiral 305 is formed, and in which the refrigerant is compressed and expanded; a low-pressure opening 203a , which communicate with the working chamber 306 is communicatively connected, and from which the refrigerant is sucked in and out; a high-pressure opening 203b , which communicate with the working chamber 306 is communicatively connected and from which the refrigerant is discharged and flows; and the same.

The upper case 301 and the middle case 302 work as protective elements to protect the compression and expansion part 203 , The upper case 301 is integral from the solid spiral 304 constructed and has the high pressure opening 203b and the low pressure port 203a on. The upper case 301 and the middle case 302 are coupled to each other by screws via a sealing member such as a gasket and an O-ring (not shown), and these are adapted to prevent the refrigerant from leaking from a connecting portion.

The wave 303 is a crankshaft passing through the middle housing 302 over a ball bearing 307 is worn and with an eccentric part 308 is eccentric with respect to the rotational center axis to an upper end side in the axial direction. The eccentric part 308 indicates the circling spiral 305 put on it via a needle bearing 309 is coupled.

The solid spiral 304 is from a plate-shaped base plate section 304 and a spiral tooth portion 304b constructed of the base plate section 304a to the middle housing 302 (in the downward direction) protrudes. The circling spiral 305 (movable spiral) meanwhile consists of a spiral tooth section 305b which is in contact with the tooth portion 304b the solid spiral 304 stands and engages in these, and a base plate section 305a constructed, which the tooth section 305b has trained on it.

Further, a rotation preventing mechanism (not shown) is disposed between the orbiting scroll 305 and the middle housing 302 arranged. The rotation preventing mechanism causes the orbiting scroll 305 to the eccentric section 308 to circle a circular turn while the shaft 303 rotated by one turn. When the wave 303 rotates, the orbiting spiral rotates 305 not, but revolves around the rotation center axis of the shaft 303 , In this embodiment, a pin-and-ring (pin-hole) type mechanism is employed as the rotation preventing mechanism.

The low-pressure opening 203a is an inlet / outlet of the low-pressure refrigerant, which is in the outer peripheral portion of the upper housing 301 is formed and with the section of the outermost diameter of the working chamber 306 is communicatively connected. The high-pressure opening 203b is an inlet / outlet of the high-pressure refrigerant, which is in the upper portion of the upper housing 301 is formed, and is formed at a position which communicates with the working chamber 306 communicatively connected in the state of the smallest volume.

Next, the drive and electric power generation part 204 described. The drive and electric power generation part 204 is below the compression and expansion part 203 in the middle case 302 arranged and is provided with a mechanism for driving the compression and expansion part 203 and provided for generating electrical energy. This drive and electric power generation mechanism has the same structure as a well-known DC motor.

In particular, the drive and electric power generation part 204 from the middle housing 302 , the wave 303 a stator 401 a rotor 402 that's the stator 401 set in rotation, a coupling part housing 403 for carrying the shaft 303 and the like.

The middle case 302 and the coupling part housing 403 work as the protective elements of the drive and electric energy generating part 204 , The middle case 302 and the coupling part housing 403 are coupled to each other by bolts via sealing members such as gasket and O-ring, and are capable of preventing the refrigerant from coming from a coupled portion between the middle housing 302 and the coupling part housing 403 withdraw. In addition, the middle case 302 and the wave 303 together components of the compression and expansion part 203 so as to reduce the size of the fluid machine.

The stator 401 is a stator coil with a coil wound thereon, and is on the inner wall surface of the middle case 302 attached. The rotor 402 is a magnet rotor with a permanent magnet held therein and has a keyway 404 on, which is formed on the inner peripheral side and on the shaft 303 is fixed by a wedge.

The coupling part housing 403 has a lead 403a projecting toward the middle housing (in the upward direction) in the form of a steeple head. An end section, the eccentric part 308 the wave 303 (At the lower end in the axial direction of the same) is opposite, is by this projection 403a over a ball bearing 405 carried. A lip seal 406 for preventing the leakage of the refrigerant and the oil between the driving and electric power generation parts 204 and the refrigerant pump 205 is between the ball bearings 405 and the coupling part housing 403 arranged.

Ice space passing through the inner wall surface of the middle case 302 and the wall surface on the side of the projection 403a of the coupling part housing 403 is formed, forms a space in which the shaft 303 , the stator 401 and the rotor 402 are arranged and forms at the same time an oil storage chamber 206a in a remaining space in which these parts are not arranged. The oil storage chamber 206a is an oil storage means for separating oil from the vapor-phase refrigerant and storing the separated oil.

Further, in the projection 403a a communication opening 206b provided a connection between the oil storage chamber 206a with the refrigerant suction port 205a the refrigerant pump 205 to effect. In the communication opening 206b is a shut-off or check valve 206c provided to allow the oil from the oil storage chamber 206a only to the refrigerant pump 205 to stream. In addition, there is an opening 206d on a downstream side of the check valve 206c in the flow direction of the oil in the communication port 206b educated. This opening 206d is a throttle mechanism for adjusting the amount of oil to an appropriate amount of the oil storage chamber 206a to the refrigerant pump 205 is supplied.

In this embodiment, the opening 206d on the downstream side of the check valve 206c formed in the direction of oil flow, but it may be on the upstream side of the check valve 206c be formed, in this embodiment, an opening with a minimum opening diameter of 0.5 mm is used to realize the proper amount of oil to the refrigerant pump 205 is supplied.

Next is the refrigerant pump 205 described. The refrigerant pump 205 is on the most downstream side of the fluid machine integrated with an expander 202 and is a refrigerant pressure supply means provided with a mechanism for supplying the refrigerant under pressure. In this embodiment, the refrigerant pressure supply mechanism of the refrigerant pump 205 have the same structure as the well-known spiral compression mechanism.

In particular, the refrigerant pump contains 205 a lower case 501 , the coupling part housing 403 ; the pump shaft 502 ; a solid spiral (shell) 503 one with the lower case 501 integrated part is; a circular spiral 504 (movable scroll), which is a moving element that revolves and is in position in a space between the coupling part housing 403 and the solid spiral 503 shifts; a working chamber 505 put the refrigerant in a space between the fixed spiral 503 and the orbiting spiral 504 supplies; a refrigerant suction port 205a , which communicate with the working chamber 505 communicates, and from which the refrigerant is sucked; a refrigerant discharge port 205b , which communicate with the working chamber 505 communicates and from which the refrigerant is discharged; and the same.

The lower case 501 and the coupling part housing 403 work as protective elements to protect the refrigerant pump 205 , The lower case 501 becomes integral from the solid spiral 503 constructed and has the refrigerant discharge opening 205b and the refrigerant suction port 205a on. Further, the lower case 501 and the coupling part housing 403 coupled together by screws via sealing members such as gasket and O-ring to prevent the refrigerant from leaking from the coupled portion. In addition, the coupling part housing 403 together to the components of the propulsion and electric energy generating part 204 so as to reduce the size of the fluid machine.

The pump shaft 502 is through the coupling part housing 403 over a ball bearing 506 carried. The pump shaft 502 gets on the shaft 303 through a coupling 507 coupled. The one-way clutch is a power transmitting means which has the function of transmitting the rotational driving force of the shaft only in the expansion mode 303 on the pump shaft 502 having.

Further, the pump shaft 502 a crankshaft with an eccentric part 508 which is eccentric with respect to the rotation center axis of the lower end side in the axial direction. The circling spiral 504 becomes rotatable at the eccentric part 508 coupled via a needle bearing.

The solid spiral 503 is from a plate-shaped base plate part 503a and a spiral tooth part 503b built, that of the base plate part 503a to the coupled part housing 403 (in the upward direction) protrudes. The circling spiral 504 is from a spiral tooth part 504b constructed, which in contact with the tooth part 503b the solid spiral 503 stands and engages in these, and the base plate part 504a has the tooth part 504b trained on it.

In addition, a rotation preventing mechanism (not shown) is provided between the orbiting scroll 504 and the coupling part housing 403 arranged. The rotation preventing mechanism causes the orbiting scroll 504 to the eccentric part 508 to circle one roundabout while the pump 502 rotated by one rotation. When the pump shaft 502 rotates, the orbiting spiral rotates 504 not, but revolves around the central axis of rotation of the pump shaft 502 , The rotation preventing mechanism in this embodiment employs the same pin-and-ring (pin-hole) type mechanism as the compression and expansion part 203 ,

The refrigerant suction port 205a is a suction port for the liquid-phase refrigerant, which is in the outer peripheral portion of the lower housing 501 is manufactured and with the section of the outermost diameter of the working chamber 505 is communicatively connected. The refrigerant discharge port 205b is the discharge port of the refrigerant that is in the lower portion of the lower housing 501 is manufactured, and is manufactured at a position with the working chamber 505 is communicatively connected.

Next, an oil supply passage 206 described. The oil feed passage 206 is as indicated by the arrow in 13 shown constructed in such a way that it communicatively connects in the series: the low-pressure opening 203a → the space between the middle housing 302 and the orbiting spiral 305 → the space in the ball bearing 307 → the oil storage chamber 206a → the communication opening 206b → the space in the ball bearing 405 → the space in the ball bearing 506 → the space between the coupling part housing 403 and the orbiting spiral 504 → the refrigerant suction opening 205a ,

Next, the operation of the vapor compression type refrigerator in this embodiment will be described. First, in the compressor mode, the control unit supplies 21 the propulsion and electric power generation part 204 with electrical energy and opens the opening / closing valve 218 and causes the control valve 219 to work as a check valve and switches the three-way valve 216 to the by-pass of the heater 213 ,

When the drive and electric power generation part 204 supplied with electrical energy, the shaft rotates 303 attached to the rotor 402 coupled to a rotating driving force or performance on the compression and expansion part 203 exercise. Here is in the compression and expansion part 203 when the orbiting spiral 305 in one direction with respect to the fixed spiral 304 revolves the volume of the working chamber 306 lowered; and when the orbiting spiral 305 revolving in a reverse direction, the volume of the working chamber becomes 306 increased. Therefore, the rotational direction of the rotary driving force becomes a direction to the volume of the working chamber 306 to decrease (hereinafter referred to as a "compression direction"). Therefore, in the compression mode, it flows out of the low-pressure port 203a sucked refrigerant into the working chamber 306 , will be in the working chamber 306 compressed, and is from the high-pressure opening 203b issued.

Here, a part of the vapor-phase refrigerant flowing out of the low-pressure port flows 203a was sucked into the oil storage chamber 206a that with the low-pressure opening 203a is communicatively connected. Since the refrigerant is mixed with oil to lubricate the mechanical sliding parts, the oil also flows into the oil storage chamber 206a together with the vapor-phase refrigerant. Since the oil has a larger specific gravity than the vapor-phase refrigerant, the oil is separated from the vapor-phase refrigerant by gravity, and is moved down to become the lowermost part of the oil storage chamber 206a saved. A wavy line 407 in 13 shows the level of oil stored during normal operation.

When the oil storage chamber 206a filled with the oil and the oil level rises, as by a wavy line 407a in 13 is shown, the vapor-phase refrigerant hardly flows into the oil storage chamber 206a and therefore, the oil hardly separates, resulting in the possibility of preventing the oil from being separated from the refrigerant more than necessary. Furthermore, this is in the oil storage chamber 206a stored oil in the same room as the stator 401 and the rotor 402 and therefore produces the effect of cooling the driving and electric power generating part 204 ,

That from the high-pressure opening 203b discharged refrigerant becomes pressurized to the radiator 207 through the control valve 219 , the heater 213 and the opening / closing valve 218 fed. Here, in the compressor mode, the opening / closing valve becomes 218 opened and the three-way valve 216 becomes the bypass passage of the heater 213 switched and therefore bypasses the engine cooling water in the hot water circuit 214 the heater 213 in the bypass and circulates in the order: the water pump 215 → the engine 201 → the three-way valve 216 → the radiator 217 → the hot water pump 215 , Therefore, the refrigerant is not heated and the heater 213 and the opening / closing valve 218 only work as refrigerant passages.

The refrigerant whose heat passes through the radiator 207 is radiated into the vapor-phase refrigerant and the liquid-phase refrigerant through the vapor-liquid separator 209 deposited. Here, in the compressor mode, the refrigerant pump 205 not operated and therefore the liquid-phase refrigerant in the vapor / liquid separator 209 not in the refrigerant pump 205 sucked.

The liquid phase refrigerant passing through the vapor / liquid separator 209 was reduced, reduced by the expansion valve 211 and absorbs heat in the evaporator 212 and gets out of the low-pressure opening 203 the integrated with an expander fluid machine 202 sucked.

With this, in the compressor mode, the refrigerant can be circulated in the order: the fluid machine integrated with an expander 202 → the radiator 207 → the vapor / liquid separator 209 → the expansion valve 211 the evaporator 212 → the fluid machine integrated with an expander 202 , Therefore, a vapor compression type refrigerator can be constructed, which heat, through the evaporator 212 was absorbed to the radiator 207 moves to thereby radiate the heat.

Here is the back pressure on the side of the oil storage chamber 206a the same as the pressure at the low pressure port 203a but the back pressure on the side of the refrigerant suction port 205a is higher than the pressure at the low pressure port 203a because the refrigerant suction port 205a with the vapor / liquid separator 209 is communicatively connected. If this pressure difference is the refrigerant in the vapor / liquid separator 209 caused, inversely to the oil storage chamber 206a over the oil feed passage 206 to flow, the high pressure refrigerant is returned to the low pressure port 203a sucked to cause a reduction in the refrigeration performance of the vapor-compression type refrigerator. Therefore, in this embodiment, the check valve prevents 206c the return flow of the refrigerant.

Next, in the expander mode, the controller connects 221 the propulsion and electric power generation part 204 with the energy storage battery 222 , closes the opening / closing valve 218 , opens the control valve 219 and turns on the three-way valve 216 on the heater 213 , If the three-way valve 216 on the heater 213 is switched, the engine cooling water is in the hot water circuit 214 circulated in the order: the water pump 215 → the engine 201 → the heater 213 → the three-way valve 216 → the radiator 217 → the water pump 215 , Therefore, the refrigerant in the heater 213 by the waste heat of the engine 201 heated. The heated refrigerant flows out of the heater 213 to the high-pressure opening 203b through the control valve 219 and flows from the high pressure port 203b in the working chamber 306 the compression and expansion part 203 , That in the working chamber 306 flowing refrigerant is vaporized and expanded to the volume of the working chamber 306 expand or expand, thereby the orbiting spiral 305 and the wave 303 in the direction of expansion of the volume of the working chamber 306 to rotate (hereinafter referred to as "expansion direction"). The expanded refrigerant flows out of the Needrigdrucköffnung 203a ,

This rotation also rotates the rotor 402 who is at the shaft 303 is coupled to change the amount of magnetic flux passing through the coil of the stator 401 to thereby pass the drive and electric power generation part 204 to operate as a generator. The generated electrical energy is stored in the electric energy storage battery 222 stored at the drive and electric power generation part 204 via the control unit 221 connected. That is, the waste heat of the engine 201 the refrigerant expands. The expanded refrigerant causes the fluid machine 202 , which is integrated with an expander to deliver mechanical energy. The mechanical energy is provided by the drive and electric power generation part 204 converted into electrical energy. In this way, heat energy is recovered.

Further, part of this mechanical energy becomes the driving force of the refrigerant pump 205 on the pump shaft 502 over the one-way clutch 507 transfer. Here circles in the refrigerant pump 205 when the pump shaft 502 rotates in the direction of expansion, the orbiting spiral 504 concerning the solid spiral 503 and therefore the working chamber is moving 505 from a position with the refrigerant suction port 205a is communicatively connected to the refrigerant discharge port 205b , Therefore, in the expander mode, this is from the refrigerant suction port 205a sucked liquid phase refrigerant from the refrigerant discharge port 205b to the heater 213 supplied under pressure and the refrigerant supplied under pressure is heated and expanded, so that the compression and expansion part 203 can give off more mechanical energy.

The compression rate of a scroll-type compression mechanism of the refrigerant pump 205 is one. Accordingly, even if the liquid-phase refrigerant enters the working chamber 505 is sucked, the liquid-phase refrigerant is not compressed, so that the refrigerant pump 205 does not cause any operating problems resulting from liquid compression. In the compressor mode, the driving force does not affect the refrigerant pump 205 over the one-way clutch 507 transferred and therefore the refrigerant pump 205 not operated.

Meanwhile, the refrigerant flows out of the low pressure port 203a through the second bypass passage 220 by the function of the shut-off or check valve 212a and radiates the heat through the radiator 207 and moves to the vapor / liquid separator 209 , Here flows a part of the low-pressure opening 203 flowing refrigerant into the oil storage chamber 206a , Accordingly, as well as the compressor mode, oil is separated and stored in the oil storage chamber 206a saved.

With this, in the expander mode, the refrigerant can be circulated in the order: the refrigerant pump 205 → the heater 213 → the fluid machine integrated with an expander → the second bypass passage 220 → the radiator 207 → the vapor / liquid separator 209 → the first bypass passage 210 → the refrigerant pump 205 , In this way, when refrigerant passes through in the heater 213 absorbed heat is expanded, mechanical energy through the integrated with an expander fluid machine 202 be generated in order to build the Rankine cycle.

Here is the back pressure on the side of the oil storage chamber 206a equal to the pressure at the low pressure port 203a , The back pressure on the side of the refrigerant suction port 205a becomes lower than the pressure at the low pressure port 203a This is done by a pressure loss that is caused when the refrigerant passes through the radiator 207 and the refrigerant line passes through and by sucking the refrigerant pump 205 caused negative pressure.

Due to this pressure difference that is in the oil storage chamber 206 stored oil to the refrigerant suction port 205a the refrigerant pump 205 over the oil feed passage 206 fed. The oil has a property after which it dissolves easily in the liquid-phase refrigerant. However, because the distance from the refrigerant suction port 205a to the mechanical sliding parts is short and a sufficient amount of oil can be supplied to the mechanically sliding parts, the oil can reach the mechanically sliding parts before the oil dissolves completely in the liquid-phase refrigerant. Therefore, the oil can sufficiently lubricate the mechanically sliding parts.

Ninth Embodiment

In the eighth embodiment described above, the fluid machine integrated with an expander became 202 described in which the shut-off or check valve 206c and the opening 206d into the communication opening 206b is set for the lubricating oil. In this embodiment, however, as shown by the cross-sectional view in FIG 14 shown only the opening 206d the communication opening 206b trained, but the shut-off or check valve 206c is not used. The other structure is the same as in the eighth embodiment.

When the fluid machine integrated with an expander 202 operated in the compressor mode, refrigerant flows back to the oil storage chamber 206a over the communication opening 206b by the pressure difference between the back pressure on the side of the oil storage chamber 206a and the back pressure on the side of the suction opening 205a , However, a reduction in the refrigerating capacity of the vapor compression type refrigerator caused by this backflow may be allowed if the reduction is as small as an amount that does not degrade the air conditioning function for the vehicle.

Therefore, the passage resistance of the oil supply passage becomes 206 through the opening 206d , Rooms in the ball bearings 405 and 506 and the space between the coupling part housing 403 and the orbiting spiral 504 passing the oil feed passage 206 set to make the determination of the amount of supply of the oil compatible with the limitation of the amount of backflow of the refrigerant. This produces the same effect as the eighth embodiment, even if the check valve 206c is not used.

Tenth Embodiment

In the eighth and ninth embodiments, the communication opening is 206b in the coupling part housing 403 made to the oil feed passage 206 build. In this embodiment, however, as shown by the cross-sectional view in FIG 15 shown a communication opening 261b with an opening 261d in the lower end side of the shaft 303 trained to the oil supply passage 261 train. The other structure is the same as that of the ninth embodiment.

Even if the communication opening 261b in the lower end side of the shaft 303 is formed, the same effect as in the ninth embodiment is effected. Further, the oil supply passage is 261 as indicated by an arrow in 16 shown to be communicatively connected in the following order: the low pressure port 203a → the space between the middle housing 302 and the orbiting spiral 305 → the space in the ball bearing 307 → the oil storage chamber 206a → the communication opening 261b → the space in the one-way clutch 507 → the space in the ball bearing 506 → the space between the coupling part housing 403 and the orbiting spiral 504 → the refrigerant suction opening 205a , Therefore, the refrigerant may be the mechanical sliding parts of the one-way clutch 507 lubricate.

Eleventh Embodiment

In the eighth, ninth, and tenth embodiments, the description of the vapor compression type refrigerator, which is the fluid machine, is provided 202 integrated with an expander integral with the compression and expansion part 203 is constructed, the drive and electric power generation part 204 , the refrigerant pump 205 and the oil supply passage 206 used. In this embodiment, however, as shown by a general construction diagram in FIG 17 shown the refrigerant pump 25 and an oil supply line 262 constructed as separate parts and the integrated with an expander fluid machine is not integral from the refrigerant pump 205 and the oil supply passage 206 built up.

The refrigerant pump 205 is an electrically driven pump that is mounted in the vehicle engine compartment and is only in the expansion mode with electrical energy from the control unit 221 supplied, and thereby operated. Therefore, this embodiment is not with the power transmission means for transmitting the driving force from the compression and expansion part 203 Mistake. However, if this refrigerant pump can 205 is operated only in the expander mode, a pump can be used, which drive power from the engine 201 or the compression and expansion part 203 via the power receiving means can be used, whereby it is operated.

The oil feed passage 262 is a conduit for connecting the low pressure port 203a to the refrigeration suction 205a and is a communicating connection means in this embodiment. The oil feed passage 262 is with a shut-off or check valve 262c provided that allows the oil from an oil tank 262a and the low pressure port 203a only to the refrigerant suction port 205a to flow, and with an opening 262d a throttle mechanism for adjusting the amount of oil on the downstream side of the check valve 262c in the direction of the oil.

The oil tank 262a is a tank having the function of a receiver, which has a space and the lubricating oil separates from the refrigerant by gravity and stores the lubricating oil. The oil tank 262a is an oil storage agent in this embodiment. The other structure is the same as in the eighth embodiment.

In the above-described construction, the control unit supplies 221 the refrigerant pump 205 not with electric power, and therefore, the same vapor compression type refrigerator is constructed as in the first embodiment. In the expander mode, the control unit supplies 221 the refrigerant pump 205 with electric power, and therefore, the same Rankine cycle as in the first embodiment is constructed.

Therefore, even if the refrigerant pump 205 and the oil supply line 262 separate from the fluid machine integrated with an expander 202 is built in the oil tank 262a stored oil to the refrigerant suction port 205a by the pressure difference between the low pressure port 203a and the refrigerant suction port 205a fed, and therefore can the mechanically sliding parts of the refrigerant pump 205 lubricate satisfactorily.

Twelfth Embodiment

In the eighth to eleventh embodiments described above, the vapor compression type refrigerator combined with the Rankine cycle has been described. In this embodiment, however, a cold generator specifically designed for the Rankine cycle will be described.

18 Fig. 10 is a schematic diagram showing an entire circuit structure of a refrigerator specifically for the Rankine cycle for recovering the waste heat from the vehicle engine 201 is constructed. First, the fluid machine functioning as an expander 202 the same structure as in the eighth embodiment. However, the compression and expansion part works 203 in the eighth embodiment, only as expansion means for outputting mechanical energy by the expansion of the refrigerant, and the driving and electric power generation part 204 only works as energy generating means for generating electrical energy by the mechanical energy.

In the specially designed for the Rankine cycle chiller works the fluid machine 202 not as a compressor and therefore the shaft is rotating 303 only in the expansion direction described above. That's why the wave can 303 at the pump shaft 502 be coupled, so that these integrally with each other without using the one-way clutch 507 rotate.

Next radiates the radiator 270 Heat the refrigerant off to cool the refrigerant. The refrigerant inlet of the radiator 270 is at the low pressure port 203a the fluid machine 202 connected by refrigerant pipes. A vapor / liquid separator 290 is a collector for separating from the radiator 270 flowing refrigerant into the vapor-phase refrigerant and the liquid-phase refrigerant.

The liquid phase refrigerant side of the vapor / liquid separator 290 and the refrigerant suction port 205a the refrigerant pump 205 are coupled to each other through refrigerant piping, so that the separated liquid-phase refrigerant to the refrigerant suction port 205a supply. The refrigerant discharge port 205b the refrigerant pump 205 is to the heater 213 coupled.

The heater 213 is a heat exchanger, which under pressure from the refrigerant pump 205 supplied refrigerant for the engine cooling water heat exchanged, thereby heating the refrigerant. The engine cooling water is through the same hot water cycle 214 as in the eighth embodiment circulates. The refrigerant outlet of the heater 213 is at the high pressure port 203b the fluid machine 202 coupled through the refrigerant line.

The control unit 221 connects the electric power generating means to the electric power storage battery 222 and performs the control of the switching of the three-way valve 216 by.

In the structure described above, the control unit connects 221 the electric power generating means with the electric energy storage battery 222 and turns on the three-way valve 216 to the heater 213 to build a Rankine cycle for circulating the refrigerant in the order: the heater 213 → the fluid machine 202 , which is integrated with an expander → the radiator 270 → the vapor / liquid separator 290 → the refrigerant pump 205 → the heater 213 , In the same way as in the eighth embodiment, energy can be stored in the electric energy storage battery 222 get saved.

Further, as in the eighth embodiment, the one in the oil storage chamber 206a stored oil to the refrigerant suction port 205a the refrigerant pump 205 can be supplied via the oil supply passage and therefore can the mechanically sliding parts of the refrigerant pump 205 lubricate satisfactorily.

Thirteenth Embodiment

The thirteenth embodiment uses a fluid machine incorporated in 19 instead of the vapor compression type fluid machine 202 which is integrated with an expander in the twelfth embodiment. The thirteenth embodiment is the same construction as the twelfth embodiment in other constitution. 19 is a cross-sectional view of the fluid machine 200 , In 19 For example, parts having the same or equivalent functions as those of the eighth embodiment described above are designated by the same reference numerals.

The fluid machine 200 is from an expansion part 203 ' , an electric power generation part 204 ' , a refrigerant pump 251 , an oil passage 263 and the like. In the fluid machine 200 are parts in the order of the refrigerant pump 251 , the electric power generation part 204 ' , the expansion part 203 ' arranged from the upstream side, which the arrangement order of parts of the integrated with an expander fluid machine 202 in the eighth embodiment is opposite.

The basic structure of the expansion part 203 ' is the same as that of the eighth embodiment, but it is different in the arrangement of the low-pressure port 203a , In this embodiment, the low pressure port is 203a in the outer peripheral portion of the middle housing 302 educated.

In the middle case 302 is a low-pressure refrigerant communication passage 302a that with a low pressure refrigerant outlet 301 of the housing 301 of the expansion part 203 ' is communicatively connected and the refrigerant after expansion in the middle housing 302 initiates in the outer peripheral portion of the middle housing 302 formed in such a way that it extends in the upward and downward direction.

The low-pressure opening 203a is formed at a position almost symmetrical to the upper end of the low-pressure refrigerant passage 302a with respect to the central axis of the shaft 303 is.

The basic structure of the electric power generating part 204 ' is the same as the electric power generation part 204 However, in the eighth embodiment, it is different that the low-pressure refrigerant passing through the low-pressure refrigerant 302a flows through an internal space in the middle housing 302 passes, in which the stator 401 and the rotor 402 are arranged, and reaches the low-pressure opening 203a ,

The refrigerant pump 251 is a refrigerant pressure supply means which supplies a liquid phase refrigerant to the expansion part 203 ' in the recovery of heat energy under pressure, and in this embodiment uses a publicly known pressure feed mechanism of the rolling piston type as a pressure feed mechanism.

20 is a cross-sectional view taken on the line XX-XX in 19 taken. 21 is a cross-sectional view taken on the line XXI-XXI in 20 taken. The refrigerant pump 251 contains a pump housing 511 , the coupling part housing 403 , a pump shaft 512 , a front panel 513 , a back plate 514 , a cylinder 515 , a pump rotor 516 and the same. The pump housing 511 has a refrigerant discharge port 205b and a refrigerant suction port 205a on.

The pump shaft 512 is rotatable through the front panel 513 and the back plate 514 over a ball bearing 517 worn and is a crankshaft with an eccentric section 518 , The pump rotor 516 is rotatable to the eccentric section 518 coupled.

The cylinder 515 is from the top and bottom through the front panel 513 and the back plate 514 stored in a sandwich and has a working space in which the pump rotor 516 works, and is formed on the inner peripheral side.

The back plate 514 has a refrigerant suction passage 514a for introducing refrigerant from the suction port 205a in the case 511 flows to the working space.

The front panel 513 has a refrigerant discharge passage 513a for introducing refrigerant in the working space to the refrigerant discharge port 205b on. At the exit of the refrigerant discharge passage 513a is a leaf valve as a check valve 513b provided, which allows the refrigerant only, to the refrigerant discharge port 205b to stream.

In addition, the front panel indicates 513 a suction-side communication passage 513c on, which causes the refrigerant suction port 205a with a mechanically sliding part B (in particular a space in which the eccentric part 518 is arranged) communicatively connected. This suction-side communication passage 513c exerts pressure on the suction side of the refrigerant pump 251 on the mechanically sliding part B to the back pressure of the mechanically sliding part B equal to the pressure of the refrigerant suction port 205a close.

The pump rotor 516 has a plain bearing 519 on the inner peripheral portion to one to the eccentric portion 518 to become coupled part. The amount of clearance between the outer diameter of the eccentric part 518 and the inner diameter of the sliding bearing 519 is about 20 μm to 40 μm.

A slider 515c always on the outer peripheral surface of the pump rotor 516 by a spring 515b is pressed in a cut section 515a on the inner peripheral side of the cylinder 515 arranged.

Further, the cylinder faces 515 a refrigerant suction port 515d on that with the refrigerant suction passage 514a and a refrigerant discharge port 515e communicating communicating with the refrigerant discharge 513a is communicatively connected.

In the 19 shown cross-sectional view of the refrigerant pump 251 represents a section of the refrigerant pump 251 which is located on the line XXI-XXI in 20 is taken to the representation of the refrigerant suction section 515d and the refrigerant discharge port 515e to facilitate.

The pump shaft 512 protrudes to the coupling part housing 403 (lower side in 19 ) and is connected to the wave 303 coupled. Here is the wave 303 at the pump shaft 512 be coupled using transmission means (for example, one-way clutch) which is capable of a driving force from the shaft 303 on the pump shaft 512 only transfer when the expansion part 203 ' gives off mechanical energy. In addition, a lip seal 406 between the pump shaft 512 and the coupling part housing 403 interposed to seal between them. Here is a sealing element with a different structure for the seal instead of the lip seal 406 be used. Furthermore, the pump shaft 512 an oil communication opening 520 on which causes the end of the coupling part housing 403 is communicatively connected to the mechanically sliding part B.

Next, an oil supply passage 263 described. The oil feed passage 263 is a means of communication for effecting the low pressure opening 203a is communicatively connected to the mechanically sliding part B. In this embodiment, the oil supply passage is 263 such that oil separated from the vapor phase refrigerant communicates with the stator 401 and the rotor 402 of the energy generating part 204 ' collides in the middle case 302 is arranged when the vapor-phase refrigerant from the low-pressure refrigerant outflow 301 to the low-pressure opening 203a moved, in an oil storage chamber 263a is stored, and as indicated by an arrow in 19 shown from the oil storage chamber 263a emanates, in the order: oil communication passage 303a the wave 303 → the shut-off valve 263c → the communication opening 520 the pump shaft 512 → the mechanical sliding part B. Here is a pressure of the oil storage chamber 263a equal to a pressure at the low pressure port 203a and a back pressure on the mechanical sliding part B is equal to the pressure of refrigerant on the side of the refrigerant suction port 205a because the suction side communication passage 513c is trained. Further, the pressure of refrigerant is on the side of the refrigerant suction port 205a lower than a pressure at the low pressure port 203a This is due to a pressure loss that is caused when refrigerant passes through the heat exchanger 270 and refrigerant line (s), and by negative pressure caused by the suction of the refrigerant pump 205 is effected. For this reason, in the oil storage chamber 263a stored oil to the mechanically sliding part B of the refrigerant pump 251 over the oil feed passage 263 supplied by this pressure difference.

Incidentally, in this embodiment, to the pump rotor 516 in rotation, free spaces of 5 microns to 20 microns between the front panel 513 and the pump rotor 516 or between the back plate 514 and the pump rotor 516 educated. For this reason, the liquid-phase refrigerant from the refrigerant pressure supply space to the mechanically sliding part B can pass through the clearances between the front panel 513 and the pump rotor 516 and between the back plate 514 and the pump rotor 516 flow (this liquid-phase refrigerant flowing to the mechanically sliding part B will be hereinafter referred to as "leakage refrigerant"). When the leakage refrigerant flows into the mechanically sliding part B, it is also assumed to be out of the oil supply passage 263 to the mechanical sliding part B supplied oil dissolves in the leakage refrigerant and therefore can not sufficiently lubricate the mechanically sliding part B.

Therefore, the present inventors studied the appropriate amount of oil supply with respect to the flow rate of leakage refrigerant which flows into the mechanical sliding part B. As a result, the inventors found that when the flow rate of oil supply is not less than 30% of the flow rate of liquid-phase refrigerant with respect to the flow rate (mass flow rate) of leakage refrigerant flowing into the mechanical sliding part B, the oil mechanically sliding part B can lubricate satisfactorily. Therefore, the amount of clearance between the outer diameter of the eccentric part 518 and the inner diameter of the sliding bearing 519 is set to a value of about 20 μm to 40 μm, thereby to reliably effect the amount of oil supply of not less than 30% of the flow rate of liquid-phase refrigerant.

Because the space between the front panel 523 and the pump rotor 516 is extremely small (for example, from 5 μm to 20 μm) in the thirteenth embodiment, a pressure loss develops when leakage refrigerant and oil pass through this clearance. Therefore, it is also recommended that a suction-side communication passage in the front panel 523 or the back plate 514 form, which causes the suction side of the refrigerant pump 251 with the space between the front panel 523 and the pump rotor 516 is communicatively connected. With this, the leakage refrigerant from the refrigerant pressure supply space to the suction side communication passage passes through the clearance between the front plate 513 and the pump rotor 516 and an inflow into the mechanically sliding part B is difficult.

In addition, a single or a plurality of through holes may be formed in both surfaces (upper and lower surfaces) of the pump rotor 516 be formed.

In the thirteenth embodiment, an example was shown in which the fluid machine 200 is applied to a device specifically designed for a Rankine cycle. However, the fluid machine can 200 be applied to a vapor compression type refrigerator combined with a Rankine cycle using a transmission mechanism (e.g., one-way clutch) capable of driving power from the shaft 303 on the pump shaft 512 only transfer if the expansion part 203 ' gives off mechanical energy.

Moreover, in the thirteenth embodiment, the apparatus specifically designed for a Rankine cycle in which the fluid machine is described has been described 200 integral from the expansion part 203 ' , the drive and power generation section 204 ' , the refrigerant pump 251 and the oil supply passage 263 is constructed. However, similarly to the eleventh embodiment, the refrigerant pump and the oil supply pipe may be separately constructed. In this case, when the oil from the oil supply line to the communication port 520 the pump shaft 512 flows, as well as in the third embodiment, the oil satisfactorily lubricate the mechanically sliding part B.

Further, in the thirteenth embodiment, specifically, the mechanically sliding part B is of the eccentric part 518 and the sliding part of the sliding bearing 519 constructed, but the mechanically sliding part B is not limited thereto.

Other Embodiments

Although the present invention has been fully described in connection with the preferred embodiments thereof with reference to the accompanying drawings, it is to be noted that various changes and modifications will become apparent to those skilled in the art.

For example, in the second embodiment described above, with the back pressure chamber 116 the mobile spiral 113 a plurality of small-diameter openings for adjusting the pressure between the working chamber V and the back pressure chamber 116 in addition to the passage 113c having a small diameter. The small diameter holes cause the back pressure chamber 116 with the suction side (low pressure side) of the working chamber V are communicatively connected. Hereby cause when the pressure in the back pressure chamber 116 has risen excessively, the openings of small diameter that the pressure from the back pressure chamber 116 exits to the working chamber V, so as to avoid an excessive increase in the back pressure. Further, the small diameter opening may be provided with a mechanism for supplying the liquid refrigerant to the low pressure side before the back pressure excessively increases. For example, the small-diameter opening may be provided with a safety valve which functions as this mechanism. For example, a ball-type valve, a valve secured by a spring, a ball-spring type valve may be used as the safety valve.

Further, the present invention can be applied to a fluid pump for supplying fluid under pressure such as a positive displacement pump including a scroll type pump and a rotary vane type pump. In addition, the above-described first to seventh embodiments may be appropriately combined.

In the eighth to eleventh embodiments described above, the compression and expansion part becomes 203 with the rotational driving force from the driving and electric power generation part 204 supplied and thereby driven. However, the compression and expansion part can 203 with the rotational driving force from the engine 201 be powered by the use of a power transmission mechanism, which is constructed by an electromagnetic clutch, a pulley and a belt.

Moreover, in the above-described eighth to twelfth embodiments, the scroll type pumping mechanism for the compression and expansion part (expansion means) is 203 and the refrigerant pump 205 applied. However, other types of compression and expansion mechanisms, such as rotation type, piston type and slider type, may be used.

Further, in the above-described eighth to twelfth embodiments, the energy recovered by the expander-integrated fluid machine becomes electric energy in the electric-power storage battery 22 saved. However, energy can be stored as kinetic energy through the use of a flywheel or as mechanical energy, such as elastic energy, through the use of a spring. In addition, the recovered energy described above can be used to drive the rotational drive energy of the engine 201 to support.

Still further, in the above-described embodiments, the oil is separated from the refrigerant only by the use of gravity. It is also recommended to form the refrigerant passage in a circular shape and to separate the oil from the refrigerant by the use of centrifugal force.

Such changes and modifications are to be understood as being within the scope of the present invention as defined by the appended claims.

Claims (14)

A fluid machine comprising: an expansion element ( 203 ) having a function of releasing mechanical energy by expansion of refrigerant, the expansion element having a low-pressure opening ( 203a ), from which low-pressure vapor-phase refrigerant flows out after its decompression and a high pressure port ( 203b ), from which high-pressure refrigerant flows in before its decompression; an electric energy generating element ( 204 ) having a function of generating electric power by using the mechanical energy; a refrigerant pressure feed element ( 205 ) for supplying refrigerant under pressure to the expansion element, the refrigerant pressure supply element having a refrigerant suction port ( 205a ), from which liquid-phase refrigerant is drawn, and a refrigerant discharge port ( 205b ) having, from which liquid phase refrigerant is discharged; and a communication part ( 206 . 261 . 262 ) to cause the low pressure port ( 203a ) of the expansion element with the Kältemittelsaugöffnung ( 205a ) of the refrigerant pressure feed element ( 205 ), wherein the communication part deposits lubricating oil from the vapor-phase refrigerant and supplies the lubricating oil to the refrigerant suction port (12); 205a ) feeds. A fluid machine according to claim 1, further comprising: a housing ( 301 . 302 . 403 . 501 ), which all of the elements expansion element ( 203 ), Electric power generating element ( 204 ) and refrigerant pressure feed element ( 205 ). Fluid machine according to claim 1 or 2, wherein the low-pressure opening ( 203a ) above the refrigerant suction port ( 205a ) is arranged. A fluid machine according to any one of claims 1 to 3, wherein: the expansion element is the low pressure port (10); 203a ), which above the electrical energy generating element ( 204 ) is arranged; and the refrigerant pressure feed element ( 205 ) the refrigerant suction port ( 205a ), which below the electric power generating element ( 204 ) is arranged. Fluid machine according to any one of claims 1 to 4, wherein: the communication part ( 206 . 261 . 262 ) separates the lubricating oil from the vapor-phase refrigerant by gravity using a difference in specific gravity between the vapor-phase refrigerant and the lubricating oil, and an oil storage part ( 206a . 262a ) for storing the separated lubricating oil. A fluid machine according to claim 5, wherein the oil storage part in the electric power generation element ( 204 ) is provided. Fluid machine according to any one of claims 1 to 6, wherein the communication part comprises a check valve ( 206c . 262c ) for preventing the liquid-phase refrigerant from the refrigerant suction port ( 205a ) to the low pressure port ( 203a ) flows back. A fluid machine according to claim 7, wherein: the communication part has a throttling mechanism ( 206d . 261d . 262d ) serially connected to the check valve; and the throttle mechanism has a refrigerant passage area smaller than a refrigerant passage area of the check valve. Fluid machine according to any one of claims 1 to 8, further comprising: a transmission part ( 507 ) for transmitting drive power from the expansion element to the refrigerant pressure supply element, wherein the refrigerant pressure supply element is operated by the drive power from the expansion element. Fluid machine according to claim 9, wherein the transmission part is a one-way clutch ( 507 ) which transmits the mechanical energy as the drive power from the expansion element only when the expansion element releases the mechanical energy. A fluid machine according to any one of claims 1 to 10, wherein: the expansion element is a compression and expansion element ( 203 ) having a function of compressing refrigerant by driving power applied thereto; the electric power generating element is a driving and electric power generating element ( 204 ), which reduces the drive power to the compression and expansion element ( 203 ) exercises; and when the compression and expansion element compresses refrigerant, the low pressure port sucks low pressure vapor phase refrigerant after it has been compressed, and the high pressure port discharges high pressure refrigerant before decompressing it. A fluid machine comprising: an expansion element ( 203 ) having a function of releasing mechanical energy by expansion of refrigerant; a refrigerant pressure feed element ( 205 ) for supplying refrigerant under pressure to the expansion element, wherein the expansion element is a low-pressure opening ( 203a ), from which low pressure vapor phase refrigerant after its decompression flows out, and a high pressure port ( 203b ), from which high-pressure refrigerant flows in after its decompression; a communication part ( 206 . 261 . 262 ), which introduces refrigerant contained in refrigerant flowing from the low-pressure port to a sliding part of the refrigerant pressure-feeding member, and an oil reservoir ( 262a ) which deposits and stores lubricating oil of refrigerant by gravity or centrifugal force. A vapor compression type refrigerator combined with a Rankine cycle, comprising: a compression and expansion element ( 203 ), which has a function of compressing and discharging refrigerant through it Driving power and a function of the release of mechanical energy by expansion of refrigerant, wherein the compression and expansion element has a low-pressure opening ( 203a ), from which low-pressure refrigerant is sucked and discharged after its decompression, and a high pressure port ( 203b ), from which high-pressure refrigerant is released and flows in before its decompression; a drive and electric energy generating element ( 204 ) having a function of applying drive power to the compression and expansion element and a function of generating electrical energy by mechanical energy; a refrigerant pressure feed element ( 205 ), which supplies refrigerant under pressure to the compression and expansion element, wherein the refrigerant pressure supply element, a refrigerant suction port ( 205a ), from which liquid-phase refrigerant is drawn, and a refrigerant discharge port (FIG. 205b ) from which liquid-phase refrigerant is discharged; and a communication part ( 206 . 261 . 262 ), which causes the low-pressure port to communicate with the refrigerant suction port, wherein the communication part deposits lubricating oil from the vapor-phase refrigerant and supplies the lubricating oil to the refrigerant suction port. A vapor compression type refrigerator combined with a Rankine cycle comprising: a compression and expansion element ( 203 ) having a function of compressing and discharging refrigerant by driving power applied thereto and a function of discharging mechanical energy by expansion of the refrigerant, the compression and expansion element having a low-pressure opening (FIG. 203a ), from which low-pressure refrigerant is sucked in and out after its compression, and a high pressure port ( 203b ), from which high-pressure refrigerant is discharged and flows in before its decompression; a drive and electric energy generating element ( 204 ) having a function of applying the driving power to the compression and expansion element and a function of generating electrical energy by mechanical energy; a refrigerant pressure feed element ( 251 ), which supplies refrigerant under pressure to the compression and expansion element, wherein the refrigerant pressure supply member having a refrigerant suction side and a mechanically sliding portion (B); a first communication part ( 513c ), by which the refrigerant suction side of the refrigerant pressure supply member is communicatively connected to the mechanically sliding portion (B) of the refrigerant pressure supply member; and a second communication part ( 263 ), which causes the low-pressure opening ( 203a ) is communicatively connected to the mechanically sliding portion (B), wherein the second communication part ( 263 ) Separates lubricating oil from the vapor-phase refrigerant and supplies the lubricating oil to the mechanically sliding portion (B).

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