JP2004278459A - Hybrid driving auxiliary machine and its controlling device - Google Patents

Hybrid driving auxiliary machine and its controlling device Download PDF

Info

Publication number
JP2004278459A
JP2004278459A JP2003073377A JP2003073377A JP2004278459A JP 2004278459 A JP2004278459 A JP 2004278459A JP 2003073377 A JP2003073377 A JP 2003073377A JP 2003073377 A JP2003073377 A JP 2003073377A JP 2004278459 A JP2004278459 A JP 2004278459A
Authority
JP
Japan
Prior art keywords
shaft
electromagnetic clutch
compressor
refrigerant
engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2003073377A
Other languages
Japanese (ja)
Other versions
JP4047205B2 (en
Inventor
Hirotomo Asa
Yasushi Suzuki
Keiichi Uno
慶一 宇野
康 鈴木
弘知 麻
Original Assignee
Denso Corp
Nippon Soken Inc
株式会社デンソー
株式会社日本自動車部品総合研究所
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp, Nippon Soken Inc, 株式会社デンソー, 株式会社日本自動車部品総合研究所 filed Critical Denso Corp
Priority to JP2003073377A priority Critical patent/JP4047205B2/en
Publication of JP2004278459A publication Critical patent/JP2004278459A/en
Application granted granted Critical
Publication of JP4047205B2 publication Critical patent/JP4047205B2/en
Application status is Expired - Fee Related legal-status Critical
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/45Hybrid prime mover

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hybrid driving auxiliary machine that has a relatively simple structure and enables operation of an accessory and power generation by a motor by reducing an engine load, and a controlling device of the hybrid driving auxiliary machine. <P>SOLUTION: The hybrid driving auxiliary machine is applied to a refrigerating cycle 200 for a vehicle equipped with a Rankine cycle 201 having a heater 250 for heating a refrigerant. This hybrid driving auxiliary machine is provided with a rotary machine 130 having functions of both an electric motor and a generator; the accessory 140 that operates as a compressor at the time of rotation in one direction and as an expander in the rotational side in the other direction by reverse inflow of a superheated steam refrigerant from the heater 250; a torque distributing mechanism 150 that enables driving torque distribution among a drive shaft 111, a rotary machine shaft 131 and an accessory shaft 141; a lock mechanism 160 that locks the drive shaft 111, when an electromagnetic clutch 120 is disengaged; and a fixing mechanism 170 that makes a rotor part 132 of the rotary machine 130 fixed, when the electromagnetic clutch 120 is engaged. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a hybrid drive auxiliary machine mounted on an idle stop vehicle or a hybrid vehicle in which an engine is stopped according to a running state and suitable for a refrigeration cycle including a Rankine cycle, and a control device therefor.
[0002]
[Prior art]
2. Description of the Related Art In recent years, there is an example in which an idle stop vehicle or a hybrid vehicle is put on the market from the viewpoint of fuel saving. In these vehicles, since the engine is stopped in accordance with the running state, the compressors in the refrigeration cycle, which operate by receiving the driving force of the engine, stop together when the engine is stopped, and the cooling function Will not be fulfilled.
[0003]
In order to solve this, for example, as shown in Patent Document 1, a pulley to which the rotation of the engine is transmitted and a compressor are connected via an electromagnetic clutch, and further connected to a rotation shaft on the side opposite to the pulley of the compressor. One using a hybrid compressor connected to a motor is known.
[0004]
Thus, when the engine is stopped, the electromagnetic clutch can be disconnected and the compressor can be operated by the motor, so that the cooling function of the refrigeration cycle is performed regardless of whether the engine is operating or stopped.
[0005]
[Patent Document 1]
JP-A-2000-130323
[0006]
[Problems to be solved by the invention]
However, in the above-described conventional technology, when the compressor is operated by the engine, the motors connected to the same rotating shaft are simultaneously rotated, and the motor has a power generation function. Will lead to worse fuel economy. In particular, when the engine is operating at a high rotation speed during high-speed running or the like, the motor also operates at a high rotation speed, and the internal magnetic flux fluctuates at a high frequency, so that iron loss increases and the load on the engine increases.
[0007]
As a countermeasure, an intermittent mechanism such as a clutch may be provided between the compressor and the motor, and the intermittent mechanism may be disconnected during operation of the engine to make the motor inoperative, but this complicates the structure.
[0008]
In view of the above problems, an object of the present invention is to provide a hybrid drive accessory and a control device therefor that enable operation of the accessory and power generation by a motor by reducing the load on the engine with a relatively simple structure. It is in.
[0009]
[Means for Solving the Problems]
The present invention employs the following technical means to achieve the above object.
[0010]
According to the first aspect of the present invention, in a hybrid drive auxiliary machine provided with a heater (250) for heating a refrigerant and applied to a refrigeration cycle (200) for a vehicle including a Rankine cycle (201), an engine of the vehicle is used. An electromagnetic clutch (120) that is provided on a drive shaft (111) that receives the driving force from (10) to rotate and drives and intermittently transmits the driving force from the engine (10), and has both functions of a motor and a generator. A rotating machine (130) and an auxiliary machine (140) that operates as a compressor that compresses the refrigerant during one-way rotation, and that operates as an expander on the other direction rotating side due to reverse flow of superheated vapor refrigerant from the heater (250). ), A drive shaft (111), a rotating machine shaft (131) of the rotating machine (130), and an auxiliary machine shaft (141) of the auxiliary machine (140). A torque distribution mechanism (150) for distributing torque to the other two shafts (131, 141), and a drive shaft from the rotating machine shaft (131) or the auxiliary machine shaft (141) when the electromagnetic clutch (120) is disconnected. When the lock mechanism (160) for preventing transmission of drive torque to the (111) and the electromagnetic clutch (120) are connected, the rotor section (132) of the rotating machine (130) is connected to the coil (120) of the electromagnetic clutch (120). 121) and a fixing mechanism (170) for attracting the rotor section (132) to a fixed state.
[0011]
Thus, when the engine (10) is operating, the electromagnetic clutch (120) can be connected to operate the accessory (140) as a compressor with the driving force of the engine (10), and the engine (10) can be stopped. At times, the electromagnetic clutch (120) is disengaged, and the auxiliary machine (140) can be operated as a compressor by the driving force of the rotating machine (130). The cycle (200) can be activated.
[0012]
Here, when the electromagnetic clutch (120) is connected, the rotor (132) of the rotating machine (130) is fixed by the fixing mechanism (170) that can be formed with a relatively simple structure using the existing members (121, 132). Can be fixed so that the rotating machine (130) does not operate as a generator, so that the load on the operating engine (10) can be reduced.
[0013]
When the refrigeration cycle (200) is stopped, the electromagnetic clutch (120) is disconnected, and the auxiliary machine (140) is operated as an expander by the superheated steam refrigerant from the heater (250), whereby the rotating machine ( 130) can be operated as a generator to generate electric power without directly using the driving force from the engine (10).
[0014]
As described in the second aspect, each shaft (111, 131, 141) corresponds to one of the sun gear (151) of the planetary gear (150), the planetary carrier (152), and the ring gear (153). By connecting, the torque distribution mechanism (150) can be easily formed.
[0015]
According to the third aspect of the invention, the drive shaft (111) is connected to the planetary carrier (152), and the lock mechanism (160) rotates only in the normal rotation direction of the drive shaft (111). A one-way clutch (160) that permits driving is characterized.
[0016]
Thereby, when the electromagnetic clutch (120) is disengaged, one of the rotating machine (130) and the auxiliary machine (140) is operated in a direction opposite to the normal rotation direction of the drive shaft (111), so that the tailgating is performed. The drive shaft (111) to be driven is locked by the one-way clutch (160), and the drive torque can be transmitted to the other of the rotating machine (130) and the auxiliary machine (140), which corresponds to an inexpensive locking mechanism. be able to.
[0017]
Further, in the invention described in claim 4, the rotating machine shaft (131) is connected to correspond to the sun gear (151), and the auxiliary machine shaft (141) is connected to correspond to the ring gear (153). It is characterized by:
[0018]
Accordingly, when the rotating machine (130) operates the auxiliary machine (140) as a compressor, the rotating machine (130) can be decelerated with respect to the rotating machine (130) and a large reduction ratio can be obtained. It is possible to use a rotary machine (130) of a mold type, and it is possible to reduce the size and cost.
[0019]
When the auxiliary machine (140) is operated as an expander and the rotating machine (130) is operated as a generator by its driving torque, the speed of the auxiliary machine (140) is increased and the speed increase ratio is increased. Therefore, the amount of power generated by the rotating machine (130) can be increased, and the size of the rotating machine (130) can be similarly reduced.
[0020]
According to a fifth aspect of the present invention, the hybrid drive accessory (100A) according to any one of the first to fourth aspects, the operation of the heater (250), the intermittent rotation of the electromagnetic clutch (120), and the rotation. And a controller (180) for controlling the operation of the machine (130), wherein the controller (180) activates the refrigeration cycle (200) when the engine (10) is operated. In this case, the electromagnetic clutch (120) is connected, the accessory (140) is operated as a compressor, and when the engine (10) is stopped, the refrigeration cycle (200) is operated. ) Is turned off, the auxiliary machine (140) is operated as a compressor by the rotating machine (130), and the refrigeration cycle (200) is stopped when the engine (10) is operated. When, cutting the electromagnetic clutch (120) is characterized by actuating the auxiliary machine (140) as the expander by the heater (250).
[0021]
Thereby, the same effects as those of the first to fourth aspects of the invention can be obtained.
[0022]
Note that the reference numerals in parentheses of the above means indicate the correspondence with specific means described in the embodiment described later.
[0023]
BEST MODE FOR CARRYING OUT THE INVENTION
(1st Embodiment)
1 to 5 show a first embodiment of the present invention. First, a specific configuration will be described with reference to FIGS.
[0024]
The hybrid drive auxiliary device 100A is applied to a refrigeration cycle 200 mounted on a so-called idle stop vehicle in which the engine 10 is stopped when the vehicle is temporarily stopped during running operation. The operation of the hybrid drive accessory 100A is controlled by the control device 180 to form the hybrid drive accessory control device 100.
[0025]
Although details will be described later, the auxiliary machine referred to here is an expansion machine that operates as a compressor that compresses the refrigerant in the refrigeration cycle 200 and that is heated by the superheated vapor refrigerant heated by the heater 250 of the Rankine cycle 201. Hereinafter, the auxiliary machine will be referred to as a compressor, and the hybrid drive auxiliary machine will be referred to as a hybrid compressor.
[0026]
As shown in FIG. 1, the refrigeration cycle 200 includes a Rankine cycle 201 including a heater 250 that uses waste heat generated by the vehicle engine 10 as a heating source.
[0027]
The condenser 210 is a heat exchanger that is connected to the discharge side (refrigerant discharge port 148b) of the compressor 140 incorporated in the hybrid compressor 100A described later, and that condenses and liquefies the refrigerant while releasing heat. The gas-liquid separator 220 is a receiver that separates the refrigerant flowing out of the condenser 210 into a gas-phase refrigerant and a liquid-phase refrigerant. The decompressor 230 decompresses and expands the liquid-phase refrigerant separated by the gas-liquid separator 220. In the present embodiment, the decompressor 230 decompresses the refrigerant in an isenthalpy manner, and at the same time, superheats the refrigerant drawn into the compressor 140. Is a temperature-type expansion valve that controls the degree of opening of the throttle so that the value becomes a predetermined value.
[0028]
The evaporator 240 is a heat exchanger that evaporates the refrigerant depressurized by the decompressor 230 and cools the conditioned air by the latent heat of evaporation at that time. The refrigerant outlet of the evaporator 240 has a refrigerant inlet of the compressor 140. A check valve 240a that allows the refrigerant to flow only to 146a is provided. The compressor 140, the condenser 210, the gas-liquid separator 220, the decompressor 230, and the evaporator 240 form a closed circuit to form the refrigeration cycle 200.
[0029]
The heater 250 is provided in a refrigerant passage connecting the compressor 140 and the condenser 210, and is a heat exchanger that heats the refrigerant by exchanging heat between the refrigerant flowing through the refrigerant passage and the engine cooling water, The three-way valve 21 switches between a case where the engine coolant flowing out of the engine 10 is circulated to the heater 250 and a case where it is not circulated.
[0030]
The radiator 22 is a heat exchanger that exchanges heat between the engine cooling water and the outside air to cool the engine cooling water, and the water pump 23 circulates the engine cooling water. The engine 10, the three-way valve 21, the radiator 22, and the water pump 23 form a hot water circuit 20. In FIG. 1, a bypass circuit that bypasses the radiator 22 to flow the cooling water, and a flow control valve that controls the amount of cooling water flowing through the bypass circuit and the amount of cooling water flowing through the radiator 22 are omitted.
[0031]
The first bypass circuit 260 is a refrigerant passage for guiding the liquid-phase refrigerant separated by the gas-liquid separator 220 to a refrigerant inlet / outlet of the heater 250 on the condenser 210 side. A check valve 260a for allowing the refrigerant to flow only from the side of the heater 220 to the heater 250 and a liquid pump 260b for circulating the liquid-phase refrigerant are provided. In this embodiment, the liquid pump 260b is an electric pump.
[0032]
The second bypass circuit 270 is a refrigerant passage connecting the refrigerant suction port 146 a of the compressor 140 (the refrigerant outlet side when operating as an expander) and the refrigerant inlet side of the condenser 210. The check valve 270 is provided with a check valve 270a that allows the refrigerant to flow only from the refrigerant suction port 146a of the compressor 140 to the refrigerant inlet side of the condenser 210.
[0033]
Further, an on-off valve 280 is provided between the condenser 210 and the heater 250. The on-off valve 280 is an electromagnetic valve. Opening this valve enables the refrigerant flow in the refrigeration cycle 200, and closing the valve enables the refrigerant flow in the Rankine cycle 201 described below. .
[0034]
In the Rankine cycle 201, the gas-liquid separator 220, the first bypass circuit 260, the liquid pump 260b, the heater 250, the compressor 140 (at this time, operating as an expander), the second bypass circuit 270, and the condenser 210 are closed. It is formed in a circuit.
[0035]
The hybrid compressor 100A mainly includes a pulley 110, an electromagnetic clutch 120, a motor 130, a compressor 140, a planetary gear 150, and the like, and details thereof will be described below with reference to FIG.
[0036]
The pulley 110 is rotatably supported by a pulley bearing 112 fixed to the front housing 101, so that the driving force of the engine 10 is transmitted via the belt 11 (FIG. 1) to rotate. The drive shaft 111 is provided at the center of the pulley 110 and is rotatably supported by a bearing 113 fixed to the front housing 101.
[0037]
A one-way clutch 160 whose outer peripheral side is fixed to the front housing 101 is provided substantially at the center of the drive shaft 111 (between the electromagnetic clutch 120 and the planetary gear 150 described later). The one-way clutch 160 forms a lock mechanism according to the present invention, and allows the drive shaft 111 to rotate in the pulley rotation direction (normal rotation direction) and prevents the drive shaft 111 from rotating in the reverse rotation direction by engagement. I do.
[0038]
The electromagnetic clutch 120 interrupts the driving force transmitted from the pulley 110 to the compressor 140, and includes a coil 121 fixed to the front housing 101 and the intermediate housing 102, and a hub 122 fixed to the drive shaft 111. . As is well known, when the coil 121 is energized, the hub 122 is attracted to the pulley 110 and the driving force of the pulley 110 is transmitted to the drive shaft 111 (clutch ON). Conversely, when the power supply to the coil 121 is cut off, the hub 122 is separated from the pulley 110, and the driving force of the pulley 110 is disconnected (clutch OFF).
[0039]
The motor 130 is a rotating machine having both functions of a motor and a generator. The motor 130 mainly includes a rotor 132 and a stator 133 and is housed in the intermediate housing 102. The motor 130 is a so-called SP motor (Surface Permanent-Magnet Motor) in which a magnet (permanent magnet) 132a is provided on an outer peripheral portion of the rotor portion 132, and a space on the inner peripheral side of the rotor portion 132 will be described later. The planet gear 150 is housed. The motor shaft (rotating machine shaft) 131 is an imaginary one indicated by a two-dot chain line at the center of the sun gear 151 of the planetary gear 150.
[0040]
The stator 133 is provided with a coil 133a, and the stator 133 is fixed to the inner peripheral surface of the intermediate housing 102 by press fitting. Then, electric power from a battery (not shown) is supplied to the coil 133a via the inverter, whereby the rotor 132 is driven to rotate.
[0041]
Here, the coil 121 of the electromagnetic clutch 120 extends through the front housing 101 and the intermediate housing 102 toward the motor 130, and a protrusion 132 b is provided on the outer periphery of the rotor 132 of the motor 130. The configuration is such that the coil 121 and the overhang portion 132b are close to and opposed to each other. When the electromagnetic clutch 120 is turned on, the overhang portion 132b is attracted to the coil 121, and the rotor portion 132 is set in a fixed state. Note that the coil 121 and the overhang portion 132b correspond to the fixing mechanism 170 in the present invention.
[0042]
Here, the compressor 140 is a fixed-capacity scroll-type compressor, and includes a fixed scroll 144 fixed in the end housing 103 on the side opposite to the pulley of the motor 130 and an eccentric shaft 143 of a compressor shaft (auxiliary shaft) 141. And a movable scroll 145 that revolves.
[0043]
By the engagement of the fixed scroll 144 and the movable scroll 145, a suction chamber 146 is formed on the outer periphery, and a compression chamber 147 is formed on the center side. The side wall of the end housing 103 is provided with a refrigerant suction port 146 a communicating with the suction chamber 146. Further, the center side of the compression chamber 147 is connected to a discharge chamber 148 via a discharge port 147a and further to a refrigerant discharge port 148b provided at an end of the end housing 103. The fixed scroll 144 is provided with a discharge valve 148a for opening and closing the discharge port 147a.
[0044]
In the compressor 140, the refrigerant sucked into the suction chamber 146 from the refrigerant suction port 146a is compressed by the compression chamber 147, and literally operates as a compressor discharged from the refrigerant discharge port 148b through the discharge port 147a and the discharge chamber 148. . In addition, when the superheated vapor refrigerant heated by the heater 250 flows into the compression chamber 147 from the refrigerant discharge port 148b, the compressor 140 compresses the movable scroll 145 by expanding the superheated vapor refrigerant. It operates as an expander driven to the reverse rotation side. When the compressor 140 is operated as an expander, the discharge valve 148a is kept open by a control device 180 described later.
[0045]
The compressor shaft 141 is rotatably supported by a bearing 142 fixed to a protruding wall 102 a protruding inward on the side opposite to the pulley of the intermediate housing 102. One end of the drive shaft 111 is fitted into the compressor shaft 141, and the compressor shaft 141 and the drive shaft 111 are rotatable independently of each other by a bearing 115. Note that a seal member 142a is provided on the motor 130 side of the compressor shaft 141 to prevent the refrigerant in the compressor 140 from leaking to the motor 130 side.
[0046]
The drive shaft 111, the motor shaft 131, and the compressor shaft 141 are connected to the planetary gear 150 as a torque distribution mechanism provided in the rotor section 132 as described above.
[0047]
As is well known, the planetary gear 150 is provided on a sun gear 151 provided at the center, a planetary carrier 152 connected to a pinion gear 152a that revolves while rotating around the outer periphery of the sun gear 151, and a further outer circumference of the pinion gear 152a. And a ring gear 153 having a ring shape.
[0048]
Here, the drive shaft 111 is connected to the planetary carrier 152, the motor shaft 131 (actually, the rotor section 132) is connected to the sun gear 151, and the compressor shaft 141 is connected to the ring gear 153. The sun gear 151 is rotatably supported by the bearing 114 independently of the drive shaft 111.
[0049]
On the other hand, returning to FIG. 1, the control device 180 receives an A / C request signal, an idle stop request signal, and the like, and switches the three-way valve 21 based on these signals, operates the liquid pump 260 b, and opens and closes the valve. The opening and closing of the 280, the intermittent (ON-OFF) of the electromagnetic clutch 120, the operation of the motor 130, and the formation of the open state of the discharge valve 148a are controlled.
[0050]
Next, the operation based on the above configuration will be described with reference to FIGS. FIG. 5 shows the relationship between the rotation speeds of the drive shaft 111, the motor 130 (motor shaft 131), and the compressor 140 (compressor shaft 141) connected to the planetary gear 150, respectively. As is well known, the abscissa indicates the coordinate position of each gear and carrier (from the right, the sun gear 151, the planetary carrier 152, and the ring gear 153), and the respective coordinate positions indicate the respective gears and carriers 151 and 152 as described above. , 153 correspond to the motor 130, the drive shaft 111, and the compressor 140. Further, the interval between the horizontal axes is determined by the gear ratio λ between the sun gear 151 and the ring gear 153. Here, the gear ratio λ is set to 0.5. The vertical axis indicates the rotation speed of each gear and carriers 151, 152, and 153, and each rotation speed has a relationship in which the three members are connected by a straight line.
[0051]
First, the cooling operation mode when there is an A / C request will be described. In this operation mode, the refrigeration cycle 200 is operated by the compressor 140 and the conditioned air is cooled by the evaporator 240.
[0052]
Specifically, the control device 180 opens the on-off valve 280 in a state where the liquid pump 260b is stopped, and operates the three-way valve 21 as shown in FIG. Circulate.
[0053]
When it is determined from the idle stop request signal that the engine 10 is operating, the electromagnetic clutch 120 of the hybrid compressor 100A is turned on, the motor 130 is stopped, and the discharge valve 148a is opened and closed according to the pressure of the refrigerant. Maintain the original shape.
[0054]
Then, in the hybrid compressor 100A, when the electromagnetic clutch 120 is turned on, the rotor portion 132 (the overhang portion 132b) of the motor 130 is attracted to the coil 121 by the fixing mechanism 170, and is brought into a fixed state. Then, the driving force of the engine 10 is transmitted to the pulley 110 and the driving shaft 111 via the belt 11, and the driving force is increased in speed by the planetary gear 150 and transmitted to the compressor 140 to operate the compressor 140 ( (A) in FIG.
[0055]
In the refrigeration cycle 200, the refrigerant circulates in the order of the compressor 140, the heater 250, the condenser 210, the gas-liquid separator 220, the pressure reducer 230, the evaporator 240, and the compressor 140. The low-pressure refrigerant decompressed by the decompressor 230 absorbs heat from the conditioned air in the evaporator 240 and evaporates, and the conditioned air is cooled. Since the engine cooling water does not circulate through the heater 250, the refrigerant is not heated by the heater 250, and the heater 250 functions as a simple refrigerant passage.
[0056]
Further, when there is an A / C request, and when it is determined from the idle stop request signal that the engine 10 has stopped, the control device 180 turns off the electromagnetic clutch 120 of the hybrid compressor 100A and sets the discharge valve 148a to the refrigerant pressure. Maintain the original shape that opens and closes according to
[0057]
Then, in the hybrid compressor 100A, when the electromagnetic clutch 120 is turned off, the rotor portion 132 (the overhang portion 132b) of the motor 130 is separated from the coil 121 and becomes rotatable. Then, control device 180 operates motor 130 in a direction opposite to the direction of rotation of compressor 140 during compression (operates as a motor). At this time, the drive shaft 111 also attempts to drive in the reverse rotation direction by way of the tailgating, but is locked by the action of the one-way clutch 160, and the driving force of the motor 130 is reduced by the planetary gear 150 and transmitted to the compressor 140, where The machine 140 is operated (FIG. 5 (A)).
[0058]
Then, by the operation of the compressor 140 by the motor 130, the refrigerant is circulated in the refrigeration cycle 200 in the same manner as described above, and the cooling function is continued.
[0059]
On the other hand, a waste heat recovery operation mode when there is no A / C request will be described. In this operation mode, the refrigeration cycle 200 is stopped and the waste heat of the engine 10 is recovered as usable energy.
[0060]
Specifically, when it is determined from the idle stop request signal that the engine 10 is operating, the control device 180 turns off the electromagnetic clutch 120 of the hybrid compressor 100A so that the discharge valve 148a is always open. maintain. Then, the rotor part 132 of the motor 130 is separated from the coil 121 and becomes rotatable.
[0061]
In addition, the liquid pump 260b is operated with the on-off valve 280 closed, and the three-way valve 21 is operated as shown in FIG. 4 to circulate the engine coolant flowing out of the engine 10 to the heater 250. Then, the refrigerant flows into the Rankine cycle 210 like the gas-liquid separator 220 → the first bypass circuit 260 → the heater 250 → the compressor (expander) 140 → the second bypass circuit 270 → the condenser 210 → the gas-liquid separator 220. Circulate.
[0062]
At this time, the superheated vapor refrigerant heated by the heater 250 flows into the compression chamber 147 from the refrigerant discharge port 148b of the compressor 140 (since the discharge valve 148a is open, it is possible to flow into the compression chamber 147). ), The enthalpy is reduced while expanding in a compression chamber 147 in an isentropic manner. Then, the orbiting scroll 145 is driven in the direction of rotation opposite to that during compression to operate as an expander. This driving force causes the driving shaft 111 to drive in the reverse rotation direction by way of tailgating, but is locked by the action of the one-way clutch 160, and the driving force of the compressor (expander) 140 is increased by the planetary gear 150. The power is transmitted to the motor 130, and the motor 130 is operated as a generator ((c) in FIG. 5). Then, the generated power is stored in a storage device such as a battery and a capacitor (not shown).
[0063]
The refrigerant flowing out of the refrigerant suction port 146a of the compressor (expander) 140 is cooled by the condenser 210, condensed and liquefied, stored in the gas-liquid separator 220, and stored in the gas-liquid separator 220. Is sent to the heater 250 side by the liquid pump 260b. The liquid pump 260b sends the liquid-phase refrigerant to the heater 250 at such a pressure that the superheated vapor refrigerant generated by being heated by the heater 250 does not flow back to the gas-liquid separator 220 side.
[0064]
According to the above description of the configuration and operation, in the present invention, when the engine 10 is operating, the electromagnetic clutch 120 is turned on, and the compressor 140 can be operated by the driving force of the engine 10. Can turn off the electromagnetic clutch 120 to operate the compressor 140 with the driving force of the motor 130, and can operate the refrigeration cycle 200 at the time of A / C request regardless of the operation or stoppage of the engine 10. .
[0065]
Here, when the electromagnetic clutch 120 is turned on, the fixing mechanism 170, which can be formed with a relatively simple configuration using existing members (the coil 121 and the protruding portion 132b of the rotor portion 132), allows the rotor portion 132 ( The overhanging portion 132b) is attracted to the coil 121 of the electromagnetic clutch 120 to be fixed, so that the motor 130 can be prevented from operating as a generator, so that the load on the operating engine 10 can be reduced. Can be.
[0066]
When the refrigeration cycle 200 is stopped, the electromagnetic clutch 120 is turned off, and the compressor 140 is operated as an expander by the superheated steam refrigerant from the heater 250, so that the motor 130 is operated as a generator and the engine 10 is operated. It is possible to generate electric power by using waste heat without directly using the driving force from the motor.
[0067]
The torque distribution mechanism 150 can be easily formed by connecting the shafts 111, 131, 141 to the sun gear 151, the planetary carrier 152, and the ring gear 153 of the planetary gear 150.
[0068]
In addition, since the drive shaft 111 is connected to the planetary carrier 152 and the lock mechanism 160 is a one-way clutch 160 that allows rotation only in the normal rotation direction of the drive shaft 111, when the electromagnetic clutch 120 is turned off, By operating one of the motor 130 and the compressor 140 in the direction opposite to the normal rotation direction of the drive shaft 111, the drive shaft 111 to be driven by the tailgating is locked by the one-way clutch 160, and the motor 130 or the auxiliary The drive torque can be transmitted to the other side of the lock 140, and the lock 140 can be used as an inexpensive lock mechanism.
[0069]
Further, since the motor shaft 131 is connected to the sun gear 151 and the compressor shaft 141 is connected to the ring gear 153, when the compressor 130 is operated by the motor 130, the speed is reduced with respect to the motor 130 and the reduction ratio thereof. Therefore, a high-speed, low-torque motor 130 can be used, and the size and cost can be reduced. Further, when the compressor 140 is operated as an expander and the motor 130 is operated as a generator by the driving torque, the speed of the compressor 140 can be increased and the speed increase ratio can be increased. The amount of power generation at 130 can be increased, and similarly, the size of motor 130 can be reduced.
[0070]
(Other embodiments)
In the first embodiment, the planetary gear 150 is used as the torque distribution mechanism. However, the planetary gear 150 may be replaced with a planetary roller, a differential gear, or the like.
[0071]
The connection between the gears of the planetary gear 150 and the carriers 151, 152, 153 and the drive shaft 111, the motor shaft 131, and the compressor shaft 141 is such that the motor shaft 131 and the compressor shaft 141 are replaced with those in the first embodiment. It may be connected. Further, the lock mechanism is not limited to the one-way clutch 160, and if the drive shaft 111 can be restrained when the electromagnetic clutch 120 is turned off, each gear, carriers 151, 152, 153, the drive shaft 111, and the motor The connection between the shaft 131 and the compressor shaft 141 may be another combination.
[0072]
Further, the compressor 140 is not limited to the scroll type among the fixed capacity type, but may be a rotary type or a through vane type. In addition, a fixed displacement type is preferable in terms of cost, but a variable displacement type may be used instead. According to this, the discharge amount when the compressor 140 is operated by the engine 10 is variable. Becomes possible.
[0073]
Furthermore, the target vehicle may be a so-called hybrid vehicle having a traveling motor and stopping the engine 10 according to predetermined traveling conditions even during traveling.
[Brief description of the drawings]
FIG. 1 is a schematic diagram showing an overall configuration in which the present invention is applied to a refrigeration cycle having a Rankine cycle.
FIG. 2 is a sectional view showing the hybrid compressor of the first embodiment in FIG.
FIG. 3 is a schematic diagram showing flows of engine cooling water and refrigerant in a cooling operation mode.
FIG. 4 is a schematic diagram showing flows of engine cooling water and refrigerant in a waste heat recovery operation mode.
FIG. 5 is a nomographic chart showing operating rotation speeds of a drive shaft, a motor, and a compressor.
[Explanation of symbols]
10 Engine
100 Hybrid compressor control device (hybrid drive auxiliary device control device)
100A hybrid compressor (hybrid drive accessory)
111 drive shaft
120 electromagnetic clutch
121 coil
130 Motor (rotary machine)
131 Motor shaft (rotating machine shaft)
132 Rotor part
140 Compressor (Auxiliary machine)
141 Compressor shaft (auxiliary shaft)
150 planetary gear (torque distribution mechanism)
151 Sun Gear
152 planetary carrier
153 ring gear
160 One-way clutch (lock mechanism)
170 Fixing mechanism
180 control unit
200 refrigeration cycle
201 Rankine cycle
250 heater

Claims (5)

  1. A heater (250) for heating a refrigerant is provided, which is applied to a refrigeration cycle (200) for a vehicle including a Rankine cycle (201),
    An electromagnetic clutch (120) that is provided on a drive shaft (111) that receives a driving force from the engine (10) of the vehicle and that rotates the driving shaft, and intermittently transmits the driving force from the engine (10);
    A rotating machine (130) having both functions of a motor and a generator,
    An auxiliary device (140) that operates as a compressor that compresses the refrigerant during one-way rotation, and that operates as an expander on the other direction rotation side due to reverse flow of superheated vapor refrigerant from the heater (250);
    The driving shaft (111) is provided between the rotating machine shaft (131) of the rotating machine (130) and the auxiliary machine shaft (141) of the auxiliary machine (140). A torque distribution mechanism (150) capable of distributing to two shafts (131, 141);
    A lock mechanism (160) for preventing transmission of drive torque from the rotating machine shaft (131) or the accessory shaft (141) to the drive shaft (111) when the electromagnetic clutch (120) is disconnected;
    When the electromagnetic clutch (120) is connected, the rotor section (132) of the rotating machine (130) is attracted to the coil (121) of the electromagnetic clutch (120) to fix the rotor section (132). And a fixing mechanism (170).
  2. The torque distribution mechanism (150) is a planetary gear (150);
    Each of the shafts (111, 131, 141) is connected to one of a sun gear (151), a planetary carrier (152), and a ring gear (153) constituting the planetary gear (150). The hybrid drive accessory according to claim 1, wherein:
  3. The drive shaft (111) is connected to the planetary carrier (152),
    The hybrid drive accessory according to claim 2, wherein the lock mechanism (160) is a one-way clutch (160) that allows the drive shaft (111) to rotate only in a normal rotation direction.
  4. The rotating machine shaft (131) is connected corresponding to the sun gear (151),
    The hybrid drive accessory according to claim 3, wherein the accessory shaft (141) is connected to the ring gear (153).
  5. A hybrid drive accessory (100A) according to any one of claims 1 to 4,
    A hybrid drive accessory control device including a control device (180) for controlling operation of the heater (250), intermittent operation of the electromagnetic clutch (120), and operation of the rotating machine (130),
    The control device (180) connects the electromagnetic clutch (120) and compresses the auxiliary device (140) when the refrigeration cycle (200) is activated when the engine (10) is activated. Work as a machine,
    When the refrigeration cycle (200) is in an operating state when the engine (10) is stopped, the electromagnetic clutch (120) is set to a disconnected state, and the auxiliary machine (140) is compressed by the rotating machine (130). Operating as
    When the refrigeration cycle (200) is stopped during operation of the engine (10), the electromagnetic clutch (120) is disconnected, and the auxiliary device (140) is operated as an expander by the heater (250). A hybrid drive accessory control device, characterized in that:
JP2003073377A 2003-03-18 2003-03-18 Hybrid drive accessory and control device thereof Expired - Fee Related JP4047205B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2003073377A JP4047205B2 (en) 2003-03-18 2003-03-18 Hybrid drive accessory and control device thereof

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2003073377A JP4047205B2 (en) 2003-03-18 2003-03-18 Hybrid drive accessory and control device thereof

Publications (2)

Publication Number Publication Date
JP2004278459A true JP2004278459A (en) 2004-10-07
JP4047205B2 JP4047205B2 (en) 2008-02-13

Family

ID=33289288

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2003073377A Expired - Fee Related JP4047205B2 (en) 2003-03-18 2003-03-18 Hybrid drive accessory and control device thereof

Country Status (1)

Country Link
JP (1) JP4047205B2 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006118754A (en) * 2004-10-19 2006-05-11 Denso Corp Vapor compression refrigerator
JP2006177588A (en) * 2004-12-21 2006-07-06 Denso Corp Vapor compression refrigerator
JP2006188156A (en) * 2005-01-06 2006-07-20 Denso Corp Vapor compressing type refrigerator
JP2006321389A (en) * 2005-05-19 2006-11-30 Denso Corp Waste heat using device for vehicle
JP2006329182A (en) * 2005-04-26 2006-12-07 Denso Corp Fluid machine and vapor compression type refrigerator
WO2013154051A1 (en) * 2012-04-12 2013-10-17 日産自動車株式会社 Fluid machine, and rankine cycle
CN107842500A (en) * 2016-09-21 2018-03-27 比亚迪股份有限公司 Dual drive compressor

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4654655B2 (en) * 2004-10-19 2011-03-23 株式会社デンソー Vapor compression refrigerator
DE102005049831B4 (en) * 2004-10-19 2014-02-13 Denso Corporation Vapor compression cooling device
JP2006118754A (en) * 2004-10-19 2006-05-11 Denso Corp Vapor compression refrigerator
JP2006177588A (en) * 2004-12-21 2006-07-06 Denso Corp Vapor compression refrigerator
JP4631426B2 (en) * 2004-12-21 2011-02-23 株式会社デンソー Vapor compression refrigerator
JP2006188156A (en) * 2005-01-06 2006-07-20 Denso Corp Vapor compressing type refrigerator
JP2006329182A (en) * 2005-04-26 2006-12-07 Denso Corp Fluid machine and vapor compression type refrigerator
JP2006321389A (en) * 2005-05-19 2006-11-30 Denso Corp Waste heat using device for vehicle
WO2013154051A1 (en) * 2012-04-12 2013-10-17 日産自動車株式会社 Fluid machine, and rankine cycle
JP2013217349A (en) * 2012-04-12 2013-10-24 Nissan Motor Co Ltd Fluid machine and rankine cycle
CN104350235A (en) * 2012-04-12 2015-02-11 三电有限公司 Fluid machine, and rankine cycle
CN107842500A (en) * 2016-09-21 2018-03-27 比亚迪股份有限公司 Dual drive compressor
CN107842500B (en) * 2016-09-21 2019-09-13 比亚迪股份有限公司 Double drive compressor

Also Published As

Publication number Publication date
JP4047205B2 (en) 2008-02-13

Similar Documents

Publication Publication Date Title
KR100528392B1 (en) Vapor-compression refrigerant cycle system with refrigeration cycle and rankine cycle
EP1233179B1 (en) Composite drive system for compressor
CN1262802C (en) Fluid machine and waste heat recovery system with the fluid machine
JP4801810B2 (en) Refrigeration equipment with waste heat utilization device
CN100443830C (en) Air-conditioner, outdoor unit and refrigeration unit
KR100716850B1 (en) Rotary sealed compressor and refrigeration cycle apparatus
DE102006013190B4 (en) Fluid pump with an expansion device and Rankine cycle with this
US20070245737A1 (en) Waste heat utilization device and control method thereof
KR100196528B1 (en) Air conditioning equipment
KR100572749B1 (en) Hybrid compressor system
JP2005030727A (en) Rankine cycle
EP1491726A1 (en) Waste heat recovery system of heat source, with rankine cycle
US5896750A (en) Device for the air conditioning of a vehicle when running and parked
DE102005032277B4 (en) Vapor compression refrigeration unit
JP4207340B2 (en) Refrigeration cycle
DE102005014129B4 (en) Waste heat of an internal combustion engine using system
US7454910B2 (en) Waste heat recovery system of heat source, with Rankine cycle
JP4242131B2 (en) Refrigeration cycle equipment
CN1261728C (en) Mixed compressor apparatus
JP2004190875A (en) Refrigerating cycle device
US7392655B2 (en) Vapor compression refrigerating device
US8415815B2 (en) Fluid machine, rankine circuit, and system for utilizing waste heat from vehicle
US7536869B2 (en) Vapor compression refrigerating apparatus
US7314356B2 (en) Fluid machine
US7028475B2 (en) Fluid machine

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20050419

A977 Report on retrieval

Effective date: 20071115

Free format text: JAPANESE INTERMEDIATE CODE: A971007

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20071120

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20071121

FPAY Renewal fee payment (prs date is renewal date of database)

Year of fee payment: 3

Free format text: PAYMENT UNTIL: 20101130

R150 Certificate of patent (=grant) or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

LAPS Cancellation because of no payment of annual fees