JP2004340139A - Fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid machine in which driving of a cooling medium compressor 7 connected is not badly affected even in a case where heat energy of a Rankine cycle L cannot be sufficiently obtained. <P>SOLUTION: This fluid machine is provided with an expander 4, the cooling medium compressor 7, and a pulley 6. A rotary shaft 21 is shared by the expander 4, the cooling medium compressor 7, and the pulley 6. In a case where heat energy from the Rankine cycle L cannot be sufficiently obtained, rotation power is inputted from a driving means such as an engine connected by the pulley 6, so that driving of the cooling medium compressor 7 connected is not badly affected. In a case where rotation power is no longer inputted from the driving means, the expander 4 using the Rankine cycle L acts as the driving means to drive the cooling medium compressor 7. Even in a case where rotation power is inputted from the driving means, the driving means can be power-assisted by rotation power generated by the expander 4 to save energy. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a fluid machine including an expansion mechanism constituting a Rankine cycle and an engine accessory driven by rotational power from the expansion mechanism.

As a prior art, there is a fluid machine disclosed in Patent Document 1. This involves incorporating an expander and a compressor in a single sealed case, converting the thermal energy generated by the action of the Rankine cycle into rotational power for the expander, and driving the compressor with this rotational power to operate the refrigeration cycle. It is for driving.
JP-A-9-250474

  However, in the above-described related art, since the expander and the compressor are completely connected in the closed case, the rotational power generated by the expander cannot be used other than by the compressor. Further, when the above-described conventional fluid machine is mounted on a vehicle and the compressor is driven by using exhaust heat of a heat engine such as a vehicle engine, sufficient thermal energy is not necessarily obtained depending on a running state. May not be. In such a case, there is a problem that the compressor cannot be operated, so that air conditioning using a refrigeration cycle circulated by the compressor cannot be performed.

  The present invention has been made in view of the above-described problems of the related art, and an object of the present invention is to make it possible to use rotational power generated by an expander not only for a compressor but also for various applications. It is another object of the present invention to provide a fluid machine which does not hinder the driving of connected equipment even when the heat energy of the Rankine cycle cannot be sufficiently obtained.

  The present invention employs the technical means described in claims 1 to 24 to achieve the above object. That is, according to the first aspect of the present invention, the expansion mechanism (4) for converting the thermal energy of the Rankine cycle (L) into rotary power and the engine accessories (7, 8) driven by rotary power are provided. The rotation shafts of the expansion mechanism (4) and the engine accessories (7, 8) are integrally connected or share a rotation shaft (21). Thereby, various engine accessories (7, 8) can be driven by the expansion mechanism (4) using the Rankine cycle (L).

  According to a second aspect of the present invention, there is provided an expansion mechanism (4) for converting thermal energy of the Rankine cycle (L) into rotational power, and engine accessories (7, 8) driven by the rotational power, The rotating shafts of the expansion mechanism (4) and the engine accessories (7, 8) are integrally connected, or share the rotating shaft (21), and one end of the rotating shaft (21) protrudes outside. And driving means connected thereto.

  Accordingly, when the thermal energy of the Rankine cycle (L) is not sufficiently obtained, the rotational power is input from a driving means such as an engine connected to the rotating shaft (21) to thereby connect the connected engine accessory (7, 8). ) Does not hinder the drive. Further, even when rotational power is not input from the driving means, the expansion mechanism section (4) using the Rankine cycle (L) can drive various engine accessories (7, 8) as the driving means. Further, even when rotational power is input from the driving means, the driving means can be power-assisted by the rotational power generated by the expansion mechanism (4), thereby saving energy.

  According to the third aspect of the present invention, the expansion mechanism (4) for converting the thermal energy of the Rankine cycle (L) into rotational power, the engine accessories (7, 8) driven by the rotational power, and the rotational power A rotary shaft of the expansion mechanism (4), the engine accessories (7, 8), and the pulley mechanism (6), which are integrally connected to each other. (21) is shared.

  This constitutes a pulley mechanism (6) for receiving the rotational power from the driving means. Accordingly, when the heat energy of the Rankine cycle (L) cannot be sufficiently obtained, the rotational power is input from the driving means such as the engine connected by the pulley mechanism section (6) to thereby connect the connected engine accessory (7). , 8).

  Further, even when rotational power is not input from the driving means, the expansion mechanism section (4) using the Rankine cycle (L) can drive various engine accessories (7, 8) as the driving means. Further, even when rotational power is input from the driving means, the driving means can be power-assisted by the rotational power generated by the expansion mechanism (4), thereby saving energy.

  According to the fourth aspect of the present invention, an expansion mechanism (4) for converting heat energy of the Rankine cycle (L) into rotational power, an engine accessory (7, 8, 30) driven by the rotational power, A motor mechanism (9) for generating a rotational driving force; and the rotating shafts of the expansion mechanism (4), the engine accessories (7, 8, 30), and the motor mechanism (9) are integrally formed. It is characterized by being connected or sharing a rotating shaft (21).

  This constitutes a motor mechanism (9) as driving means. Accordingly, when the thermal energy of the Rankine cycle (L) is not sufficiently obtained, the rotational power is input from the motor mechanism (9) connected to the rotating shaft (21), thereby connecting the connected engine accessory (7, 8, 30) does not hinder driving. In addition, even when rotational power is not input from the motor mechanism (9), the expansion mechanism (4) using the Rankine cycle (L) serves as a driving unit to drive various engine accessories (7, 8, 30). Can be driven.

  Further, by driving the motor mechanism (9) with the expansion mechanism (4), it is possible to generate electric power with the motor mechanism (9). The generated power can be supplied to other auxiliary machines or stored in a storage battery. In addition, even when rotational power is input from the motor mechanism section (9), the rotational power generated by the expansion mechanism section (4) can assist the power of the motor mechanism section (9), thereby saving energy.

  The fifth aspect of the invention is characterized in that heat generated by an engine is used as a refrigerant heating means of the Rankine cycle (L). This is because it can be easily obtained as a heat source for driving the engine accessories (7, 8). In particular, if the driving means is an engine and the exhaust heat of the engine is used to heat the refrigerant of the Rankine cycle (L), the heat energy generated by the engine is recovered and the rotational power is increased. As a result, energy saving (fuel saving) can be achieved.

  The invention according to claim 6 is characterized in that the expansion mechanism (4) is of a variable capacity type whose capacity can be arbitrarily changed. The high and low pressure of the Rankine cycle (L) greatly differs depending on the state of the heat exchanger due to the external environment, the amount of heat obtained, the flow rate of the Rankine refrigerant, and the like. When the pressure changes greatly, the efficiency of the expansion mechanism (4) is also greatly affected.

  The Rankine cycle (L) side is maintained so that the state of the Rankine cycle (L) side is kept constant so that the efficiency of the expansion mechanism (4) whose design specification is determined under certain operating conditions is operated at the highest point. Although there is a control method, in the present invention, by making the expansion mechanism (4) a variable displacement type, the efficiency of the expansion mechanism (4) can be maximized regardless of the operating conditions of the Rankine cycle (L). it can.

  The invention according to claim 7 is characterized in that an opening / closing means (3) for interrupting the inflow of the refrigerant is provided on the upstream side of the refrigerant of the expansion mechanism (4). In a system using an engine, in a cold start in winter or the like, fuel efficiency and exhaust gas deteriorate unless the temperature of the cold engine is raised early. For this reason, there is a case where auxiliary equipment such as a viscous coupling is bothersomely installed in order to increase the load on the engine and obtain a warm-up.

  When the present fluid machine is applied to such a system and the engine is used as a drive unit of the fluid machine, if the opening / closing means (3) is closed when the engine needs to be warmed up, the rotating shaft (21) ), The expansion mechanism (4) is rotated, and the inlet side of the expansion mechanism (4) is depressurized until it approaches a vacuum because the supply of the refrigerant is stopped. Then, the load on the engine increases due to the decompression work, and the warm-up is promptly performed. After the warm-up, the opening / closing means (3) is opened to reduce the engine load, or the operation shifts to Rankine cycle (L) operation.

  When the warm-up is not required and the Rankine operation is not performed, the expansion mechanism (4) rotates together with the rotating shaft (21) and acts as a load to reverse power saving. Open, the load is only the stirring resistance of the Rankine refrigerant, and the increased load can be made so small that the load can be ignored.

  According to an eighth aspect of the present invention, the expansion mechanism (4) and the rotating shaft (21) are connected via an expander one-way clutch (45). The connection via the expander one-way clutch (45) interferes with the rotation of the rotating shaft (21), that is, the operation of the engine accessories (7, 8) even when the expansion mechanism (4) is stopped. Of course, it is possible to make the load so small as to be negligible.

  According to a ninth aspect of the present invention, the driving means or the pulley mechanism (6) and the rotating shaft (21) are connected via a driving input one-way clutch (61). This is because when the drive means stops and the engine auxiliary equipment (7, 8) is driven by the expansion mechanism (4), the drive means or the pulley mechanism (6) connected to the drive means and the drive input one-way. By coupling via the clutch (61), the rotation of the rotating shaft (21), that is, the operation of the engine accessories (7, 8) is not hindered even when the driving means is stopped. The load increasing on the part (4) can be made so small that it can be ignored.

  According to the tenth aspect of the present invention, the pulley mechanism (6) includes a damper (62) that absorbs torque fluctuations or a limiter (6) that cuts off power transmission at a predetermined torque value or more when excessive torque is applied. 63). This makes it possible to absorb torque fluctuations of the engine accessories (7, 8) and the expansion mechanism (4). Further, even when the engine accessories (7, 8) are locked or the like, it is possible to prevent the pulley mechanism (6) from idling so as not to apply an excessive load to the driving means, thereby preventing damage to each device.

  An eleventh aspect of the present invention is characterized in that the engine accessory (7) is a refrigerant compression mechanism (7) constituting a refrigeration cycle (R). This uses rotational power generated in the expansion mechanism (4) for refrigerant compression work.

  The twelfth aspect of the present invention is characterized in that the expansion mechanism (4) is arranged between the pulley mechanism (6) and the refrigerant compression mechanism (7). Thus, the structure of the refrigerant compression mechanism (7) can be the same as that of a normal refrigerant compressor, and the present fluid machine can be made compact.

  According to a thirteenth aspect of the present invention, the refrigerant compression mechanism (7) is of a variable displacement type capable of arbitrarily changing a compression capacity. Thereby, when the drive means stops and the refrigerant compression mechanism (7) is driven only by the expansion mechanism (4), the compression capacity of the refrigerant compression mechanism (7) is controlled to be small, and the expansion mechanism (4) is controlled. ) Can be lightened. Further, in a system using an engine as described in the seventh aspect, when it is desired to warm up the engine quickly, it is possible to increase the load on the engine as the driving means by controlling the compression capacity to be large.

  In the invention according to claim 14, the same type of refrigerant is used in the Rankine cycle (L) constituting the expansion mechanism (4) and the refrigeration cycle (R) constituting the refrigerant compression mechanism (7). Features. Thereby, the refrigerant seal between the expansion mechanism (4) and the refrigerant compression mechanism (7) does not have to be strict.

  The invention according to claim 15 is characterized in that a space between the expansion mechanism (4) and the refrigerant compression mechanism (7) is sealed by a cylindrical seal (43b). Thus, as compared with the case where the shaft seal 22 is provided, the assembling of the fluid machine can be simplified and the cost can be suppressed. Further, the mechanical loss due to the tightening force of the shaft seal 22 is reduced, which is more effective for fuel saving.

  In the invention according to claim 16, the present invention is applied to a refrigeration cycle (R) capable of hot gas bypass operation in which the discharge gas refrigerant of the refrigerant compression mechanism (7) is decompressed and directly flows into the refrigerant evaporator (14). It is characterized by: This is because, as described in the description of the thirteenth aspect, in a situation where the engine is to be warmed up quickly, the temperature of the cooling water of the engine is not sufficiently high, and the hot water heater for heating the room is not effective.

  Therefore, as described above, the refrigerant compression mechanism (7) is driven to have an engine load, and the gas refrigerant discharged from the refrigerant compression mechanism (7) flows directly into the refrigerant evaporator (14). Thereby, it is possible to heat the room at an early stage and make the room comfortable.

  In the invention according to claim 17, the expansion mechanism (4) is provided on the rotating shaft (21) on the side opposite to the side where the driving means, the pulley mechanism (6), or the motor mechanism (9) is connected. It is characterized by a structure that connects. This makes it possible to share parts other than the expansion mechanism (4) even if the expansion mechanism (4) is attached or not depending on the specification.

  The expansion mechanism (4) is characterized in that the expansion mechanism (4) is of a scroll type in which the movable scroll (53) revolves with respect to the fixed scroll (52b). This is a structure in which the scroll-type expansion mechanism (4) does not need to penetrate the rotation shaft (21), so that the configuration can be simplified.

  According to the nineteenth aspect, the rotating shaft (21) and the expansion mechanism (4) are driven by the drive force generated by the expansion mechanism (4) to increase or decrease the orbital radius of the orbiting scroll (53). It is characterized in that it is connected via a crank mechanism (58). Thus, during the expansion operation of the expansion mechanism (4), the sealing performance between the fixed scroll (52) and the orbiting scroll (53) can be improved, and the operation of the expansion mechanism (4) is stopped. In this case, the rotational load can be reduced.

  According to a twentieth aspect of the present invention, the engine accessory (8) is an alternator mechanism (8) for generating electric power by rotational power. This uses rotational power generated in the expansion mechanism (4) for power generation work. The invention according to claim 21 is characterized in that the alternator mechanism (8) is arranged between the pulley mechanism (6) and the expansion mechanism (4). Thus, the structure of the alternator mechanism (8) can be the same as that of a normal alternator, and the expansion mechanism (4) does not obstruct the ventilation to the alternator mechanism (8).

  Further, in the invention according to claim 22, the engine accessory (8) is a fan means (30) for blowing air by rotational power. This uses rotational power generated by the expansion mechanism (4) for air blowing work. In the invention according to claim 23, the fan means (30) and the motor mechanism (9) integrally connect the rotating shaft, and the motor mechanism (9) and the expansion mechanism (4) It is characterized in that it is connected between the rotating shafts via an expander one-way clutch (45).

  That is, by connecting via the expander one-way clutch (45), even if the expansion mechanism (4) is stopped, the driving of the fan means (30) by the motor mechanism (9) is not hindered. Needless to say, the load increased on the motor mechanism (9) can be made so small that it can be ignored.

  In the invention according to claim 24, the fan means (30) and the motor mechanism (9) integrally connect the rotating shaft, and the motor mechanism (9) and the expansion mechanism (4) The rotary shaft is connected via a driven crank mechanism (58) for increasing or decreasing the orbital radius of the orbiting scroll (53) by a driving force generated by the expansion operation of the expansion mechanism (4).

  Thus, during the expansion operation of the expansion mechanism (4), the sealing performance between the fixed scroll (52) and the orbiting scroll (53) can be improved, and the operation of the expansion mechanism (4) is stopped. In this case, the rotational load can be reduced. Incidentally, the reference numerals in the parentheses of the above-described units are examples showing the correspondence with specific units described in the embodiments described later.

(1st Embodiment)
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a sectional view showing the structure of the fluid machine according to the first embodiment of the present invention. In this embodiment, the present fluid machine is mounted on a vehicle, a rotary compressor is provided in a refrigeration cycle R of a vehicle air conditioner by obtaining rotational power from an engine, and Rankine heats the refrigerant by exhaust heat of the engine. The expander 4 in the cycle L is integrally formed.

  The fluid machine is broadly classified according to functions, and an expander (expansion mechanism) 4 that converts the heat energy of the Rankine cycle L into rotational power, a refrigerant compressor (refrigerant compression mechanism) 7 as an engine accessory, and an illustration. And a pulley (pulley mechanism) 6 that receives rotational power from a driving means such as an engine. The expander 4, the refrigerant compressor 7, and the pulley 6 share a shaft (rotating shaft) 21.

  First, the pulley 6 is provided with a damper portion 62 for absorbing torque fluctuations of the refrigerant compressor 7 and the expander 4, and a predetermined torque value so as not to apply an excessive load to the engine when the refrigerant compressor 7 locks or the like. This is a so-called DL pulley having the limiter 63 that idles and interrupts power transmission. The pulley 6 and the shaft 21 are connected via a drive input one-way clutch 61. Note that a configuration in which one end of the shaft 21 is protruded to the outside without providing the pulley 6, and a driving unit may be connected thereto.

  The Rankine cycle L includes a liquid supply pump 1 for supplying a refrigerant, an evaporative heater 2 for heating and evaporating a liquid refrigerant passing through a liquid refrigerant passage 2b with heat of engine cooling water passing through a cooling water passage 2a, and a high pressure refrigerant. An expander 4 that expands to generate a rotational force and a condenser 5 that cools and condenses the refrigerant are connected in this order by refrigerant pipes to form a closed loop. In the present embodiment, an on-off valve (opening / closing means) 3 such as an electromagnetic valve for interrupting the flow of the refrigerant is provided upstream of the expander 4.

  FIG. 2 is a sectional view taken along line AA in FIG. 1 and shows the structure of the expander 4. The expander 4 is called a rotary type. The expander 4 forms a closed expansion stroke working chamber 49 in order to guide the high-pressure gas into the inside and take out the work generated in the expansion process as rotational power of the shaft 21. The expansion stroke working chamber 49 is formed by being enclosed while being sealed by the following configuration.

  First, a crescent-shaped space is formed by being surrounded by the cylindrical inner wall of the cylinder 42 and the cylindrical outer wall of the sleeve 47 which is arranged while forming the rotor contact line 51 therewith. Further, the tip of the vane 48 is joined to the outer wall of the sleeve 47 by the hinge portion 48a, so that the crescent-shaped space is divided into two.

  Both end surfaces of the space divided into two have small gaps such that the front side plate 41, the rear side plate 43, the sleeve 47, and the vane 48 can move relative to each other. Are closed so that two closed working chambers 49 and 50 are formed.

  The rotor 46 is eccentric from the center of the inner wall of the cylinder 42 and attached to the shaft 21 via an expander one-way clutch 45. The sleeve 47 is fitted so as to form an oil film on the outer peripheral surface of the rotor 46 and to cover the gap with enough clearance to allow relative movement between them.

  An annular passage 43b is carved in the rear side plate 43 on the side that comes into sliding contact with the rotor 46, and a plate suction passage 43a communicating with the annular passage 43b is bored inside the rear side plate 43. The other end of the plate suction passage 43a communicates with an expander suction port 71a provided in the front housing 71.

  On the other hand, an axial suction passage 46a, which is open on the surface of the rotor 46 that is in sliding contact with the rear side plate 43 and is in fluid communication with the plate annular passage 43b, is formed with a certain depth in the axial direction. A radial suction passage 46b, which in turn extends radially to the surface of the rotor 46, is drilled therethrough. In the vicinity of the vane 48 of the sleeve 47, a sleeve suction port 47a penetrating in the thickness direction is provided.

  The refrigerant gas flowing from the expander suction port 71a of the front housing 71 passes through the plate suction passage 43a inside the rear side plate 43 and reaches the plate annular passage 43b, where the rotor 46 always slides and opens in the same positional relationship as this. Flows into the axial suction passage 46a on the end surface of the sleeve 47, reaches the sleeve 47 via the radial suction passage 46b, and is blocked by the inner wall surface.

  However, since the sleeve suction passage 47a is formed in the sleeve 47 only in a certain angle range, the refrigerant gas flows into the room inside the cylinder 42 and the expansion stroke operation chamber 49 only when the rotor radial suction passage 46b is opened. Inflow. The cylinder 42 is further provided with a vane groove 42b for accommodating the vane 48 therein with a gap capable of relatively moving while sealing the refrigerant gas.

  Since the sleeve 47 is connected to the vane 48 by the hinge portion 48a, the sleeve 47 moves together with the vane 48 and slides on the inner wall surface with the rotor 46. The space between the rear side plate 43 and the shaft 21 is sealed by the expander shaft seal 22.

  Next, the actual operation will be described. FIG. 3 is an explanatory diagram for explaining the operation of the expander 4 in the structure of FIGS. (A) When high-pressure gas is supplied from the Rankine cycle L side at a shaft rotation angle of 0 °, the high-pressure gas flows into the expansion stroke working chamber 49 through the front housing 71 → the rear side plate 43 → the rotor 46 → the sleeve 47. The inflowing high-pressure gas expands while being surrounded by the inner wall of the cylinder 42, the outer wall of the sleeve 47, the vane 48, the front side plate 41, the rear side plate 43, the vane hinge 48a, and the rotor contact line 51.

  Due to this expansion energy, the sleeve 47 shifts the rotor contact line 51 clockwise and shifts to the state of (b) a shaft rotation angle of 90 °. At this time, the expander one-way clutch 45 is integrated with the shaft 21 and rotates the shaft 21 by the same 90 °. Further, since the vane 48 is engaged with the sleeve 47 at the hinge portion 48a, the vane 48 moves in the direction in which the vane 48 is pulled out by the hinge portion 48a during the 90 ° movement.

  At (c) a shaft rotation angle of 180 ° and (d) a shaft rotation angle of 270 °, as the sealed high-pressure gas expands, the sleeve 47 is moved and shifts to a state of 90 ° to 270 °. During that time, the movement of the sleeve 47 is transmitted to the shaft 21 via the expander one-way clutch 45, and is also rotated from 180 ° to 270 °.

  When the expansion further proceeds, (a) the shaft rotation angle returns to 360 °, that is, 0 °, and the high-pressure gas in the expansion-stroke working chamber 49 expands to the discharge high-low working chamber 50 in the figure of 0 ° and shifts. Become. At the same time, a new expansion stroke working chamber 49 into which a new high-pressure gas flows is formed and appears. As long as the high-pressure gas flows in this way, the expansion machine 4 repeats the above-described state change due to the expansion of the high-pressure gas. Then, the shaft 21 continues to be driven.

  Next, an operation mode of the fluid machine will be described, including a structural description of the refrigerant compressor 7. The refrigerant compressor 7 is a variable displacement type compressor whose compression capacity can be arbitrarily changed, and is referred to as a single-swash plate type variable displacement compressor.

<Air conditioning mode>
When the operation of the air conditioner is required, the shaft 21 is rotated by the rotational power of the engine via the belt and the pulley 6, and the lug plate 76 integrally attached to the shaft 21 is also rotated. As a result, the swash plate angle varying mechanism 77 and the swash plate 78 that engage with the lug plate 76 rotate, and the piston 79 is reciprocated via the shoe 78a.

  As a result, the refrigerant is compressed and circulated through a refrigeration cycle R (not shown) to perform an air conditioning operation. Incidentally, reference numeral 72 denotes a crankcase, 73 denotes a cylinder case, 74 denotes a rear housing, and 75 denotes a valve plate.

  If a large cooling performance is not required, the inclination angle of the swash plate 78 is reduced by the input signal to the variable control valve 80, the stroke of the piston 79 is reduced, and the compression capacity of the refrigerant compressor 7 is reduced. The power consumption from the engine is reduced according to the cooling capacity. When cooling performance is not required at all, zero inclination operation is performed in which the inclination angle of the swash plate 78 is zero (vertical), that is, the piston stroke is zero, and the power consumption from the engine is minimized.

  When the exhaust heat of the engine is not sufficient in the air conditioning mode as described above, the Rankine refrigerant is not pressurized by the liquid supply pump 1 on the Rankine cycle L side, so that the high pressure gas is not supplied to the expander 4. At this time, the expander 4 does not start operation. Since the shaft 21 and the expander 4 are interposed via the expander one-way clutch 45, the rotation of the shaft 21, that is, the operation of the refrigerant compressor 7 does not hinder the operation even when the expander 4 is stopped. The increase in power consumption from the engine is also small.

  Conversely, when there is engine exhaust heat in the air conditioning mode, the Rankine refrigerant is pressurized by the liquid supply pump 1 on the Rankine cycle L side to supply high-pressure gas to the expander 4. The supply of the high-pressure gas causes the expander 4 to start operation (rotation). From the start of rotation, until the rotation speed of the expander 4 reaches the rotation speed of the shaft 21 (the refrigerant compressor 7) (that is, the rotation speed of the expander 4 <the rotation speed of the shaft 21), the action of the expander one-way clutch 45 is performed. Therefore, the expander 4 is in the idling state, and does not hinder the rotation of the shaft 21 (the refrigerant compressor 7).

  During this time, since no load acts on the expander 4, the rotation speed increases, and finally reaches the rotation speed of the shaft 21 (the refrigerant compressor 7). At this time, for the first time, the expander one-way clutch 45 is released from idling, and the shaft 21 and the expander 4 are integrated. By this action, the rotational power of the expander 4 acts on the shaft 21, and the load for driving the refrigerant compressor 7 is shared by the expander 4, thereby reducing power consumption from the engine and realizing power saving. I do.

<Idle stop mode>
If it is necessary to start air conditioning even when the engine is stopped, such as when the engine is stopped, the refrigerant compressor 7 is operated by the rotational power of the expander 4. When the exhaust heat is available even when the engine is stopped, the operation of the Rankine cycle L is continued regardless of the stop of the engine. Since the engine is stopped, the pulley 6 directly connected to the engine via the belt is in a stopped state. However, since the drive input one-way clutch 61 is disposed between the pulley 6 and the shaft 21 and can idle, the shaft 21 continues to rotate by the rotational power of the expander 4 even when the pulley 6 is stopped.

  The rotation of the shaft 21 allows the refrigerant compressor 7 to continue operating. Thus, even when the engine is stopped, the operation of the refrigerant compressor 7, that is, the air conditioner using the exhaust heat can be performed. Conversely, idle stop can be performed while maintaining a comfortable indoor space, realizing fuel saving. In this state, since the rotational power from the engine is lost and only the rotational power of the expander 4 is used, the refrigerant compressor 7 has a small inclination angle of the swash plate 78 so as to generate only the necessary minimum cooling capacity. It controls to the capacity state. Next, features of the present embodiment will be described. First, an expander 4 that converts the heat energy of the Rankine cycle L into rotational power and a refrigerant compressor 7 as an engine accessory driven by the rotational power are provided. Each of the expander 4 and the refrigerant compressor 7 Are connected integrally. Thus, the refrigerant compressor 7 can be driven by the expander 4 using the Rankine cycle L.

  Further, an expander 4 that converts the thermal energy of the Rankine cycle L into rotational power and a refrigerant compressor 7 as an engine accessory driven by the rotational power are provided. Each of the expander 4 and the refrigerant compressor 7 Are integrally connected, and one end of the shaft 21 is protruded to the outside, and driving means is connected thereto.

  Accordingly, when sufficient heat energy of the Rankine cycle L cannot be obtained, the driving of the connected refrigerant compressor 7 is not hindered by inputting rotational power from the engine connected to the shaft 21. Further, even when rotational power is not input from the engine, the expander 4 using the Rankine cycle L can serve as a driving unit to drive the refrigerant compressor 7. Further, even when the rotational power is input from the engine, the engine can be power assisted by the rotational power generated by the expander 4, thereby saving energy.

  The expansion device 4 includes an expander 4 that converts heat energy of the Rankine cycle L into rotational power, a refrigerant compressor 7 as an engine accessory driven by the rotational power, and a pulley 6 that receives the rotational power. And the rotary shafts of the refrigerant compressor 7 and the pulley 6 are integrally connected.

  This is a configuration in which the pulley 6 is configured to receive rotational power from the engine. Thus, when sufficient heat energy of the Rankine cycle L is not obtained, the driving of the connected refrigerant compressor 7 is not hindered by inputting rotational power from the engine connected by the pulley 6.

  Further, even when rotational power is not input from the engine, the expander 4 using the Rankine cycle L can serve as a driving unit to drive the refrigerant compressor 7. Further, even when the rotational power is input from the engine, the engine can be power assisted by the rotational power generated by the expander 4, thereby saving energy.

  Further, the heat generated by the engine is used as the refrigerant heating means of the Rankine cycle L. This is because it can be easily obtained as a heat source for driving the refrigerant compressor 7. In particular, if the driving means is used as an engine and the refrigerant of the Rankine cycle L is heated by using the exhaust heat of the engine, the heat energy generated in the engine is recovered and reduced as rotational power, thereby saving energy (saving energy). Fuel efficiency).

  The expander 4 and the shaft 21 are connected via an expander one-way clutch 45. By being connected via the expander one-way clutch 45, the rotation of the shaft 21, that is, the operation of the refrigerant compressor 7 is not hindered even when the expander 4 is stopped. The load can be so small that it can be ignored.

  In the above-described configuration, the expander one-way clutch 45 is interposed between the expander 4 and the shaft 21, but may be deleted. In this case, when Rankine operation is not performed, the expander 4 rotates together with the shaft 21 and acts as a load to reverse power saving. However, in this case, the load is only the stirring resistance of the Rankine refrigerant, and the increased load may be ignored. It will be minor.

  In this case, an on-off valve 3 for interrupting the flow of the refrigerant may be provided on the upstream side of the refrigerant of the expander 4. In a cold start of a vehicle equipped with an engine in winter or the like, fuel efficiency and exhaust gas deteriorate unless the temperature of the cold engine is raised early. For this reason, there is a case where auxiliary equipment such as a viscous coupling is bothersomely installed in order to increase the load on the engine and obtain a warm-up.

  When the present fluid machine is applied to such a vehicle, and the engine is used as a driving means of the present fluid machine, if the on-off valve 3 is closed when the engine needs to be warmed up, the expander 4 and the shaft 21 together with the shaft 21 at the time of engine start-up. Since the supply of the refrigerant is stopped at the inlet side of the expander 4, the pressure is reduced until the pressure approaches a vacuum. Then, the load on the engine increases due to the decompression work, and the warm-up is promptly performed.

  When the warm-up is not required and the Rankine operation is not performed, the expander 4 rotates together with the shaft 21 and acts as a load to go back to the power saving. It becomes only the stirring resistance of the refrigerant and can be made so small that the increased load can be ignored.

  The engine or the pulley 6 and the shaft 21 are connected via a drive input one-way clutch 61. This is because when the engine is stopped and the refrigerant compressor 7 is driven by the expander 4, the engine or the pulley 6 connected to the engine is connected via the drive input one-way clutch 61 to stop the engine. In this case, the rotation of the shaft 21, that is, the operation of the refrigerant compressor 7 is not hindered, and the load that increases on the expander 4 can be reduced to a negligible level.

  In addition, the pulley 6 has a damper portion 62 that absorbs torque fluctuations, or a limiter portion 63 that cuts off power transmission at a predetermined torque value or more when excessive torque is applied. Thereby, torque fluctuations of the refrigerant compressor 7 and the expander 4 can be absorbed. In addition, even when the refrigerant compressor 7 is locked or the like, it is possible to prevent the pulley 6 from idling so as not to apply an excessive load to the driving means, thereby preventing damage to each device.

  The engine accessory is the refrigerant compressor 7 that forms the refrigeration cycle R. This uses the rotational power generated by the expander 4 for refrigerant compression work. Further, the expander 4 is arranged between the pulley 6 and the refrigerant compressor 7. Thereby, the structure of the refrigerant compressor 7 can be the same as that of a normal refrigerant compressor, and the fluid machine can be configured to be small.

  The refrigerant compressor 7 is of a variable displacement type whose compression capacity can be arbitrarily changed. That is, when the engine is stopped and the refrigerant compressor 7 is driven only by the expander 4, the compression capacity of the refrigerant compressor 7 can be controlled to be small, and the load on the expander 4 can be reduced. Further, when it is desired to quickly warm up the engine in a vehicle equipped with the engine, it is possible to increase the load on the engine as the driving means by controlling the compression capacity to a large value.

  Further, the same type of refrigerant is used in the Rankine cycle L constituting the expander 4 and the refrigeration cycle R constituting the refrigerant compressor 7. Thereby, it is not necessary to make the refrigerant seal between the expander 4 and the refrigerant compressor 7 strict.

(2nd Embodiment)
FIG. 4 is a cross-sectional view illustrating a structure of a fluid machine according to a second embodiment of the present invention. The difference from the above-described first embodiment is that a motor (motor mechanism) 9 is configured between the expander 4 and the refrigerant compressor 7 in place of the absence of the pulley 6, and a configuration close to a so-called electric compressor It has become. The fluid machine is mounted on a vehicle such as a fuel cell vehicle, for example, and generates rotational power by a motor to drive a refrigerant compressor (refrigerant compression mechanism) 7 in a refrigeration cycle R of a vehicle air conditioner. For example, an expander (expansion mechanism) 4 in the Rankine cycle L for heating the refrigerant by the exhaust heat of the FC stack is integrally formed.

  The expander 4 that converts the heat energy of the Rankine cycle L into rotational power and the refrigerant compressor 7 as an engine accessory have the same structure as in the first embodiment described above, and a description thereof will be omitted. The motor 9 is configured together with the expander 4 in the front housing 71, and roughly includes a stator portion 91 and a rotor portion 92. The expander 4, the motor 9, and the refrigerant compressor 7 share a shaft (rotating shaft) 21. Next, the operation of the fluid machine will be described.

<Air conditioning mode>
When the operation of the air conditioner is necessary, the shaft 21 is rotated by the rotational power of the motor 9 and the refrigerant compressor 7 is driven. As a result, the refrigerant is compressed and circulated through a refrigeration cycle R (not shown) to perform an air conditioning operation. If the exhaust heat from the FC stack is not sufficient in such an air-conditioning mode, the Rankine refrigerant is not pressurized by the liquid supply pump on the Rankine cycle L side, so that the high-pressure gas is not supplied to the expander 4. At this time, the expander 4 does not start operation.

  Since the shaft 21 and the expander 4 are interposed via the expander one-way clutch 45, the rotation of the shaft 21, that is, the operation of the refrigerant compressor 7 does not hinder the operation even when the expander 4 is stopped. The amount of increase in power consumption from the motor 9 is also small. Conversely, when there is exhaust heat from the FC stack in the air-conditioning mode, the Rankine refrigerant is pressurized by the liquid supply pump on the Rankine cycle L side to supply high-pressure gas to the expander 4. The supply of the high-pressure gas causes the expander 4 to start operation (rotation).

  From the start of rotation, until the rotation speed of the expander 4 reaches the rotation speed of the shaft 21 (the refrigerant compressor 7) (that is, the rotation speed of the expander 4 <the rotation speed of the shaft 21), the action of the expander one-way clutch 45 is performed. Therefore, the expander 4 is in the idling state, and does not hinder the rotation of the shaft 21 (the refrigerant compressor 7). During this time, since no load acts on the expander 4, the rotation speed increases, and finally reaches the rotation speed of the shaft 21 (the refrigerant compressor 7).

  At this time, for the first time, the expander one-way clutch 45 is released from idling, and the shaft 21 and the expander 4 are integrated. By this action, the rotational power of the expander 4 acts on the shaft 21, and the load for driving the refrigerant compressor 7 is shared by the expander 4. As a result, power consumption from the motor 9 is reduced, and power saving is achieved. Realize.

<No power supply / power generation mode>
When it is necessary to operate air conditioning even when power is not supplied for driving the refrigerant compressor 7, the refrigerant compressor 7 is operated by the rotational power of the expander 4. When the waste heat from the FC stack is available, the operation of the Rankine cycle L is continued. Although the power supply to the motor 9 is stopped, the shaft 21 continues to rotate by the rotational power of the expander 4. The rotation of the shaft 21 allows the refrigerant compressor 7 to continue operating. Further, since the rotor 92 of the motor 9 is also rotated by the rotation of the shaft 21, the motor 9 can function as a generator to obtain electric power.

  As a result, even when the power supply is stopped, the operation of the refrigerant compressor 7, that is, the air conditioner using the exhaust heat can be performed, a comfortable indoor space can be maintained, and the electric power is returned by the electric power generated by the motor 9, thereby realizing energy saving. In this state, since the rotational power from the motor 9 is lost and only the rotational power of the expander 4 is used, the inclination angle of the swash plate 78 is small so that the refrigerant compressor 7 generates only the minimum necessary cooling capacity. This is to control to a small capacity state. Next, features of the present embodiment will be described. The expander 4 includes an expander 4 that converts heat energy of the Rankine cycle L into rotational power, a refrigerant compressor 7 as an engine accessory driven by the rotational power, and a motor 9 that generates rotational driving force. And the respective rotary shafts of the refrigerant compressor 7 and the motor 9 are integrally connected. In this case, the motor 9 is configured as a driving means. When the heat energy of the Rankine cycle L is not sufficiently obtained, the motor 9 is connected by inputting rotational power from the motor 9 connected to the shaft 21. It does not hinder the driving of the refrigerant compressor 7.

  Further, even when rotational power is not input from the motor 9, the expander 4 using the Rankine cycle L can serve as a driving unit to drive the refrigerant compressor 7. Further, by driving the motor 9 with the expander 4, it is possible to generate electric power with the motor 9. The generated power can be supplied to other auxiliary machines or stored in a storage battery. Further, even when the rotational power is input from the motor 9, the power of the motor 9 can be assisted by the rotational power generated by the expander 4, thereby saving energy.

(Third embodiment)
In the present embodiment, the expander 4 of the present invention is of a variable displacement type. FIG. 5 is a view showing the structure of the front side plate 41 of the variable displacement type expander 4. The front side plate 41 is divided into two parts, an outer 41a and an inner 41b. The outer 41a is provided with a hollow shape having an inner diameter slightly larger than the outer diameter of the inner 41b, and the inner 41b is incorporated in the hollow portion. The inner 41b is rotatable with respect to the outer 41a.

  The inner 41b is provided with a discharge port 41c connected to the inside of the expander 4, and the refrigerant gas that has completed the expansion process is discharged from the main discharge port 41c, and is connected to a circuit constituting the Rankine cycle L via a discharge pipe (not shown). Is sent. The inner 41b can be rotated by an actuator (not shown) to change the rotation direction (phase) with respect to the outer 41a by receiving a signal from inside or outside according to the operation state of the expander 4.

  FIG. 6 is an explanatory diagram illustrating the operation of the expander. The operation of the expander 4 described in the first embodiment will be further described separately for the expansion stroke and the discharge stroke, involving the discharge port 41c. As described above, the introduced high-pressure gas (a) expands from the state of the expansion stroke working chamber 49 with the shaft rotation angle of 0 ° to the state of the discharge stroke working chamber 50 with the shaft rotation angle of 360 °, that is, 0 °. I do. At this time, the gas in the discharge stroke working chamber 50 starts to pass through the discharge port 41c formed in the front side plate 41. When the state of the discharge stroke working chamber 50 is reached, the high-pressure gas stops expanding, and shifts to a discharge stroke in which the high-pressure gas is discharged from the discharge port 41c by the rotation of the rotor 46.

  (B) Discharge stroke of shaft rotation angle 90 ° to (d) Shaft rotation angle of 270 ° All of the working chambers 50 are in the discharge stroke, and the high-pressure gas is discharged to the outside from the discharge port 41c with the movement of the sleeve 47. move on. Therefore, the introduced high-pressure gas expands to a position that communicates with the discharge port 41c (the state of the discharge stroke working chamber 50 at a shaft rotation angle of 0 °), and thereafter shifts to discharge. This switching is determined by whether or not the discharge port 41c communicates with the working chamber. In other words, it is determined by the position of the discharge port 41c.

  Here, for example, when the low pressure (discharge side pressure) increases, the refrigerant gas in the expansion process in the expander 4 should be discharged earlier (for example, at about 270 ° instead of 360 ° of the shaft rotation angle). Otherwise, the pressure in the expansion stroke working chamber 49 will be lower than the Rankine low pressure, and rather than recovering the expansion energy of the refrigerant gas, it will require a decompression work to pull the refrigerant gas to a low pressure, thus deteriorating the efficiency. (This is called an overexpansion phenomenon.)

  However, in the state of the shaft rotation angle of 270 °, the expansion stroke working chamber 49 cannot be discharged because it has not yet been communicated with the discharge port 41c, and the decompression work is started. Conversely, when the low pressure of the Rankine cycle L becomes low, although the expansion energy can still be extracted from the refrigerant gas in the exhaust stroke working chamber 50, the refrigerant passes through the discharge port 41c during the exhaust stroke. It shifts (this is called an underexpansion phenomenon). This also causes the efficiency of the expander to deteriorate.

  Next, FIG. 7 is an explanatory diagram for explaining the variable operation of the variable displacement type expander. (A) Shaft rotation angle 0 °: When the discharge port 41c is at the position shown in the figure, the expansion stroke working chamber 49 goes into the state shown in the figure after a 360 ° expansion stroke, and becomes the discharge stroke working chamber 50 communicating with the discharge port 41c. The transition to the above has been described above. (B) Shaft rotation angle 270 °: Assuming now that the low pressure of the Rankine cycle L is rising, the inner 41b of the front side plate 41 is moved counterclockwise, for example, 90 ° by a control signal from inside or outside by an actuator (not shown). Rotate. The discharge port 41c moves to the position shown in the figure at a shaft rotation angle of 270 °. At this time, the discharge stroke working chamber 50 that leads to the discharge port 41c earlier shifts to the discharge stroke.

  Comparing the discharge stroke working chamber 50 with a shaft rotation angle of 0 ° and the discharge stroke working chamber 50 with a shaft rotation angle of 270 °, the volume at 270 ° is smaller than 0 °. This is, of course, because the 270 ° shifts to the discharge stroke earlier in the expansion stroke. In other words, when the low pressure of the Rankine cycle L is rising, the excess is similar to that at the shaft rotation angle of 0 °. That is, the expansion can be reduced. Therefore, the efficiency of the expander can be increased by moving the discharge port 41c.

  (C) Shaft rotation angle 180 ° ・ (d) Shaft rotation angle 90 °: When the low pressure of the Rankine cycle L further rises, the discharge port 41c is moved to a position of 180 ° and a position of 90 °, and the amount of movement is larger. If so, the volume at the time of transition to the discharge stroke can be reduced earlier. By making the volume of the expander 4 variable in this way, it is possible to operate the expander 4 at the maximum efficiency point in accordance with the state of the Rankine cycle L.

  Next, features of the present embodiment will be described. The expander 4 is of a variable capacity type whose capacity can be arbitrarily changed. The high and low pressures of the Rankine cycle L vary greatly depending on the state of the heat exchanger due to the external environment, the amount of heat obtained, the flow rate of the Rankine refrigerant, and the like. If the pressure changes greatly, the efficiency of the expander 4 will be greatly affected. There is also a method of controlling the Rankine cycle L side so that the state of the Rankine cycle L side is kept constant so that the efficiency of the expander 4 whose design specifications are determined assuming certain operating conditions is operated at the highest point. In the present invention, by using the expander 4 as a variable displacement type, the efficiency of the expander 4 can be maximized regardless of the operating conditions of the Rankine cycle L.

(Fourth embodiment)
FIG. 8 is an enlarged partial cross-sectional view showing a seal structure of an expander section of a fluid machine according to a fourth embodiment of the present invention. In the first embodiment, since the shaft seal 22 is disposed between the expander 4 and the refrigerant compressor 7, the Rankine refrigerant and the refrigerated refrigerant can each select an optimum refrigerant exclusively used. However, when the Rankine refrigerant and the refrigeration refrigerant are the same or the same type of refrigerant is selected, a minute leak can be tolerated even if the seal between the expander 4 and the refrigerant compressor 7 is not strict, and a substantial problem is caused. No points occur.

  Therefore, in the fourth embodiment shown in FIG. 8, a cylindrical seal portion 43b is provided in a portion corresponding to the shaft 21 of the rear side plate 43 instead of the shaft seal 22. The cylindrical seal forms a sufficiently small gap with respect to the outer peripheral surface of the shaft 21 so that an oil film is easily formed on the outer peripheral surface of the shaft 21 and, in combination with the longitudinal distance, substantially seals the flow of the refrigerant gas. It has an inner peripheral surface as shown in FIG.

  By installing the cylindrical seal portion 43b, compared to the case where the shaft seal 22 is installed, not only the assemblability can be improved and the cost is reduced, but also the mechanical loss due to the tightening force of the shaft seal 22 is reduced, and fuel consumption is reduced. Is more effective for

(Fifth embodiment)
In the present embodiment, the fluid machine according to the present invention is applied to a refrigeration cycle having a hot gas bypass circuit. FIG. 9 is a schematic diagram of a refrigeration cycle R having the hot gas bypass circuit. The refrigerant compressor 7 integrated with the expander 4 is driven by an engine (not shown) via a pulley 6. A refrigerant condenser 11 is connected to a discharge side of the refrigerant compressor 7 via a first solenoid valve 10. A first pressure reducing device 13 is connected to an outlet side of the refrigerant condenser 11 via a check valve 12. The first pressure reducing device 13 is configured by a capillary tube (fixed throttle) in this example.

  The outlet side of the first pressure reducing device 13 is connected to the refrigerant evaporator 14, and the outlet side of the refrigerant evaporator 14 is connected to the suction side of the refrigerant compressor 7 via the accumulator 15. On the other hand, a hot gas bypass passage 16 that directly connects the discharge side of the refrigerant compressor 7 to the inlet side of the refrigerant evaporator 14 is provided. In this bypass passage 16, a second solenoid valve 17 and a second pressure reducing device 18 are connected in series. It is provided in. In the present embodiment, the second pressure reducing device 18 is constituted by a constant-pressure valve that opens when the discharge pressure of the refrigerant compressor 7 exceeds a predetermined value.

  The refrigerant evaporator 14 is installed in an air conditioning case (two-dot chain line) of the air conditioner, and cools air (indoor air or outside air) blown by the air blower 19 in the cooling mode. In the heating mode, the refrigerant evaporator 14 serves as a radiator because the high-temperature refrigerant gas (hot gas) flows from the hot gas bypass passage 16 to heat the air. In the air-conditioning case, a hot-water heating heat exchanger 20 that heats blast air using hot water from the engine as a heat source is installed downstream of the refrigerant evaporator 14. Air-conditioned air is blown into the room from an outlet (not shown) provided on the downstream side.

  In a situation where the engine is to be warmed up quickly, the temperature of the cooling water of the engine is not sufficiently high, so that the hot water heater for heating the room is not effective. Therefore, as described in the first embodiment, the refrigerant compressor 7 is driven to generate an engine load, and the gas refrigerant discharged from the refrigerant compressor 7 is caused to flow directly into the refrigerant evaporator 14, thereby making the indoor Can be heated early to make it comfortable.

(Sixth embodiment)
FIG. 10 is a cross-sectional view illustrating a structure of a fluid machine according to a sixth embodiment of the present invention. In the present embodiment, the fluid machine is mounted on a vehicle, an alternator 8 for a vehicle is obtained by obtaining rotational power from an engine, and an expander 4 in a Rankine cycle L for heating a refrigerant by exhaust heat of the engine is integrally formed. It is what was constituted.

  The fluid machine is broadly classified into functions and includes an expander (expansion mechanism) 4 for converting the heat energy of the Rankine cycle L into rotational power, an alternator (alternator mechanism) 8 as an engine accessory, an engine (not shown), and the like. And a pulley (pulley mechanism) 6 that receives rotational power from the driving means. The expander 4, the alternator 8, and the pulley 6 share a shaft (rotating shaft) 21.

  First, the pulley 6 and the shaft 21 are connected via a drive input one-way clutch 61. The alternator 8 is a well-known one. Generally, a stator portion 83 and a rotor portion 84 are formed in a front housing 81 and a rear housing 82, and a regulator portion 86 is arranged in the rear housing 82 and the middle housing 85. Become composed.

  With the alternator 8 at the center, the expander 4 is disposed on the opposite end side of the pulley 6. FIG. 11 is a cross-sectional view taken along the line BB in FIG. 10 illustrating the structure of the expander 4. The expander 4 of this embodiment is a so-called scroll in which two spirals of a fixed scroll 52b and a movable scroll 53 mesh. It is a type expander. The high-pressure gas flowing from the suction port 52a provided at the center of the expander housing 52 expands in the working chamber formed by the engagement of the two spirals, and the expansion energy causes the movable scroll 53 to rotate to the outer peripheral side while being rotationally driven. And flows out of the discharge port 52d through the discharge passage 52c.

  Further, the expander 4 and the shaft 21 of the present embodiment are connected via a driven crank mechanism 58. This is to increase or decrease the orbital radius of the orbiting scroll 53 by the driving force generated by the expansion operation of the expander 4. FIG. 12 is a perspective view showing the structure of the driven crank mechanism 58, and FIG. 13 is a view as viewed from C in FIG. A key portion 21a is integrally formed at an end of the shaft 21, and the key portion 21a is formed at an angle θ in the same direction as the rotation direction with respect to a line passing through the center of the shaft 21, as shown in FIG. It is formed so as to be inclined.

  On the other hand, the bush 55 is provided with a groove 55a that is fitted to the key portion 21a and receives rotational power, and the groove 55a is installed so that the longitudinal dimension of the groove is longer than the key portion 21a. The dimensional difference is the distance between the two spiral bodies on the side forming the closed space between the spiral body of the fixed scroll 52 and the spiral body of the movable scroll 53 on a straight line passing through the center of the bush 55 and along the moving direction of the bush 55. Is smaller than.

  The width dimension of the groove is set to be larger than the key width dimension so that the bush 55 can smoothly slide in the longitudinal direction while being in contact with the key portion 21a. A balance weight 56 is integrally attached to the bush 55 so as to cancel the centrifugal force caused by the revolving motion of the orbiting scroll 53. FIG. 14 is a diagram illustrating the direction in which the bush 55 moves by the action of a force.

  (A) is a state in which the expander 4 is driven, and as shown in the figure, when a driving force F1 from the expander 4 is applied, a component force F1θ is generated to push up the bush 55 along the key groove, The distance from the center of the shaft 21 to the center of the bush 55, that is, the orbital radius R of the orbiting scroll 53 becomes large (R1).

  On the other hand, (b) shows a state in which the expander 4 is idling, and as shown in the figure, when an idling resistance F2 from the expander 4 is applied, a component force F2θ that attempts to push down the bush 55 along the keyway. Occurs, and the distance from the center of the shaft 21 to the center of the bush 55, that is, the orbital radius R of the orbiting scroll 53 becomes small (R2). Details of the operation are described in Japanese Patent Application Laid-Open No. 7-49090 filed earlier by the present applicant. Next, the operation mode of the fluid machine including the operation of the expander 4 will be described.

<Power generation mode>
When the power demand is large and the alternator 8 needs to be operated, the shaft 21 is rotated by the driving force from the engine via the belt, and the rotor unit 84 integrally attached to the shaft 21 also rotates. As a result, the alternator 8 generates electric power to cover the power demands of the engine accessories and the like and to charge a battery (not shown).

  Here, when a large amount of power is not required, the generated voltage is adjusted by the regulator unit 86 incorporated in the alternator 8 to reduce the amount of power generation, that is, reduce the driving force from the engine, and reduce the amount of power generated by the engine according to the required amount of power generation. We try to reduce power consumption. When power generation is not required at all, a non-power generation operation for minimizing power consumption from the engine is also performed by the regulator unit 86.

  When the engine exhaust heat is not sufficient in the power generation mode as described above, the Rankine refrigerant is not pressurized by a liquid supply pump or the like (not shown) on the Rankine cycle L side, so that the high-pressure gas is not supplied to the expander 4. At this time, the expander 4 does not start operation. However, the driven crank mechanism 58 and the movable scroll 53 described above are rotated by the rotation of the shaft 21 (the movable scroll 53 revolves).

  Here, since the driven crank mechanism 58 is arranged between the shaft 21 and the movable scroll 53, the driven crank mechanism 58 operates the driven scroll mechanism 53 unless the expander 4 generates a driving force due to the expansion operation. The orbital radius of the orbiting motion is reduced, a gap is created between the orbiting scroll 53 and the fixed scroll 25b, and no fluid work (vacuum operation work or gas stirring work) is performed depending on the orbital movement of the orbiting scroll 53. In addition, the driving force consumption due to the orbiting of the movable scroll 53 can be made extremely small.

  Of course, if the user does not want to idle the movable scroll 53, a one-way driving force transmission mechanism such as a one-way clutch may be provided between the shaft 21 and the movable scroll 53 in place of the driven crank mechanism 58 to reduce the idle rotation of the movable scroll 53. Can be avoided. Due to such a configuration via the driven crank mechanism 58 and the one-way clutch, the rotation of the shaft 21, that is, the operation of the alternator 8 is not hindered even when the expansion machine 4 stops the expansion operation. The increase in power consumption is also negligible.

  Conversely, when the engine exhaust heat is sufficient in the power generation mode, the Rankine refrigerant is pressurized by a liquid supply pump (not shown) on the Rankine cycle L side, and the high-pressure gas is supplied to the expander 4. The supply of the high-pressure gas causes the expander 4 to start operation (revolution). From the start of operation, until the revolution speed of the expander 4 reaches the rotation speed of the shaft 21 (alternator 8) (that is, the revolution speed of the expander 4 <the rotation speed of the shaft 21), the operation of the driven crank mechanism 58 or the one-way clutch is performed. Therefore, the expander 4 is in the idling state and does not hinder the rotation of the shaft 21 (alternator 8).

  During this time, since no load acts on the expander 4, the orbital speed of the expander 4 increases and finally reaches the rotation speed of the shaft 21 (alternator 8). At this time, for the first time, the driven crank mechanism 58 or the one-way clutch is released from idling, and the shaft 21 and the expander 4 are integrated. By this action, the revolving drive force of the expander 4 acts on the shaft 21, and the operating load of the alternator 8 is shared by the expander 4. As a result, power consumption from the engine is reduced, and power saving is realized. In the present embodiment, the expander 4 is of a scroll type, but the same effect can be obtained with other types of expanders.

<Idle stop mode>
Even when the engine is stopped, such as in idle stop, there is usually demand for power. When the power of the storage battery alone is insufficient, it is necessary to generate power, and the alternator 8 is operated by the rotational driving force of the expander 4. When the engine is stopped and the exhaust heat is available, the operation of the Rankine cycle L is continued regardless of the stop of the engine.

  Since the engine is stopped, the pulley 6 directly connected to the engine via the belt is in a stopped state, but a drive input one-way clutch 61 is disposed between the pulley 6 and the shaft 21 so that the idle can be performed. Even when the pulley 6 is stopped, the shaft 21 continues to rotate by the driving force of the expander 4. The alternator 8 can be operated by the rotation of the shaft 21. As a result, the alternator using the exhaust heat, that is, the power generation can be performed even when the engine is stopped.

  Conversely, idle stop can be performed while maintaining power supply, thereby realizing fuel economy. The alternator 8 controls the regulator 86 to generate a smaller amount of electric power so as to generate only the minimum necessary electric power, since the driving force from the engine is lost and the operation is performed only by the driving force of the expander 4.

<Non-power generation mode>
The operation of the alternator 8 is suspended when the power demand is small, when the storage battery is about to be overcharged, or when the engine operation efficiency is poor due to aggressive fuel-saving operation (the power generation work is reduced by the regulator 86 to zero). To). Even in this case, if there is engine exhaust heat, the Rankine operation is continued, and the driving force generated by the expander 4 is transmitted from the shaft 21 to the driving input one-way clutch 61 to the pulley 6, and further to the engine torque via the belt. Offer. Thus, the driving force of the expander 4 can assist the driving force of the engine. Therefore, the load on the engine is reduced, and especially when the operation efficiency of the engine is poor, it is possible to lead to fuel-saving operation. Next, features of the present embodiment will be described. First, the shaft 21 has a structure in which the expander 4 is connected to the driving means or the side opposite to the side to which the pulley 6 is connected. This makes it possible to share parts other than the expander 4 even if the expander 4 is attached or not depending on the specification. The expander 4 is of a scroll type in which the movable scroll 53 revolves with respect to the fixed scroll 52b. This is a structure in which the scroll type expander 4 does not need to penetrate the shaft 21, so that the configuration can be simplified.

  The shaft 21 and the expander 4 are connected via a driven crank mechanism 58 that increases and decreases the orbital radius of the orbiting scroll 53 by a driving force generated by the expansion operation of the expander 4. Thereby, during the expansion operation of the expander 4, the sealing performance between the fixed scroll 52b and the movable scroll 53 can be improved, and when the operation of the expander 4 is stopped, the rotational load can be reduced. .

  The engine accessory was an alternator 8 that generates electric power using rotational power. This uses rotational power generated by the expander 4 for power generation work. Further, an alternator 8 is arranged between the pulley 6 and the expander 4. Thus, the structure of the alternator 8 can be the same as that of a normal alternator, and the expander 4 does not obstruct the ventilation to the alternator 8.

(Seventh embodiment)
FIG. 15 is a partial sectional view showing the structure of the fluid machine according to the seventh embodiment of the present invention. The fluid machine of the present embodiment includes, for example, a blower fan (fan means) 30 that blows air to various heat exchangers of a vehicle, and a motor 9 that drives the blower fan 30, for example, heats the refrigerant by exhaust heat of the engine. The expander 4 in the Rankine cycle L to be performed is integrally formed. Therefore, the present fluid machine is roughly divided into functions, and the blower fan 30 as an engine accessory, the expander 4 that converts the heat energy of the Rankine cycle L into rotational power, the blower fan 30 is driven, and And a motor 9 for converting rotational power into electric energy.

  The blower fan 30 is integrally fastened to the shaft 21 of the motor 9 by a bolt (not shown), and has a structure in which the rotating shafts of the motor 9 and the expander 4 are connected via an expander one-way clutch 45. I have. However, when the scroll type expander 4 is used as in the embodiment shown in FIG. 15, instead of the expander one-way clutch 45, it is connected via a driven crank mechanism 58 similar to the sixth embodiment described above. It may have a structure.

  The motor 9 for generating rotational power has a structure similar to that of the second embodiment, and the scroll-type expander 4 for converting the heat energy of the Rankine cycle L to rotational power has the same structure as that of the above-described sixth embodiment. Therefore, the description is omitted. The fan 30 in FIG. 15 uses a well-known centrifugal multi-blade fan (sirocco fan). The expander 4 is hermetically housed in a case separate from the motor 9 and is fastened by bolts (not shown). The expander 4 is under a Rankine cycle refrigerant atmosphere, and is separated from the motor 9 by a shaft seal 22. Next, the operation of the fluid machine will be described.

<When Rankine cycle is running>
When the Rankine cycle is operating, the expander 4 drives the rotor 92 and the shaft 21 of the motor 9. An electromotive force is generated in the motor 9 by this driving. In other words, the rotation of the motor 9 driven by the expander 4 is caused to function as a power generator this time to generate power. At this time, the fan 30 sharing the shaft 21 is also driven at the same time. That is, the fan 30 is driven at the same rotation speed as the motor 9.

  As a result, thermal energy is generated by the action of the expander 4, and the generated power is supplied to other auxiliary equipment or stored in a storage battery, thereby eliminating the need for power generation by an alternator or the like, thereby saving the power of the vehicle. Can be realized. At the same time, the fan 30 is operated to contribute to heat dissipation and the like. Conversely, no special power is required for heat dissipation, and power saving of the vehicle can be realized.

  Further, by adjusting the power generation load of the motor 9 on the circuit, the rotation speed of the fan 30 can be changed. When more heat radiation is required, the rotation speed of the expander 4 can be increased by lowering the power generation load, and the rotation speed of the fan 30 can also be increased. This indicates that the driving force of the expander 4 can be arbitrarily distributed to the generator and the fan 30 by adjusting the power generation load of the motor 9 on the circuit.

  Of course, when the necessity of heat radiation is reduced, the power generation load is increased to increase the power generation amount, and conversely, the rotation speed of the fan 30 can be reduced to reduce the work amount of the fan 30. Further, if the power generation load is extremely reduced, the independent operation of the substantial fan 30 by the expander 4 is also possible.

<When Rankine cycle is not operating>
When the heat energy for operating the Rankine cycle is insufficient, the expander 4 cannot be driven. Even in this case, there is a case where heat needs to be released, and the fan 30 must be driven. At this time, a voltage is applied to the motor 9 from an external power supply (not shown) through a power supply line (not shown). When the motor 9 starts rotating, the fan 30 sharing the shaft 21 also starts operating.

  By the way, since the Rankine cycle is not operating, the expander 4 is not performing expansion work, and the movable scroll 53 of the expander is dragged by the shaft 21 driven by the motor 9. However, since the one-way clutch 45 (or the driven crank mechanism 58) is disposed between the shaft 21 and the movable scroll 53, the drag operation of the movable scroll 53 can be avoided while the expander 4 is stopped.

  It goes without saying that the rotation speed of the fan 30 can be adjusted by the voltage applied to the motor 9. By operating the motor 9 when the Rankine cycle is not operating, the fan 30 can be operated even when there is not enough heat energy, and heat radiation can be realized.

<When large air volume is required>
When a large heat radiation that may cause overheating is required, the rotation speed of the fan 30 must be increased. At this time, at the same time as the operation of the expander 4, a voltage is applied to the motor 9 to rotate it as an electric motor. As a result, the fan 30 is driven by adding the driving force of the motor 9 to the driving force of the expander 4, so that a fan having a high rotation speed can be obtained.

<Other embodiments>
FIG. 16 is a partial sectional view showing another embodiment of the fluid machine in FIG. In the configuration described above, a sirocco-type fan is used for the blower fan (fan means) 30 as an engine accessory, but only an axial-flow fan is used. With this, the same operation and effect as described above can be obtained. The present invention does not limit the type of the blower fan 30, and another type of blower fan may be used.

(Other embodiments)
In the above-described embodiment, the refrigerant compressor / alternator and the blower fan have been described as examples of the engine accessory driven by the expander. However, the present invention is not limited to this, and the hydraulic pressure for generating the hydraulic pressure for power steering is described. A pump, a water pump that circulates engine cooling water, and a device such as a viscous coupling that is a start-up auxiliary heat source during cold start may be used. In addition, the present invention may be applied not only to vehicles but also to the driving of rotating equipment in stationary engine drive systems such as engine driven air conditioners.

FIG. 1 is a cross-sectional view illustrating a structure of a fluid machine according to a first embodiment of the present invention. It is AA sectional drawing in FIG. 1, and shows the structure of an expander. FIG. 3 is an explanatory diagram for explaining the operation of the expander in the structure of FIGS. It is a sectional view showing the structure of the fluid machine in a 2nd embodiment of the present invention. It is a figure showing the structure of the front side plate of the variable displacement type expander in a third embodiment of the present invention. It is explanatory drawing explaining operation | movement of an expander. It is explanatory drawing explaining the variable operation | movement of a variable displacement type expander. It is a partial section enlarged drawing showing the seal structure of the expander part of the fluid machine in a 4th embodiment of the present invention. It is a mimetic diagram of a refrigeration cycle which has a hot gas bypass circuit in a 5th embodiment of the present invention. It is sectional drawing which shows the structure of the fluid machine in 6th Embodiment of this invention. It is BB sectional drawing in FIG. 10 explaining the structure of an expander. It is a perspective view showing the structure of the driven crank mechanism in a 6th embodiment of the present invention. It is C view in FIG. It is a figure explaining the direction which a bush moves by the action of force. It is a fragmentary sectional view showing the structure of the fluid machine in a 7th embodiment of the present invention. FIG. 16 is a partial cross-sectional view illustrating another embodiment of the fluid machine in FIG. 15.

Explanation of reference numerals

3 opening / closing valve (opening / closing means)
4 Expander (expansion mechanism)
6 Pulley (Pulley mechanism)
7 Refrigerant compressor (refrigerant compression mechanism, engine auxiliary equipment)
8 Alternator (alternator mechanism, engine accessory)
9 Motor (motor mechanism)
14 Refrigerant evaporator 21 Shaft (rotary axis)
30 blower fan (fan means)
43b cylindrical seal 45 expander one-way clutch 52 fixed scroll 53 movable scroll 58 driven crank mechanism 61 drive input one-way clutch 62 damper 63 limiter R refrigeration cycle L Rankine cycle

Claims (24)

An expansion mechanism (4) for converting heat energy of the Rankine cycle (L) into rotational power;
Engine accessories (7, 8) driven by rotational power,
A fluid machine, wherein the respective rotation shafts of the expansion mechanism (4) and the engine accessories (7, 8) are integrally connected or share a rotation shaft (21). An expansion mechanism (4) for converting heat energy of the Rankine cycle (L) into rotational power;
Engine accessories (7, 8) driven by rotational power,
The rotating shafts of the expansion mechanism (4) and the engine accessories (7, 8) are integrally connected or share a rotating shaft (21), and one end of the rotating shaft (21) is A fluid machine characterized by projecting outside and connecting drive means thereto. An expansion mechanism (4) for converting heat energy of the Rankine cycle (L) into rotational power;
Engine accessories (7, 8) driven by rotational power;
A pulley mechanism (6) for receiving rotational power;
The rotating shafts of the expansion mechanism (4), the engine accessories (7, 8), and the pulley mechanism (6) are integrally connected or share a rotating shaft (21). And fluid machinery. An expansion mechanism (4) for converting heat energy of the Rankine cycle (L) into rotational power;
Engine accessories (7, 8, 30) driven by rotational power;
A motor mechanism (9) for generating a rotational driving force;
The rotating shafts of the expansion mechanism (4), the engine accessories (7, 8, 30) and the motor mechanism (9) are integrally connected or share a rotating shaft (21). A fluid machine characterized by the above.   The fluid machine according to any one of claims 1 to 4, wherein heat generated by an engine is used as refrigerant heating means of the Rankine cycle (L).   The fluid machine according to any one of claims 1 to 4, wherein the expansion mechanism (4) is a variable capacity type whose capacity can be arbitrarily changed.   The fluid machine according to any one of claims 2 to 4, wherein an opening / closing means (3) for interrupting the inflow of the refrigerant is provided on the upstream side of the refrigerant of the expansion mechanism (4).   The fluid machine according to any one of claims 2 to 4, wherein the expansion mechanism (4) and the rotating shaft (21) are connected via an expander one-way clutch (45).   The drive means or the pulley mechanism (6) and the rotary shaft (21) are connected via a drive input one-way clutch (61). Fluid machinery.   The pulley mechanism section (6) has a damper section (62) for absorbing a torque fluctuation or a limiter section (63) for cutting off power transmission at a predetermined torque value or more when excessive torque is applied. The fluid machine according to claim 3, wherein   The fluid machine according to any one of claims 1 to 4, wherein the engine accessory (7) is a refrigerant compression mechanism (7) constituting a refrigeration cycle (R).   The fluid machine according to claim 11, wherein the expansion mechanism (4) is disposed between the pulley mechanism (6) and the refrigerant compression mechanism (7).   The fluid machine according to claim 11, wherein the refrigerant compression mechanism (7) is of a variable capacity type capable of arbitrarily changing a compression capacity.   12. The refrigerant of the same type is used for the Rankine cycle (L) constituting the expansion mechanism (4) and the refrigeration cycle (R) constituting the refrigerant compression mechanism (7). A fluid machine according to claim 1.   The fluid machine according to claim 14, wherein a space between the expansion mechanism (4) and the refrigerant compression mechanism (7) is sealed by a cylindrical seal (43b).   12. A refrigerating cycle (R) capable of hot gas bypass operation in which a refrigerant gas discharged from said refrigerant compression mechanism (7) is decompressed and directly flows into a refrigerant evaporator (14). A fluid machine according to claim 1.   A structure in which the expansion mechanism (4) is connected to a side of the rotating shaft (21) opposite to a side to which the driving means, the pulley mechanism (6), or the motor mechanism (9) is connected; The fluid machine according to any one of claims 2 to 4, characterized in that:   The fluid according to any one of claims 2 to 4, wherein the expansion mechanism (4) is of a scroll type in which a movable scroll (53) revolves with respect to a fixed scroll (52b). machine.   The rotating shaft (21) and the expansion mechanism (4) are driven crank mechanisms (58) that increase or decrease the orbital radius of the orbiting scroll (53) by a driving force generated by the expansion operation of the expansion mechanism (4). The fluid machine according to claim 18, wherein the fluid machine is connected via a fluid path.   The fluid machine according to any one of claims 1 to 4, wherein the engine accessory (8) is an alternator mechanism (8) that generates electric power by rotational power.   The fluid machine according to claim 20, wherein the alternator mechanism (8) is disposed between the pulley mechanism (6) and the expansion mechanism (4).   The fluid machine according to claim 4, wherein the engine accessory (30) is a fan means (30) that blows air by rotational power.   The fan means (30) and the motor mechanism section (9) integrally connect a rotating shaft, and the motor mechanism section (9) and the expansion mechanism section (4) have an expander one-way between the rotating shafts. 23. The fluid machine according to claim 22, wherein the fluid machine is connected via a clutch (45).   The fan means (30) and the motor mechanism (9) integrally connect a rotating shaft, and the motor mechanism (9) and the expansion mechanism (4) are connected between the rotating shafts by the expansion mechanism. 23. The unit according to claim 18 or 22, wherein the unit is connected via a driven crank mechanism (58) that increases or decreases the orbital radius of the orbiting scroll (53) by a driving force generated by an expansion operation of the unit (4). Fluid machinery.

Images