JP2013083259A - Refrigerant pumping apparatus, and method for driving the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerant pump for pumping the refrigerant that can improve the power consumption, noise, heat generation, and wear.SOLUTION: The refrigerant pump 2 can be driven by a first drive unit 6 and a second drive unit via a planetary gear mechanism 5. The planetary gear mechanism 5 has a first input shaft 7 for the first drive unit 6 and a second input shaft 8 for the second drive unit. A clutch 22 is provided, which directly couples the input shafts 7, 8 in at least one operational state.

Description

  The present invention includes a refrigerant pump that can be driven by a first drive unit and a second drive unit via a planetary gear mechanism, and the planetary gear mechanism includes a first input shaft and a first drive shaft for the first drive unit. The present invention relates to a refrigerant pressure feeding device having a second input shaft for a second drive unit. The invention further relates to a method for driving a refrigerant pumping device.

  A refrigerant pumping device of the type mentioned at the beginning is known from the prior art. For example, Patent Document 1 describes a refrigerant pump for a cooling circuit of an internal combustion engine. This refrigerant pump includes a pump gear and a pump shaft connected to the pump gear in a torque resistant manner, and the pump shaft can be coupled to the internal combustion engine via a winding transmission attached to the crankshaft. Yes. A planetary gear mechanism is arranged between the pump shaft and the winding transmission so that the rotation speed of the crankshaft and the rotation speed of the pump shaft are different, and this planetary gear mechanism is preferably an electric motor. Can be connected to. With such a refrigerant pump, it is possible to widely vary the pumping capacity of the refrigerant pump. However, such a refrigerant pump has unfavorable operating characteristics particularly in terms of power consumption, noise, heat generation, and wear due to the planetary gear mechanism. Similar refrigerant pressure feeding devices are also disclosed in Patent Literature 2, Patent Literature 3, and Patent Literature 4.

German Patent Application No. 102006041687 German Patent Application No. 10214637 German Patent Invention No. 6020050000638 German Patent Application No. 102006048050

  Therefore, the present invention solves the above-described problems, and in particular, provides a refrigerant pressure-feeding device that can set a wide range of fluctuations in the pressure-feeding capacity of the refrigerant pump, and on the other hand has preferable operating characteristics in the above aspects. And

  This object is achieved by a refrigerant pumping device having the features of claim 1 of the present invention. The refrigerant pressure feeding device is provided with a clutch, and the input shafts are directly coupled to each other in at least one operating state via the clutch. The refrigerant pump can be driven by the first drive unit and the second drive unit via the planetary gear mechanism. This means that the refrigerant pump can be driven only by the first drive unit, or only by the second drive unit, or by the joint of both drive units. The first drive unit is connected to the planetary gear mechanism via a first input shaft, and the second drive unit is connected to the planetary gear mechanism via a second input shaft. Power transmission via two input shafts, that is, power transmission corresponding to each of the first drive unit or the second drive unit is performed to the planetary gear mechanism, and the refrigerant pump is transmitted via the planetary gear mechanism. Power is transmitted to the. Due to the large number of moving parts in the planetary gear mechanism, there are unfavorable operating characteristics in the refrigerant pumps known from the prior art, especially due to the rolling of the gear. In particular, the friction loss is very high, which has an undesirable effect on energy consumption, noise, heat generation and wear.

  For this reason, a clutch is provided in the present invention. Via this clutch, the input shafts for the first drive unit and the second drive unit can be directly connected to each other in at least one operating state. If the input shafts are directly connected to each other, they will have the same rotational speed. This means that being directly connected to each other is not indirectly connected via a planetary gear mechanism or a gear of the planetary gear mechanism. More specifically, the connection between the input shafts is a direct and direct connection, whereby both input shafts have the same rotational speed. Therefore, the input shaft can be connected in a torque resistant manner by this clutch. In at least one operating state, it is possible to cover at least a part of the output range desired for the refrigerant pumping device or the refrigerant pump. If operation outside the output range is desired, the input shafts are decoupled from each other in other operating states and are not directly connected to each other. Therefore, in such other operating ranges, there may still be undesirable operating characteristics. However, since the coupling of the input shaft is performed at least temporarily by the clutch, the time ratio of the other operation range to the entire operation time of the refrigerant pressure feeding device is remarkably reduced. Therefore, the operating characteristics are improved as a whole.

  In a further embodiment of the present invention, the planetary gear mechanism comprises a sun gear, an outer ring gear, and a planet carrier comprising at least one planetary gear that transmits power between the sun gear and the outer ring gear, The sun gear is connected to the first input shaft, the planet carrier is connected to the second input shaft, and the refrigerant pump is connected to the output shaft connected to the outer ring gear. This planetary gear mechanism basically has a known structure. The two drive units are connected to the sun gear or the planet carrier, i.e. directly linked to them. Here, the rotation speed of the sun gear corresponds to the rotation speed of the first input shaft, and the rotation speed of the planet carrier corresponds to the rotation speed of the second input shaft. In contrast, the refrigerant pump is driven at a rotational speed corresponding to the rotational speed of the output shaft, that is, the rotational speed of the outer ring gear. The term “connection” here refers to a connection in a generally direct relationship, so that the rotational speeds of the elements connected to each other always coincide.

  In the above configuration, the sun gear is directly connected to the planet carrier in the at least one operating state by the clutch, so that both rotate at the same rotational speed. Therefore, the first drive unit and the second drive unit are also directly connected. By fixing the sun gear and the planet carrier relative to each other, the planet gear does not rotate relative to the sun gear or the outer ring gear. Furthermore, the outer ring gear is also fixed with respect to the sun gear and the planet carrier by connecting the input shafts to each other, so that in one operating state, the output shaft is the same as the first input shaft and the second input shaft. Will have a rotational speed. In this way, in at least one operating state, the friction loss of the planetary gear mechanism is significantly reduced, which has a positive influence on the operating characteristics.

  In a further embodiment of the invention, the input shafts are indirectly connected only via a planetary gear mechanism in a first operating state, which is one of a plurality of operating states, and directly in the second operating state. Connected. As described above, the input shafts are directly connected to each other in at least one operating state (one of a plurality of operating states). This at least one operating state corresponds to the second operating state described above. On the other hand, in the first operating state, the input shafts are only indirectly connected to each other via a planetary gear mechanism. Thus, in the first operating state, the clutch is not used to connect the input shafts to each other, but rather to release them. In this way, the refrigerant pumping device can be driven over a wide output range and wear losses are reduced in the second operating state. For this reason, the refrigerant pumping device is preferably driven in this operating state.

  In a further embodiment of the invention, in the third operating state, the input shaft is indirectly connected only via a planetary gear mechanism and the first input shaft is fixed by a clutch. Thus, the third operating state primarily corresponds to the first operating state, but in contrast, the first input shaft is fixed using the clutch. For example, the clutch couples the first input shaft and the stationary element, and performs an operation corresponding to a brake or a parking brake. In the third operating state, the first input shaft is completely fixed. Therefore, the clutch can prevent the first input shaft from rotating. In the third operating state, since the first input shaft and the first drive unit are fixed by the clutch, the refrigerant pump is driven using only the second drive unit.

  In a further embodiment of the invention, power is transmitted between the planet carrier and the second drive unit by means of a winding transmission. For example, a seating surface for the power transmission means of the transmission device is formed around the planet carrier. On the other hand, the first drive unit is preferably fixedly coupled to the first input shaft.

  In a further embodiment of the invention, the first drive unit is an electric motor and the second drive unit is an internal combustion engine. The refrigerant pressure feeding device is usually attached to an internal combustion engine or a driving device equipped with the internal combustion engine. The refrigerant pressure feeding device is used for pressure feeding of the refrigerant for cooling the internal combustion engine. The internal combustion engine is usually controlled to have a constant rotational speed and / or a constant torque, the former being derived from the target rotational speed and the latter being derived from the target torque. The target rotational speed and / or the target torque is determined by a driver of a vehicle equipped with a driving device and / or a driver assistance system attached to the vehicle. Therefore, the rotation speed of the second drive unit is not adjusted to a necessary value in the refrigerant pressure feeding device. On the other hand, the electric motor can be controlled such that the refrigerant pressure feeding device is driven at a desired output. It is possible to adjust the electric motor according to the control and / or adjustment of the output of the refrigerant pump.

  The refrigerant pressure feeding device is a component of a drive device including an internal combustion engine. The invention also relates to a drive device comprising a (second) drive unit, preferably formed as an internal combustion engine, to which the refrigerant pumping device according to the above embodiment is attached.

  The invention further relates in particular to a method of driving a refrigerant pumping device according to the above embodiment, wherein the refrigerant pumping device can be driven by a first drive unit and a second drive unit via a planetary gear mechanism. And the planetary gear mechanism includes a first input shaft for the first drive unit and a second input shaft for the second drive unit. The input shafts are directly connected to each other via a clutch in at least one operating state. This refrigerant pumping device can take further embodiments as described above. As detailed above, the clutch is used to connect the input shafts directly to each other in at least one operating range.

  In a further embodiment of the invention, the input shafts are indirectly connected only via a planetary gear mechanism in the first operating state and directly connected to each other in the second operating state. Such a method has already been mentioned above. The second operating state corresponds to at least one operating state in which the input shafts are directly connected to each other by a clutch. On the other hand, in the first operating state, the input shafts can have different rotational speeds, and the input shafts are connected to each other only via the planetary gear mechanism.

  In a further embodiment of the invention, in the third operating state, the input shaft is indirectly connected only via a planetary gear mechanism and the first input shaft is fixed by a clutch. In the first operating state, the first input shaft is rotatable, but in the third operating state, the first input shaft is fixed by the clutch. Here, similar to the first operating state, the input shaft is indirectly connected only via the planetary gear mechanism.

  In a further embodiment of the invention, only one drive unit or both drive units drive in the first operating state and / or only the second drive unit drives in the second operating state, And / or in the third operating state, only the second drive unit drives. In the first operating state, the input shafts are indirectly connected to each other only via the planetary gear mechanism, and the first input shaft is not fixed using a clutch, that is, is rotatable. Furthermore, only one or both of the drive units are used simultaneously to drive the refrigerant pump. On the other hand, in the second operation state and / or the third operation state, only the second drive unit drives, while the first drive unit is in the non-drive state. In particular, in the second operating state, the first input shaft, and thus the first drive unit, can be driven by the second drive unit to enter a rotating state.

  Hereinafter, the present invention will be described in more detail with reference to exemplary embodiments shown in the drawings, but the present invention is not limited thereto.

It is longitudinal direction sectional drawing of the refrigerant | coolant pumping apparatus provided with the refrigerant | coolant pump and the planetary gear mechanism. It is a schematic diagram of the refrigerant | coolant pumping apparatus in a 1st operation state. It is a schematic diagram of the refrigerant | coolant pumping apparatus in a 2nd operation state. It is a schematic diagram of the refrigerant | coolant pumping apparatus in a 3rd operation state. It is the graph which plotted the output of the refrigerant pump in each operation state with respect to the number of rotations.

  FIG. 1 is a cross-sectional view of a refrigerant pressure feeding device 1 including a refrigerant pump 2 mainly composed of an impeller 3 and a refrigerant regulator 4. For example, the flow rate of the refrigerant passing through the refrigerant pump 2 can be adjusted by the refrigerant regulator 4 by control and / or adjustment by adjusting the cross-sectional area. The impeller 3 of the refrigerant pump 2 can be driven by a first drive unit 6 and a second drive unit (not shown) via a planetary gear mechanism 5. For this drive, the planetary gear mechanism 5 comprises a first input shaft 7 for the first drive unit 6 and a second input shaft 8 for the second drive unit. The first drive unit 6 is directly connected to the first input shaft 7. The second drive unit is connected to the second input shaft 8 via the winding transmission 9. Therefore, a seat surface 10 for winding means 11 such as a transmission belt is formed on the end surface of the second input shaft 8.

  The first input shaft 7 is directly connected to the sun gear 12 of the planetary gear mechanism 5. On the other hand, the second input shaft 8 is directly connected to the planet carrier 13 or formed by the planet carrier 13 itself. A plurality of, especially three, planetary gears 14 are rotatably mounted on the planetary carrier 13, so that the sun gear 12 and the outer ring gear 15 of the planetary gear mechanism 5 are interposed via the planetary gears 14. Power transmission is performed. The outer ring gear 15 is connected to the refrigerant pump 2 or its impeller 3 via the output shaft 16 of the planetary gear mechanism 5. The planetary gear mechanism 5 is disposed in the housing 17. Inside, the second input shaft 8 and the planet carrier 13 are supported via a bearing 18, and the outer ring gear 15 and the output shaft 16 are supported via a bearing 19. A bearing 20 is provided between the first input shaft 7 and the second input shaft 8. The bearings 18, 19, 20 are preferably configured as rolling bearings. Furthermore, in order to seal the planetary gear mechanism 5 against the periphery of the housing 17, at least one sealing means 21 is provided on the end face of the planetary gear mechanism 5, in particular in the form of a sealing ring.

  A clutch 22 is provided between the input shaft 7 and the input shaft 8. This can be brought into at least three operating states by the regulator 23. Here, the clutch 22 includes a slider 24, a slider base 25, at least one synchronization ring 26 (here, two synchronization rings 26), and one or a plurality of friction rings 27. In the exemplary embodiment, a friction ring 27 is disposed for each of the synchronization rings 26. The slider base 25 is connected to the first input shaft 7 in terms of torque resistance. At the same time, the slider 24 is coupled to the slider base 25 in a torsion-resistant manner, but is supported so as to be slidable in the axial direction with respect to the rotating shaft 28 of the planetary gear mechanism 5. By sliding the slider 24 in the axial direction, the clutch 22 and the refrigerant pressure feeding device 1 can be put into various operating states. In the first operating state shown in FIG. 1, the slider 24 is in the center, so that the input shaft 7 and the input shaft 8 are respectively rotatable and are connected to each other only via the planetary gear mechanism 5. Yes. In particular, in the second operation state (in this operation state, the slider 24 is moved to the left), the input shaft 7 and the input shaft 8 are directly connected to each other. Therefore, in this second operating state, the input shaft 7 and the input shaft 8 have the same rotational speed. In the third operating state in which the slider 24 has moved to the right, the first input shaft 7 is fixed, thereby making rotational movement impossible. However, at this time, the input shaft 7 and the input shaft 8 are connected to each other only via the planetary gear mechanism 5.

  Various operating states will be described below with reference to FIGS. FIG. 2 shows a first operating state. It is clear that the slider 24 is in the neutral position, so that the input shaft 7 and the input shaft 8 are freely movable and are connected to each other only via the planetary gear mechanism 5. In the first operating state, the refrigerant pump 2 can be driven only by the first drive unit 6, for example. In that case, the maximum volume flow rate pumped by the refrigerant pump 2 is determined by the electric motor 6. In this way, for example, after-run of the refrigerant pump 2 after the internal combustion engine is deactivated can be realized. Such after-run is important so that local boiling does not occur in a cooling circuit (not shown) in which the refrigerant acts by the refrigerant pump 2. The maximum volume flow rate is independent of the rotational speed of the internal combustion engine and depends only on the maximum output of the electric motor 6.

  On the other hand, the refrigerant pump 2 can be driven by both the electric motor 6 and the internal combustion engine. In the low speed range of an internal combustion engine, it may be desirable to increase the volumetric flow rate, for example to meet the requirements of a heater system, especially when the ambient temperature is low. In this case, the electric motor 6 can be used in addition to the internal combustion engine to drive the refrigerant pump 2. Thereby, a larger volume flow rate can be realized. Similarly, the electric motor 6 is further operated in order to increase the volume flow rate pumped by the refrigerant pump 2 when the internal combustion engine is in a high load and low rotational speed state. As a result, the internal combustion engine can be optimally cooled even in a low rotation range. There is no need to suppress the output of the internal combustion engine because the volumetric flow rate is small. Finally, the refrigerant pump 2 may be driven only by the internal combustion engine. While the internal combustion engine is operating, the second input shaft 8 is continuously driven. In the first operating state, the motor 6 can be used as a generator to supply electricity to the power supply system, for example, in accordance with the output distribution in the planetary gear mechanism 5.

  FIG. 3 shows a second operating state. Here, the input shaft 7 and the input shaft 8 are directly connected to each other, and they have the same rotational speed. Here, the sun gear 12 is coupled to the planet carrier 13 in a torque resistant manner. At this time, the planetary gear mechanism 5 is integrally rotated, and in this integral rotation, the input shaft 7, the input shaft 8, and the output shaft 16 rotate at the same rotational speed. The refrigerant pump 2 is driven only by the internal combustion engine, and thus is driven via the second input shaft 8. Thus, the maximum volume flow obtained is smaller than in the first operating state, but is sufficient for most purposes. Since the volumetric flow rate is smaller, the required driving force is also smaller. When the planetary gear mechanism 5 rotates integrally, the planetary gear 14 does not rotate or roll. In this way, the friction loss of the planetary gear mechanism 5 is reduced, and as a result, more favorable operating characteristics with respect to noise, heat generation and wear can be obtained.

  FIG. 4 shows the refrigerant pressure feeding device 1 in the third operating state. In this operating state, the first input shaft 7 is fixed in a torque-resistant manner, for example, fixed to the housing 17. The electric motor 6 cannot be used to drive the refrigerant pump 2. The transmission gear ratio of the planetary gear mechanism 5 is a constant transmission gear ratio between the second input shaft 8 and the output shaft 6. In the third operating state, when the load on the internal combustion engine is high and the rotational speed is high, the heat generated by the internal combustion engine can be exhausted.

  FIG. 5 is a graph showing the relationship between the maximum output P of the refrigerant pump 2 and the rotational speed n of the internal combustion engine. Here, transition line 29 and transition line 30 are the maximum possible output in the first operating state, transition line 31 is the maximum possible output in the second operating state, and transition line 32 is the maximum possible output in the third operating state. Is the output. The transition line 29 indicates the maximum output when the refrigerant pump 2 is driven only by the electric motor 6 in the first operating state. Therefore, this maximum output does not depend on the rotational speed of the internal combustion engine. The transition line 30 indicates the maximum output P when the refrigerant pump 2 is driven by both the electric motor 6 and the internal combustion engine in the first operating state. The minimum value of the maximum output P coincides with the maximum output of the electric motor 6, and the portion of the maximum output obtained by the internal combustion engine depends on the rotational speed of the internal combustion engine. In the second operating state in which the input shaft 7 and the input shaft 8 are directly connected to each other by the clutch 22, the maximum output is minimum, and in addition, this maximum output depends on the rotational speed of the internal combustion engine. . In this way, if only a small volume flow of refrigerant needs to be pumped by the refrigerant pump 2 in order to sufficiently cool the internal combustion engine and / or supply refrigerant to other elements, The output of the pump 2 and thus the loss output can be greatly reduced. Therefore, more preferable operating characteristics can be obtained. In the third operating state, the first input shaft 7 is fixed to the housing 17, for example. Thereby, it becomes the transition line 32 of the characteristic of the refrigerant | coolant pumping apparatus 1 known from a prior art.

DESCRIPTION OF SYMBOLS 1 Refrigerant pumping apparatus 2 Refrigerant pump 3 Impeller 4 Refrigerant regulator 5 Planetary gear mechanism 6 First drive unit 7 First input shaft 8 Second input shaft 9 Winding transmission device 10 Seat surface 11 Winding means 12 Sun Gear 13 Planetary carrier 14 Planetary gear 15 Outer ring gear 16 Output shaft 17 Housing 18 Bearing 19 Bearing 20 Bearing 21 Sealing means 22 Clutch 23 Adjuster 24 Slider 25 Slider base 26 Synchronization ring 27 Friction ring 28 Rotating shaft 29 Transition line 30 Transition line 31 Transition line 32 Transition line

Claims (10)

A refrigerant pump (2) that can be driven by a first drive unit (6) and a second drive unit via a planetary gear mechanism (5) is provided, and the planetary gear mechanism (5) is connected to the first drive unit. A refrigerant pumping device (1) comprising a first input shaft (7) for (6) and a second input shaft (8) for the second drive unit,
A refrigerant pressure feeding device comprising a clutch (22) for directly connecting the input shafts (7, 8) to each other in at least one operating state. The planetary gear mechanism (5) includes a sun gear (12), an outer ring gear (15), and at least one planetary gear (which transmits power between the sun gear (12) and the outer ring gear (15)). 14) a planet carrier (13) having
The sun gear (12) is connected to the first input shaft (7), the planet carrier (13) is connected to the second input shaft (8), and the refrigerant pump is connected to the outer ring gear (15). The refrigerant pressure feeding device according to claim 1, wherein the refrigerant pressure feeding device is connected to an output shaft (16) connected to the refrigerant. The input shafts (7, 8) are indirectly connected only through the planetary gear mechanism (5) in the first operating state of the plurality of operating states, and in the second operating state. The refrigerant pressure feeding device according to claim 1 or 2, wherein the refrigerant pressure feeding devices are directly connected to each other. In the third operating state, the input shafts (7, 8) are indirectly connected only via the planetary gear mechanism (5), and the first input shaft (7) is connected to the clutch (22). The refrigerant pressure feeding device according to claim 3, wherein the refrigerant pressure feeding device is fixed. The power transmission between the planet carrier (13) and the second drive unit is performed by a winding transmission (9) according to any one of claims 1 to 4. Refrigerant pumping device. The refrigerant pressure feeding device according to any one of claims 1 to 5, wherein the first drive unit (6) is an electric motor and the second drive unit is an internal combustion engine. A method for driving the refrigerant pumping device (1) according to any one of claims 1 to 6,
The refrigerant pumping device (1) includes a refrigerant pump (2), and the refrigerant pump can be driven by a first drive unit (6) and a second drive unit via a planetary gear mechanism (5), In a method wherein the planetary gear mechanism (5) comprises a first input shaft (7) for the first drive unit (6) and a second input shaft (8) for the second drive unit. ,
Method according to claim 1, characterized in that the input shafts (7, 8) are directly connected to each other in at least one operating state via a clutch (22). The input shafts (7, 8) are indirectly connected only via the planetary gear mechanism (5) in the first operating state and directly connected to each other in the second operating state. The method according to claim 7. In the third operating state, the input shafts (7, 8) are indirectly connected only via the planetary gear mechanism (5), and the first input shaft (7) is fixed by the clutch (22). 9. The method of claim 8, wherein: In the first operating state, only one drive unit or both drive units drive,
And / or in the second operating state, only the second drive unit is driven,
10. The method according to claim 9, wherein only the second drive unit drives in the third operating state.

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