CN1769709A - Hybrid compressor device - Google Patents
Hybrid compressor device Download PDFInfo
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- CN1769709A CN1769709A CN 200510120094 CN200510120094A CN1769709A CN 1769709 A CN1769709 A CN 1769709A CN 200510120094 CN200510120094 CN 200510120094 CN 200510120094 A CN200510120094 A CN 200510120094A CN 1769709 A CN1769709 A CN 1769709A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/45—Hybrid prime mover
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Abstract
In a hybrid compressor for a vehicle where a vehicle engine is stopped when the vehicle is temporally stopped, a pulley, a motor and a compressor can be driven in independent from each other, and are connected to a sun gear, planetary carriers and a ring gear of a planetary gear. A rotational speed of the motor is adjusted by a controller, so that a rotational speed of the compressor is changed with respect to a rotational speed of the pulley. Accordingly, production cost of the hybrid compressor and the size thereof can be reduced, while a cooling function can be ensured even when the vehicle engine is stopped.
Description
The application divides an application, and original application is: application number: 02152797.0, and the applying date: on November 28th, 2002, denomination of invention: hybrid compressor device.
Technical field
The present invention relates to a kind of hybrid compressor device, it is applicable to the cooling cycle system that is installed on the idle stop vehicle, and when the motor of this vehicle temporarily stopped at vehicle, motor also stopped.
Background technique
Recently, to the increase in demand of idle stop vehicle, this is in order to save fuel oil consumption.Only depend at compressor under the situation of vehicle motor driving, when vehicle temporarily stopped, its motor also stopped, thereby had also stopped by engine-driven compressor in the cooling cycle system.In order to address this problem, in the traditional hybrid compressor device disclosed in the JP-A-2000-130323 (corresponding to USP No.6,375,436), the driving force of motor is passed to belt pulley by solenoid clutch, and an end of compressor rotating shaft links to each other with this belt pulley.And the other end of compressor rotating shaft links to each other with a motor.Correspondingly, when motor stops, the solenoid clutch closure, compressor is by motor driven, so the running of cooling cycle system can be irrelevant with the running of motor.
Yet this hybrid compressor device needs solenoid clutch, is used for the driving source of conversion compressor between motor (during engine running) and motor (when motor stops).Thereby the cost of production of this hybrid compressor device increases.And this compressor turns round by one of motor and these two kinds of driving sources of motor.Thereby the flow of this compressor and size need be set according to the maximum heat load of cooling cycle system in each drive source drives power scope.For example, directly selected refrigerating mode (fast-refrigerating pattern), the thermal load of compressor to reach maximum after the vehicle launch in summer.Thereby the flow of compressor and size will be set to and satisfy the maximum heat load, thereby have increased the size of compressor.
Summary of the invention
The present invention has considered the problem of front, and its objective is provides a kind of hybrid compressor device, can reduce its manufacture cost and size, and can guarantee its refrigeration performance after vehicle motor stops.
Another object of the present invention provides a kind of hybrid compressor device, although it with the low cost manufacturing, has reliability preferably.
According to the present invention, hybrid compressor device comprises a belt pulley, and it rotates under the driving of vehicle motor, when vehicle temporarily stops, vehicle motor also stops, a motor, and it rotates coming under the electric drive of vehicle battery, a compressor, compressor is by the driving force of belt pulley and the driving force running of motor, and a driving mechanism, driving mechanism are used for changing and transmitting rotating force, and a control unit, control unit is used to adjust the rotating speed of motor.Here, compressor is used to compress the refrigeration agent of the cooling cycle system of vehicle.A running shaft of a running shaft of driving mechanism and belt pulley, motor and a running shaft of compressor link to each other, so that the rotating speed of the rotating speed of belt pulley and motor changes and passes to compressor.In hybrid compressor device, belt pulley, motor and compressor are set up so that they can rotate independently.And control unit is by adjusting motor changes compressor with respect to the rotating speed of belt pulley rotational speed.Correspondingly, the rotational speed of compressor can increase or reduce with respect to the rotational speed of belt pulley, thereby changes the flow of compressor.When the thermal load at refrigerating mode (under the fast-refrigerating pattern) cooling cycle system reaches maximum, can increase the rotational speed of the rotational speed of compressor by the rotational speed of adjusting motor than belt pulley, can increase the flow of compressor effectively.Thereby the size of compressor and flow can be set smallerly.On the contrary, can reduce the rotational speed of the rotational speed of compressor, can reduce the flow of compressor by the rotational speed of adjusting motor than belt pulley.Thereby, compressor after refrigerating mode finishes, can be promptly with normal refrigeration mode under the thermal load of cooling cycle system adapt.And, even when motor because (being in) dallied and to be stopped (state) and stop, and during the rotational speed vanishing of belt pulley, compressor can turn round by motor.Thereby, even in the idle running stop time, refrigerating operation can not keep with a lower one-tenth originally owing to not using solenoid clutch yet.
Optimal way is, driving mechanism is a planetary train, comprise a sun gear, a planetary carrier and a ring gear, and the running shaft of belt pulley, motor and compressor are connected on sun gear, planetary carrier and the ring gear of planetary train.Here, being connected and at random changing between sun gear, planetary carrier and the ring gear of the running shaft of belt pulley, motor and compressor and planetary train.For example, the running shaft of compressor is connected to planetary carrier, and the running shaft of belt pulley is connected to sun gear, and the running shaft of motor is connected to ring gear.Perhaps, the running shaft of belt pulley is connected to planetary carrier, and the running shaft of motor is connected to sun gear, and the running shaft of compressor is connected to ring gear.Again or, the running shaft of motor is connected to sun gear, the running shaft of compressor is connected to ring gear, and the running shaft of compressor is connected to planetary carrier.
Optimal way is, a locking framework is set, and locking framework is used for the running shaft of locking motor when motor stops.In this case, when motor stops compressor and turns round by the driving force of belt pulley, control unit by detecting owing to be connected to the fluctuation that the leakage variation of the magnetic line of force of the motor that the rotation of the driving mechanism of compressor produces detects the induced voltage of motor.Correspondingly, when compressor produces similar locked such trouble, the rotation minimizing or the vanishing of driving mechanism, therefore, it is smaller that the fluctuation of induced voltage just becomes.Thereby the unusual running of compressor can be easily detected by the fluctuation of using the motor magnetic line of force effectively.
Hybrid compressor device of the present invention can be applied to a kind of on the vehicle that its motor can stop under the operating condition of determining, this vehicle has a drive motor, comes powered vehicle.
On the other hand, in hybrid compressor, the compressor of refrigeration agent that is used for the compression refrigeration circulatory system is by being that one of driver element and motor turn round at least, compressor comprises a negative pressuren zone, enters here a discharge region before the refrigeration agent compression, the refrigeration agent that compressed flows into here, and an oil separation unit, oil separation unit is used for separating the lubricant oil that is included in the refrigeration agent in the refrigeration agent, and the lubricant oil that is used for having separated is kept at discharge region.Moreover driving mechanism is arranged at least one the centre in compressor and driver element and the motor, is used for changing at least one rotational speed of driver element and motor, makes it be delivered to compressor.In addition, motor and driving mechanism all are placed in the casing, and it has an oil inlet passage, enters casing so that be stored in the lubricant oil of discharge region by oil inlet passage, and the inside of casing is connected with the negative pressuren zone of compressor by communication passage.
Correspondingly, the lubricant oil that is included in the refrigeration agent is separated in refrigeration agent by oil separation unit, and the lubricant oil that has separated is introduced into casing.Moreover the lubricant oil of introducing casing is recycled to the negative pressuren zone of compressor from casing.Therefore, lubricant oil always can be supplied to the driving mechanism in the casing, thereby has improved the reliability of driving mechanism.Moreover because motor also is placed in the casing, motor can be cooled off by lubricant oil, thereby has improved the reliability of motor.Because lubricant oil is separated in refrigeration agent by oil separation unit, circulate in the refrigeration agent of cooling cycle system and contain lubricant oil hardly.Thereby lubricant oil can be attached on the heat exchanger such as the vaporizer in the cooling cycle system, thereby prevents that the thermal conversion efficiency of heat exchanger from reducing.
Optimal way is that casing can hold compressor, motor and driving mechanism.And casing has an inlet hole, and it is that refrigeration agent is inhaled in the compressor by it in that side of placing motor and driving mechanism.Thereby motor and driving mechanism can cool off effectively by the refrigeration agent that enters casing.
Moreover, oil inlet passage is first relief passage, the discharge region of compressor is connected with box house by it, and the inside of pressure from the discharge region of compressor towards casing reduces, communication passage is second relief passage, box house is connected with the negative pressuren zone of compressor by it, and the negative pressuren zone towards compressor reduces and pressure is from the inside of casing.Thereby lubricant oil can circulate between compressor and casing reposefully.
Description of drawings
Other purposes of the present invention and advantage can be from below in conjunction with clearly seeing the accompanying drawing detailed description of the preferred embodiment, wherein:
Fig. 1 is the complete schematic representation of the cooling cycle system can the typical case used of expression the present invention;
Fig. 2 is the sectional view of expression according to first embodiment's of the present invention shown in Figure 1 hybrid compressor device;
Fig. 3 is the front elevation of the epicyclic train watched of the arrow III of expression from Fig. 2;
Fig. 4 A is compressor displacement and the control characteristic figure of thermal load relation of first embodiment's of expression cooling cycle system, Fig. 4 B be represent first embodiment compressor displacement and the control characteristic figure of the relation between the compressor rotational speed.
Fig. 5 is the rotational speed figure of belt pulley, compressor and the motor of expression hybrid compressor shown in Figure 2.
Fig. 6 is the sectional view of expression second embodiment's of the present invention hybrid compressor device.
Fig. 7 is the rotational speed figure of belt pulley, compressor and motor of second embodiment's of expression hybrid compressor device.
Fig. 8 is the sectional view of expression the 3rd embodiment's of the present invention hybrid compressor device.
Fig. 9 is the rotational speed figure of belt pulley, compressor and motor of the 3rd embodiment's of expression hybrid compressor device.
Figure 10 is the front elevation of expression the 4th the embodiment's of the present invention epicyclic train that comprises groove part and protruding part.
Figure 11 is the schematic representation of amplification of the magnetic line of force of the 4th embodiment's of expression the magnetic line of force of motor and leakage.
Figure 12 is that the 4th embodiment's of expression the fluctuation of induced voltage of motor is with respect to time relation figure.
Figure 13 is the flow chart of the 4th embodiment's of expression detection motor induced voltage fluctuation with the control procedure of protection vehicle motor.
Figure 14 is the sectional view that is illustrated in the hybrid compressor of making amendment on the 4th embodiment.
Figure 15 is the sectional view of expression the 5th embodiment's of the present invention hybrid compressor device.
Figure 16 is the sectional view of expression the 6th embodiment's of the present invention hybrid compressor device.
Embodiment
Describe the preferred embodiments of the present invention with reference to the accompanying drawings in detail.
(first embodiment)
Be described now with reference to Fig. 1-5 couple of first embodiment of the present invention.In Fig. 1, hybrid compressor device 100 is typically applied in the cooling cycle system 200 that is installed on the idle stop vehicle, and this vehicle is when temporarily stopping, and its motor 10 also stops.Hybrid compressor device 100 comprises a hybrid compressor 101 and a control unit 160.Cooling cycle system 200 comprises such as compressor 130, condenser 210, the parts of expansion valve 220 and vaporizer 230.These parts sequentially connect by refrigerant pipe 240, form a closed loop.Compressor 130 has constituted hybrid compressor 101.The refrigeration agent of compressor 130 compression cycle in cooling cycle system reaches a high temperature and high pressure.Refrigeration agent condensation in condenser 210 of having compressed, chilled refrigeration agent expands with adiabatic state in expansion valve 220.Dilated refrigeration agent is vaporized in vaporizer 230, air by vaporizer 230 since the latent heat of vaporization of the refrigeration agent of having vaporized cool off.Vapourizing temperature sensor 231 is located at air downstream one side of vaporizer 230, is used to detect by the temperature of vaporizer 230 chilled air (flowing through the temperature of the air of vaporizer) Te.The temperature T e that flows through the air of vaporizer is a representational numerical value that is used for the thermal load of definite cooling cycle system 200.
In the present invention, as what describe in the back, compressor 130 drives by operation belt pulley 110 and motor 120 according to the thermal load of cooling cycle system 200.Thereby the discharge capacity of compressor 130 and size can only depend on one of them running of belt pulley 110 and motor 120 to come the discharge capacity of compressor driven and size smaller than those.For example, the discharge capacity of compressor 130 and size can be set to the 1/2-1/3 that comes the discharge capacity and the size of compressor driven by the running of one of belt pulley 110 and motor 120.The running shaft 111 of belt pulley, motor 120, and the running shaft 131 of compressor is connected to planetary train 150, planetary train 150 is arranged on 140 li of casings as driving mechanism.The rotational speed of the rotational speed of belt pulley 110 and motor 120 is by planetary train 150 changes and pass to compressor 130.As shown in Figure 3, planetary train 150 comprises a sun gear 151 at its center, is connected to the planetary carrier 152 on the small gear 152a, and is arranged on the outside of small gear 152a, the ring gear 153 on sun gear 151 opposites.Each small gear 152a rotation, and around sun gear 151 rotations.When planetary train 150 rotation, between the driving force (ring gear torque) of the driving force (planetary carrier torque) of the driving force (sun gear torque) of sun gear 151, planetary carrier 152 and ring gear 153, satisfy following relation.
Planetary carrier torque=sun gear torque+ring gear torque
Here, belt pulley running shaft 111 is connected on the sun gear 151, and motor 120 is connected on the ring gear 153.Compressor rotating shaft 131 is connected on the planetary carrier 152.
Secondly, the running according to first embodiment's said structure will be described below.101 li of hybrid compressors, compressor 130 turns round by the rotary driving force of belt pulley 110, the rotary driving force of motor 120 by planetary train 150.The rotational speed of motor 120 is regulated by control unit 160, and the rotational speed of compressor 130 is with respect to the rotational speed increase and the minimizing of belt pulley 110.
Fig. 5 has provided sun gear 151, the rotational speed of planetary carrier 152 and ring gear 153.In the abscissa of Fig. 5, the position of planetary carrier 152 is determined by the ring gear 153 and the gear ratio of sun gear 151.Here, gear ratio is set to 0.5.Sun gear 151, the rotational speed of planetary carrier 152 and ring gear 153 is arranged on the straight line of Fig. 5.Control unit 160 is calculated the rotational speed of belt pulley 110 by the rotational speed signal of motor 10.Then, as Fig. 4 A, shown in the 4B, control unit 160 determines that the rotational speed of compressor 130 is with the required compressor displacement of the thermal load of guaranteeing cooling cycle system 200.In Fig. 5, straight line is signed in definite rotational speed of compressor 130 by the calculating rotational speed of belt pulley 110.Because the rotational speed of motor 120 is positioned on the elongation line of straight line, the rotational speed of motor 120 is determined according to Fig. 5.Like this, motor 120 turns round under the rotational speed of determining.
Moreover the running control of motor 120 is described in detail with reference to Fig. 5.In refrigerating mode (fast-refrigerating pattern), it is maximum that the thermal load of cooling cycle system 200 reaches, and shown in Fig. 5 cathetus A, the rotational speed of motor 120 increases, to such an extent as to the rotational speed of compressor 130 is than the rotational speed height of belt pulley 110.Thereby the discharge capacity of compressor 130 increases, and compressor 130 can turn round according to the high heat load of cooling cycle system 200.
Under the normal refrigeration mode after refrigerating mode finishes, the discharge capacity of the increase of compressor 130 is unwanted.Thereby shown in Fig. 5 cathetus B, the rotational speed of motor 120 reduces, and the rotational speed of compressor 130 is lower than the rotational speed of belt pulley 110.Thereby the discharge capacity of compressor 130 reduces to the required discharge capacity of normal refrigeration mode.
When the thermal load of cooling cycle system 200 further reduces, when the discharge capacity of compressor 130 became superfluous, motor 120 was with opposite sense of rotation running, and shown in Fig. 5 cathetus C, and the rotational speed of compressor is set to 0.Thereby the discharge capacity of compressor 130 is set to 0.That is to say that the discharge capacity of compressor 130 can be set to 0 by the rotational speed of governor motor 120, and does not need to use solenoid clutch in the prior art.In this case, motor 120 receives the rotating force that comes from the planetary carrier 152 that is connected on the compressor 130, rotates to produce electric power by opposite sense of rotation.
Under normal refrigeration mode, when vehicle ran at high speed, motor 120 was with opposite sense of rotation running, and shown in straight line D, and compressor 130 turns round under the rotational speed identical with straight line B.Thereby can keep normal refrigeration mode, the discharge capacity under the situation of the normal refrigeration mode the when discharge capacity of guaranteeing compressor 130 is moved with normal speed with vehicle is identical.Straight line C in Fig. 5, under the situation of D, motor 120 can produce electric power, so storage battery 20 is recharged with opposite sense of rotation running.And, when idle stop vehicle temporarily stops, and when motor 10 also stops, that is to say, when the rotational speed of belt pulley 110 becomes 0, in the time of shown in Fig. 5 cathetus E, motor 120 is with a middle rotational speed running, and it is identical with the rotational speed shown in Fig. 5 cathetus B that the rotational speed of compressor 130 keeps.Therefore, even when motor 10 stopped, compressor 130 required discharge capacities also can be guaranteed, and the running of cooling cycle system 200 can continue.
Secondly, the running effect that description is had the hybrid engine device of said structure.The rotational speed of compressor 130 can be passed through rotational speed increase and the minimizing of the rotational speed of governor motor 120 with respect to belt pulley 110.Thereby the discharge capacity of compressor 130 can change according to the rotational speed of belt pulley 110 and the rotational speed of motor 120.Moreover the rotational speed of compressor 130 can increase than the rotational speed of belt pulley 110, so that the discharge capacity of compressor 130 can increase than the discharge capacity of the compressor of prior art.Thereby the size of compressor 130 and discharge capacity can be provided with smallerly than the prior art.On the contrary, the rotational speed of compressor 130 can be lower than the rotational speed of belt pulley 110, so that the discharge capacity of compressor 130 reduces.The thermal load of the cooling cycle system 200 under the normal refrigeration mode after therefore, compressor 130 can respond refrigerating mode fast and finishes.And, even when motor 10 owing to dally and to stop, and the rotational speed of belt pulley 110 becomes at 0 o'clock, compressor 130 can turn round by the running of motor 120.Therefore, at the idle running stop phase, refrigeration mode can keep with low cost, does not need to use solenoid clutch.
Because the running shaft 131 of compressor 130 is connected on the planetary carrier 152, the driving force of the driving force of belt pulley 110 and motor 120 can be applied on the running shaft 131 of compressor by the planetary train 150 that comprises sun gear 151, planetary carrier 152 and ring gear 153.Therefore, the energy of the energy of belt pulley 110 and motor 120 can be supplied to compressor 130, thereby has reduced the load of motor 10.Moreover belt pulley running shaft 111 is connected to sun gear 151, and motor 120 is connected to ring gear 153.Therefore, belt pulley running shaft 111, compressor rotating shaft 131 and motor 120 can be connected respectively on sun gear 151, planetary carrier 152 and the ring gear 153 with a simple structure.As a result, can reduce the manufacture cost of hybrid compressor 101.Because the discharge capacity of compressor 130 can change by the rotational speed of governor motor 120, hybrid compressor 101 can use the compressor 130 of fixed displacement, thereby further reduces the manufacture cost of hybrid compressor 101.
In aforesaid first embodiment, the spin axis 121 of motor 120 has been described.Yet in fact, motor 120 rotates by motor drive shaft (121).
(second embodiment)
Be described referring now to Fig. 6 and 7 couples of second embodiments of the present invention.
In second embodiment, as shown in Figure 6, compare with first embodiment, planetary train 150 is arranged on the rotor portion 120a of motor 120, and the running shaft and the compressor rotating shaft 131 of belt pulley running shaft 111, motor 120 are connected on the planetary train 150.Moreover, to compare with first embodiment, hybrid compressor 101 has increased solenoid clutch 170 and overrunning clutch 180.Here, surperficial permanent magnet motor (surface permanent-magnet motor) (SP motor) is used as motor 120, and permanent magnet is positioned on the excircle of rotor portion 120a in surperficial permanent magnet motor.Planetary train 150 is arranged in the space of rotor portion 120a inner circumference one side.Belt pulley running shaft 111 is connected on the planetary carrier 152, and the rotor portion 120a of rotor 120 is connected on the sun gear 151.Compressor rotating shaft 131 is connected on the ring gear 153.Rotor portion 120a and ring gear 153 can be independent of belt pulley running shaft 111 by bearing 114 and rotate.
Moreover the running of hybrid compressor with structure of second embodiment who talks about previously is described below with reference to Fig. 7.At refrigerating mode, need the maximum pump discharge of compressor, solenoid clutch 170 is connected, and the driving force of belt pulley 110 passes to compressor rotating shaft 131 by planetary train 150 from belt pulley running shaft 111.In this case, compressor 130 runnings, overrunning clutch 180 is in idle condition.At this moment, shown in Fig. 7 cathetus F, motor 120 rotates with the direction opposite with belt pulley 110 sense of rotation, thereby makes the rotational speed of compressor 130 be higher than the rotational speed of belt pulley 110, and has increased the discharge capacity of compressor 130.Along with the rotational speed increase of motor 120, the rotational speed of compressor 130 also increases.
Under the normal refrigeration mode after refrigerating mode finishes, solenoid clutch 170 is connected, motor 120 and compressor 130 main driving force runnings by belt pulley 110, and overrunning clutch 180 is in idle condition.At this moment, because compressor 130 is carried out compression work, the running moment of torsion of compressor 130 is higher than the running moment of torsion of motor 120.Thereby shown in Fig. 7 cathetus G, the rotational speed of compressor 130 is lower than belt pulley 110, and the discharge capacity of compressor 130 reduces.On the other hand, motor 120 is as generator, and with a rotational speed running that is higher than belt pulley 110, and motor 120 accumulators 20 charge.Here, the rotational speed along with motor 120 reduces the rotational speed increase of compressor 130.
When motor 10 stopped, solenoid clutch 170 cut out, and compressor 130 is by the driving force running of motor 120.At this moment, shown in Fig. 7 cathetus H, motor 120 antiports, and the driving force of motor 120 oppositely imposes on belt pulley running shaft 111.In this case, belt pulley 110 is by unidirectional clutch 180 lockings, and the driving force of motor 120 passes to compressor 130.Here, the rotational speed along with motor 120 increases or reduces, the rotational speed increase or the minimizing of compressor 130.Even when motor 10 runnings, if solenoid clutch 170 cuts out, compressor 130 can turn round by reverse direction actuation motor 120, stops as motor 10.
As mentioned above, because the SP motor is used as motor 120, planetary train 150 can be arranged in the space of rotor 120a effectively, thereby has reduced the size of hybrid compressor 101.And, belt pulley running shaft 111, motor 120 and compressor rotating shaft 131 are connected respectively to planetary carrier 152, on sun gear 151 and the ring gear 153.Therefore, compressor 130 can be very big with respect to the reduction speed ratio of motor 120, and motor 120 can have a high rotational speed and a low moment of torsion, thereby reduced the size and the manufacture cost thereof of hybrid compressor 101.
And, in second embodiment, provide solenoid clutch 170 and overrunning clutch 180.Thereby, even it is when motor 10 running, lower and when having enough electrical power storage in storage battery 20, compressor 130 can be turned round by the electric power that use comes from storage battery 20 by motor 120 when the thermal load of cooling cycle system 200.Thereby the running of motor 10 can be lowered than (operational ratio), thereby has improved the fuel consume performance.In second embodiment, other parts and aforesaid first embodiment are similar.
(the 3rd embodiment)
Be described referring now to Fig. 8 and 9 couples of the 3rd embodiments of the present invention.As shown in Figure 8, in the 3rd embodiment, compare with second embodiment, another overrunning clutch (second overrunning clutch) 190 is added in the hybrid compressor 101.Second overrunning clutch 190 allows motor 120 only by the direction rotation opposite with belt pulley 110 sense of rotation.Second overrunning clutch 190 is set between the rotor portion 120a and casing 140 of motor 120.
In the 3rd embodiment, the running of hybrid compressor 101 and second embodiment difference under following situation are at refrigerating mode, normal refrigeration mode after refrigerating mode finishes, the normal refrigeration mode after the refrigerating mode in the refrigeration mode when refrigeration mode when motor 10 stops and motor 10 runnings finishes.Shown in Fig. 9 cathetus G (G is corresponding with Fig. 7 cathetus), in second above-mentioned embodiment, motor 120 and compressor 130 are by the driving force running of belt pulley 110.Yet in the 3rd embodiment, shown in Fig. 9 cathetus I, motor 120 is locked and stop along the sense of rotation of belt pulley 110 by second overrunning clutch 190.Therefore, all driving forces of belt pulley 110 can pass to compressor 130, and the rotational speed of compressor 130 is with respect to the rotational speed increase of belt pulley 110.
Therefore, being used for drive motor 120 has not just needed with the driving force that produces electric power, and the load of motor 10 reduces, thereby has improved the fuel consume performance.Moreover because motor 120 is not carried out the operation that produces electric power, the control that electric power is produced has not just needed.And 130 electric power has not needed from motor 120 to compressor, and the energy consumption of storage battery can reduce.Exchanged even be connected to the motor drive shaft 121 of planetary train 150 and the position of compressor rotating shaft 131, the running effect identical with second embodiment also can obtain.In the 3rd embodiment, other parts are identical with aforesaid second embodiment.
(the 4th embodiment)
To be described with reference to Figure 10-14 couple of the 4th embodiment of the present invention now.In the 4th embodiment, to compare with the 3rd embodiment, the protective function of the unusual running measuring ability of compressor 130 and protection motor 10 is added in the hybrid compressor device 100.As shown in figure 10, in the 4th embodiment, be provided with groove part 150a and protruding part 150b at the excircle of ring gear 153, compressor rotating shaft 131 is connected on the ring gear 153.As shown in figure 11, the magnetic line of force results between rotor portion 120a and the stationary part 123.The sub-fraction magnetic line of force leaks into the radially inner side of rotor portion 120a, and the radial outside of stator 123.When ring gear rotation, when the magnetic line of force leaks simultaneously, just change once at the magnetic resistance of rotor portion 120a radially inner side every process groove part 150a and protruding part 150b with groove part 150a and protruding part 150b.Like this, the magnetic line of force in the stator 123 changes.Thereby, below the induced voltage V of definition in the formula (1) result from the two ends of a coil 123a of stator 123.
V＝N×dΦ/dt……(1)
Here, N is the number of turn of coil 123a, and Φ is a magnetic flux, and t is the time.The fluctuation of the induced voltage at coil 123a two ends can calculate by Finite Element Method (FEM).Result of calculation is shown in Figure 12.As seeing among Figure 12, the fluctuation of induced voltage can be determined by control unit 160, even is under the lower operating condition at compressor 130, the rotational speed of 2000rpm for example, that is, and the running lower limit of compressor 130.
Secondly, the control operation of detection induced voltage V and protection motor 10 is as follows with reference to the flow chart description among Figure 13.At step S1, determine whether air-conditioning (A/C) is opened.That is,, determine whether to receive the air conditioning desired signal at step S1.When air-conditioning quilt is opened, that is, when the decision of step S1 is YES (being), determine at step S2 whether motor 10 turns round.When the decision of step S1 was NO (denying), control program finished, and restarted from initial step.When step S2 determines motor 10 runnings, determine at step S3 whether compressor 130 needs to only depend on the driving of motor 120 to turn round.Here, settling the standard is that thermal load according to cooling cycle system 200 is set.Thermal load can be divided into the high heat load under the refrigerating mode, middle thermal load and low load under the normal refrigeration mode.Compressor 130 turns round by motor 10 and motor 120 under refrigerating mode usually, only depends on motor 10 to turn round usually under normal refrigeration mode.Moreover under low load model, compressor 130 only depends on motor 120 to turn round usually.
When determining that at step S3 compressor 130 does not need to only depend on motor 120 to drive, that is, when the decision at step S3 was NO (denying), at step S4, the wait state of compressor 130 was kept.Here, the rotational speed of predetermined compressor 130 increases and stablizes 0.5s, and wait state keeps 0.5s at step S4.Then, at step S5, solenoid clutch 170 is connected.At step S6, determine whether compressor 130 needs to only depend on motor 10 to turn round.When the thermal load of cooling cycle system 200 is thermal load under the normal refrigeration mode, that is, when determining that at step S6 compressor 130 need only depend on motor 10 to turn round, stop in the running of step S7 motor 120.Specifically, as what describe in the third embodiment, when motor 120 was locked by second overrunning clutch 190, the energising of motor 120 was stopped.Like this, compressor 130 only depends on the driving force running of motor 10.
At step S8, whether the fluctuation of determining to result from the induced voltage at coil 123a two ends surpasses predetermined value.When the fluctuation of determining induced voltage during, can determine to be connected to compressor 130 on the ring gear 153 by original rotational speed running less than predetermined value.At step S9, solenoid clutch 170 is closed.When step S8 determines fluctuation more than or equal to predetermined value, can determine that compressor 130 runs well, and compressor 130 is by motor 10 runnings.
On the other hand, when determining that at step S2 the running of motor 10 stops or when step S3 determines that compressor 130 need only depend on motor 120 runnings, closing at step S10 solenoid clutch 170.Then, at step S11, motor 120 runnings, compressor 130 is by motor 120 runnings.At step S12, the running of compressor 130 unusual (locked) detects by the current value (currentvalue) of motor 120.When determining that at step S6 compressor 130 does not need to only depend on motor 10 runnings, in 120 runnings of step S11 motor, and compressor 130 is by motor 10 and motor 120 runnings.At step S12, come execute exception to detect by the current value that is supplied to motor 120.
When compressor 130 during by motor 120 runnings, if compressor 130 similar locked such running takes place when unusual, running can detect by the current value of motor 120 at step S12 unusually.In the 4th embodiment, when compressor 130 was similar to locked such running and takes place unusually, the rotational speed that is connected to the ring gear 153 of compressor 130 reduced or becomes 0, and the fluctuation of the induced voltage of coil 123a has also reduced.Therefore, just do not needed other detection device, the running of compressor 130 can be come out by the surge detection of induced voltage unusually.Compressor rotating shaft 131 is connected on the ring gear 153, fluted part 153a and protruding part 153b on the excircle of ring gear 153.Because groove part 153a and protruding part 153b are provided with near the position of the radially inner side of magnet 122, so the fluctuation of induced voltage can detect at an easy rate.Moreover when the fluctuation of detected induced voltage during less than reference value, that is, when compressor 130 was similar to locked such running and takes place unusually, solenoid clutch 170 cut out.Therefore, can prevent motor 10 overloads, thereby protect motor 10.
As shown in figure 14, motor 120 can be connected on the ring gear 153, and compressor rotating shaft 131 can be connected on the sun gear 151.In this case, compressor rotating shaft 131 comprises the second rotor portion 131a, and cylindrical side Monday of the second rotor portion 131a is positioned at inner circumference one side of rotor portion 120a.Moreover the second rotor portion 131a comprises groove part 150a and protruding part 150b.Even in this case, also can obtain same running effect.
(the 5th embodiment)
Referring now to Figure 15 the 5th embodiment of the present invention is described.In the 5th embodiment, show with identical label with the similar parts of previously described those embodiments, and its detailed description is omitted.
In the 5th embodiment, as shown in figure 15, motor 120 and planetary train 150 are arranged in the motor casing 331.And suction port 331a is formed in the excircle part of motor casing 331, and safety check 380 is arranged among the suction port 331a.Refrigeration agent flows out from the vaporizer 230 of cooling cycle system 200, flows into the motor casing 331 from suction port 331a.Safety check 380 prevents that refrigeration agent from passing through suction port 331a and flowing out from motor casing 331.Moreover shaft sealer 395 is arranged between belt pulley running shaft 111 and the motor casing 331, and shaft sealer 395 prevents that refrigeration agent and lubricant oil from flowing out from motor casing 331.
Suction port 372a is formed among the sidewall 331c, toward each other, and opens and closes by movable orbiting scroll 343 on two positions on the circumference.When a suction port 372a opened, the inner space of suction chamber 347 and motor casing 331 can interconnect.By suction port 372a, the pressure in the motor casing 331 can be identical with the pressure in the suction chamber 347, that is, identical with the pressure of the refrigeration agent that sucks.In the present invention, suction chamber 347 is corresponding with the suction area (suction area) of compressor 130.Opening 331e is limited by outstanding wall 331d at the downside of outstanding wall 331d, and its position is higher bottom than the small gear 152a of planetary train 150 and the meshing zone between the ring gear 153.Moreover, storage wall 331b is set, storage wall 331b is used to preserve the lubricant oil that is introduced in the predetermined quantity in the motor casing 331.Owing to be provided with opening 331e, lubricant oil can be kept in the storage wall 331b by predetermined quantity.The position of the suction port 372a of downside is lower than the upper end of storage wall 331b.
Compression cover 341 is fixed on the quiet whirlpool dish 344 side relative with motor casing 331, and is separated into drain chamber 346 and accumulator 341a by compression cover 341 and dish 344 spaces that limit, quiet whirlpool by partitioning wall 341c.Pressing chamber 345 and drain chamber 346 are coiled the floss hole 344a at 344 centers and are interconnected by being arranged on quiet whirlpool.In partitioning wall 341c, be provided with the discharge orifice 341d of a minor diameter.Drain chamber 346 and accumulator 341a interconnect by discharge orifice 341d.By discharge orifice 341d, the interior refrigerant pressure of the pressure in the accumulator 341a and drain chamber 346 is identical.In the present invention, accumulator 341a is corresponding to the discharge area of compressor 130.
Secondly, the running of hybrid compressor with structure of the 5th above-mentioned embodiment will be described below.As describing among first and second embodiments, the rotational speed of compressor 130 can increase by the sense of rotation with respect to the rotational speed of the rotational speed governor motor 120 of belt pulley 110 and motor 120 and reduce.
When compressor 130 runnings, refrigeration agent is drawn in the motor casing 331 from suction port 331a, and flows through around motor 120 with around planetary train 150.Then, refrigeration agent flows into the suction chamber 347 from suction port 372a, and is compressed towards the whirlpool at pressing chamber 345 centers dish 343,344.Refrigerant compressed flows into the drain chamber 346 from floss hole 344a, and arrives centrifugal separaton 360 from discharge orifice 341d.At this moment, the lubricant oil that just is comprised in the refrigeration agent such as whirlpool dish 135,344 and eccentric shaft 134 such sliding partss lubricates.When refrigerant compressed flow through discharge orifice 341d, its flowing velocity increased, and flowed into the bottom of centrifugal separaton 360 spirally.Because it is bigger than refrigeration agent to be included in the proportion of the lubricant oil in the refrigeration agent, lubricant oil separates with refrigeration agent on the sidewall of accumulator 341a, and is stored in the downside of accumulator 341a.Refrigeration agent and lubricating oil separation, compressor 130 is flowed out from floss hole 341b in the inside of the centrifugal separaton 360 of flowing through.
Be stored in the lubricant oil of accumulator 341a downside, because the pressure of accumulator 341a inner refrigerant, that is, and the compression pressure of refrigeration agent, and be introduced into the motor casing 331 from the first decompression communication passage 371.The lubricant oil of introducing is stored in the motor casing 331, up to the top that reaches storage wall 331b, the lower position of motor 120 and the mate of small gear 152a and ring gear 153.Moreover because the pressure in the pressure ratio accumulator 341a in the motor casing 331 is low, the refrigeration agent that is included in the lubricant oil is vaporized in motor casing 331.Therefore, the lubricant oil that contains refrigeration agent is ejected on motor 120 and the planetary train 150.When the liquid surface of lubricant oil surpassed the top of storage wall 331b, lubricant oil flowed into suction chamber 347 from the suction port 372a that setting is lower than storage wall 331b top, so whirlpool dish 135,344 and eccentric shaft 134 are lubricated.
As mentioned above, in the 5th embodiment, the lubricant oil that is included in the refrigeration agent separates with refrigeration agent by the centrifugal separaton in the accumulator 341a 360, and separated lubricating oil is introduced in the motor casing 331 by the first decompression communication passage 371.Then, the lubricant oil of introducing is recycled to the suction chamber 347 of compressor 130 from motor casing 331.Therefore, lubricant oil can be supplied to the planetary train 150 in the motor casing 331 always, thereby has improved the reliability of planetary train 150.And, because motor 120 also is arranged in the motor casing 331, thus motor 120 can lubricated oil cooling but, thereby improved the reliability of motor 120.Moreover, replace and improve planetary train 150 and motor 120 reliabilities, can reduce the size of planetary train 150 and motor 120.
Because lubricant oil is separated in refrigeration agent by centrifugal separaton 360, the refrigeration agent that circulates in 200 li of cooling cycle systems contains lubricant oil hardly.Therefore, lubricant oil not can attached to be arranged on 200 li of cooling cycle systems such as on the such heat exchanger of vaporizer 230, thereby the heat exchange efficiency of the device 230 that avoids evaporating is because lubricant oil former thereby reduce.Moreover because suction port 331a is arranged in the motor casing 331, the low-temperature refrigerant before planetary train 150 and motor 120 can be compressed cools off effectively, thereby further improves the reliability of motor 120 and planetary train 150.Because the inner space of accumulator 341a and motor casing 331 interconnects by the first decompression communication passage 371, isolated lubricant oil can be incorporated into by the discharge pressure of refrigeration agent in the motor casing 331, can prevent that also a large amount of refrigerant compressed from turning back to motor casing 331 simultaneously.
Because storage wall 331b is arranged in the motor casing 331, the liquid surface of lubricant oil can remain on the small gear 152a that is higher than planetary train 150 and the position of the meshing zone between the ring gear 153.Therefore, when planetary train 150 runnings, lubricant oil can be supplied to planetary train 150 fully, and planetary train 150 also must lubricatedly arrive.The lubricant oil that exceeds storage wall 331b top turns back to compressor 130 again by suction port 372a.
When not using hybrid compressor 101, its temperature reduces, and refrigeration agent is condensed in motor casing 331 or in the compressor 130.Then, the lubricant oil in motor casing 331 or the compressor 130 may overflow from suction port 331a with condensed refrigerant.Yet because suction port 331a has safety check 380, so lubricant oil can not overflow from suction port 331a with condensed refrigerant.Therefore, hybrid compressor 101 can not restart, and lubricant oil can not be supplied to planetary train 150 and compressor 130 yet, thereby prevents such as planetary train 150 and taken place by locked such trouble by locked and compressor 130.
Moreover compressor 130 is scroll compressors, and motor casing 331 and floss hole 341b are arranged on the both end sides that is positioned at the compressing area of compressor 130 on the axial direction of compressor rotating shaft 131.Therefore, hybrid compressor 101 can be constructed at an easy rate.Moreover, the suction port 331a in being arranged on motor casing 331, the suction port that another directly is communicated with suction chamber 347 can also be set.When suction port 331a only was arranged in motor casing 331, refrigeration agent absorbed heat from planetary train 150 and motor 120.Therefore, the temperature of refrigeration agent raises, and refrigeration agent can expand.When dilated refrigeration agent was compressed by compressor 130, the compression efficiency of compressor 130 reduced.Therefore, if when all being provided with suction port 331a on the casing of motor casing 331 and compressor 130, it can limit the expansion of refrigeration agent, and planetary train 150 and motor 120 can be cooled.Even in the 5th embodiment, the rotational speed of compressor 130 also can change by the rotational speed of governor motor 120 with respect to belt pulley 110 rotational speeies.In the 5th embodiment, compressor 130 also can be arranged in the motor casing 331.
(the 6th embodiment)
Referring now to Figure 16 the 6th embodiment of the present invention is described.In the 6th embodiment, be provided with the second decompression communication passage 372b, replaced the suction port 372a that describes among the 5th embodiment.Specifically, suction port 331a is arranged to directly be communicated with suction chamber 347, but suction port 372a, storage wall 331b among Figure 15 and opening 331e have cancelled.That is, the space of motor casing 331 and compressor 130 are kept apart.
The second decompression communication passage 372b is set to a communication passage, and the inner space of motor casing 331 and the suction chamber 347 of compressor 130 are interconnected.The second decompression communication passage 372b has a predetermined minor diameter as the first decompression communication passage 371.The inner space of motor casing 331 is communicated with suction chamber 347 by the second decompression communication passage 372b, and the interior refrigerant pressure of motor casing 331 reduces pressure in the communication passage 372b owing to damping function reduces second.Thereby, because first and second decompression communication passage 371, the 372b, in the accumulator 341a, in the motor casing 331 and the refrigerant pressures in the suction chamber 347 reduce successively.That is, the pressure of motor casing 331 inner refrigerants is set between the suction pressure and the discharge pressure in the accumulator 341a in suction chamber 347.Therefore, lubricant oil can circulation between accumulator 341a, motor casing 331 and suction chamber 347 reposefully.Therefore, lubricant oil can be supplied to planetary train 150 and motor 120 fully so that planetary train 150 and motor 120 can be lubricated oil lubricate and cool off, thereby improved the reliability of planetary train 150 and motor 120.In the 6th embodiment, the same among other parts and aforesaid the 5th embodiment.
(other embodiment)
Can use planetary roller (planetary roller) or differential gear to replace planetary train 150 among the aforesaid embodiment.Connection between connection between planetary train 150 and the belt pulley 110, motor 120 and the compressor 130 can be adopted other linkage structure, does not need not to be restricted in the linkage structure among the aforesaid embodiment.In the present invention, when the driving torque of the driving torque of belt pulley 110 and motor 120 increases, and the driving torque that increases is when passing to compressor 130, and linkage structure can suitably change.For example, motor 120 can be connected on the sun gear 151, and belt pulley running shaft 111 can be connected on the ring gear 153.In this case, compressor rotating shaft 31 is connected on the planetary carrier 152.
In fixed volume formula compressor, compressor 130 can be rolling piston compressor or sliding-vane compressor (through vane type compressor), and is not limited to scroll compressor.Moreover compressor 130 can be a variable displacement compressor, such as swash-plate-type compressor, to replace fixed volume formula compressor.In this case, the variable displacement of compressor 130 can further increase.The present invention can be applied to multi-power driven vehicle, and this automobile comprises that a drive motor is used for powered vehicle, and vehicle motor 10 stops under certain predetermined operating condition of vehicle.
Although the present invention showed and describe with reference to the preferred embodiment of front, but under the situation of the scope of the invention that does not depart from claim and limited, its form and details can change, and this is conspicuous for those of ordinary skill in the art.
Claims (9)
1. hybrid compressor device comprises:
Driver element (110), described driver element (110) rotates by the driving force that reception comes from external drive source;
Motor (120), described motor (120) rotates by the electric power that reception comes from external power supply;
Compressor (130), described compressor (130) is turned round by in driver element and the motor at least one, and described compressor is used for the refrigeration agent of the compression refrigeration circulatory system, and compressor comprises
Before being compressed, suction area (347), refrigeration agent be introduced into wherein,
Discharge region (341a), refrigerant compressed flows into wherein, and
Oil separation unit (360), described oil separation unit (360) is used for and will be included in system
Lubricant oil in the cryogen is separated in refrigeration agent, and separated lubricating oil is stored in the discharge region;
Driving mechanism (150), driving mechanism (150) be arranged in compressor and driver element (110) and the motor (120) at least any between, driving mechanism is used for changing at least one rotational speed of driver element and motor, and it is passed to compressor;
Casing (331), described casing (331) is used to hold motor and driving mechanism; And
Form the device of oily guiding channel (371), the lubricant oil that is stored in discharge region (341a) is introduced in the casing by oily guiding channel (371),
Wherein, (172a 172b) is communicated with suction area by communication passage in the inner space of casing.
2. hybrid compressor device according to claim 1, wherein:
In compressor and the casing at least one has suction port (331a), and refrigeration agent is introduced in the suction area (347) of compressor from suction port (331a).
3. hybrid compressor device according to claim 1, wherein:
Casing is set to and can holds compressor, motor and driving mechanism; And
Casing has suction port (331a), and a side of motor and driving mechanism is being set, and refrigeration agent is drawn into the compressor from suction port (331a).
4. according to any one described hybrid compressor device of claim 1-3, wherein:
The oil guiding channel is a decompression communication passage (371), and discharge region is communicated with the inner space of casing by it, and the pressure that comes from discharge region reduces in communication passage.
5. according to any one described hybrid compressor device of claim 1-3, wherein:
Driving mechanism (150) comprises a plurality of displaceable elements (152a, 153);
Casing has storage wall (331b), and storage wall (331b) is used for the lubricant oil of storing predetermined quantity in casing;
Storage wall has the top, and described top is in the contact area that is higher than between the moveable part; And
Communication passage is arranged on the position on the top that is lower than storage wall.
6. hybrid compressor device according to claim 1, wherein:
The oil guiding channel is the first decompression communication passage (371), and discharge region is by the internal communication of it and casing, and reduces towards box house pressure from discharge region; And
Communication passage is the second decompression communication passage (172b), and box house is communicated with suction area by it, and reduces towards suction area pressure from box house.
7. according to any one described hybrid compressor device of claim 1-3, lubricating oil separation unit wherein is arranged on the centrifugal separaton (360) in the discharge region.
8. hybrid compressor device according to claim 2 also comprises
Be arranged on the safety check (380) of suction port, described safety check (380) is used to prevent that lubricant oil from flowing out in casing by suction port.
9. hybrid compressor device according to claim 1, wherein:
Compressor comprises a compressing area (137,345), and compressing area (137,345) are used for compressed refrigerant, and a floss hole (341b), and refrigerant compressed is discharged into the outside of compressor from floss hole (341b); And
Casing and floss hole are arranged on the both sides of compressing area on the spin axis direction of compressor.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001366706 | 2001-11-30 | ||
| JP2001366706 | 2001-11-30 | ||
| JP2002196053 | 2002-07-04 | ||
| JP2002223638 | 2002-07-31 | ||
| JP2002284142 | 2002-09-27 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB021527970A Division CN1261728C (en) | 2001-11-30 | 2002-11-28 | Mixed compressor apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1769709A true CN1769709A (en) | 2006-05-10 |
Family
ID=36751193
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200510120094 Pending CN1769709A (en) | 2001-11-30 | 2002-11-28 | Hybrid compressor device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1769709A (en) |
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2002
- 2002-11-28 CN CN 200510120094 patent/CN1769709A/en active Pending
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