JP2005042685A - Hybrid compressor device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hybrid compressor device capable of improving reliability during high rotation of a compressor, in the device provided at its internal part with a gear change mechanism. <P>SOLUTION: In the hybrid compressor device where rotary shafts 111, 121, and 131 of a pulley 110, a motor 120, and a compressor 130 are connected to a gear change mechanism 150 capable of varying the number of revolutions for transmission, and by a control device 160, the number Nm of revolutions of the motor 120 is adjusted, and the number Np of revolutions of the compressor 130 is increased or decreased according to the Number Np of revolutions of the pulley 110, the control device 160 is provided with a number of revolutions control means to control such that the number Nc of revolutions of the compressor 130 does not exceed a predetermined given value Nmax. This constitution enables improvement of reliability during high rotation of the compressor. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a hybrid compressor device suitable for being applied to a so-called idle stop vehicle or a refrigeration cycle device mounted on a hybrid vehicle in which an engine is stopped according to a traveling state.

  In recent years, there has been an example where an idle stop vehicle, a hybrid vehicle, or the like whose engine is stopped according to a traveling state is put on the market from the viewpoint of fuel saving. In order to deal with these vehicles, a hybrid compressor that can be operated by a driving force of a motor in addition to a driving force of an engine has been put into practical use.

  In the Japanese Patent Application No. 2002-284142, the present inventors previously connected a pulley shaft, a motor shaft, and a compressor shaft to a hybrid compressor so that the rotational speed can be varied from one shaft to the other two shafts. There has been proposed a hybrid compressor apparatus that is provided with a speed change mechanism and that can adjust the rotational speed of the motor with respect to the rotational speed of the pulley to increase or decrease the rotational speed of the compressor.

  As a result, the discharge amount of the compressor can be varied depending on the number of rotations, and a small and inexpensive hybrid compressor apparatus is realized without requiring the function of varying the discharge capacity of the compressor.

  However, in the above device, although the rotation speed of the compressor can be varied, consideration has not been given to the allowable upper limit rotation speed. Therefore, depending on the conditions of the rotation speed of the pulley and the motor, the compressor is very high. In some cases, it may be operated by rotation. For example, it has a portion lacking in reliability related to durability.

  In view of the above problems, an object of the present invention is to provide a hybrid compressor device that has a transmission mechanism inside and that can improve the reliability at the time of high rotation of the compressor.

  In order to achieve the above object, the present invention employs the following technical means.

  In the first aspect of the present invention, the pulley (110) that is rotationally driven by the engine (10) and the power source (20) are driven to rotate, and the rotational speed is controlled by the control device (160). Motor (120), a compressor (130) that compresses refrigerant in the refrigeration cycle apparatus (200), and the respective rotation shafts (111, 121,) of the pulley (110), the motor (120), and the compressor (130). 131) and a speed change mechanism (150) that can transmit the rotation speed from each rotation shaft (111, 121, 131) to the other rotation shafts (111, 121, 131) by changing the number of rotations. The controller (160) adjusts the rotational speed (Nm) of the motor (120), and the rotational speed (Nc) of the compressor (130) increases or decreases with respect to the rotational speed (Np) of the pulley (110). High In the lid compressor apparatus, the control device (160) includes a rotation speed suppressing means for suppressing the rotation speed (Nc) of the compressor (130) so as not to exceed a predetermined value (Nmax). .

  Thereby, the reliability at the time of high rotation of a compressor (130) can be improved.

  In the invention according to claim 2, the rotation speed suppression means adjusts the rotation speed (Nm) of the motor (120) when the rotation speed (Nc) of the compressor (130) exceeds a predetermined value (Nmax). It is characterized by that.

  As a result, the reliability of the compressor (130) can be improved without adding a special configuration (without adding extra cost).

  In the invention according to claim 3, the rotation speed suppression means is operated on the speed increasing side with respect to the rotation speed at which the compressor (130) is shifted by the pulley (110) by the drive of the motor (120). When the rotational speed (Nc) of the compressor (130) exceeds a predetermined value (Nmax), the rotational speed of the motor (120) is set to zero.

  Thereby, since the rotation speed (Nm) of the motor (120) is not added to the compressor (130), the rotation speed (Nc) of the compressor (130) can be suppressed and the reliability can be improved.

  In the invention according to claim 4, the electromagnetic clutch (170) for intermittently driving the driving force from the engine (10) transmitted to the rotating shaft (111) of the pulley (110), and the rotating shaft (111) of the pulley (110). ) And a lock mechanism (180) that locks the transmission mechanism (150) side of the rotating shaft (111) when the electromagnetic clutch (170) is disengaged. When the rotational speed (Nc) of (130) exceeds a predetermined value (Nmax), the electromagnetic clutch (170) is disconnected and the compressor (130) is operated by the driving force of only the motor (120). Yes.

  Thereby, since the rotation speed (Np) of the pulley (110) is not added to the compressor (130), the rotation speed (Nc) of the compressor (130) can be suppressed and the reliability can be improved.

  The invention according to claim 5 is characterized in that the control device (160) sets the predetermined value (Nmax) larger as the cooling load of the refrigeration cycle device (200) becomes smaller.

  As a result, the operating speed range of the compressor (130) can be expanded in accordance with the cooling load as compared with the case where a uniform predetermined value (Nmax) is set, so that the variable speed function of the original compressor (130) can be increased. It can be used effectively.

  In the invention described in claim 6, the compressor (130) is a variable capacity compressor (130) that can change the discharge capacity per one rotation, and the control device (160) is the compressor (130). The predetermined value (Nmax) is set larger as the discharge amount obtained by multiplying the discharge capacity per rotation of the compressor (130) by the rotation speed (Nc) of the compressor (130) decreases. When the number of rotations (Nc) exceeds a predetermined value (Nmax), the discharge capacity is varied to the smaller side.

  Thereby, since the substantial predetermined value (Nmax) can be increased by reducing the load (discharge capacity) of the compressor (130), the reliability of the compressor (130) can be improved.

  The predetermined value (Nmax) is determined from the durability limit of the compressor (130) as in the invention described in claim 7, or the compressor (130) as in the invention described in claim 8. It can be determined from the noise limit.

  Further, as in the ninth aspect of the invention, the speed change mechanism (150) is a planetary gear (150), and each rotating shaft (111, 121, 131) is a sun gear (151) constituting the planetary gear (150). ), It is possible to easily cope with the planetary carrier (152) and the ring gear (153).

  In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description mentioned later.

(First embodiment)
A first embodiment of the present invention is shown in FIG. 1 to FIG. 5, and a specific configuration will be described with reference to FIG. As shown in FIG. 1, the hybrid compressor apparatus 100 is applied to a refrigeration cycle apparatus 200 mounted on a so-called idle stop vehicle in which the engine 10 is stopped when the vehicle is temporarily stopped during traveling operation. And a control device 160.

  Here, the refrigeration cycle apparatus 200 forms a known refrigeration cycle, and is provided with a compressor 130 that constitutes the hybrid compressor 101 described later. The compressor 130 compresses the refrigerant in the refrigeration cycle to a high temperature and a high pressure, and hereinafter, a condenser 210 that condenses and liquefies the compressed refrigerant, an expansion valve 220 that adiabatically expands the liquefied refrigerant, and an expanded refrigerant. The evaporator (cooling heat exchanger) 230 that cools the air passing through itself by the latent heat of vaporization is sequentially connected by the refrigerant pipe 240 to form a closed circuit. An evaporator temperature sensor 231 for detecting the actual cooled air temperature (evaporator rear air temperature Te) is provided on the downstream side of the air flow of the evaporator 230.

  The hybrid compressor 101 mainly includes a pulley 110, an electromagnetic clutch 170, a motor 120, a compressor 130, and a planetary gear 150, and details thereof will be described below with reference to FIG.

  The pulley 110 is rotatably supported by a pulley bearing 112 fixed to the front housing 141, and the driving force of the engine 10 is transmitted via the belt 11 (FIG. 1) to be rotationally driven. The pulley rotation shaft 111 is provided at the center of the pulley 110 and is rotatably supported by a bearing 113 fixed to the front housing 141.

  The electromagnetic clutch 170 interrupts the driving force transmitted from the pulley 110 to the compressor 130 via a planetary gear 150 described later, and is connected to one end of the coil 171 fixed to the front housing 141 and the pulley rotating shaft 111. And a fixed hub 172. As is well known, when the coil 171 is energized, the electromagnetic clutch 170 attracts the hub 172 to the pulley 110 and transmits the driving force of the pulley 110 to the pulley rotating shaft 111 (clutch ON). On the contrary, when the power supply to the coil 171 is cut off, the hub 172 is separated from the pulley 110, and the driving force of the pulley 110 is disconnected (clutch OFF).

  The motor 120 mainly includes a rotor portion 120 a and a stator portion 123 and is accommodated in the intermediate housing 142. This motor 120 is a so-called SP motor (Surface Permanent-Magnet Motor) in which a magnet 122 is provided on the outer peripheral portion of the rotor portion 120a, and a planetary gear 150, which will be described later, using the space on the inner peripheral side of the rotor portion 120a. Is housed. The motor rotating shaft 121 is an aerial one indicated by a one-dot chain line at the center of the sun gear 151.

  The stator portion 123 is provided with a coil 123a, and the stator portion 123 is fixed to the inner peripheral surface of the intermediate housing 142 by press fitting. And the rotor part 120a is rotationally driven by the electric power from the battery 20 as a power supply being supplied to the coil 123a.

  Here, the compressor 130 is a fixed capacity compressor in which the discharge capacity per rotation is set as a predetermined value, more specifically, a known scroll compressor, and is an end on the side opposite to the pulley of the motor 120. A fixed scroll 134 fixed in the housing 143 and a movable scroll 135 revolving by an eccentric shaft 133 of the compressor rotating shaft 131 are provided.

  By meshing the fixed scroll 134 and the movable scroll 135, a suction chamber 136 is formed on the outer peripheral portion, and a compression chamber 137 is formed on the center side. Then, the refrigerant sucked into the suction chamber 136 from the suction port 136 a provided in the side wall of the end housing 143 is compressed in the compression chamber 137, then passes through the discharge chamber 138, and is discharged from the bottom wall of the end housing 143. It is made to discharge from the exit 138a.

  The compressor rotating shaft 131 is rotatably supported by a bearing 132 fixed to a protruding wall 142a that protrudes inward on the side opposite to the pulley of the intermediate housing 142. The compressor rotation shaft 131 is fitted with the other end of the pulley rotation shaft 111 so that the compressor rotation shaft 131 and the pulley rotation shaft 111 can be rotated independently of each other by a bearing 115.

  The rotation shafts 111, 121, 131 of the pulley 110, the motor 120, and the compressor 130 are connected to the planetary gear 150 as a speed change mechanism provided in the rotor portion 120a as described above.

  As is well known, the planetary gear 150 is provided at the outer periphery of the sun gear 151 provided at the center, the planetary carrier 152 connected to the pinion gear 152a that revolves while rotating on the outer periphery of the sun gear 151, and the pinion gear 152a. Ring-shaped ring gear 153.

  Here, the pulley rotation shaft 111 is connected to the planetary carrier 152, the motor rotation shaft 121 (in reality, the rotor portion 120 a) is connected to the sun gear 151, and the compressor rotation shaft 131 is connected to the ring gear 153. Yes. The sun gear 151 is supported by a bearing 114 so as to be rotatable independently of the pulley rotation shaft 111.

  A one-way clutch 180 whose outer peripheral side is fixed to the front housing 141 is provided between the hub 172 of the pulley rotation shaft 111 and the planetary gear 150 (planetary carrier 152). The one-way clutch 180 allows the pulley rotation shaft 111 to rotate in the pulley rotation direction, and prevents the rotation drive by meshing with the reverse rotation direction. The one-way clutch 180 corresponds to the lock mechanism of the present invention.

  On the other hand, referring back to FIG. 1, the control device 160 includes an A / C request signal, an engine speed signal, an environment information signal (a set temperature signal set by the occupant, an inside air temperature signal, an outside air temperature signal), and an evaporator temperature sensor 231. The evaporator rear air temperature (Te) signal and the like are input, and the operation of the motor 120 and the on / off of the electromagnetic clutch 170 are controlled based on these signals.

  Specifically, the electric power from the battery 20 is varied to vary the operating rotational speed of the motor 120. In addition, by turning on and off the current to the coil 171 of the electromagnetic clutch 170, the pulley 110 and the pulley rotating shaft 111 are intermittently connected.

  Further, the control device 160 stores the control characteristics shown in FIG. 3 in advance, and determines the refrigerant discharge amount of the compressor 130 that satisfies the cooling capacity required for the refrigeration cycle apparatus 200 (FIG. 3A). Then, the rotational speed of the compressor 130 (hereinafter referred to as the compressor rotational speed Nc) for securing the refrigerant discharge amount is determined (FIG. 3B).

  Here, the necessary cooling capacity of the refrigeration cycle apparatus 200 is the target evaporator temperature (target air temperature) Teo calculated from the environment information signal (set temperature signal, inside air temperature signal, outside air temperature signal) by a predetermined arithmetic expression. And the evaporator rear air temperature (actual air temperature) Te (necessary cooling capacity = Te−Teo). As the required cooling capacity increases, the refrigerant discharge amount increases.

  The refrigerant discharge amount is a discharge amount per time obtained by multiplying the discharge capacity per rotation of the compressor 130 by the compressor rotation speed Nc, and the refrigerant discharge volume increases as the compressor rotation speed Nc increases. .

  Furthermore, based on the collinear diagram in the planetary gear 150 shown in FIG. 5, the rotational speed of the motor 120 (hereinafter referred to as the motor rotational speed) from the rotational speed of the pulley 110 (hereinafter referred to as the pulley rotational speed Np) and the compressor rotational speed Nc. Nm).

  Specifically, the compressor rotational speed Nc is expressed by the planetary carrier 152 (pulley rotational shaft) with respect to the pulley rotational speed Np (the value obtained by multiplying the engine rotational speed Ne by the pulley ratio ip) as shown in the following formula 1. 111) and the ring gear 153 (compressor rotating shaft 131) and the rotation speed changed by the gear ratio λ1 and the motor rotating speed Nm, the sun gear 151 (motor rotating shaft 121) and the ring gear 153 (compressor rotating shaft 131). The motor speed Nm can be calculated from the sum of the rotational speed changed by the gear ratio λ2 between them. In the present embodiment, since the motor 120 is operated in the reverse rotation direction, the numerical value of the motor rotation speed Nm is negatively expressed in Equation 1. (Detailed operation based on the nomograph will be described later).

(Equation 1)
Nc = Ne × ip × λ1-Nm × λ2
Next, the operation based on the above configuration will be described using the flowchart shown in FIG. 4 and the alignment chart shown in FIG. The present invention is characterized in that there is provided a rotational speed suppressing means for suppressing the compressor rotational speed Nc so as not to exceed the upper limit rotational speed Nmax (predetermined predetermined value) determined from the durability limit. Yes.

  The collinear chart shown in FIG. 5 shows the relationship among the rotational speeds of the pulley 110, the motor 120, and the compressor 130 respectively connected to the planetary gear 150. As is well known, the horizontal axis indicates the coordinate position of each gear and carrier (sun gear 151, planetary carrier 152, ring gear 153) from the left, and each coordinate position includes the respective gear and carrier 151, 152 as described above. , 153 coupled to the motor 120, the pulley 110, and the compressor 130.

  Further, the interval of the horizontal axis coordinate is determined by the gear ratio λ1 between the planetary carrier 152 and the ring gear 153 and the gear ratio λ2 between the sun gear 151 and the ring gear 153 described in Expression 1. On the vertical axis, the rotation speeds of the gears and the carriers 151, 152, and 153 are shown, and the rotation speeds have a relationship in which the three members are connected by a straight line.

  Hereinafter, the operation control based on the control flow shown in FIG. 4 will be described. First, in step S100, various information (A / C request signal, engine speed Ne signal, environmental information signal, evaporator rear air temperature Te signal, etc.) is read.

  In step S110, it is determined from the A / C request signal whether the A / C switch is ON. If the determination is NO, the operation of the refrigeration cycle apparatus 200 is unnecessary and the compressor 130 does not need to be operated, so the electromagnetic clutch 170 is turned off (the motor 120 is also turned off) in step S120.

  However, if it is determined in step S130 that the A / C switch is ON, the operation control of the compressor 130 is performed according to the traveling state of the vehicle and the required cooling capacity as follows.

  In step S130, it is determined from the engine speed Ne signal whether the engine 10 is operating. If it is determined that the engine 10 is in operation, the electromagnetic clutch 170 is turned on in step S140.

  Next, it is determined whether or not assistance by the motor 120 is necessary from the required cooling capacity calculated based on the environmental information signal and the evaporator rear air temperature Te signal in step S150. Here, the case where the assistance is necessary means that, for example, the required cooling capacity is higher than a predetermined value as in cooldown in midsummer, and the driving force of the motor 120 is added to the driving force of the pulley 110 to increase the refrigerant discharge amount. It means that the compressor 130 needs to be operated.

  If it is determined in step S150 that the motor 120 needs to be assisted, a motor rotation speed Nm is set in step S160. In this step, first, the motor rotation speed Nm is set based on Equation 1. Further, as will be described later, this is a step for finely adjusting the motor rotation speed Nm.

  In step S170, the compressor rotational speed Nc is compared with the upper limit rotational speed Nmax. If it is determined that the compressor rotational speed Nc is lower than the upper limit rotational speed Nmax, both the pulley 110 (belt 11) and the motor 120 are determined in step S180. The compressor 130 is operated by the driving force.

  This is an operation corresponding to (a) in the collinear chart shown in FIG. 5, and by operating the motor 120 in the reverse rotation direction, the compressor 130 is operated on the higher rotation side than the pulley 110, and the refrigerant discharge Increase the amount to respond to the cooldown.

  However, for example, depending on the driving conditions of the vehicle (acceleration at high speed, climbing, downshift, etc.), the engine speed Ne (the pulley speed Np associated therewith) is as indicated by the black arrow in FIG. As a result, the compressor rotational speed Nc may increase as shown in FIG. 5A and exceed the upper limit rotational speed Nmax.

  In such a case, the determination in step S170 is negative, and the process returns to step S160 to set the motor rotation speed Nm again. Here, the motor rotation speed Nm is reduced by a predetermined rotation speed (white arrow in the motor in FIG. 5), and steps S160 to S170 are repeated until the compressor rotation speed Nc becomes lower than the upper limit rotation speed Nmax ( The white arrow in the compressor in FIG. 5) and the operation state in (c) in FIG.

  In the present embodiment, step S160 and step S170 correspond to the rotational speed suppressing means.

  On the other hand, if it is determined as NO in step S150, that is, it is a situation where the normal required cooling capacity is sufficient as after the cool-down (the required cooling capacity is lower than a predetermined value), and if it is determined that motor assist is unnecessary, in step S190 The compressor 120 is operated by the driving force of only the pulley 110 with the motor 120 in a non-operating state (the motor rotation speed Nm is zero).

  The operating state at this time corresponds to (D) in FIG. 5, and the compressor rotation speed Nc is lower than that in the cases (A) to (C), and the refrigerant discharge amount is reduced.

  If NO in step S130, that is, if it is determined that the engine 10 has stopped as in idling stop, the electromagnetic clutch 170 is turned OFF in step S200, and the compressor 130 is operated only by the driving force of the motor 120 in step S210. Let

  At this time, by driving the motor 120 in the reverse rotation direction, the pulley rotation shaft 111 similarly tries to operate in the reverse rotation direction, is locked by the one-way clutch 180, receives a speed change corresponding to the gear ratio λ2, and receives the compressor 130. Will operate ((e) in FIG. 5).

As described above, in the present invention, the compressor 130 is provided with the upper limit rotational speed Nmax determined from the durability limit. For example, when the compressor rotational speed Nc exceeds the upper limit rotational speed Nmax depending on the running condition of the vehicle. Since the compressor rotational speed Nc is suppressed with respect to the upper limit rotational speed Nmax by adjusting the motor rotational speed Nm, the durability of the compressor 130 at the time of high rotational speed is not added. (Reliability) can be improved.
(Second Embodiment)
A second embodiment of the present invention is shown in FIGS. In the second embodiment, the rotational speed suppressing means is configured by steps S170 and S190 in the control flow shown in FIG. 6 with respect to the first embodiment.

  That is, as described in the first embodiment, the compressor 130 is operated on the speed increasing side with respect to the rotation speed changed by the pulley 110 by the assistance of the motor 120 (step S160), and the result is NO in step S170. If it is determined that the compressor rotational speed Nc has exceeded the upper limit rotational speed Nmax (as shown in (a) in FIG. 7), the process proceeds to step S190, and the motor 120 is set in a non-operating state (the motor rotational speed Nm is zero). The compressor 130 is operated by the driving force of only the pulley 110 ((f) in FIG. 5).

Thereby, the compressor rotation speed Nc can be set to a lower rotation side than the upper limit rotation speed Nmax, and the durability (reliability) of the compressor 130 can be improved.
(Third embodiment)
A third embodiment of the present invention is shown in FIG. In the third embodiment, the rotational speed suppressing means is configured by steps S170, S200, and S210 in the control flow shown in FIG. 8 with respect to the first embodiment.

  That is, as described in the first embodiment, if it is determined in step S170 that the compressor rotation speed Nc has exceeded the upper limit rotation speed Nmax as shown in FIG. In step S210, the electromagnetic clutch 170 is turned OFF, and the compressor 130 is operated only by the driving force of the motor 120 ((e) in FIG. 5).

Thereby, the compressor rotation speed Nc can be made lower than the upper limit rotation speed Nmax, and the durability (reliability) of the compressor 130 can be improved.
(Fourth embodiment)
A fourth embodiment of the present invention is shown in FIGS. In the fourth embodiment, the upper limit number of rotations Nmax is not set uniformly with respect to the first embodiment, but is varied according to the cooling load of the refrigeration cycle apparatus 200. The cooling load is obtained from the outside air temperature, the operating torque of the compressor 130, the high-pressure side refrigerant pressure, and the like.

  Here, as shown in the control characteristics of FIG. 9, the upper limit rotational speed Nmax is set to be larger as the cooling load is smaller. This means that the operating torque of the compressor 130 becomes smaller as the cooling load becomes smaller, so that the durability of the compressor 130 can be ensured even if the upper limit rotational speed Nmax is increased.

  In the control flow shown in FIG. 10, step S155 is provided between step S150 and step S160, and an upper limit rotational speed Nmax corresponding to the cooling load at that time is set.

As a result, the operating speed range of the compressor 130 can be expanded in accordance with the cooling load as compared with the case where the uniform upper limit speed Nmax is set, so that the variable speed function of the original compressor 130 can be effectively utilized. The durability (reliability) of the compressor 130 can be improved.
(Fifth embodiment)
FIG. 11 shows a fifth embodiment of the present invention. In the fifth embodiment, the compressor 130 is a variable displacement compressor that can change the discharge capacity per rotation, and the rotation speed suppressing means is in the control flow shown in FIG. It is configured by step S170 and step S171.

  The compressor 130 has a swash plate connected to a piston, for example, as in a known swash plate compressor, and the control device 160 adjusts the inclination angle of the swash plate and the stroke of the piston, thereby varying the discharge capacity. It is assumed (not shown).

  Then, as the operation control of the compressor 130, in step S170 in FIG. 11, that is, when the compressor rotational speed Nc exceeds the upper limit rotational speed Nmax, the discharge capacity of the compressor 130 is decreased by a predetermined amount in step S171. . In step S172, it is determined whether or not the discharge capacity has reached a minimum value that can be varied. If the value is the minimum value, the process proceeds to step S160, and if not, the process proceeds to step S155.

By varying the discharge capacity to the smaller side, the refrigerant discharge amount obtained by multiplying the discharge capacity by the compressor rotation speed Nc is reduced, and the required cooling capacity with respect to the cooling load is also reduced. Based on the control characteristics described in FIG. By resetting the upper limit rotation speed Nmax (step S155), the substantial upper limit rotation speed Nmax can be increased, so that the durability (reliability) of the compressor 130 can be improved.
(Other embodiments)
In the first to fifth embodiments, the upper limit number of rotations Nmax of the compressor 130 is set from the reliability limit related to the durability. You may make it set.

  Further, the connection of the rotary shafts 111, 121, and 131 to the planetary gear 150 may be in other combinations. In this case, the adjustment of the rotational speed Nm of the motor 120 (step S160) may be determined on the side where the rotational speed Nc of the compressor 130 decreases on the common gland diagram. As the speed change mechanism, a planetary roller or a differential gear may be used instead of the planetary gear 150.

  Furthermore, the target vehicle is not limited to an idle stop vehicle, and may be a so-called hybrid vehicle that includes a traveling motor and that stops the engine 10 according to a predetermined traveling condition even during traveling.

It is a schematic diagram which shows the whole structure in embodiment of this invention. It is sectional drawing which shows a hybrid compressor. (A) is a control characteristic figure which shows the compressor discharge amount with respect to required cooling capacity, (b) is a control characteristic figure which shows the compressor discharge amount with respect to compressor rotation speed. It is a flowchart which shows the control flow in 1st Embodiment. It is a collinear diagram which shows the rotation speed of the pulley in 1st Embodiment, a motor, and a compressor. It is a flowchart which shows the control flow in 2nd Embodiment. It is a collinear diagram which shows the rotation speed of the pulley, motor, and compressor in 2nd Embodiment. It is a flowchart which shows the control flow in 3rd Embodiment. It is a control characteristic figure which shows the upper limit number of rotations with respect to cooling load. It is a flowchart which shows the control flow in 4th Embodiment. It is a flowchart which shows the control flow in 5th Embodiment.

Explanation of symbols

10 Engine 20 Battery (Power)
DESCRIPTION OF SYMBOLS 100 Hybrid compressor apparatus 101 Hybrid compressor 110 Pulley 111 Pulley rotating shaft 120 Motor 121 Motor rotating shaft 130 Compressor 131 Compressor rotating shaft 150 Planetary gear (transmission mechanism)
151 Sun gear 152 Planetary carrier 153 Ring gear 160 Control device 170 Electromagnetic clutch 180 One-way clutch (lock mechanism)
200 Refrigeration cycle equipment

Claims (9)

A pulley (110) rotationally driven by the engine (10);
A motor (120) that is driven to rotate by receiving power from the power source (20), and whose rotational speed is controlled by the controller (160);
A compressor (130) for compressing the refrigerant in the refrigeration cycle apparatus (200);
Connected to the respective rotation shafts (111, 121, 131) of the pulley (110), the motor (120), and the compressor (130), the other rotations from the respective rotation shafts (111, 121, 131). A transmission mechanism (150) that can transmit the shaft (111, 121, 131) with a variable number of rotations;
The controller (160) adjusts the rotational speed (Nm) of the motor (120), and the rotational speed (Nc) of the compressor (130) with respect to the rotational speed (Np) of the pulley (110). In the hybrid compressor device in which is increased or decreased,
The control device (160) has a rotation speed suppressing means for suppressing the rotation speed (Nc) of the compressor (130) so as not to exceed a predetermined value (Nmax). .   The rotation speed suppression means adjusts the rotation speed (Nm) of the motor (120) when the rotation speed (Nc) of the compressor (130) exceeds the predetermined value (Nmax). The hybrid compressor apparatus according to claim 1.   The rotation speed suppression means operates by driving the motor (120) so that the compressor (130) operates at a higher speed than the rotation speed changed by the pulley (110), and the compressor (130) 2. The hybrid compressor apparatus according to claim 1, wherein the rotational speed of the motor (120) is set to zero when the rotational speed (Nc) of the motor (120) exceeds the predetermined value (Nmax). An electromagnetic clutch (170) for intermittently driving the driving force from the engine (10) transmitted to the rotating shaft (111) of the pulley (110);
A locking mechanism (180) that is provided on the rotating shaft (111) of the pulley (110) and locks the transmission mechanism (150) side of the rotating shaft (111) when the electromagnetic clutch (170) is disengaged; Have
The rotational speed suppression means disconnects the electromagnetic clutch (170) and drives only the motor (120) when the rotational speed (Nc) of the compressor (130) exceeds the predetermined value (Nmax). 2. The hybrid compressor apparatus according to claim 1, wherein the compressor (130) is operated.   The said control apparatus (160) sets the said predetermined value (Nmax) large, so that the cooling load of the said refrigerating-cycle apparatus (200) becomes small. Hybrid compressor device. The compressor (130) is a variable capacity compressor (130) that can vary the discharge capacity per rotation,
The controller (160) reduces the predetermined value (Nmax) as the discharge amount obtained by multiplying the discharge capacity per rotation of the compressor (130) by the rotation speed (Nc) of the compressor (130) decreases. Set a larger value,
The said rotational speed suppression means changes the said discharge capacity to the small side when the rotational speed (Nc) of the said compressor (130) exceeds the said predetermined value (Nmax). Hybrid compressor device.   The hybrid compressor apparatus according to any one of claims 1 to 6, wherein the predetermined value (Nmax) is determined from a durability limit of the compressor (130).   The hybrid compressor apparatus according to any one of claims 1 to 6, wherein the predetermined value (Nmax) is determined from a noise limit of the compressor (130). The speed change mechanism (150) is a planetary gear (150),
Each of the rotating shafts (111, 121, 131) is connected to correspond to one of a sun gear (151), a planetary carrier (152), and a ring gear (153) constituting the planetary gear (150). The hybrid compressor apparatus according to any one of claims 1 to 8, wherein the hybrid compressor apparatus is provided.

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