Power transmission device

Abstract

This power transmission device comprises a drive unit (10), an input shaft (20), a first output shaft (40), a second output shaft (50), an output shaft switching unit (25), and a current detection unit (73). The first output shaft is rotated by a driving force transmitted from the input shaft, and transmits the driving force to a first output object (49, 150). The second output shaft is disposed in a position different from the first output shaft, is rotated by the driving force transmitted from the input shaft, and transmits the driving force to a second output object (59, 160) different from the first output object. The output shaft switching unit switches between a first output state and a second output state. The current detection unit detects a drive current in the drive unit. The load when the first output shaft rotates is different from the load when the second output shaft rotates. The power transmission device comprises a determination unit (71). When the drive unit is operating in a steady state, the determination unit uses the drive current detected by the current detection unit to determine which of the first output shaft and the second output shaft is rotating.

Description

Power transmission device Cross-reference to related applications

[0001] This application is based on Japanese Patent Application No. 2024-197529 filed on November 12, 2024, the contents of which are incorporated herein by reference.

[0002] The present disclosure relates to a power transmission device capable of transmitting a driving force transmitted to an input shaft to a first output shaft and a second output shaft.

[0003] Conventionally, as a technology related to a power transmission device capable of transmitting a driving force transmitted to an input shaft to a first output shaft and a second output shaft, a technology related to a magnetic gear motor described in Patent Document 1 is known. In the technology described in Patent Document 1, the driving force input to the rotating shaft as the input shaft can be transmitted to the first output shaft and the second output shaft, and it is configured to be switchable between two operating modes. In Patent Document 1, it is possible to switch between a first mode in which the first output shaft and the second output shaft rotate in synchronization and a second mode in which the second output shaft is out of synchronization with the rotation of the first output shaft.

[0004] Japanese Unexamined Patent Application Publication No. 2023-000506

[0005] Here, in a power transmission device such as that of Patent Document 1, when high accuracy is required for the operation control of the first output shaft and the second output shaft, in order to ensure the accuracy of the operation control, a process of performing the operation of either one while the other of the first output shaft and the second output shaft is stopped is assumed. In such a case, it is necessary to appropriately determine the operating states of the first output shaft and the second output shaft (that is, whether the first output shaft and the second output shaft are operating or stopped).

[0006] In particular, depending on the device to which the power transmission device is applied, the input shaft, the first output shaft, and the second output shaft may be housed in different spaces, and it is also assumed that the states of the first output shaft and the second output shaft cannot be directly grasped visually or the like.

[0007] In view of the above points, the present disclosure provides a power transmission device capable of appropriately determining the operating states of a first output shaft and a second output shaft in a power transmission device capable of transmitting a driving force transmitted to an input shaft to the first output shaft and the second output shaft.

[0008] A power transmission device according to a first aspect of this disclosure includes a drive unit, an input shaft, a first output shaft, a second output shaft, an output shaft switching unit, and a current detection unit. The drive unit generates a driving force by power supply. The input shaft rotates due to the input of the driving force from the drive unit. The first output shaft rotates due to the driving force transmitted from the input shaft and transmits the driving force to a first output object. The second output shaft is positioned differently from the first output shaft and rotates due to the driving force transmitted from the input shaft, and also transmits the driving force to a second output object different from the first output object.

[0009] The output shaft switching unit switches between a first output state and a second output state. The first output state restricts the rotation of the second output shaft due to the driving force while allowing the rotation of the first output shaft due to the driving force. The second output state restricts the rotation of the first output shaft due to the driving force while allowing the rotation of the second output shaft due to the driving force. The current detection unit detects the drive current in the drive unit.

[0010] The load when the first output shaft rotates is different from the load when the second output shaft rotates. The power transmission device has a determination unit. The determination unit determines which of the first and second output shafts is rotating when the operation of the drive unit is in a steady state. At this time, the determination unit makes the determination using the drive current detected by the current detection unit, a first criterion indicating the first output state in normal conditions, and a second criterion indicating the second output state in normal conditions.

[0011] With such a power transmission device, the output shaft switching unit can be used to switch between a first output state and a second output state, enabling highly accurate control of the operation of both the first and second output shafts.

[0012] Furthermore, in a power transmission system, the load when the first output shaft rotates is different from the load when the second output shaft rotates. Therefore, the steady-state drive current behaves differently in the first output state, when the first output shaft rotates, and in the second output state, when the second output shaft rotates.

[0013] In other words, the power transmission device can reliably determine which of the first and second output shafts is rotating by utilizing the difference in the behavior of the drive current caused by the load on the first and second output shafts in a steady state. Since the power transmission device makes its determination using the detection results of the current detection unit, it can appropriately determine the operating state of the first output state and the second output state without being affected by the visibility of the first output shaft, etc.

[0014] Furthermore, a power transmission device according to a second aspect of this disclosure includes a drive unit, an input shaft, a first output shaft, a second output shaft, an output shaft switching unit, and a current detection unit. The drive unit generates a driving force by power supply. The input shaft rotates due to the input of the driving force from the drive unit. The first output shaft rotates due to the driving force transmitted from the input shaft and transmits the driving force to a first output object. The second output shaft is positioned differently from the first output shaft and rotates due to the driving force transmitted from the input shaft, and also transmits the driving force to a second output object different from the first output object.

[0015] The output shaft switching unit switches between a first output state and a second output state. The first output state restricts the rotation of the second output shaft due to the driving force while allowing the rotation of the first output shaft due to the driving force. The second output state restricts the rotation of the first output shaft due to the driving force while allowing the rotation of the second output shaft due to the driving force. The current detection unit detects the drive current in the drive unit.

[0016] The load when the first output shaft rotates is different from the load when the second output shaft rotates. The power transmission device includes a determination unit. The determination unit determines which of the first and second output shafts is rotating when the operation of the drive unit is in a transient state. At this time, the determination unit makes the determination using the drive current detected by the current detection unit, a first criterion indicating the first output state under normal conditions, and a second criterion indicating the second output state under normal conditions.

[0017] With such a power transmission device, the output shaft switching unit can be used to switch between a first output state and a second output state, enabling highly accurate control of the operation of both the first and second output shafts.

[0018] Furthermore, in a power transmission device, the load when the first output shaft rotates is different from the load when the second output shaft rotates. Therefore, the drive current exhibits different transient behavior in the first output state, when the first output shaft rotates, and in the second output state, when the second output shaft rotates.

[0019] In other words, the power transmission device can reliably determine which of the first and second output shafts is rotating by utilizing the difference in the behavior of the drive current during transient states, which is caused by the load on the first and second output shafts. Since the power transmission device makes its determination using the detection results of the current detection unit, it can appropriately determine the operating state of the first output state and the second output state without being affected by the visibility of the first output shaft, etc.

[0020] Furthermore, the power transmission device according to the third aspect of this disclosure includes a drive unit, an input shaft, a first output shaft, a second output shaft, an output shaft switching unit, and a rotational speed detection unit. The drive unit generates a driving force by power supply. The input shaft rotates due to the input of the driving force from the drive unit. The first output shaft rotates due to the driving force transmitted from the input shaft and transmits the driving force to a first output object. The second output shaft is positioned differently from the first output shaft and rotates due to the driving force transmitted from the input shaft, and also transmits the driving force to a second output object different from the first output object.

[0021] The output shaft switching unit switches between a first output state and a second output state. The first output state restricts the rotation of the second output shaft due to the driving force while allowing the rotation of the first output shaft due to the driving force. The second output state restricts the rotation of the first output shaft due to the driving force while allowing the rotation of the second output shaft due to the driving force. The rotation speed detection unit detects the rotation speed of the input shaft due to the driving force of the drive unit.

[0022] The load when the first output shaft rotates is different from the load when the second output shaft rotates. The power transmission device includes a determination unit. The determination unit determines which of the first and second output shafts is rotating when the operation of the drive unit is in a transient state. At this time, the determination unit makes a determination using the rotational speed detected by the rotational speed detection unit, a first criterion indicating the first output state under normal conditions, and a second criterion indicating the second output state under normal conditions.

[0023] With such a power transmission device, the output shaft switching unit can be used to switch between a first output state and a second output state, enabling highly accurate control of the operation of both the first and second output shafts.

[0024] Furthermore, in the power transmission device, the load when the first output shaft rotates is different from the load when the second output shaft rotates. For this reason, the rotational speed detected by the rotational speed detection unit exhibits different behavior in transient states between the first output state, when the first output shaft rotates, and the second output state, when the second output shaft rotates.

[0025] In other words, the power transmission device can reliably determine which of the first and second output shafts is rotating by utilizing the difference caused by the load on the first and second output shafts in relation to the behavior of the rotational speed detected by the rotational speed detection unit during transient states. Since the power transmission device makes its determination using the detection results of the rotational speed detection unit, it can appropriately determine the operating state of the first output state and the second output state without being affected by the visibility of the first output shaft, etc.

[0026] The above-mentioned and other purposes, features and advantages of this disclosure will become clearer from the following detailed description with reference to the attached drawings. This is a configuration diagram of an integrated valve to which the power transmission device according to the first embodiment is applied. This is a configuration diagram of a refrigeration cycle including the integrated valve. This is a cross-sectional view of the III-III section in Figure 1. This is a block diagram of the control system of the integrated valve according to the first embodiment. This is an explanatory diagram showing the configuration of the drag generation unit according to the first embodiment. This is a cross-sectional view showing the drag generation unit in the first embodiment. This is an explanatory diagram showing the first output state of the integrated valve according to the first embodiment. This is an explanatory diagram showing the second output state of the integrated valve according to the first embodiment. This is an explanatory diagram showing an example of a determination map according to the first embodiment. This is an explanatory diagram showing an example of changes in rotational speed and drive current when transitioning from a transient state to a steady state in the second embodiment. This is a block diagram of the control system of the integrated valve according to the third embodiment. This is an explanatory diagram showing an example of changes in rotational speed and drive current when transitioning from a transient state to a steady state in the third embodiment. This is a configuration diagram of an integrated pump unit to which the power transmission device according to the fourth embodiment is applied. This is a configuration diagram of a heat transfer medium circuit including the integrated pump unit. This is an explanatory diagram showing the first output state of the integrated pump unit according to the fourth embodiment. This is an explanatory diagram showing the second output state of the integrated pump unit according to the fourth embodiment.

[0027] Several embodiments for carrying out this disclosure are described below with reference to the drawings. In each embodiment, parts corresponding to matters described in a prior embodiment may be denoted by the same reference numerals, and redundant descriptions may be omitted. If only a part of the configuration is described in each embodiment, other parts of the configuration can be applied to other embodiments described in advance. Not only can parts that are explicitly shown to be combinable in each embodiment be combined, but embodiments can also be partially combined even if not explicitly shown, as long as there is no particular impediment to the combination.

[0028] (First Embodiment) An embodiment applying the power transmission device according to the present disclosure will be described with reference to Figures 1 to 9. In the first embodiment, the power transmission device according to the present disclosure is applied to an integrated valve V which integrates a plurality of valve devices in a fluid circuit. As shown in Figure 1, the integrated valve V is configured to transmit the output destination of the driving force output by the drive motor 11 by switching between the first pressure reducing section VA side and the second pressure reducing section VB side using the power transmission device 1.

[0029] As shown in Figure 2, the first pressure reducing section VA and the second pressure reducing section VB in the first embodiment constitute an integrated valve V that has the function of integrating two expansion valves connected in parallel to each other in a refrigeration cycle 100, which is a vapor compression type refrigeration cycle.

[0030] Specifically, the configuration of the refrigeration cycle 100 according to the first embodiment will be described with reference to Figure 2. The refrigeration cycle 100 includes a compressor 110, a condenser 111, a first pressure reduction section VA, a second pressure reduction section VB, a first evaporator 113, and a second evaporator 114.

[0031] In the first embodiment, the compressor 110 is an electric compressor that inhales, compresses, and discharges a refrigerant. The refrigeration cycle 100 is a subcritical cycle in which the high-pressure refrigerant pressure does not exceed the critical pressure of the refrigerant, and a fluorocarbon refrigerant (for example, R134a) is used as the refrigerant circulating in the vapor compression type refrigeration cycle.

[0032] The condenser 111 dissipates the heat from the refrigerant discharged from the compressor 110, causing it to condense. A refrigerant branching section 112 is located on the refrigerant outlet side of the condenser 111. The refrigerant branching section 112 branches the flow of refrigerant flowing out of the condenser 111 into a flow of refrigerant toward the first pressure reduction section VA and a flow of refrigerant toward the second pressure reduction section VB.

[0033] The first pressure reducing section VA constitutes a part of the integrated valve V according to the first embodiment and reduces the pressure of a portion of the refrigerant condensed in the condenser 111. A first evaporator 113 is connected downstream of the refrigerant flow in the first pressure reducing section VA. The first evaporator 113 evaporates the refrigerant by allowing it to absorb external heat, which has been reduced in pressure in the first pressure reducing section VA.

[0034] The second pressure reducing section VB, like the first pressure reducing section VA, constitutes part of the integrated valve V and reduces the pressure of the remaining portion of the refrigerant condensed in the condenser 111. A second evaporator 114 is connected downstream of the refrigerant flow in the second pressure reducing section VB. The second evaporator 114 evaporates the refrigerant by allowing it to absorb external heat, which has been reduced in pressure in the second pressure reducing section VB.

[0035] A refrigerant confluence section 115 is connected to the downstream side of the refrigerant flow in the first evaporator 113 and the downstream side of the refrigerant flow in the second evaporator 114. The refrigerant confluence section 115 combines the refrigerant flow from the first evaporator 113 and the refrigerant flow from the second evaporator 114 and discharges them to the intake side of the compressor 110.

[0036] As shown in Figure 2, the integrated valve V according to the first embodiment is configured by integrating the portions from the inlet side of the refrigerant branching section 112 in the refrigeration cycle 100 to the outlet side of the first pressure reducing section VA and the second pressure reducing section VB. That is, the integrated valve V has the functions of the refrigerant branching section 112, the functions of the first pressure reducing section VA, and the functions of the second pressure reducing section VB.

[0037] Next, the specific configuration of the integrated valve V according to the first embodiment will be described with reference to the drawings. As shown in Figure 1, the integrated valve V has a drive unit 10 that generates driving force and a main body 30 having a refrigerant flow path including a first pressure reducing unit VA and a second pressure reducing unit VB, and includes a power transmission device 1 according to the present disclosure. The power transmission device 1 transmits the rotational driving force generated by the drive unit 10 by switching it to either the first pressure reducing unit VA side or the second pressure reducing unit VB side using magnetic force.

[0038] Here, the integrated valve V is positioned vertically in the refrigeration cycle 100. Vertical positioning means that the axial direction of the valve body in the first pressure reducing section VA and the second pressure reducing section VB is approximately parallel to the direction of gravity, and the drive unit 10 is positioned above the main body 30.

[0039] As shown in Figure 1, the drive unit 10 constitutes the upper part of the integrated valve V and is adjacent to the upper surface of the main body 30. The drive unit 10 includes a drive motor 11 that generates rotational driving force by power supply, an input shaft 20 to which the driving force generated by the drive motor 11 is input, and an output shaft switching unit 25 for switching the output destination of the driving force input from the input shaft 20.

[0040] The drive motor 11 is a motor that can be driven by position feedback control and has a rotor 12, a stator 13, and a shaft 14. For example, a three-phase brushless motor or a stepping motor can be used as the drive motor 11.

[0041] The shaft 14 is rotatably supported by a motor holding plate 15 that forms the upper surface of the integrated valve V. A rotor 12 is attached to the shaft 14 and rotates integrally with the rotor 12. The shaft 14 is the output shaft of the drive motor 11 and also constitutes part of the input shaft of the power transmission device 1.

[0042] The stator 13 is fixed to a motor case or motor holding plate 15 (not shown) and has stator coils. The rotor 12 is cylindrical in shape, and the stator 13 is located inside the rotor 12. Multiple pairs of magnets, each consisting of an N pole and a S pole, are arranged circumferentially on the rotor 12. For example, four N poles and four S poles may be arranged on the circumferential surface of the rotor 12, making the number of poles Pr of the rotor 12 eight. The stator 13 and rotor 12 output a driving force to rotate the shaft 14 by electromagnetic force.

[0043] As shown in Figure 1, the drive unit 10 houses a circuit unit 70. The circuit unit 70 has a circuit board equipped with multiple electronic components for controlling the drive motor 11. Furthermore, the circuit unit 70 can perform control related to the switching operation of the output shaft in the integrated valve V (i.e., control of the output shaft switching unit 25). Details of the circuit unit 70 will be described later with reference to Figure 4.

[0044] On the lower end side of the shaft 14 of the drive motor 11, an input shaft 20 is joined. The input shaft 20 is attached so that its axis coincides with the extension line of the axis of rotation of the shaft 14. Therefore, the input shaft 20 rotates integrally with the rotor 12 and the shaft 14 by the drive of the drive motor 11.

[0045] An input-side magnet 21 is formed at the lower end of the input shaft 20. As described above, the input shaft 20 rotates together with the rotor 12 etc. when the rotational driving force generated by the drive motor 11 is input. Since the input-side magnet 21 is formed integrally with the input shaft 20, it rotates with the input of the rotational driving force generated by the drive motor 11.

[0046] As shown in FIGS. 1 and 3, the input-side magnet 21 is formed in a disk shape at the lower end of the input shaft 20, and on its side surface (that is, the outer peripheral surface of the disk shape), at least one set of a pair of magnets consisting of a N pole 21N and a S pole 21S is arranged along the circumferential direction. In this example, since there is one N pole 21N and one S pole 21S each, the number of poles Pin of the input-side magnet 21 is 2.

[0047] As shown in FIG. 1, the main body part 30 that constitutes the lower part of the integrated valve V has a mechanism housing part 35 that houses various mechanisms for realizing the pressure reducing functions of the first pressure reducing part VA and the second pressure reducing part VB, and a flow path forming part 60 in which a refrigerant flow path through which the refrigerant of the refrigeration cycle 100 flows is formed. The mechanism housing part 35 is arranged in the upper part of the main body part 30, and the flow path forming part 60 constitutes the lower part of the main body part 30. The internal space (that is, the mechanism housing part 35 and the pressure vessel 37) formed in the main body part 30 corresponds to an example of the housing space.

[0048] The pressure vessel 37 is formed in a bottomed cylindrical shape and is arranged below the drive part 10 including the drive motor 11 and the input shaft 20. The pressure vessel 37 partitions the space on the drive part 10 side in the integrated valve V and the power transmission device 1 and the space on the main body part 30 side including the first output shaft 40 etc., and seals the space on the main body part 30 side. In other words, the pressure vessel 37 cooperates with the upper part of the flow path forming part 60 to constitute the outer shell of the mechanism housing part 35.

[0049] Since the space on the main body 30 side includes a space through which the refrigerant circulating in the refrigeration cycle 100 in the integrated valve V flows, the pressure vessel 37 prevents the refrigerant (high-pressure refrigerant) flowing on the main body 30 side from leaking into the space on the drive unit 10 side.

[0050] The pressure vessel 37 is made of, for example, a non-magnetic material or a material having a predetermined magnetic permeability. Specifically, the pressure vessel 37 is made of stainless steel that has been given magnetism by work hardening to transform an austenitic stainless steel such as SUS304, aluminum, or SUS305 into martensite.

[0051] As described above, the mechanism housing section 35 of the integrated valve V houses various components for realizing the pressure reduction function of the first pressure reduction section VA and various components for realizing the pressure reduction function of the second pressure reduction section VB.

[0052] The various components for realizing the pressure reduction function of the first pressure reduction unit VA include a first output shaft 40, a first bearing member 47, a first screw member 48, and a first valve body 49. The various components for realizing the pressure reduction function of the second pressure reduction unit VB include a second output shaft 50, a second bearing member 57, a second screw member 58, and a second valve body 59.

[0053] First, the various components for realizing the pressure reduction function of the first pressure reduction unit VA will be described. The first output shaft 40 of the integrated valve V according to the first embodiment is an output shaft that rotates due to the rotational driving force generated by the drive unit 10 and outputs rotational driving force to the first valve body 49 which constitutes the first pressure reduction unit VA. The first valve body 49 corresponds to an example of the first output target object.

[0054] As shown in Figure 1, the first output shaft 40 is positioned so as to have its rotation axis on the extension of the rotation axes of the shaft 14 and input shaft 20 described above, and has a large diameter portion 41 and a small diameter portion 42. The large diameter portion 41 is formed in a cylindrical shape and constitutes the upper part of the first output shaft 40. Therefore, the large diameter portion 41 is housed in the mechanism housing portion 35 of the main body portion 30.

[0055] Furthermore, the large-diameter portion 41 is formed such that, with respect to its radial dimension, the outer diameter side surface is located at least closer to the outer side surface of the pressure vessel 37. The inner diameter dimension of the large-diameter portion 41 is larger than the outer diameter dimension of the substantially cylindrical recess formed in the central part of the upper surface of the pressure vessel 37.

[0056] An output magnet 45 is positioned in the upper part of the large-diameter section 41. As shown in Figures 1 and 3, the output magnet 45 is formed in a cylindrical shape, similar to the large-diameter section 41, and is composed of multiple pairs of magnets, each consisting of an N pole 45N and an S pole 45S, arranged at approximately equal intervals along the circumference. In this example, there are 20 N poles 45N and 20 S poles 45S, so the number of poles Pf of the output magnet 45 is 40. The output magnet 45 has a different number of poles than the input magnet 21 and can be described as a multi-pole magnet with a larger number of poles than the input magnet 21.

[0057] As described above, the input-side magnet 21 of the input shaft 20 is positioned inside the recess formed on the upper surface of the pressure vessel 37. The output-side magnet 45 is positioned radially outward from the recess of the pressure vessel 37. As shown in Figures 1 and 3, the output-side magnet 45 is positioned opposite the input-side magnet 21 via the wall portion that constitutes the recess of the pressure vessel 37. Therefore, the rotational driving force input to the input shaft 20 can be transmitted to the first output shaft 40 by the magnetic force acting between the input-side magnet 21 and the output-side magnet 45.

[0058] The small-diameter portion 42 of the first output shaft 40 is formed in a cylindrical shape with a smaller diameter than the large-diameter portion 41, and extends downward from the lower part of the large-diameter portion 41. The second output shaft 50, which will be described later, is arranged inside the small-diameter portion 42.

[0059] A first valve body 49 is positioned at the lower end of the small-diameter section 42. The first valve body 49 corresponds to the valve body in the first pressure reducing section VA and is formed in a cylindrical shape with an outer diameter smaller than the inner diameter of the small-diameter section 42. The first valve body 49 is a cylindrical valve body formed with a larger outer diameter than the second valve body 59, which will be described later, and it makes the load on the rotation of the first output shaft 40 in the first output state greater than the load on the rotation of the second output shaft 50 in the second output state.

[0060] Here, a groove is formed at the lower end of the small-diameter portion 42. The groove is formed by recessing the inner surface of the cylindrical small-diameter portion 42 in a groove-like shape, and extends upward from the lower end edge of the small-diameter portion 42.

[0061] Furthermore, a protruding portion is formed on the upper end side of the first valve body 49. The protruding portion is formed by making the outer surface of the cylindrical first valve body 49 protrude radially outward and extends downward from the upper edge of the first valve body 49. In addition, the outer diameter of the protruding portion is formed to be smaller than the inner diameter of the groove. Therefore, the protruding portion of the first valve body 49 can be fitted into the groove of the small diameter portion 42. At this time, a certain distance is provided between the inner surface of the groove and the outer surface of the protruding portion.

[0062] As a result, the cooperation of the groove and the protrusion allows the first valve body 49 to rotate in accordance with the rotational movement of the first output shaft 40, and the rotational driving force transmitted to the first output shaft 40 can be transmitted to the first valve body 49. Furthermore, the cooperation of the groove and the protrusion allows the first output shaft 40 to move relative to the first valve body 49 in the rotational axis direction (i.e., vertical direction).

[0063] As shown in Figure 1, a first bearing member 47 is positioned at the lower part of the mechanism housing 35 formed in the main body 30. The first bearing member 47 is fixed to the lower part of the mechanism housing 35 of the main body 30 and rotatably supports the first output shaft 40. The first bearing member 47 also allows vertical movement of the first output shaft 40 within a predetermined range.

[0064] A first threaded member 48 is positioned below the first bearing member 47. The first threaded member 48 is fixed within the first valve chamber 65, which constitutes the flow path forming portion 60 of the main body 30, and has a threaded hole. A female thread shape is formed inside the threaded hole of the first threaded member 48, and a male thread shape is formed on the outer circumferential surface of the first valve body 49.

[0065] The male thread of the first valve body 49 is screwed into a screw hole formed in the first screw member 48, forming a screw mechanism. As a result, when the first valve body 49 rotates, the first valve body 49 can move in the direction of rotation, making it possible to adjust the opening degree in the first pressure reducing section VA.

[0066] Next, various components for realizing the pressure reduction function of the second pressure reduction unit VB will be described. The second output shaft 50 of the integrated valve V rotates due to the rotational driving force generated by the drive unit 10 and is an output shaft for outputting rotational driving force to the second valve body 59 which constitutes the second pressure reduction unit VB. The second valve body 59 corresponds to an example of the second output target object.

[0067] As shown in Figure 1, the second output shaft 50 is positioned so as to have its axis of rotation on the extension of the axis of rotation of the shaft 14 and input shaft 20 described above, and has a cylindrical portion 51 and a shaft portion 52. The axis of rotation of the second output shaft 50 also coincides with the axis of rotation of the first output shaft 40.

[0068] The cylindrical portion 51 is formed in a cylindrical shape and constitutes the upper part of the second output shaft 50. The cylindrical portion 51 is positioned so as to be radially inward relative to the large diameter portion 41 of the first output shaft 40 and radially outward relative to the recess of the pressure vessel 37. Therefore, the cylindrical portion 51 is housed within the mechanism housing portion 35 of the main body portion 30.

[0069] A magnetic flux modulation unit 55 is located in the upper part of the cylindrical portion 51. The magnetic flux modulation unit 55 is a magnetic modulation unit that modulates the magnetic flux between the input magnet 21 and the output magnet 45, and is formed integrally with the second output shaft 50.

[0070] As shown in Figures 1 and 3, the magnetic flux modulation section 55 is formed in a cylindrical shape, similar to the cylindrical section 51, and has a plurality of magnetic sections 55A and a plurality of non-magnetic sections 55B. The magnetic sections 55A and non-magnetic sections 55B are fan-shaped, and the magnetic sections 55A are arranged in parallel at approximately equal intervals along the circumference. The non-magnetic sections 55B are arranged between the magnetic sections 55A. For example, the magnetic sections 55A can be pole pieces made of a soft magnetic material (e.g., an iron-based metal), and the non-magnetic sections 55B can be made of a non-magnetic material (e.g., stainless steel or resin).

[0071] The number of poles Pp of the magnetic flux modulation unit 55 is the same as the sum of the number of poles Pin of the input magnet 21 and the number of poles Pf of the output magnet 45. In the first embodiment, the number of poles Pin of the input magnet 21 is 2, and the number of poles Pf of the output magnet 45 is 40, so the number of poles Pp of the magnetic flux modulation unit 55 is 42. That is, the magnetic flux modulation unit 55 is composed of 21 magnetic parts 55A and 21 non-magnetic parts 55B.

[0072] As described above, the input-side magnet 21 of the input shaft 20 is positioned inside the recess in the pressure vessel 37. The output-side magnet 45 of the first output shaft 40 is positioned radially outward from the magnetic flux modulation unit 55 of the second output shaft 50. As shown in Figures 1 and 3, the magnetic flux modulation unit 55 is positioned to face the input-side magnet 21 and the output-side magnet 45 via the wall surface constituting the pressure vessel 37. Therefore, the magnetic flux modulation unit 55 can modulate the magnetic flux acting between the input-side magnet 21 and the output-side magnet 45.

[0073] Furthermore, when the rotation of the second output shaft 50 is stopped, the rotational driving force input to the input shaft 20 can be transmitted to the second output shaft 50 by the magnetic force acting between the input magnet 21, the output magnet 45, and the magnetic flux modulation unit 55.

[0074] The shaft portion 52 of the second output shaft 50 is an axial portion that extends downward from the lower part of the cylindrical portion 51 and is formed integrally with the cylindrical portion 51. As described above, the shaft portion 52 is inserted inside the small diameter portion 42 of the cylindrical first output shaft 40. The second valve body 59 is positioned at the lower end of the shaft portion 52.

[0075] The second valve body 59 corresponds to the valve body in the second pressure reducing section VB and constitutes the valve body of a so-called needle valve. The second valve body 59 is formed with a smaller outer diameter than the first valve body 49, which is a cylindrical valve body, thereby reducing the load on the rotation of the second output shaft 50 in the second output state.

[0076] As shown in Figure 1, a through hole 52A is formed at the lower end of the shaft portion 52. The through hole 52A is drilled so as to extend axially upward from the lower end of the shaft portion 52, including the rotation axis of the second output shaft 50.

[0077] Furthermore, a protruding piece 59A is formed on the upper end side of the second valve body 59. The protruding piece 59A protrudes upward from the upper end of the second valve body 59 along the axis of rotation of the second valve body 59. The outer diameter of the protruding piece 59A is smaller than the inner diameter of the insertion hole 52A formed in the shaft portion 52. Therefore, the protruding piece 59A of the second valve body 59 can be inserted into the insertion hole 52A of the shaft portion 52 and engaged with the insertion hole 52A of the shaft portion 52. At this time, a predetermined gap can be provided between the inner surface of the insertion hole 52A and the outer surface of the protruding piece 59A.

[0078] As a result, the through hole 52A and the protruding piece 59A work together to rotate the second valve body 59 in accordance with the rotational movement of the second output shaft 50, thereby transmitting the rotational driving force transmitted to the second output shaft 50 to the second valve body 59. Furthermore, the through hole 52A and the protruding piece 59A work together to move the second output shaft 50 relative to the second valve body 59 in the rotational axis direction (i.e., vertical direction).

[0079] As shown in Figure 1, a second bearing member 57 is positioned above the first bearing member 47 in the lower part of the mechanism housing 35 formed in the main body 30. The second bearing member 57 is fixed to the main body 30 between the first output shaft 40 and the second output shaft 50, and rotatably supports the second output shaft 50. The second bearing member 57 also allows vertical movement of the second output shaft 50 within a predetermined range.

[0080] A second threaded member 58 is positioned below the second bearing member 57, the first bearing member 47, and the first threaded member 48. The second threaded member 58 is fixed within the second valve chamber 67, which is located below the first valve chamber 65, and has a threaded hole. A female thread shape is formed inside the threaded hole of the second threaded member 58, and a male thread shape is formed on the outer circumferential surface of the second valve body 59.

[0081] The male thread of the second valve body 59 is screwed into a threaded hole formed in the second threaded member 58, forming a threaded mechanism. As a result, when the second valve body 59 rotates, the second valve body 59 can move in the direction of rotation, making it possible to adjust the opening degree in the second pressure reducing section VB.

[0082] The configuration of the flow path forming section 60 in the integrated valve V will now be described. As shown in Figure 1, the flow path forming section 60 is located in the lower part of the main body 30 of the integrated valve V. The flow path forming section 60 is the part in which a refrigerant flow path 62 is formed for the inflow and outflow of refrigerant circulating in the refrigeration cycle 100 to the first pressure reducing section VA and the second pressure reducing section VB of the integrated valve V.

[0083] Furthermore, the main body portion 30 according to the first embodiment constitutes the body portion (i.e., part of the housing) of the integrated valve V, and is formed from a cast material (for example, AC4C) using an Al-Si-Mg aluminum alloy.

[0084] The flow path forming section 60 of the main body 30 has an inlet 61, a first outlet 63, and a second outlet 64, and a refrigerant flow path 62 is formed to connect them. The inlet 61 is formed on the left side of the main body 30. As shown in Figure 2, in the integrated valve V according to the first embodiment, the inlet 61 is connected to the outlet side of the condenser 111 of the refrigeration cycle 100.

[0085] Furthermore, a first outlet 63 and a second outlet 64 are formed on the right side of the main body 30. On the right side of the main body 30, the first outlet 63 is formed above the second outlet 64. As shown in Figure 2, the first outlet 63 is connected to the refrigerant inlet side of the first evaporator 113 in the refrigeration cycle 100, and the second outlet 64 is connected to the refrigerant inlet side of the second evaporator 114 in the refrigeration cycle 100.

[0086] As shown in Figure 1, in the main body 30, a first valve chamber 65 and a second valve chamber 67 are formed between the inlet 61 and the first outlet 63 and second outlet 64. The first valve chamber 65 is a valve chamber that houses the first valve body 49 and the like which constitute the first pressure reducing section VA, and is formed below the mechanism housing section 35. The first valve chamber 65 is in communication with the mechanism housing section 35 located above it.

[0087] A first screw member 48 is fixed to the first valve chamber 65. Therefore, the first valve body 49 moves in the direction of the rotation axis inside the first valve chamber 65 by a screw mechanism formed in cooperation with the first screw member 48.

[0088] A first valve seat 66 is formed in the lower part of the first valve chamber 65, which can contact a first valve body 49 that moves up and down. The integrated valve V can adjust the throttling opening in the first pressure reducing section VA by adjusting the relative positional relationship of the first valve body 49 with respect to the first valve seat 66. A refrigerant flow path 62 extending toward the first outlet 63 is connected near the first valve seat 66 in the first valve chamber 65.

[0089] The second valve chamber 67 is a valve chamber that houses the second valve body 59 and other components that constitute the second pressure reducing section VB, and is formed below the first valve chamber 65. The second valve chamber 67 is in communication with the first valve chamber 65, which is located above it.

[0090] A second screw member 58 is fixed to the second valve chamber 67. Therefore, the second valve body 59 moves in the direction of the rotation axis inside the second valve chamber 67 by a screw mechanism formed in cooperation with the second screw member 58.

[0091] A second valve seat 68 is formed in the lower part of the second valve chamber 67, which can contact a second valve body 59 that moves up and down. The integrated valve V can adjust the throttling opening in the second pressure reducing section VB by adjusting the relative positional relationship of the second valve body 59 with respect to the second valve seat 68. A refrigerant flow path 62 extending toward the second outlet 64 is connected near the second valve seat 68 in the second valve chamber 67.

[0092] In the integrated valve V, the refrigerant branching section 112 in the refrigeration cycle 100 is formed by the portion where the first valve chamber 65 and the second valve chamber 67 are in communication.

[0093] In the integrated valve V according to the first embodiment, an output shaft switching unit 25 is provided to switch the output destination of the rotational driving force generated by the drive motor 11 to either the first output shaft 40 or the second output shaft 50. The output shaft switching unit 25 is composed of a switching coil 26 and a switching yoke 27 arranged along the outer surface of the pressure vessel 37, and a switching member 80 arranged inside the mechanism housing 35.

[0094] As shown in Figure 1, etc., the switching member 80 constituting the output shaft switching section 25 is located inside the mechanism housing section 35 and is arranged to be movable along the axial direction of the first output shaft 40, etc. The switching member 80 is formed in a cylindrical shape having a first rotation restricting section 80A and a second rotation restricting section 80B.

[0095] As shown in Figure 3, the inner diameter of the cylindrical switching member 80 is smaller than the maximum outer diameter of the pressure vessel 37, and larger than the outer diameter of the large-diameter portion 41 of the first output shaft 40. Therefore, the switching member 80 can move within the mechanism housing 35, passing between the pressure vessel 37 and the first output shaft 40, along the axial direction of the output shaft.

[0096] A first rotation restricting portion 80A is located at the lower part of the switching member 80. The first rotation restricting portion 80A is an annular portion formed to extend radially inward from the lower end of the cylindrical switching member 80. As shown in Figure 1, the first rotation restricting portion 80A is located below the large diameter portion 41 of the first output shaft 40.

[0097] The upper surface of the first rotation restricting unit 80A moves closer to and further away from the lower surface of the large-diameter portion 41 of the first output shaft 40 as the switching member 80 moves up and down. In other words, by controlling the operation of the output shaft switching unit 25, the upper surface of the first rotation restricting unit 80A can be brought into contact with the lower surface of the large-diameter portion 41 of the first output shaft 40.

[0098] Furthermore, a member-side magnet 81 is positioned on the outer diameter side of the first rotation restricting portion 80A. The member-side magnet 81 is positioned so that one of its poles (for example, the north pole) faces radially outward.

[0099] As shown in Figure 1, a second rotation restricting portion 80B is positioned on the upper part of the switching member 80. The second rotation restricting portion 80B is an annular portion formed to extend radially inward from the upper end of the cylindrical switching member 80. The second rotation restricting portion 80B is located above the upper surface of the large-diameter portion 41 of the first output shaft 40 and the upper surface of the cylindrical portion 51 of the second output shaft 50.

[0100] The lower surface of the second rotation restricting section 80B moves away from and closer to the upper surface of the cylindrical portion 51 of the second output shaft 50 as the switching member 80 moves up and down. In other words, by controlling the energization of the switching coil 26, the lower surface of the second rotation restricting section 80B can be brought into contact with the upper surface of the cylindrical portion 51 of the second output shaft 50.

[0101] Here, the switching coil 26 and switching yoke 27 that constitute the output shaft switching section 25 are arranged to face the member-side magnet 81 of the switching member 80 via the side wall of the pressure vessel 37. The switching coil 26 is a DC coil arranged in a ring shape surrounding the side wall of the pressure vessel 37. The switching coil 26 can switch between flowing current in a predetermined direction and flowing current in the opposite direction.

[0102] The switching yoke 27 is a magnetic yoke configured to connect the upper and lower sides of the annular switching coil 26 via the outer diameter side of the switching coil 26. The switching yoke 27 can also be described as an annular iron member having a groove shape that is open on the radially inward side (i.e., the side facing the side wall of the pressure vessel 37). In this case, the switching coil 26 is arranged inside the groove shape.

[0103] When a direct current is passed through the switching coil 26 configured in this way to generate a magnetic field, magnetic forces of different poles are generated at the upper and lower ends of the switching yoke 27. In the following description, the lower end of the switching yoke 27 will be referred to as the first magnetic force generating section 27A, and the upper end of the switching yoke 27 will be referred to as the second magnetic force generating section 27B.

[0104] When current is passed through the switching coil 26, the magnetic field generated in the switching coil 26 generates magnetic fields in the first magnetic field generating unit 27A and the second magnetic field generating unit 27B, respectively. The polarity of the magnetic fields generated in the first magnetic field generating unit 27A and the second magnetic field generating unit 27B is controlled by the direction of the current flowing through the switching coil 26.

[0105] For example, when a current is passed through the switching coil 26 in a predetermined direction, the magnetic force generated in the first magnetic force generating unit 27A is an S pole, and the magnetic force generated in the second magnetic force generating unit 27B is an N pole. Then, when a current is passed through the switching coil 26 in the opposite direction to the predetermined direction, the magnetic force generated in the first magnetic force generating unit 27A is an N pole, and the magnetic force generated in the second magnetic force generating unit 27B is an S pole.

[0106] Furthermore, since the first magnetic force generating unit 27A and the second magnetic force generating unit 27B are mounted so as to be in contact with the side wall surface of the pressure vessel 37, the magnetic force generated by energizing the switching coil 26 can be applied radially inward through the side wall of the pressure vessel 37.

[0107] As a result, the output shaft switching unit 25 can move the switching member 80 up and down inside the mechanism housing unit 35 by switching the type of magnetic pole in the switching yoke 27 and applying magnetic force between it and the member-side magnet 81 of the switching member 80.

[0108] As shown in Figure 1, the first rotation restricting portion 80A and the second rotation restricting portion 80B of the switching member 80 have a drag force generating portion 85 formed therein. The drag force generating portion 85 of the first rotation restricting portion 80A is formed in the portion of the first rotation restricting portion 80A that faces the lower surface of the large diameter portion 41 of the first output shaft 40.

[0109] The drag generating portion 85 of the second rotation restricting portion 80B is formed in the portion of the second rotation restricting portion 80B that faces the upper surface of the cylindrical portion 51 of the second output shaft 50. The drag generating portions 85 of the first rotation restricting portion 80A and the second rotation restricting portion 80B are formed in an annular shape centered on the center of the cylindrical switching member 80 and the position of the rotation axes of the first output shaft 40 and the second output shaft 50.

[0110] In the first rotation restricting section 80A and the second rotation restricting section 80B, the drag generating section 85 is formed in an annular shape, with a plurality of protrusions 85A and a plurality of recesses 85B arranged alternately along the circumferential direction of the annulus. As shown in Figure 5, the protrusions 85A and recesses 85B in the drag generating section 85 are formed to extend radially from the central position of the annular drag generating section 85.

[0111] Here, the drag force generating portion 85 of the first rotation restricting portion 80A is positioned opposite the lower surface of the large-diameter portion 41 of the first output shaft 40, and is arranged to be able to contact the lower surface of the large-diameter portion 41 as the switching member 80 moves up and down. The lower surface of the large-diameter portion 41 of the first output shaft 40 is an example of an opposing surface. As shown in Figure 1, etc., a drag force generating portion 86 having a plurality of protrusions 86A and recesses 86B is formed on the lower surface of the large-diameter portion 41 of the first output shaft 40.

[0112] The drag generating section 86 on the first output shaft 40 side is formed in an annular shape, similar to the drag generating section 85 of the first rotation restricting section 80A. In the drag generating section 86 on the first output shaft 40 side, a plurality of protrusions 86A and recesses 86B extend radially from the center of the annulus, and the protrusions 86A and recesses 86B are arranged alternately in the circumferential direction.

[0113] As a result, when the first rotation restricting part 80A is brought into contact with the lower surface of the large-diameter portion 41 of the first output shaft 40, the convex portion 85A and the concave portion 86B, and the concave portion 85B and the convex portion 86A can be brought into contact in an interlocked state, as shown in Figure 6. Here, the switching member 80 is movable in the axial direction of the output shaft, but is positioned so as not to rotate around the axis of the output shaft. For this reason, by interlocking the resistance force generating portion 85 of the first rotation restricting part 80A with the resistance force generating portion 86 on the first output shaft 40 side, a resistance force against the rotational driving force of the first output shaft 40 can be generated, thereby inhibiting and stopping the rotation of the first output shaft 40.

[0114] The drag force generating portion 85 of the second rotation restricting portion 80B is positioned opposite the upper surface of the cylindrical portion 51 of the second output shaft 50, and is arranged to be able to contact the upper surface of the cylindrical portion 51 as the switching member 80 moves up and down. The upper surface of the cylindrical portion 51 of the second output shaft 50 is an example of an opposing surface. As shown in Figure 1, etc., a drag force generating portion 87 having a plurality of protrusions 87A and recesses 87B is formed on the upper surface of the cylindrical portion 51 of the second output shaft 50.

[0115] The drag generating section 87 on the second output shaft 50 side is formed in an annular shape, similar to the drag generating section 85 of the second rotation restricting section 80B. In the drag generating section 87 on the second output shaft 50 side, multiple protrusions 87A and recesses 87B extend radially from the center of the annulus, and the protrusions 87A and recesses 87B are arranged alternately in the circumferential direction.

[0116] As a result, when the second rotation restricting part 80B is brought into contact with the upper surface of the cylindrical part 51 of the second output shaft 50, the convex part 85A and the concave part 87B, and the concave part 85B and the convex part 87A can be made to contact in an interlocked state, as shown in Figure 6. As described above, the switching member 80 is positioned so as not to rotate around the axis of the output shaft. For this reason, by interlocking the resistance force generating part 85 of the second rotation restricting part 80B with the resistance force generating part 87 on the second output shaft 50 side, a resistance force against the rotational driving force of the second output shaft 50 can be generated, thereby inhibiting and stopping the rotation of the second output shaft 50.

[0117] As described above, the drive unit 10 of the integrated valve V houses a circuit unit 70. The circuit unit 70 has a circuit board equipped with multiple electronic components for controlling the drive motor 11. Furthermore, the circuit unit 70 performs control related to the switching operation of the output shaft in the integrated valve V (i.e., control of the output shaft switching unit 25).

[0118] As shown in Figure 4, the circuit unit 70 is electrically connected to a drive motor 11, which is composed of a three-phase motor, and a battery B. The battery B supplies power to various electrical devices in the vehicle, and for example, a rechargeable secondary battery (a lithium-ion battery in this embodiment) is used. The circuit unit 70 receives input power from the battery B and outputs a drive current to drive the drive motor 11.

[0119] The circuit unit 70 has electronic components such as an ECU for controlling the operation of the integrated valve V, and acts as a control unit for the operation of the first pressure reducing unit VA and the second pressure reducing unit VB. The circuit unit 70 also has a determination unit 71, a three-phase inverter circuit 72, and a drive current sensor 73.

[0120] The determination unit 71 constitutes part of the control unit and determines whether the integrated valve V is in the first output state or the second output state during operation. In other words, the determination unit 71 determines whether the first output shaft 40 is rotating or stopped, and whether the second output shaft 50 is rotating or stopped. Specifically, the determination unit 71 determines whether it is in the first output state or the second output state by referring to a determination map stored in the ROM of the circuit unit 70. Details of the determination map will be explained later with reference to the drawings.

[0121] Furthermore, the drive current sensor 73 is a sensor for detecting the drive current supplied to the stator coils of each phase in the stator 13 of the three-phase motor. The drive current sensor 73 is an example of a current detection unit. The three-phase inverter circuit 72 is a power conversion circuit that converts DC power supplied from the battery B into AC power, and is composed of a combination of multiple MOSFETs (Metal-Oxide-Semiconductor Field-Effect Transistors). The three-phase inverter circuit 72 is electrically connected to the battery B and the three-phase motor, and converts the DC power from the battery B into three-phase AC power, which is then supplied to the stator coils of each phase of the three-phase motor.

[0122] In the integrated valve V according to the first embodiment, the power transmission device 1 switches between a first output state in which the amount of pressure reduction of the first pressure reduction section VA can be adjusted via the first output shaft 40, and a second output state in which the amount of pressure reduction of the second pressure reduction section VB can be adjusted via the second output shaft 50, thereby adjusting the amount of pressure reduction.

[0123] The switching operation of the integrated valve V to the first output state and the second output state, and the adjustment operation of the pressure reduction amount will be explained below with reference to the drawings. In the integrated valve V and power transmission device 1, when a driving force is generated by the start of operation of the drive motor 11, the driving force is transmitted from the input shaft 20 to the first output shaft 40 and the second output shaft 50 through the cooperation of the input side magnet 21, the output side magnet 45, and the magnetic flux modulation unit 55.

[0124] Here, in order to achieve the first output state, it is necessary to inhibit the rotation of the second output shaft 50. Specifically, in the output shaft switching unit 25, the switching member 80 is moved by the magnetic force generated due to the energization of the switching coil 26, thereby stopping the rotation of the second output shaft 50.

[0125] More specifically, by applying a DC current in a predetermined direction to the switching coil 26, the first magnetic force generating section 27A of the switching yoke 27 generates a magnetic force with a polarity different from that of the member-side magnet 81 located on the outer surface of the switching member 80. As a result, a magnetic force acts in an attractive manner between the first magnetic force generating section 27A of the switching coil 26 and the member-side magnet 81 of the switching member 80.

[0126] As a result, as shown in Figure 7, the switching member 80 moves downward along the axial direction due to the action of magnetism, bringing the second rotation restricting part 80B into contact with the upper surface of the cylindrical part 51 of the second output shaft 50. At this time, the drag force generating part 85 of the second rotation restricting part 80B and the drag force generating part 87 on the second output shaft 50 side engage, generating a drag force that inhibits the rotation of the second output shaft 50, thereby stopping the rotation of the second output shaft 50.

[0127] Furthermore, when the second rotation restricting unit 80B comes into contact with the upper surface of the cylindrical portion 51 of the second output shaft 50, the power supply to the switching coil 26 can be stopped. When the power supply to the switching coil 26 is stopped, the electromagnetic force from the switching yoke 27 stops, but the magnetic force of the member-side magnet 81 of the switching member 80 acts as an attractive force on the first magnetic force generating unit 27A of the switching yoke 27. Therefore, even when the power supply to the switching coil 26 is stopped, the second rotation restricting unit 80B can maintain the state in which the rotation of the second output shaft 50 is stopped.

[0128] Then, by moving the switching member 80 downward along the axial direction, the first rotation restricting unit 80A is separated from the lower surface of the large-diameter portion 41 on the first output shaft 40. As a result, the first output shaft 40 becomes rotatable by the driving force transmitted from the input shaft 20 without being obstructed by the switching member 80.

[0129] In other words, the integrated valve V and the power transmission device 1 can move the switching member 80 by supplying a DC current in a predetermined direction to the switching coil 26, thereby inhibiting the rotation of the second output shaft 50 while simultaneously allowing the rotation of the first output shaft 40, thereby achieving the first output state.

[0130] In the first output state, the first output shaft 40 receives the driving force generated by the drive motor 11 and becomes capable of outputting to the first valve body 49, which is the first output target. When the drive motor 11 is driven in the first output state, the rotational driving force generated by the drive motor 11 is transmitted to the first output shaft 40 and the second output shaft 50 through magnetic interaction between the input side magnet 21, the magnetic flux modulation unit 55, and the output shaft switching unit 25.

[0131] At this time, the second output shaft 50 remains stationary due to the output shaft switching unit 25 and the switching member 80, etc., while the first output shaft 40 rotates at a predetermined reduction ratio relative to the rotation of the drive motor 11. In the first embodiment, the reduction ratio is 20, given the configuration of the input side magnet 21, the magnetic flux modulation unit 55, and the output side magnet 45.

[0132] Thus, according to the integrated valve V of the first embodiment, the first output shaft 40 and the first valve body 49 can be moved by operating the drive motor 11 in the first output state. That is, by controlling the rotation direction of the drive motor 11 in the first output state, the first valve body 49 can be moved closer to or further away from the first valve seat 66, thereby enabling adjustment of the throttle opening of the first pressure reducing section VA.

[0133] Furthermore, with the integrated valve V and power transmission device 1, when achieving the first output state, the switching member 80 inside the mechanism housing 35 is moved by magnetic force from the switching coil 26 and switching yoke 27 outside the mechanism housing 35. Therefore, switching to the first output state can be achieved without damaging the internal environment of the mechanism housing 35 (i.e., the high-pressure environment).

[0134] Furthermore, according to the integrated valve V and power transmission device 1, the switching member 80 moves along the axial direction of the first output shaft 40, etc., and applies an axial load to the second output shaft 50, thereby hindering the rotation of the second output shaft 50. The first output shaft 40 and the second output shaft 50 are arranged on the same central axis, one on the inside and the other on the outside. Therefore, when an axial load is applied to the second output shaft 50, the effect on the rotational movement of the first output shaft 40 can be suppressed.

[0135] Furthermore, in the integrated valve V and power transmission device 1, a drag force generating unit 85 is positioned on the second rotation restricting unit 80B of the switching member 80, and a drag force generating unit 87 is positioned on the upper surface of the cylindrical portion 51 of the second output shaft 50. When achieving the first output state, the drag force generating unit 85 on the switching member 80 side contacts the drag force generating unit 87 on the second output shaft 50 side, generating a drag force (frictional force) to inhibit the rotation of the second output shaft 50.

[0136] The drag generating section 85 and the drag generating section 87 each have a plurality of recesses and protrusions that extend radially from the center of rotation. Therefore, when the drag generating section 85 and the drag generating section 87 are brought into contact, the protrusions 85A and recesses 87B, and the recesses 85B and protrusions 87A can be made to contact in an interlocked state. This increases the drag force that inhibits the rotation of the second output shaft 50, and the integrated valve V and the power transmission device 1 can reliably achieve the first output state.

[0137] Next, the second output state in the integrated valve V and the power transmission device 1 will be explained with reference to Figure 8. The second output state is a state in which the drive motor 11 and the output shaft switching unit 25 control the operation of the drive motor 11 and the output shaft switching unit 25, thereby allowing the output of driving force from the second output shaft 50 while simultaneously limiting the output of driving force from the first output shaft 40.

[0138] Here, in order to achieve the second output state, it is necessary to inhibit the rotation of the first output shaft 40. Specifically, the switching member 80 is moved by the magnetic force generated by energizing the switching coil 26, thereby stopping the rotation of the first output shaft 40.

[0139] In more detail, by applying a DC current in a predetermined direction to the switching coil 26, the second magnetic force generating section 27B of the switching yoke 27 generates a magnetic force with a polarity different from that of the member-side magnet 81 located on the outer surface of the switching member 80. In other words, a DC current in the opposite direction to that in the first output state flows through the switching coil 26. As a result, a magnetic force acts in an attractive manner between the second magnetic force generating section 27B of the switching coil 26 and the member-side magnet 81 of the switching member 80.

[0140] As a result, as shown in Figure 8, the switching member 80 moves upward along the axial direction due to the action of magnetism, bringing the first rotation restricting part 80A into contact with the lower surface of the large diameter portion 41 of the first output shaft 40. At this time, the resistance generating part 85 of the first rotation restricting part 80A and the resistance generating part 86 on the first output shaft 40 side engage, generating a resistance force that inhibits the rotation of the first output shaft 40, thereby stopping the rotation of the first output shaft 40.

[0141] Furthermore, when the first rotation restricting unit 80A and the lower surface of the large-diameter portion 41 of the first output shaft 40 come into contact, the power supply to the switching coil 26 can be stopped. When the power supply to the switching coil 26 is stopped, the electromagnetic force from the switching yoke 27 stops, but the magnetic force of the member-side magnet 81 of the switching member 80 acts as an attractive force on the second magnetic force generating unit 27B of the switching yoke 27. Therefore, even when the power supply to the switching coil 26 is stopped, the rotation of the first output shaft 40 can be kept stopped by the first rotation restricting unit 80A.

[0142] Then, by moving the switching member 80 upward along the axial direction, the second rotation restricting unit 80B moves away from the upper surface of the cylindrical portion 51 on the second output shaft 50. As a result, the second output shaft 50 becomes rotatable by the driving force transmitted from the input shaft 20 without being obstructed by the switching member 80.

[0143] In other words, the integrated valve V and power transmission device 1 move the switching member 80 by supplying a DC current to the switching coil 26 in the opposite direction to that in the first output state, thereby inhibiting the rotation of the first output shaft 40 while simultaneously allowing the rotation of the second output shaft 50. In other words, the integrated valve V and power transmission device 1 can achieve the second output state by controlling the DC current supplied to the switching coil 26.

[0144] Even in the second output state, when the drive motor 11 is driven, the rotational driving force generated by the drive motor 11 is transmitted to the first output shaft 40 and the second output shaft 50 by magnetic interaction between the input side magnet 21, the magnetic flux modulation unit 55, and the output shaft switching unit 25. In the second output state, the first output shaft 40 receives the driving force generated by the drive motor 11, but its rotation is hindered by resistance caused by the output shaft switching unit 25, etc.

[0145] Therefore, in the second output state, the rotation caused by the driving force transmitted to the second output shaft 50 is not hindered by resistance caused by the output shaft switching unit 25 or the like. Consequently, in the second output state, the second output shaft 50 receives the driving force generated by the drive motor 11 and becomes capable of outputting to the second valve body 59, which is the output destination.

[0146] Then, when the drive motor 11 is driven in the second output state shown in Figure 8, the rotational driving force generated by the drive motor 11 is transmitted to the first output shaft 40 and the second output shaft 50 by magnetic interaction between the input-side magnet 21, the magnetic flux modulation unit 55, and the output shaft switching unit 25. At this time, the first output shaft 40 remains stationary due to the magnetic force of the output shaft switching unit 25, but the second output shaft 50 rotates at a predetermined reduction ratio relative to the rotation of the drive motor 11. In this embodiment, the reduction ratio is 21, given the configuration of the input-side magnet 21, the magnetic flux modulation unit 55, and the output-side magnet 45.

[0147] Thus, with the integrated valve V, the second output shaft 50 and the second valve body 59 can be moved by operating the drive motor 11 in the second output state. That is, by controlling the rotation direction of the drive motor 11 in the second output state, the second valve body 59 can be moved closer to or further away from the second valve seat 68, thereby enabling adjustment of the throttling opening of the second pressure reducing section VB.

[0148] Furthermore, with the integrated valve V and power transmission device 1, when achieving the second output state, the switching member 80 inside the mechanism housing 35 is moved by magnetic force from the switching coil 26 and switching yoke 27 outside the mechanism housing 35. Therefore, switching to the second output state can be achieved without damaging the internal environment (i.e., the high-pressure environment) of the mechanism housing 35.

[0149] Furthermore, according to the integrated valve V and power transmission device 1, the switching member 80 moves along the axial direction of the first output shaft 40, applying an axial load to the first output shaft 40 and inhibiting its rotation. The first output shaft 40 and the second output shaft 50 are arranged on the same central axis, one on the inside and the other on the outside. Therefore, when an axial load is applied to the first output shaft 40, the effect on the rotational movement of the second output shaft 50 can be suppressed.

[0150] Furthermore, in the integrated valve V and power transmission device 1, a drag force generating unit 85 is positioned on the first rotation restricting unit 80A of the switching member 80, and a drag force generating unit 86 is positioned on the lower surface of the large diameter portion 41 of the first output shaft 40. When realizing the second output state, the drag force generating unit 85 on the switching member 80 side contacts the drag force generating unit 86 on the first output shaft 40 side, generating a drag force (frictional force) to inhibit the rotation of the first output shaft 40.

[0151] The drag generating section 85 and the drag generating section 86 each have a plurality of recesses and protrusions that extend radially from the center of rotation. Therefore, when the drag generating section 85 and the drag generating section 86 are brought into contact, the protrusions 85A and recesses 86B, and the recesses 85B and protrusions 86A can be made to interlock. This increases the drag force that inhibits the rotation of the first output shaft 40, and the integrated valve V and the power transmission device 1 can reliably achieve the second output state.

[0152] As shown in Figures 7 and 8, the integrated valve V and power transmission device 1 can output the driving force generated by a single drive motor 11 by switching between a first output state outputting to the first output shaft 40 and a second output state outputting to the second output shaft 50. As a result, the integrated valve V and power transmission device 1 can achieve the operation equivalent to two valve devices, the first pressure reducing section VA and the second pressure reducing section VB, with just one drive motor 11 as the drive source.

[0153] As a result, the integrated valve V and power transmission device 1 make it possible to realize a valve device in a fluid circuit that requires multiple temperature states (for example, the refrigerant temperatures of the first evaporator 113 and the second evaporator 114), such as the refrigeration cycle 100 shown in Figure 2, with a single drive source. Furthermore, by realizing the drive source of multiple valve devices as an integrated valve V, the occupied space can be reduced compared to when each valve device is provided individually, thus enabling miniaturization of the fluid circuit in terms of space occupied.

[0154] According to the integrated valve V and power transmission device 1, in both the first output state and the second output state, rotational driving force is transmitted via a magnetic gear composed of an input-side magnet 21, a magnetic flux modulation unit 55, and an output-side magnet 45. By using the magnetic gear, the rotational driving force generated by the drive motor 11 is reduced at a reduction ratio determined for each output state and transmitted to the output shaft side. As a result, the integrated valve V and power transmission device 1 can output the rotational driving force generated by the drive motor 11 to the first valve body 49 or the second valve body 59 while reducing it at a reduction ratio determined for each and increasing the torque.

[0155] In the first output state shown in Figure 7 and the second output state shown in Figure 8, the rotational driving force generated by the drive motor 11 is transmitted to both the first output shaft 40 and the second output shaft 50. In other words, regardless of whether rotation is permitted or restricted on the first output shaft 40 and the second output shaft 50, the rotational driving force generated by the drive motor 11 acts on both output shafts.

[0156] In other words, since the driving force is continuously transmitted to the output shaft on the side whose rotation is restricted, it is possible to suppress positional displacement at the timing when rotation of the output shaft is permitted, and thus improve the accuracy of the opening degree control related to the first pressure reduction section VA and the second pressure reduction section VB.

[0157] Furthermore, in this state, the first output state and the second output state can be switched by changing the direction of the DC current flowing through the switching coil 26. Therefore, with the integrated valve V and power transmission device 1, the opening degree adjustment of the first pressure reducing section VA and the opening degree adjustment of the second pressure reducing section VB can be switched quickly, thereby improving the responsiveness of the fluid circuit operation switching.

[0158] As shown in Figure 1, the input shaft 20 constituting the integrated valve V and power transmission device 1 is located in the drive unit 10, and the first output shaft 40 and the second output shaft 50 are located in the mechanism housing 35 of the main body 30. The mechanism housing 35 of the main body 30 is separated from the drive unit 10 via the pressure vessel 37, and the mechanism housing 35 is in communication with the space constituting the flow path forming section 60 of the main body 30.

[0159] In other words, in the integrated valve V and power transmission device 1, the first output shaft 40 and the second output shaft 50 are arranged in the space through which the high-pressure refrigerant flowing in the refrigeration cycle 100 passes, and are separated from the drive unit 10 side by a pressure vessel 37. Therefore, a refrigerant sealing structure using the pressure vessel 37 can be realized, and the influence of the refrigerant on the operation of the drive unit 10 can be suppressed.

[0160] In the integrated valve V and power transmission device 1 configured in this way, in order to control the operation of the first valve body 49 and the second valve body 59 with high precision, it is necessary to appropriately determine the operating state of the first output shaft 40 and the second output shaft 50. In particular, in the integrated valve V, since the first output shaft 40 and the second output shaft 50 are housed in a mechanism housing section 35 which is configured inside the pressure vessel 37, the state of the first output shaft 40 and the second output shaft 50 cannot be directly grasped by sight or other means.

[0161] In the integrated valve V, the load (torque) when the first output shaft 40 rotates in the first output state is set to be greater than the load (torque) when the second output shaft 50 rotates in the second output state. Part of the difference in load between the first output shaft 40 and the second output shaft 50 is due to the difference in the output objects to which the rotational driving force is transmitted, and is influenced by the physical properties of the first valve body 49 and the second valve body 59 (i.e., the difference in outer diameter dimensions).

[0162] Furthermore, the large-diameter portion 41 of the first output shaft 40 has a larger outer diameter than the cylindrical portion 51 of the second output shaft 50, and the small-diameter portion 42 of the first output shaft 40 has a larger outer diameter than the shaft portion 52 of the second output shaft 50. Therefore, the difference in load between the first output shaft 40 and the second output shaft 50 includes the difference in physical properties, including the outer diameter dimensions of the first output shaft 40 and the second output shaft 50.

[0163] Both the first output shaft 40 and the second output shaft 50 rotate due to the rotational driving force generated by the drive motor 11. In a steady state, where the output of the drive motor 11 remains constant over time, the difference in load between the first output shaft 40 and the second output shaft 50 manifests as a difference in the drive current of the drive motor 11.

[0164] In the first embodiment, in a steady state, the difference in drive current that appears due to the load when the first output shaft 40 and the second output shaft 50 rotate is used to determine whether the first output shaft 40 or the second output shaft 50 is rotating.

[0165] When determining the operating state of the first output shaft 40 and the second output shaft 50, a determination map stored in the ROM of the circuit unit 70 is used. The determination map according to the first embodiment is configured to associate the relationship between the drive current and torque in the drive motor 11 in a steady state.

[0166] As described above, in the first output state, as shown in Figure 7, the rotation of the second output shaft 50 is restricted, while the rotation of the first output shaft 40 is permitted. Therefore, in the first output state, the rotational load (torque) of the first output shaft 40, including the influence of the first valve body 49, is expressed as the first reference torque Toa.

[0167] The first reference torque Toa refers to the rotational load when the first output shaft 40 is operating smoothly in the first output state without locking, and can be considered the rotational load in the first output state under normal conditions.

[0168] In the integrated valve V and power transmission device 1, the load (torque) applied to the drive motor 11 and the magnitude of the drive current applied to the drive motor 11 are in a corresponding relationship according to the characteristics of the drive motor 11. As shown in Figure 9, in the integrated valve V and power transmission device 1, the first reference torque Toa for the first output state in which the first output shaft 40 performs rotational operation corresponds to the first reference drive current KCa.

[0169] In the integrated valve V and power transmission device 1, when the drive motor 11 generates rotational driving force, if the drive current detected by the drive current sensor 73 is the first reference drive current KCa, it can be determined that the second output shaft 50 is stopped and the first output shaft 40 is rotating. In other words, if the drive current in the steady state is the first reference drive current KCa, it can be determined that the first output state is in operation without visually inspecting the state of the first output shaft 40 and the second output shaft 50.

[0170] As shown in Figure 9, in the determination map according to the first embodiment, a certain range centered on the first reference drive current KCa is defined as the first reference current range Ra. The first reference current range Ra is determined considering the variation in torque of the first output shaft 40 in a steady state, and is provided in order to accurately determine the first output state regardless of the variation in torque.

[0171] On the other hand, in the second output state, as shown in Figure 8, the rotation of the first output shaft 40 is restricted, while the rotation of the second output shaft 50 is permitted. Therefore, in the second output state, the second reference torque Tob is shown as the rotational load (torque) of the second output shaft 50, including the influence of the second valve body 59, etc. As described above, the torque associated with the rotation of the second output shaft 50 is also set to be small compared to the rotation of the first output shaft 40, so the second reference torque Tob is a smaller value than the first reference torque Toa.

[0172] The second reference torque Tob refers to the rotational load when the second output shaft 50 is operating smoothly in the second output state without locking, and can be considered the rotational load in the second output state under normal conditions.

[0173] In the integrated valve V and power transmission device 1, the load (torque) applied to the drive motor 11 and the magnitude of the drive current applied to the drive motor 11 are in a corresponding relationship according to the characteristics of the drive motor 11. As shown in Figure 9, in the integrated valve V and power transmission device 1, the second reference torque Tob for the second output state in which the second output shaft 50 rotates corresponds to the second reference drive current KCb. The second reference drive current KCb is smaller than the first reference drive current KCa.

[0174] In the integrated valve V and power transmission device 1, when the drive motor 11 generates rotational driving force, if the drive current detected by the drive current sensor 73 is the second reference drive current KCb, it can be determined that the first output shaft 40 is stopped and the second output shaft 50 is rotating. In other words, if the drive current in the steady state is the second reference drive current KCb, it can be determined that the second output state is in operation without visually inspecting the state of the first output shaft 40 and the second output shaft 50.

[0175] As shown in Figure 9, in the determination map according to the first embodiment, a certain range centered on the second reference drive current KCb is defined as the second reference current range Rb. The second reference current range Rb is determined considering the variation in torque of the second output shaft 50 in a steady state, and is provided in order to accurately determine the second output state regardless of the torque variation.

[0176] In this way, by using the detected value of the drive current sensor 73 in a steady state and the determination map shown in Figure 9, the integrated valve V and the power transmission device 1 can determine whether the first output shaft 40 is rotating or the second output shaft 50 is rotating. This allows for an appropriate determination of whether the system is in the first output state or the second output state, and enables the maintenance of high accuracy in the operation control of the first output shaft 40 and the second output shaft 50.

[0177] As described above, according to the integrated valve V and power transmission device 1 of the first embodiment, the output shaft switching unit 25 can switch between the first output state shown in Figure 7 and the second output state shown in Figure 8. As a result, the integrated valve V and power transmission device 1 can suppress the influence of the operation of one of the first output shaft 40 and the second output shaft 50 on the other, and can achieve highly accurate operation control of the first output shaft 40 and the second output shaft 50.

[0178] Furthermore, in the integrated valve V and power transmission device 1, the load (torque) when the first output shaft 40 rotates is different from the load (torque) when the second output shaft 50 rotates. For this reason, the steady-state drive current behaves differently in the first output state when the first output shaft 40 rotates and in the second output state when the second output shaft 50 rotates.

[0179] In other words, the integrated valve V and power transmission device 1 can reliably determine which of the first output shaft 40 and the second output shaft 50 is rotating by utilizing the difference in the behavior of the drive current caused by the load on the first output shaft 40 and the second output shaft 50 in a steady state. Since the integrated valve V and power transmission device 1 make their determination using the detection results of the drive current sensor 73, they can appropriately determine the operating state of the first output state and the second output state without being affected by the visibility of the first output shaft 40, etc.

[0180] As shown in Figure 1, the large-diameter portion 41 of the first output shaft 40 has a larger outer diameter than the cylindrical portion 51 of the second output shaft 50, and the small-diameter portion 42 of the first output shaft 40 has a larger outer diameter than the shaft portion 52 of the second output shaft 50. Therefore, the difference in load between the first output shaft 40 and the second output shaft 50 includes a difference derived from the physical properties of the first output shaft 40 and the second output shaft 50, including their outer diameters.

[0181] Furthermore, a cylindrical first valve body 49 is used as the first output object in the first output shaft 40, and a needle valve second valve body 59 is used as the second output object in the second output shaft 50. Therefore, the difference in load between the first output shaft 40 and the second output shaft 50 includes differences arising from the physical properties of the first valve body 49 and the second valve body 59, including their external shapes.

[0182] Thus, in the integrated valve V and power transmission device 1, the physical properties of the first output shaft 40 and the first valve body 49, and the second output shaft 50 and the second valve body 59, clearly create a difference in load on the first output shaft 40 and the second output shaft 50. As a result, the integrated valve V and power transmission device 1 can generate a clear difference in the drive current in a steady state, and maintain a high level of accuracy when determining the first output state and the second output state.

[0183] Furthermore, since the circuit section 70 is used to control the operation of the drive motor 11, it is a configuration that is generally installed in any device having a drive motor 11. Therefore, with the integrated valve V and power transmission device 1, there is no need to add any new configurations, and the first output state and the second output state can be determined by applying the determination method.

[0184] In the above-described embodiment, the load when the first output shaft 40 rotates was set to be greater than the load when the second output shaft 50 rotates, thereby creating a difference in load between the first output shaft 40 and the second output shaft 50. However, the embodiment is not limited to this configuration. It is sufficient to create a difference in load between the first output shaft 40 and the second output shaft 50. For example, the load when the first output shaft 40 rotates may be set to be less than the load when the second output shaft 50 rotates.

[0185] Alternatively, the difference in load between the first output shaft 40 and the second output shaft 50 may be provided by the difference in frictional force generated between the first output shaft 40 and the first bearing member 47, and between the second output shaft 50 and the second bearing member 57. In the case of the integrated valve V, the difference in load between the first output shaft 40 and the second output shaft 50 may be realized using the frictional force generated between the first valve body 49 and the first screw member 48, and between the second valve body 59 and the second screw member 58.

[0186] In the embodiment described above, the difference in load on the first output shaft 40 and the second output shaft 50 was achieved by employing different types of valve bodies, with the first valve body 49 being a cylindrical valve body and the second valve body 59 being a needle valve. However, the embodiment is not limited to this. For example, even when employing the same type of valve body, the difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by making the external dimensions of the first valve body 49 and the second valve body 59 different. Alternatively, the difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by making the constituent materials (e.g., density, etc.) of the first valve body 49 and the second valve body 59 different.

[0187] Furthermore, if a difference in load can be achieved between the first output shaft 40 and the second output shaft 50, various configurations can be adopted. For example, a difference in load can be achieved between the first output shaft 40 and the second output shaft 50 by varying the amount of pressure applied to the first valve body 49 and the first valve seat 66, and between the second valve body 59 and the second valve seat 68. Alternatively, a difference in load can be achieved between the first output shaft 40 and the second output shaft 50 by varying the differential pressure before and after the first pressure reduction section VA and the differential pressure before and after the second pressure reduction section VB.

[0188] Furthermore, in the integrated valve V of the first embodiment, the fluid controlled by the first pressure reducing section VA and the second pressure reducing section VB was the refrigerant circulating in the refrigeration cycle 100, but the invention is not limited to this embodiment.

[0189] In other words, it is also possible to apply this to an integrated valve that combines multiple valve devices arranged in two different fluid circuits: one controlled by a first valve body 49 operating on a first output shaft 40, and the other by a second valve body 59 operating on a second output shaft 50. In this case, the difference arising from the physical properties (e.g., viscosity) of the fluid controlled by the first valve body 49 operating on the first output shaft 40 and the fluid controlled by the second valve body 59 operating on the second output shaft 50 may be included in the difference in load on the first output shaft 40 and the second output shaft 50.

[0190] (Second Embodiment) Next, a second embodiment, which differs from the embodiment described above, will be described with reference to Figure 10. In the first embodiment, the determination was made using the value of the drive current detected by the drive current sensor 73 in a steady state. In the second embodiment, a determination method will be described for controlling the acceleration of the drive motor 11 so that it exhibits the same behavior during the transient period until it transitions to either steady state. Specifically, the determination method according to the second embodiment can be applied when both the first output shaft 40 and the second output shaft 50 are stopped and the system transitions to a steady state via a transient state.

[0191] A transient state is a non-steady state that occurs when transitioning from one steady state to another, and is different from both states in terms of the time-dependent change in state. In the case of integrated valve V, when transitioning from the second output state to the first output state, a transient state occurs in order to move towards the steady state related to the first output state, and when transitioning from the first output state to the second output state, a transient state occurs in order to move towards the steady state related to the second output state.

[0192] Furthermore, the integrated valve V and power transmission device 1 according to the second embodiment are the same as those of the first embodiment, except for the manner of operation control in the first output state and the second output state, and the configuration for determining the operating state of the first output shaft 40 and the second output shaft 50. In other words, the other configurations of the integrated valve V, etc., of the second embodiment (for example, the drive unit 10, the main body 30, etc.) are the same as those of the first embodiment. For this reason, in the following description, the differences between the integrated valve V and power transmission device 1 according to the second embodiment and the first embodiment will be described in detail, and descriptions of other parts will be omitted.

[0193] In the integrated valve V and power transmission device 1 of the second embodiment, the output control of the drive motor 11 is performed so that, in both the first output state and the second output state, the change in the rotational speed of the rotating output shaft remains the same until it reaches a predetermined rotational speed (i.e., a steady-state rotational speed Ns). Specifically, acceleration control by the drive motor 11 is performed so that the behavior of the rotational speed in the first output state and the second output state remains the same even while the rotational speed (i.e., rotational speed) of the rotating output shaft reaches a steady-state rotational speed Ns.

[0194] In this disclosure, the rotational speed when the first output shaft 40 is rotated in the first output state is referred to as the first rotational speed Na, and the rotational speed when the second output shaft 50 is rotated in the second output state is referred to as the second rotational speed Nb. The drive current of the drive motor 11 when the first output shaft 40 is rotated in the first output state is referred to as the first drive current Ca, and the drive current of the drive motor 11 when the second output shaft 50 is rotated in the second output state is referred to as the second drive current Cb.

[0195] In the second embodiment, the output control of the drive motor 11 described above is performed. As a result, as shown in Figure 10, the behavior of the first rotational speed Na in the first output state is the same as the behavior of the second rotational speed Nb in the second output state. As a result, the first rotational speed Na and the second rotational speed Nb become the steady rotational speed Ns at the same timing (time ts), and at time ts, the transient period Pt ends and the steady period Ps begins.

[0196] When the system enters a steady-state period Ps, the output of the drive motor 11 is controlled to maintain a steady-state rotational speed Ns, regardless of whether it is in the first or second output state. In other words, in the steady state, the drive motor 11 is controlled to maintain a steady-state rotational speed Ns, so the output is controlled to make the acceleration zero.

[0197] The behavior of the drive current when the output of the drive motor 11 is controlled in this manner will be explained separately for the first output state and the second output state. First, the behavior of the first drive current Ca when the first output shaft 40 is rotated in the first output state will be explained.

[0198] As shown in Figure 10, when the rotation of the first output shaft 40 begins in the first output state, the drive motor 11 is controlled to drive so that the rotational speed of the first output shaft 40 (first rotational speed Na) becomes the steady-state rotational speed Ns. At this time, since the first output shaft 40 changes from a stopped state to a state of rotating at the steady-state rotational speed Ns, a predetermined acceleration control is performed, and the first drive current Ca also gradually shows an increasing value. During this transient period Pt, the first drive current Ca does not exceed the steady-state drive current Cs corresponding to the steady-state rotational speed Ns.

[0199] When the first rotational speed Na reaches the steady rotational speed Ns and the system transitions to the steady-state period Ps, the first drive current Ca is equal to the steady-state drive current Cs. During the steady-state period Ps, the drive motor 11 is controlled to maintain the steady rotational speed Ns, so the first drive current Ca is equal to the steady-state drive current Cs.

[0200] Next, we will explain the behavior of the second drive current Cb when the second output shaft 50 is rotated in the second output state. As described above, when the rotation of the second output shaft 50 is started in the second output state, the drive motor 11 is controlled to drive so that the rotational speed of the second output shaft 50 (second rotational speed Nb) becomes the steady-state rotational speed Ns.

[0201] At this time, the drive control of the drive motor 11 related to the second output state is performed so that it behaves in the same way as the first rotational speed Na related to the first output shaft 40, and this is carried out from the stopped state until it reaches the steady state related to the first output state.

[0202] In the power transmission device 1, the second output shaft 50 is formed with a smaller diameter than the first output shaft 40, and the rotational load of the second output shaft 50 is set to be smaller than the rotational load of the first output shaft 40. In other words, during the transient period Pt of the second output state, the drive motor 11 is controlled to rotate the second output shaft 50, which has a smaller rotational load than the first output shaft 40, at the same rotational speed as the first output shaft 40.

[0203] Therefore, the second drive current Cb during the transient period Pt of the second output state is larger than the first drive current Ca during the transient period Pt of the first output state, corresponding to the difference in rotational load between the first output shaft 40 and the second output shaft 50. As shown in Figure 10, the second drive current Cb is larger than the steady-state drive current Cs even when the second rotational speed Nb has not yet reached the steady-state rotational speed Ns.

[0204] As a result, even when acceleration control is performed on the drive motor 11 during the transient period Pt, the integrated valve V and power transmission device 1 according to the second embodiment exhibit a significant difference in the behavior of the first drive current Ca and the second drive current Cb during the transient period Pt. By using the difference in the behavior of the drive currents during the transient period Pt, the power transmission device 1 and the like according to the second embodiment can accurately determine whether it is in the first output state or the second output state.

[0205] As shown in Figure 10, even in the first output state, when the first rotational speed Na reaches the steady rotational speed Ns, the system transitions from the transient period Pt to the steady period Ps. When transitioning to the steady period Ps, the first drive current Ca represents the steady drive current Cs corresponding to the steady rotational speed Ns. Even in the steady period Ps related to the first output state, the drive motor 11 is controlled to maintain the steady rotational speed Ns, so the first drive current Ca maintains the steady drive current Cs.

[0206] The determination map according to the second embodiment is configured using the difference in drive current caused by the difference in rotational load of the first output shaft 40 and the second output shaft 50 during the transient period Pt between the first output state and the second output state. Therefore, in the second embodiment, even when the drive control of the drive motor 11 is performed so that the rotational speeds of the first output shaft 40 and the second output shaft 50 are equal during the transient period Pt, it is possible to determine whether it is the first output state or the second output state using the difference in drive current during the transient period Pt. For example, if the maximum value of the drive current during the transient period Pt is greater than the steady-state drive current Cs, it can be determined that it is the second output state in which the second output shaft 50 is rotating.

[0207] In the power transmission device 1 according to the second embodiment, the behavior of the drive current during the transient period Pt is made different by providing a difference in rotational load between the first output shaft 40 and the second output shaft 50. Therefore, in the second embodiment, it is possible to determine whether the first output shaft 40 is rotating or the second output shaft 50 is rotating by utilizing the difference in rotational load between the first output shaft 40 and the second output shaft 50.

[0208] As a result, the integrated valve V and the power transmission device 1 can appropriately determine whether they are in the first output state or the second output state, and can maintain high accuracy in controlling the operation of the first output shaft 40 and the second output shaft 50.

[0209] As described above, according to the power transmission device 1 of the second embodiment, the output shaft switching unit 25 can switch between the first output state and the second output state, similar to the embodiment described above. As a result, the power transmission device 1 can achieve highly accurate control of the operation of the first output shaft 40 and the operation of the second output shaft 50.

[0210] Furthermore, in the integrated valve V and power transmission device 1, the load (torque) when the first output shaft 40 rotates is different from the load (torque) when the second output shaft 50 rotates. For this reason, the drive current in transient states behaves differently in the first output state when the first output shaft 40 rotates and in the second output state when the second output shaft 50 rotates.

[0211] In other words, the integrated valve V and power transmission device 1 make the value of the drive current in the transient state different due to the difference in rotational load between the first output shaft 40 and the second output shaft 50, and use the difference in the value of the drive current to reliably determine which of the first output shaft 40 and the second output shaft 50 is rotating. Since the integrated valve V and power transmission device 1 make the determination using the detection result of the drive current sensor 73, they can appropriately determine the operating state of the first output state and the second output state without being affected by the visibility of the first output shaft 40, etc.

[0212] Similar to the embodiment described above, the large-diameter portion 41 of the first output shaft 40 has a larger outer diameter than the cylindrical portion 51 of the second output shaft 50, and the small-diameter portion 42 of the first output shaft 40 has a larger outer diameter than the shaft portion 52 of the second output shaft 50. Therefore, the difference in load between the first output shaft 40 and the second output shaft 50 includes the difference in physical properties, including the outer diameter dimensions of the first output shaft 40 and the second output shaft 50.

[0213] Furthermore, a cylindrical first valve body 49 is used as the first output object in the first output shaft 40, and a needle valve second valve body 59 is used as the second output object in the second output shaft 50. Therefore, the difference in rotational load between the first output shaft 40 and the second output shaft 50 includes the difference in physical properties, including the external shape of the first valve body 49 and the second valve body 59.

[0214] Thus, in the integrated valve V and power transmission device 1, the physical properties of the first output shaft 40 and the first valve body 49, and the second output shaft 50 and the second valve body 59, clearly create a difference in rotational load between the first output shaft 40 and the second output shaft 50. As a result, the integrated valve V and power transmission device 1 can generate a clear difference in the drive current during transient states, and maintain high accuracy when determining the first output state and the second output state.

[0215] Furthermore, in the second embodiment, the same method as in the first embodiment can be used to provide a difference in load between the first output shaft 40 and the second output shaft 50. That is, as long as there is a difference between the load on the first output shaft 40 and the load on the second output shaft 50, the magnitude of that difference is not limited.

[0216] Alternatively, the difference in load between the first output shaft 40 and the second output shaft 50 may be provided by the difference in frictional force generated between the first output shaft 40 and the first bearing member 47, and between the second output shaft 50 and the second bearing member 57. In the case of the integrated valve V, the difference in load between the first output shaft 40 and the second output shaft 50 may be realized using the frictional force generated between the first valve body 49 and the first screw member 48, and between the second valve body 59 and the second screw member 58.

[0217] In the above-described embodiment, the difference in load on the first output shaft 40 and the second output shaft 50 was achieved by employing different types of valve bodies as the first valve body 49 and the second valve body 59, but the embodiment is not limited to this. For example, even when the same type of valve body is employed, the difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by making the external dimensions of the first valve body 49 and the second valve body 59 different. Alternatively, the difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by making the constituent materials (e.g., density, etc.) of the first valve body 49 and the second valve body 59 different.

[0218] Furthermore, if a difference in load can be achieved between the first output shaft 40 and the second output shaft 50, various configurations can be adopted. For example, a difference in load can be achieved between the first output shaft 40 and the second output shaft 50 by varying the amount of pressure applied to the first valve body 49 and the first valve seat 66, and between the second valve body 59 and the second valve seat 68. Alternatively, a difference in load can be achieved between the first output shaft 40 and the second output shaft 50 by varying the differential pressure before and after the first pressure reduction section VA and the differential pressure before and after the second pressure reduction section VB.

[0219] Furthermore, in the integrated valve V of the second embodiment, the fluid controlled by the first pressure reducing section VA and the second pressure reducing section VB was the refrigerant circulating in the refrigeration cycle 100, but the invention is not limited to this embodiment.

[0220] In other words, it is also possible to apply this to an integrated valve that combines multiple valve devices arranged in two different fluid circuits: one controlled by a first valve body 49 operating on the first output shaft 40, and the other by a second valve body 59 operating on the second output shaft 50. In this case, the difference in load on the first output shaft 40 and the second output shaft 50 may be realized by the physical properties (e.g., viscosity) of the fluid controlled by the first valve body 49 operating on the first output shaft 40 and the fluid controlled by the second valve body 59 operating on the second output shaft 50.

[0221] (Third Embodiment) Next, a third embodiment, which differs from the embodiments described above, will be explained with reference to Figures 11 and 12. In the third embodiment, the determination method for cases where acceleration control, as in the second embodiment, is not performed as drive control by the drive motor 11 during the transient period until transitioning to any steady state is addressed. For this reason, in the third embodiment, differences arise in the behavior of the drive current during the transient period Pt and the steady period, and in the length of the transient period, due to the difference in rotational load on the first output shaft 40 and the second output shaft 50.

[0222] In the third embodiment, the difference in rotational speed of the drive unit 10 during this transient state is used to determine the operating state of the first output shaft 40 and the second output shaft 50. For this reason, in the third embodiment, the configuration of the circuit unit 70 and the determination map for determining the operating state of the first output shaft 40 and the second output shaft 50 differ from those of the embodiments described above.

[0223] In other words, the integrated valve V and other components of the power transmission device 1 (for example, the drive unit 10, the main body 30, etc.) are the same as in the embodiment described above. For this reason, in the following description, the differences between the integrated valve V and power transmission device 1 of the third embodiment and the embodiment described above will be explained in detail, and the explanation of other parts will be omitted.

[0224] First, the circuit unit 70 according to the third embodiment will be described with reference to Figure 11. In the third embodiment, the circuit unit 70 is housed in the drive unit 10 of the integrated valve V, similar to the embodiment described above. The circuit unit 70 has a circuit board equipped with a plurality of electronic components for controlling the drive motor 11. Furthermore, the circuit unit 70 performs control related to the switching operation of the output shaft in the integrated valve V (i.e., control of the output shaft switching unit 25).

[0225] As shown in Figure 11, the circuit unit 70 is electrically connected to a drive motor 11, which is composed of a three-phase motor, and a battery B. The circuit unit 70 also has electronic components such as an ECU for controlling the operation of the integrated valve V, and acts as a control unit for the operation of the first pressure reducing unit VA and the second pressure reducing unit VB. The circuit unit 70 also has a determination unit 71, a three-phase inverter circuit 72, and a rotation speed sensor 74. The determination unit 71 and the three-phase inverter circuit 72 have the same configuration as in the embodiment described above, so a further explanation will be omitted.

[0226] The rotational speed sensor 74 is a sensor for detecting the rotational speed of the drive motor 11, which is composed of a three-phase motor. The rotational speed sensor 74 is an example of a rotational speed detection unit. Since the input shaft 20 is joined to the lower end of the shaft 14 of the drive motor 11, it can be said that the rotational speed sensor 74 detects the rotational speed of the input shaft 20.

[0227] Next, in the integrated valve V and power transmission device 1 according to the third embodiment, the output control of the drive current of the drive motor 11 during the transient period Pt and the drive control during the steady-state period Ps are performed under the same conditions regardless of whether it is the first output state or the second output state. That is, the time change of the drive current starts under the same conditions in the transient period Pt of the first output state (hereinafter, the first transient period Pta) and the transient period of the second output state (hereinafter, the second transient period Ptb). Also, the start time of the steady-state period of the first output state (hereinafter, the first steady-state period Psa) and the start time of the steady-state period of the second output state (hereinafter, the second steady-state period) are different.

[0228] First, with reference to Figure 12, the behavior of the drive current and rotational speed when the first output shaft 40 is rotated in the first output state will be explained for the power transmission device 1 according to the third embodiment. In the power transmission device 1 according to the third embodiment, when the system transitions to the first output state and the first transient period Pta begins, a drive current is applied to the drive motor 11 so as to increase at a predetermined rate. The application of the drive current drives the drive motor 11 to output a drive force in a predetermined manner, which is then transmitted to the first output shaft 40.

[0229] The first output shaft 40 begins to rotate in response to the transmission of driving force. At this time, the rotational speed of the first output shaft 40 in the first output state (first rotational speed Na) increases over time, approaching the steady-state rotational speed Ns. The change in the rotational speed of the first output shaft 40 is influenced by the rotational load applied to the first output shaft 40.

[0230] In the third embodiment as well, when the first rotational speed Na reaches the steady rotational speed Ns (time ta), the first transient period Pta ends and the system transitions to the first steady period Psa. Upon transitioning to the first steady period Psa, the output of the drive motor 11 is controlled so that the first rotational speed Na becomes the steady rotational speed Ns. In other words, during the first steady period Psa, the drive motor 11 is controlled so that the first rotational speed Na maintains the steady rotational speed Ns, and output control is performed so that the acceleration becomes zero.

[0231] At this time, a first drive current Ca is applied to the drive motor 11 during the first steady period Psa, regardless of the rotational load of the first output shaft 40, so as to be necessary to maintain the first rotational speed Na at a steady rotational speed Ns. In this case, the first drive current Ca is called the first steady-state drive current Csa. As shown in Figure 12, during the first steady period Psa, the first steady-state drive current Csa is continuously applied as the first drive current Ca.

[0232] Next, the behavior of the drive current and rotational speed when the second output shaft 50 is rotated in the second output state will be described for the power transmission device 1 according to the third embodiment. As described above, when the rotation of the second output shaft 50 is started in the second output state, the second transient period Ptb is started and the drive motor 11 is controlled. At this time, a second drive current Cb is applied to the drive motor 11 such that the value of the drive current increases at the same rate as in the case of the first transient period Pta in the first output state.

[0233] The driving force generated by the drive motor 11 when the second drive current Cb is applied is transmitted to the second output shaft 50, and rotation at the second rotational speed Nb begins. As described above, the cylindrical portion 51 of the second output shaft 50 is formed to have a smaller outer diameter than the large-diameter portion 41 of the first output shaft 40, and the shaft portion 52 of the second output shaft 50 is formed to have a smaller outer diameter than the small-diameter portion 42 of the first output shaft 40. For this reason, the rotational load on the second output shaft 50 is set to be smaller than the rotational load on the first output shaft 40.

[0234] Therefore, when a drive current is applied to the drive motor 11 that exhibits behavior of increasing at the same rate in both the first and second output states, the rotational speed of the second output shaft 50, which has a small rotational load (second rotational speed Nb), increases at an earlier timing than the first rotational speed related to the first output shaft 40. In other words, during the transient period Pt, the second rotational speed Nb related to the second output shaft 0, which has a small rotational load, tends to be larger than the first rotational speed Na related to the first output shaft 40, which has a large rotational load.

[0235] Therefore, in the third embodiment, a difference in the rotational load between the first output shaft 40 and the second output shaft 50 causes a difference in the first rotational speed Na and the second rotational speed Nb during the transient period. For this reason, by detecting and using the rotational speed during the transient period Pt with the rotational speed sensor 74, it is possible to accurately determine whether the system is in the first output state or the second output state without relying on visual inspection or other means.

[0236] Then, the second transient period Ptb related to the second output state ends when the second rotational speed Nb reaches the steady rotational speed Ns (time tb), and the system transitions to the second steady period Psb. As described above, since the rotational load of the second output shaft 50 is smaller than the rotational load of the first output shaft 40, when the drive control of the drive motor 11 is performed under the same conditions, the second rotational speed Nb increases at an earlier timing than the first rotational speed Na. For this reason, the period during which the second rotational speed Nb reaches the steady rotational speed Ns is shorter than the period during which the first rotational speed Na reaches the steady rotational speed Ns.

[0237] Therefore, according to the third embodiment, a difference in the duration required for the first transient period Pta and the second transient period Ptb occurs due to the difference in rotational load between the first output shaft 40 and the second output shaft 50. Accordingly, according to the third embodiment, by using the difference in the duration required for the first transient period Pta and the second transient period Ptb, it is possible to accurately determine whether the system is in the first output state or the second output state without relying on visual inspection or other means.

[0238] When transitioning to the second steady-state period Psb in the second output state, as described above, the drive motor 11 is controlled to maintain the second rotational speed Nb at a steady-state rotational speed Ns. At this time, a second drive current Cb is applied to the drive motor 11 during the second steady-state period Psb, regardless of the rotational load of the second output shaft 50, to maintain the second rotational speed Nb at a steady-state rotational speed Ns. In this case, the second drive current Cb is called the second steady-state drive current Csb. As shown in Figure 12, during the second steady-state period Psb, the second steady-state drive current Csb is continuously applied as the second drive current Cb.

[0239] Here, the rotational load of the second output shaft 50 is smaller than that of the first output shaft 40. Therefore, in order to achieve the same rotational speed, the second output shaft 50, which has a smaller rotational load, can be operated with a smaller drive current applied to the drive motor 11 than the first output shaft 40, which has a larger rotational load. In other words, as shown in Figure 12, the second steady-state drive current Csb in the second steady-state period Psb is smaller than the first steady-state drive current Csa in the first steady-state period Psa.

[0240] According to the third embodiment, a difference in rotational load between the first output shaft 40 and the second output shaft 50 results in a difference between the first steady-state drive current Csa during the first steady-state period Psa and the second steady-state drive current Csb during the second steady-state period Psb. Therefore, according to the third embodiment, by using the difference between the first steady-state drive current Csa and the second steady-state drive current Csb, it is possible to accurately determine whether the system is in the first output state or the second output state without relying on visual inspection or other means.

[0241] The determination map according to the third embodiment can be configured using the difference in drive current caused by the difference in rotational load between the first output shaft 40 and the second output shaft 50 during the first transient period Pta and the second transient period Ptb. Therefore, in the third embodiment, even if acceleration control is not performed for the drive control of the drive motor 11 during the transient period, it is possible to determine whether the system is in the first output state or the second output state using the difference in drive current during the transient period Pt.

[0242] Furthermore, the determination map according to the third embodiment can be constructed using the difference between the period required for the first transient period Pta and the period required for the second transient period Ptb. Since the difference between the period required for the first transient period Pta and the period required for the second transient period Ptb is caused by the difference in rotational load of the first output shaft 40 and the second output shaft 50, by using this difference, it is possible to accurately determine whether the system is in the first output state or the second output state without relying on visual inspection or other means.

[0243] Furthermore, the determination map according to the third embodiment can also be configured using the difference between the first steady-state drive current Csa and the second steady-state drive current Csb. Since the difference between the first steady-state drive current Csa and the second steady-state drive current Csb is caused by the difference in rotational load on the first output shaft 40 and the second output shaft 50, by using this difference, it is possible to accurately determine whether the system is in the first output state or the second output state without relying on visual inspection or other means.

[0244] Furthermore, according to the power transmission device 1 of the third embodiment, by combining multiple factors such as the difference in drive current values ​​during the transient period, the difference in the duration required for the transient period, and the difference in drive current values ​​during the steady-state period, it is possible to accurately determine whether the system is in the first output state or the second output state without relying on visual inspection or other means.

[0245] As a result, the integrated valve V and power transmission device 1 according to the third embodiment can appropriately determine whether they are in the first output state or the second output state, and can maintain high accuracy in controlling the operation of the first output shaft 40 and the second output shaft 50.

[0246] As described above, according to the power transmission device 1 of the third embodiment, the output shaft switching unit 25 can switch between the first output state and the second output state, similar to the embodiment described above. As a result, the power transmission device 1 can achieve highly accurate control of the operation of the first output shaft 40 and the operation of the second output shaft 50.

[0247] Furthermore, in the integrated valve V and power transmission device 1, the load (torque) when the first output shaft 40 rotates is different from the load (torque) when the second output shaft 50 rotates. For this reason, the manner in which the rotational speed changes in the transient state is different between the first output state when the first output shaft 40 rotates and the second output state when the second output shaft 50 rotates.

[0248] In other words, the integrated valve V and power transmission device 1 can reliably determine which of the first output shaft 40 and second output shaft 50 is rotating using at least one of the following: the value of the rotational speed in the transient state, the time required to transition to a steady state, and the value of the drive current in the steady state. Since the integrated valve V and power transmission device 1 make their determination using the detection results of the rotational speed sensor 74, they can appropriately determine the operating state of the first output state and the second output state without being affected by the visibility of the first output shaft 40, etc.

[0249] Similar to the embodiment described above, the cylindrical portion 51 of the second output shaft 50 is formed with a smaller outer diameter than the large-diameter portion 41 of the first output shaft 40, and the shaft portion 52 of the second output shaft 50 is formed with a smaller outer diameter than the small-diameter portion 42 of the first output shaft 40. Therefore, the difference in load between the first output shaft 40 and the second output shaft 50 includes the difference in physical properties, including the outer diameter dimensions of the first output shaft 40 and the second output shaft 50.

[0250] Furthermore, a cylindrical first valve body 49 is used as the first output object in the first output shaft 40, and a needle valve second valve body 59 is used as the second output object in the second output shaft 50. Therefore, the difference in load between the first output shaft 40 and the second output shaft 50 includes the difference in physical properties, including the external shape of the first valve body 49 and the second valve body 59.

[0251] Thus, in the integrated valve V and power transmission device 1, the physical properties of the first output shaft 40 and the first valve body 49, and the second output shaft 50 and the second valve body 59, clearly create a difference in load on the first output shaft 40 and the second output shaft 50. As a result, the integrated valve V and power transmission device 1 can generate a clear difference in the value of the rotational speed in the transient state, the time required to transition to the steady state, and the value of the drive current in the steady state, thereby maintaining a high level of accuracy when determining the first output state and the second output state.

[0252] Furthermore, in the third embodiment, the same method as in the above-described embodiment can be used to provide a difference in load between the first output shaft 40 and the second output shaft 50. That is, as long as there is a difference between the load on the first output shaft 40 and the rotational load on the second output shaft 50, the relative magnitude of the loads is not limited.

[0253] Alternatively, the difference in load between the first output shaft 40 and the second output shaft 50 may be provided by the difference in frictional force generated between the first output shaft 40 and the first bearing member 47, and between the second output shaft 50 and the second bearing member 57. In the case of the integrated valve V, the difference in load between the first output shaft 40 and the second output shaft 50 may be realized using the frictional force generated between the first valve body 49 and the first screw member 48, and between the second valve body 59 and the second screw member 58.

[0254] In the above-described embodiment, the difference in load on the first output shaft 40 and the second output shaft 50 was achieved by employing different types of valve bodies as the first valve body 49 and the second valve body 59, but the embodiment is not limited to this. For example, even when the same type of valve body is employed, the difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by making the external dimensions of the first valve body 49 and the second valve body 59 different. Alternatively, the difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by making the constituent materials (e.g., density, etc.) of the first valve body 49 and the second valve body 59 different.

[0255] Furthermore, if a difference in load can be achieved between the first output shaft 40 and the second output shaft 50, various configurations can be adopted. For example, a difference in load can be achieved between the first output shaft 40 and the second output shaft 50 by varying the amount of pressure applied to the first valve body 49 and the first valve seat 66, and between the second valve body 59 and the second valve seat 68. Alternatively, a difference in load can be achieved between the first output shaft 40 and the second output shaft 50 by varying the differential pressure before and after the first pressure reduction section VA and the differential pressure before and after the second pressure reduction section VB.

[0256] Furthermore, in the integrated valve V of the third embodiment, the fluid controlled by the first pressure reducing section VA and the second pressure reducing section VB was the refrigerant circulating in the refrigeration cycle 100, but the invention is not limited to this embodiment.

[0257] In other words, it is also possible to apply this to an integrated valve that combines multiple valve devices arranged in two different fluid circuits: one controlled by a first valve body 49 operating on the first output shaft 40, and the other by a second valve body 59 operating on the second output shaft 50. In this case, the difference in load on the first output shaft 40 and the second output shaft 50 may be realized by the physical properties (e.g., viscosity) of the fluid controlled by the first valve body 49 operating on the first output shaft 40 and the fluid controlled by the second valve body 59 operating on the second output shaft 50.

[0258] (Fourth Embodiment) Next, a fourth embodiment, which differs from the embodiments described above, will be described with reference to Figures 13 to 16. In the embodiments described above, the power transmission device 1 was applied to an integrated valve V having a first pressure reducing section VA and a second pressure reducing section VB, but the fourth embodiment differs from the embodiments described above in that it is applied to an integrated pump unit P having a first pump PA and a second pump PB.

[0259] As shown in Figure 14, in the integrated pump unit P and power transmission device 1 according to the fourth embodiment, the configuration of the first output object and the second output object to which driving force is transmitted from the first output shaft 40 and the second output shaft 50 has been changed from the above-described embodiment. In addition, the configuration of the flow path forming section 60 has been changed in the fourth embodiment.

[0260] In other words, the integrated pump unit P and power transmission device 1 according to the fourth embodiment have a drive unit 10, an input shaft 20, a mechanism housing unit 35, a first output shaft 40, a second output shaft 50, etc., similar to the embodiments described above. The configuration of the drive unit 10, input shaft 20, mechanism housing unit 35, first output shaft 40, second output shaft 50, etc. in the fourth embodiment is the same as in the embodiments described above, so a further explanation will be omitted.

[0261] First, the system configuration having the integrated pump unit P according to the fourth embodiment will be described with reference to Figure 13. As described above, the integrated pump unit P according to the fourth embodiment has a first pump PA and a second pump PB. The first pump PA is a fluid machine that pumps fluid in a fluid circuit, and the second pump PB is a fluid machine that is located at a different position from the first pump PA and pumps fluid in the fluid circuit.

[0262] As shown in Figure 13, in the fourth embodiment, the first pump PA is located in the first heat transfer medium circuit 130, and the second pump PB is located in the second heat transfer medium circuit 140. The first heat transfer medium circuit 130 is configured such that the cooler core 131 and the first pump PA are connected by a first heat transfer medium flow path 133 so that the heat transfer medium can circulate. The cooler core 131 is an air conditioning heat exchanger that cools the blown air supplied to the air-conditioned space from a blower fan (not shown) by the coldness of the first heat transfer medium circulating in the first heat transfer medium circuit 130.

[0263] The second heat transfer medium circuit 140 is configured such that the heat transfer medium can circulate through the equipment heat exchanger 141 and the second pump PB via the second heat transfer medium flow path 143. The equipment heat exchanger 141 is a heat exchanger for adjusting the heat generated in the equipment to be temperature controlled (for example, a battery or motor generator, etc.) by heat exchange with the heat transfer medium.

[0264] Furthermore, the components of the first heat transfer medium circuit 130 and the second heat transfer medium circuit 140 are not limited to those shown in Figure 14, and many more components can be arranged. Also, the components arranged in the first heat transfer medium circuit 130 and the second heat transfer medium circuit 140 are not necessarily limited to the cooler core 131 or the equipment heat exchanger 141. Any equipment capable of exchanging heat with the heat transfer medium can be arranged in the first heat transfer medium circuit 130 and the second heat transfer medium circuit 140.

[0265] Next, the first output object and the second output object according to the fourth embodiment will be described with reference to Figure 13. As shown in Figure 13, the first impeller 150, which is the first output object, is joined to the lower end of the small diameter portion 42 of the first output shaft 40. The first impeller 150 constitutes a part of the first pump PA and pumps the heat transfer medium in the first heat transfer medium passage 133 as the first output shaft 40 rotates.

[0266] The first impeller 150 is formed in the shape of a disc with its center on the rotation axis of the first output shaft 40, and is configured to pressurize a heat transfer medium as it rotates. A shaft through hole 151 is formed at the rotation center of the first impeller 150. The impeller shaft 161, which is provided at the rotation center of the second impeller 160, is rotatably inserted through the shaft through hole 151.

[0267] The upper end of the impeller shaft 161, which constitutes the second impeller 160, is positioned within the insertion hole 52A of the second output shaft 50. As a result, the rotational driving force transmitted to the second output shaft 50 is transmitted to the second impeller 160, which is the second output object, through the cooperation of the insertion hole 52A and the impeller shaft 161.

[0268] The second impeller 160, like the first impeller 150, is formed in a disc shape with its center on the rotation axis of the second output shaft 50, and is configured to pressurize a heat transfer medium as it rotates. The impeller shaft 161 is positioned along the rotation axis at the rotation center of the second impeller 160. The external dimensions of the impeller shaft 161 are smaller than the internal diameter of the shaft through hole 151 in the first impeller 150. This allows the second impeller 160 to be rotated without affecting the first impeller 150, even with the impeller shaft 161 inserted through the shaft through hole 151.

[0269] In the integrated pump unit P and power transmission device 1 according to the fourth embodiment, the second impeller 160 is formed to have a smaller outer diameter than the first impeller 150. Therefore, the load when rotating the second impeller 160 by the second output shaft 50 is configured to be smaller than the load when rotating the first impeller 150 by the first output shaft 40.

[0270] Furthermore, the size of each blade in the second impeller 160 is smaller than the size of each blade in the first impeller 150. As a result, the amount of heat transfer medium scraped when the second impeller 160 rotates is smaller than the amount of heat transfer medium scraped when the first impeller 150 rotates. In this respect as well, the load when the second impeller 160 is rotated by the second output shaft 50 is smaller than the load when the first impeller 150 is rotated by the first output shaft 40.

[0271] Next, the configuration of the flow path forming section 60 in the integrated pump unit P according to the fourth embodiment will be described with reference to Figure 13, etc. As shown in Figure 13, the flow path forming section 60 according to the fourth embodiment has a first heat medium flow path 133 which constitutes part of the first heat medium circuit 130, a through hole 135, and a second heat medium flow path 143 which constitutes part of the second heat medium circuit 140.

[0272] As shown in Figure 14, the first heat transfer medium flow path 133 formed in the flow path forming section 60 has a first heat transfer medium inlet 132 and a first heat transfer medium outlet 134, and the first impeller 150 is housed between the first heat transfer medium inlet 132 and the first heat transfer medium outlet 134. The first heat transfer medium inlet 132 is an opening that supplies the heat transfer medium of the first heat transfer medium circuit 130 to the first pump PA. The first heat transfer medium outlet 134 is an opening that allows the heat transfer medium pumped by the first pump PA to flow out to other components of the first heat transfer medium circuit 130 (for example, the cooler core 131).

[0273] Furthermore, the second heat transfer medium flow path 143 formed in the flow path forming section 60 has a second heat transfer medium inlet 142 and a second heat transfer medium outlet 144, and the second impeller 160 is housed between the second heat transfer medium inlet 142 and the second heat transfer medium outlet 144. The second heat transfer medium inlet 142 is an opening that supplies the heat transfer medium of the second heat transfer medium circuit 140 to the second pump PB. The second heat transfer medium outlet 144 is an opening that allows the heat transfer medium pumped by the second pump PB to flow out to other components of the second heat transfer medium circuit 140 (for example, an equipment heat exchanger 141).

[0274] Here, a through hole 135 is formed between the first heat transfer medium flow path 133 and the second heat transfer medium flow path 143 in the flow path forming section 60. The through hole 135 is formed to connect the first heat transfer medium flow path 133 and the second heat transfer medium flow path 143, and is coaxial with the rotation axes of the first output shaft 40 and the second output shaft 50.

[0275] As shown in Figure 13, a waterproof bearing 155 having a shaft hole 156 is positioned inside the through hole 135. The impeller shaft 161 of the second impeller 160 is inserted through the shaft hole 156 of the waterproof bearing 155. As a result, the waterproof bearing 155 suppresses the inflow and outflow of the heat transfer medium between the first heat transfer medium circuit 130 and the second heat transfer medium circuit 140 in the flow path forming section 60, while simultaneously rotatably supporting the second impeller 160.

[0276] In the fourth embodiment, the first screw member 48 and the second screw member 58 are not arranged inside the flow path forming section 60. This is because there is no need to displace the first impeller 150 and the second impeller 160 in the axial direction of the first output shaft 40 or the like.

[0277] According to the integrated pump unit P and power transmission device 1 of the fourth embodiment configured in this way, the first output state and the second output state can be switched by controlling the operation of the output shaft switching unit 25, similar to the embodiment described above.

[0278] When switching to the first output state, the integrated pump unit P and the power transmission device 1 move the switching member 80 downward along the axial direction by controlling the operation of the output shaft switching unit 25, bringing the second rotation restricting unit 80B into contact with the upper surface of the cylindrical portion 51 of the second output shaft 50. As a result, as shown in Figure 15, the drag force generating unit 85 of the second rotation restricting unit 80B and the drag force generating unit 87 on the second output shaft 50 side engage, stopping the rotation of the second output shaft 50.

[0279] As the switching member 80 moves downward along the axial direction, the first rotation restricting unit 80A moves away from the lower surface of the large-diameter portion 41 on the first output shaft 40. As a result, the drag force generating portion 85 of the first rotation restricting unit 80A moves away from the drag force generating portion 86 on the first output shaft 40 side, thus allowing rotation of the first output shaft 40. In other words, the integrated pump unit P and power transmission device 1 according to the fourth embodiment can achieve the first output state by supplying a DC current in a predetermined direction to the switching coil 26.

[0280] As a result, in the integrated pump unit P and power transmission device 1 in the first output state, the first impeller 150 can be rotated while the second impeller 160 is stopped, and the heat transfer medium of the first heat transfer medium circuit 130 can be pumped by the first pump PA.

[0281] When switching to the second output state, the integrated pump unit P and the power transmission device 1 move the switching member 80 upward along the axial direction by controlling the operation of the output shaft switching unit 25, bringing the first rotation restricting unit 80A into contact with the lower surface of the large diameter portion 41 of the first output shaft 40. As a result, as shown in Figure 16, the drag force generating unit 85 of the first rotation restricting unit 80A and the drag force generating unit 86 on the first output shaft 40 side engage, stopping the rotation of the first output shaft 40.

[0282] Then, as the switching member 80 moves upward along the axial direction, the second rotation restricting unit 80B moves away from the upper surface of the cylindrical portion 51 on the second output shaft 50. As a result, the drag generating unit 85 of the second rotation restricting unit 80B moves away from the drag generating unit 87 on the second output shaft 50 side, and thus rotation of the second output shaft 50 is permitted. In other words, the integrated pump unit P and power transmission device 1 according to the fourth embodiment can achieve the second output state by supplying a DC current to the switching coil 26 in the opposite direction to that in the first output state.

[0283] As a result, in the integrated pump unit P and power transmission device 1 in the second output state, the second impeller 160 can be rotated while the first impeller 150 is stopped, and the heat transfer medium of the second heat transfer medium circuit 140 can be pumped by the second pump PB.

[0284] In the integrated pump unit P and power transmission device 1 according to the fourth embodiment, the circuit section 70 is the same as in the first embodiment described above, and the circuit section 70 includes electronic components such as an ECU for controlling the operation of the integrated valve V. The circuit section 70 has a determination unit 71, a three-phase inverter circuit 72, and a drive current sensor 73.

[0285] Furthermore, in the integrated pump unit P, the load (torque) when the first output shaft 40 rotates is set to be greater than the load (torque) when the second output shaft 50 rotates in the second output state. Part of the difference in load between the first output shaft 40 and the second output shaft 50 is due to the difference in the output objects to which the rotational driving force is transmitted, and is influenced by the physical properties of the first impeller 150 and the second impeller 160 (i.e., the difference in outer diameter dimensions).

[0286] Furthermore, the large-diameter portion 41 of the first output shaft 40 has a larger outer diameter than the cylindrical portion 51 of the second output shaft 50, and the small-diameter portion 42 of the first output shaft 40 has a larger outer diameter than the shaft portion 52 of the second output shaft 50. Therefore, the difference in load between the first output shaft 40 and the second output shaft 50 includes the difference in physical properties, including the outer diameter dimensions of the first output shaft 40 and the second output shaft 50.

[0287] Therefore, in the fourth embodiment, in a steady state, it is possible to determine whether the first output shaft 40 or the second output shaft 50 is rotating by utilizing the difference in drive current that appears due to the load when the first output shaft 40 and the second output shaft 50 rotate, respectively.

[0288] In the fourth embodiment, when determining the operating state of the first output shaft 40 and the second output shaft 50, a determination map stored in the ROM of the circuit unit 70 is used. The determination map according to the fourth embodiment is configured in the same way as in the first embodiment described above, associating the relationship between the drive current and torque in the drive motor 11 in a steady state, as shown in Figure 9.

[0289] According to the integrated pump unit P of the fourth embodiment, similar to the first embodiment, it is possible to determine whether the first output shaft 40 is rotating or the second output shaft 50 is rotating by using the detected value of the drive current sensor 73 in a steady state and the determination map shown in Figure 9. This makes it possible to appropriately determine whether the state is the first output state or the second output state, and to maintain high accuracy in the operation control of the first output shaft 40 and the second output shaft 50.

[0290] Furthermore, since the circuit section 70 is used for controlling the operation of the drive motor 11, it is a configuration that is generally installed in any device having a drive motor 11. Accordingly, according to the integrated pump unit P and power transmission device 1 of the fourth embodiment, there is no need to add any new configurations, and the first output state and the second output state can be determined by applying the determination method.

[0291] As described above, the power transmission device 1 according to the fourth embodiment can be applied to an integrated pump unit P having a first pump PA and a second pump PB, and the effects and advantages derived from the configuration and operation common to the above-described embodiments can be obtained.

[0292] In the fourth embodiment described above, the drive current in the steady state is used to determine whether the first output shaft 40 or the second output shaft 50 is rotating. However, other configurations can be adopted. That is, similar to the third embodiment, the drive current sensor 73 can be used to determine whether the first output shaft 40 or the second output shaft 50 is rotating by using the value of the drive current in the transient state and the determination map shown in Figure 10.

[0293] Furthermore, by placing a rotational speed sensor 74 on the circuit section 70 and adopting the determination map shown in Figure 12, it is also possible to adopt the same determination method as in the third embodiment. That is, in the integrated pump unit P, it is possible to determine whether the first output shaft 40 is rotating or the second output shaft 50 is rotating using the detected rotational speed value in the transient state.

[0294] In the fourth embodiment as well, the same method as in the above-described embodiment can be used to provide a difference in load between the first output shaft 40 and the second output shaft 50. That is, as long as there is a difference between the load on the first output shaft 40 and the load on the second output shaft 50, the magnitude of that difference is not limited.

[0295] Alternatively, the difference in load between the first output shaft 40 and the second output shaft 50 may be provided by the difference in frictional force generated between the first output shaft 40 and the first bearing member 47, and between the second output shaft 50 and the second bearing member 57.

[0296] In the fourth embodiment, the difference in load on the first output shaft 40 and the second output shaft 50 was achieved by the difference in the external shape of the first impeller 150 and the second impeller 160, but the embodiment is not limited to this. The difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by using different types of impellers in the first impeller 150 and the second impeller 160. Alternatively, the difference in load on the first output shaft 40 and the second output shaft 50 may be achieved by using different materials (e.g., density, etc.) for the first impeller 150 and the second impeller 160.

[0297] Furthermore, if a difference in load can be achieved between the first output shaft 40 and the second output shaft 50, various configurations can be adopted. For example, in the integrated pump unit P, the fluids controlled by the first pump PA and the second pump PB are the heat transfer medium of the first heat transfer medium circuit 130 and the heat transfer medium of the second heat transfer medium circuit 140, which constitute different fluid circuits. For this reason, a difference in load can be achieved between the first output shaft 40 and the second output shaft 50 by the physical properties (e.g., viscosity) of the heat transfer mediums related to the first heat transfer medium circuit 130 and the second heat transfer medium circuit 140.

[0298] To give a specific example, by making the viscosity of the heat transfer medium circulating in the second heat transfer medium circuit 140 lower than the viscosity of the heat transfer medium circulating in the first heat transfer medium circuit 130, the load when the second output shaft 50 rotates may be made smaller than the load when the first output shaft 40 rotates.

[0299] Alternatively, a difference in load on the first output shaft 40 and the second output shaft 50 may be realized by the difference between the flow rate and head of the fluid pumped by the first impeller 150 and the flow rate and head of the fluid pumped by the second impeller 160. Furthermore, a difference in load on the first output shaft 40 and the second output shaft 50 may be realized by the difference between the state of the fluid when it is pumped by the first impeller 150 (for example, whether it is stationary or in a flowing state) and the state of the fluid when it is pumped by the second impeller 160.

[0300] This disclosure is not limited to the embodiments described above, and can be modified in various ways without departing from the spirit of this disclosure, as follows.

[0301] In the above-described embodiment, the driving force was transmitted to the first output shaft 40 or the second output shaft 50 non-contactually via the mutually acting magnetic forces of the input magnet 21, the output magnet 45, and the magnetic flux modulation unit 55. However, the system is not limited to this configuration. For example, it is also possible to employ a configuration in which the driving force from the input shaft 20 is reduced by a predetermined reduction ratio and transmitted to the first output shaft 40 or the second output shaft 50 using a mechanical configuration such as a planetary gear mechanism.

[0302] Furthermore, in the above-described embodiment, as shown in Figures 7 and 8, the switching member 80 was moved using the magnetic force generated by the output shaft switching unit 25 to achieve a state in which the rotation of one of the first output shaft 40 and the second output shaft 50 is restricted while the rotation of the other is allowed. However, the switching operation of the first output shaft 40 and the second output shaft 50 by the output shaft switching unit 25 is not limited to this embodiment. Various embodiments can be adopted as long as the output shaft switching unit 25 can switch between a state in which the rotation of one of the first output shaft 40 and the second output shaft 50 is restricted while the rotation of the other is allowed.

[0303] In the integrated valve V according to the above embodiment, valve bodies were used as both the first and second output objects, and in the integrated pump unit P, impellers were used as both the first and second output objects. However, the components that can be used as the first and second output objects are not necessarily limited to the same type of component, and different types of components may be used as the first and second output objects. For example, it is possible to use a valve body as the first output object and an impeller as the second output object.

[0304] The features of the power transmission device disclosed herein are as follows: (Item 1) A drive unit (10) that generates a driving force by power supply; an input shaft (20) that rotates by the input of the driving force of the drive unit; a first output shaft (40) that rotates by the driving force transmitted from the input shaft and transmits the driving force to a first output object (49, 150); a second output shaft (50) that is positioned differently from the first output shaft, rotates by the driving force transmitted from the input shaft, and transmits the driving force to a second output object (59, 160) different from the first output object; an output shaft switching unit (25) that switches between a first output state that restricts the rotation of the second output shaft by the driving force and allows the rotation of the first output shaft by the driving force, and a second output state that restricts the rotation of the first output shaft by the driving force and allows the rotation of the second output shaft by the driving force; and a current detection unit (73) that detects the driving current in the drive unit. A power transmission device comprising: a determination unit (71) that determines which of the first and second output shafts is rotating, using the drive current detected by the current detection unit, a first reference indicating the first output state in normal conditions, and a second reference indicating the second output state in normal conditions, when the operation of the drive unit is in a steady state.(Item 2) The device comprises: a drive unit (10) that generates driving force by power supply; an input shaft (20) that rotates by input of the driving force from the drive unit; a first output shaft (40) that rotates by the driving force transmitted from the input shaft and transmits driving force to a first output object (49, 150); a second output shaft (50) positioned differently from the first output shaft, which rotates by the driving force transmitted from the input shaft and transmits driving force to a second output object (59, 160) different from the first output object; an output shaft switching unit (25) that switches between a first output state that restricts the rotation of the second output shaft by the driving force and allows the rotation of the first output shaft by the driving force, and a second output state that restricts the rotation of the first output shaft by the driving force and allows the rotation of the second output shaft by the driving force; and a current detection unit (73) that detects the driving current in the drive unit. A power transmission device having a determination unit (71) that determines which of the first and second output shafts is rotating, using the drive current detected by the current detection unit, a first reference indicating the first output state in normal conditions, and a second reference indicating the second output state in normal conditions, when the operation of the drive unit is in a transient state.(Item 3) The system includes: a drive unit (10) that generates a driving force by power supply; an input shaft (20) that rotates by the input of the driving force from the drive unit; a first output shaft (40) that rotates by the driving force transmitted from the input shaft and transmits the driving force to a first output object (49, 150); a second output shaft (50) that is positioned differently from the first output shaft, rotates by the driving force transmitted from the input shaft, and transmits the driving force to a second output object (59, 160) different from the first output object; an output shaft switching unit (25) that switches between a first output state that restricts the rotation of the second output shaft by the driving force and allows the rotation of the first output shaft by the driving force, and a second output state that restricts the rotation of the first output shaft by the driving force and allows the rotation of the second output shaft by the driving force; and a rotation speed detection unit (74) that detects the rotation speed of the input shaft by the driving force from the drive unit. A power transmission device having a determination unit (71) that determines which of the first and second output shafts is rotating, using the rotational speed detected by the rotational speed detection unit, a first standard indicating the first output state in normal conditions, and a second standard indicating the second output state in normal conditions, when the operation of the drive unit is in a transient state. (Item 4) The power transmission device according to any one of items 1 to 3, wherein the difference between the load when the first output shaft rotates and the load when the second output shaft rotates is due to the physical properties of the first output object (49, 150) and the second output object (59, 160). (Item 5) The power transmission device according to any one of Items 1 to 4, wherein the first output object (49, 150) and the second output object (59, 160) are configured as members for controlling the flow of fluid, and the difference between the load when the first output shaft rotates and the load when the second output shaft rotates is due to the physical properties of the fluid controlled by the first output object and the fluid controlled by the second output object. (Item 6) The power transmission device according to any one of Items 1 to 5, wherein the first output shaft and the second output shaft are each located inside a housing space (35) partitioned from the space in which the input shaft is located.

[0305] This disclosure is described in accordance with the embodiments, but it is understood that this disclosure is not limited to such embodiments or structures. This disclosure also includes various modifications and variations within the equivalence. In addition, various combinations and forms, as well as other combinations and forms that include only one, more, or fewer of those elements, fall within the scope and concept of this disclosure.

Claims

1. The device comprises: a drive unit (10) that generates driving force by power supply; an input shaft (20) that rotates by input of the driving force from the drive unit; a first output shaft (40) that rotates by the driving force transmitted from the input shaft and transmits driving force to a first output object (49, 150); a second output shaft (50) positioned differently from the first output shaft, which rotates by the driving force transmitted from the input shaft and transmits driving force to a second output object (59, 160) different from the first output object; an output shaft switching unit (25) that switches between a first output state that restricts the rotation of the second output shaft by the driving force and allows the rotation of the first output shaft by the driving force, and a second output state that restricts the rotation of the first output shaft by the driving force and allows the rotation of the second output shaft by the driving force; and a current detection unit (73) that detects the driving current in the drive unit. A power transmission device comprising: a determination unit (71) that determines which of the first and second output shafts is rotating, using the drive current detected by the current detection unit, a first reference indicating the first output state in normal conditions, and a second reference indicating the second output state in normal conditions, when the operation of the drive unit is in a steady state.

2. The device comprises: a drive unit (10) that generates driving force by power supply; an input shaft (20) that rotates by input of the driving force from the drive unit; a first output shaft (40) that rotates by the driving force transmitted from the input shaft and transmits driving force to a first output object (49, 150); a second output shaft (50) positioned differently from the first output shaft, which rotates by the driving force transmitted from the input shaft and transmits driving force to a second output object (59, 160) different from the first output object; an output shaft switching unit (25) that switches between a first output state that restricts the rotation of the second output shaft by the driving force and allows the rotation of the first output shaft by the driving force, and a second output state that restricts the rotation of the first output shaft by the driving force and allows the rotation of the second output shaft by the driving force; and a current detection unit (73) that detects the driving current in the drive unit. A power transmission device having a determination unit (71) that determines which of the first and second output shafts is rotating, using the drive current detected by the current detection unit, a first reference indicating the first output state in normal conditions, and a second reference indicating the second output state in normal conditions, when the operation of the drive unit is in a transient state.

3. The system comprises: a drive unit (10) that generates driving force by power supply; an input shaft (20) that rotates by input of the driving force from the drive unit; a first output shaft (40) that rotates by the driving force transmitted from the input shaft and transmits driving force to a first output object (49, 150); a second output shaft (50) positioned differently from the first output shaft, which rotates by the driving force transmitted from the input shaft and transmits driving force to a second output object (59, 160) different from the first output object; an output shaft switching unit (25) that switches between a first output state that restricts the rotation of the second output shaft by the driving force and allows the rotation of the first output shaft by the driving force, and a second output state that restricts the rotation of the first output shaft by the driving force and allows the rotation of the second output shaft by the driving force; and a rotation speed detection unit (74) that detects the rotation speed of the input shaft by the driving force from the drive unit. A power transmission device having a determination unit (71) that determines which of the first and second output shafts is rotating, using the rotational speed detected by the rotational speed detection unit, a first reference indicating the first output state under normal conditions, and a second reference indicating the second output state under normal conditions, when the operation of the drive unit is in a transient state.

4. The power transmission device according to any one of claims 1 to 3, wherein the difference between the load when the first output shaft rotates and the load when the second output shaft rotates is due to the physical properties of the first output object (49, 150) and the second output object (59, 160).

5. The power transmission device according to any one of claims 1 to 3, wherein the first output object (49, 150) and the second output object (59, 160) are configured as members for controlling the flow of fluid, and the difference between the load when the first output shaft rotates and the load when the second output shaft rotates is due to the physical properties of the fluid controlled by the first output object and the fluid controlled by the second output object.

6. The power transmission device according to any one of claims 1 to 3, wherein the first output shaft and the second output shaft are each arranged inside a housing space (35) partitioned from the space in which the input shaft is located.

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