JP6931774B2 - Temperature control system, vehicle - Google Patents

Description

The present invention relates to a temperature adjustment unit, a temperature adjustment system, and a vehicle provided with the temperature adjustment unit that adjusts the temperature to be adjusted. In particular, the present invention relates to a temperature control unit, a temperature control system, and the like that temperature-harmonize a power storage device or an inverter device mounted on a vehicle such as an electric vehicle or a hybrid vehicle.

In a vehicle such as a hybrid vehicle that has multiple power sources and is equipped with a secondary battery as one of them, the cell of the secondary battery is the current flowing inside the battery due to charging and discharging, the internal resistance of the battery cell, and the cell. Heat is generated due to the contact resistance of the connected body. The temperature of the secondary battery greatly affects the life. Cooling the battery cells by blowing air at room temperature or heating at extremely low temperatures is very important for improving the output of the battery system and reducing the number of cells.

However, there is a limit to securing a sufficiently wide installation area for the secondary battery in order to secure a space in the vehicle, and a plurality of battery cells are arranged in a housing having a limited size. Normally, forced air cooling means is used to achieve air cooling by blowing air to adjust the temperature of the secondary battery, which is the target of temperature adjustment. As a matter of course, when the output density of the battery becomes high, it is desired to increase the output of the device such as the temperature adjustment unit and the temperature adjustment system. Increasing the output will lead to an increase in the size of the device. On the other hand, miniaturization of the device is also required. Needless to say, achieving high output and miniaturization at the same time is a highly difficult theme.

In the cooling device shown in Patent Document 1 and the like, an axial blower or a centrifugal blower configured separately in a housing including a heating element is often used. In order to dispose an independent blower as a device in the housing, a blower having an ability to cool the heating element and a region for a flow path through which the cooling air passes are required. The cooling capacity is largely due to the size of the fan. In the cooling device shown in Patent Document 2 and the like, there is a case where a fan case is not provided because it contradicts the miniaturization of the housing. The fan case is a mechanism for increasing the static pressure of the blower, and has the effect of controlling the discharge flow of the fan in an arbitrary direction and rectifying it. Therefore, if the fan case is omitted, there is a problem that the output efficiency of the blower is lowered and the turbulent noise is increased.

Patent Document 3 and the like show a centrifugal blower that is frequently used in a temperature control unit, a temperature control system, and the like that temperature-harmonize a power storage device mounted on a vehicle such as an electric vehicle and a hybrid vehicle, or an inverter device.

A typical case will be described as a comparative example with respect to the temperature adjustment unit using the centrifugal blower shown in Patent Document 3 and the like. FIG. 14 is a cross-sectional view showing a temperature harmonizing unit of a comparative example. A temperature-matched object 350 is housed inside the housing 310 of the comparative example shown in FIG. In the scroll casing 1120, the air discharged from the forward fan 400 is integrated in the circumferential direction. In the scroll casing 1120, the distance between the side wall 1121 and the rotation shaft 1112a gradually increases. Therefore, the air flow 301 discharged from the forward fan 400 is biased toward the inner peripheral surface 1121a side of the side wall 1121. Therefore, in order to make the air flow 301 supplied into the housing 310 uniform, it is necessary to install a rectifying mechanism 1310 such as a duct 1311 inside the housing 310.

However, in the centrifugal blower 1100 using the forward fan 400, the distance L from the center of gravity G of the centrifugal blower 1100 to the discharge hole 1123 becomes long. Therefore, when the centrifugal blower 1100 is attached to the housing 310, the temperature control unit 1010 has an unbalanced and unstable physique. Therefore, the temperature adjustment unit 1010 may be fixed to a surrounding member via the mounting portion 1124. In this case, the mounting portion 1124 is required to have various shape changes in order to be suitable for the environment in which the temperature adjustment unit 1010 is used.

In particular, when the rectifying mechanism 1310 is configured separately from the housing 310, it is necessary to consider the distance from the center of gravity G to the rectifying mechanism 1310. Generally, the distance from the center of gravity G to the rectifying mechanism 1310 becomes long. Therefore, the physique of the temperature control unit tends to be unbalanced.

As described above, in the temperature control unit according to the comparative example, there is an increasing technological trend of reducing noise and downsizing and rationalizing the physique of the temperature control unit itself with the intention of further improving the performance. An object of the present invention is to solve the above problems.

Japanese Unexamined Patent Publication No. 10-93274 Japanese Unexamined Patent Publication No. 2005-933793 Japanese Unexamined Patent Publication No. 2013-104365

In order to achieve the above object, the temperature control unit of the present invention includes an impeller, a rotary drive source, a fan case, a housing, a branch duct portion, and a plurality of intake chambers. The impeller includes a rotation axis in the center, a substantially disk-shaped impeller disk arranged on a surface perpendicular to the rotation axis, and a plurality of impellers erected on the side of an intake hole on one side of the impeller disk. It has a moving blade. The rotational drive source includes a shaft and is connected to the impeller via the shaft. The fan case has a substantially cylindrical side wall formed around the rotation axis, a circular intake hole centered on the rotation axis on a plane perpendicular to the rotation axis, and a side wall in a direction along the rotation axis. It has a discharge hole located on the opposite side of the intake hole. The housing includes an outer surface to which the fan case is attached, and a temperature-adjusted object is housed inside. The branch duct portion branches the air flowing from the discharge hole. An intake chamber is provided on the inflow surface to be temperature-controlled.

As described above, according to the present invention, a small temperature control unit capable of efficiently blowing air even to a housing containing densely arranged parts is provided with a simple structure. be able to.

FIG. 1A is a cross-sectional view showing a temperature control unit according to the first embodiment of the present invention. FIG. 1B is a perspective view showing a temperature control unit according to the first embodiment of the present invention. FIG. 2 is a perspective view showing an example of common parts in the temperature control unit according to the first embodiment of the present invention. FIG. 3 is a cross-sectional view showing a temperature harmonizing unit according to a second embodiment of the present invention. FIG. 4 is a cross-sectional view showing the temperature harmonizing unit according to the third embodiment of the present invention. FIG. 5 is a cross-sectional view showing the temperature harmonizing unit according to the fourth embodiment of the present invention. FIG. 6A is a diagram showing the rotor blade shape (the blade cross-sectional shape on the plane perpendicular to the rotation axis of the forward fan) of the impeller used for the temperature adjustment unit in the comparative example. FIG. 6B is a diagram showing the rotor blade shape (the blade cross-sectional shape on the plane perpendicular to the rotation axis of the rearward fan) of the impeller used in the temperature adjustment unit in the present invention. FIG. 7A is a diagram showing an absolute outflow angle by enlarging a main part of the moving blade (blade shape of a forward fan) shown in FIG. 6A. FIG. 7B is a diagram showing an absolute outflow angle by enlarging a main part of the moving blade (blade shape of the rearward fan) shown in FIG. 6B. FIG. 7C is a graph showing the efficiency characteristics of the impeller used for the temperature harmonizing unit in the present invention and the impeller of the comparative example. FIG. 7D is a graph showing the relationship between the flow coefficient and the pressure coefficient characteristic with respect to the impeller used for the temperature adjustment unit in the present invention and the impeller of the comparative example. FIG. 7E is a graph showing the relationship between the air volume and the wind pressure with respect to the impeller used for the temperature harmonizing unit in the present invention and the impeller of the comparative example. FIG. 8A is a perspective view showing a mode when a diffuser is added to the impeller according to the first to fourth embodiments. FIG. 8B is a front perspective view showing the diffuser according to the first to fourth embodiments. FIG. 8C is a rear perspective view showing the diffuser according to the first to fourth embodiments. FIG. 9 is a system configuration diagram showing an outline of the temperature harmonization system according to the fifth embodiment of the present invention. FIG. 10 is a system configuration diagram showing an outline of another temperature control system according to the fifth embodiment of the present invention. FIG. 11 is a system configuration diagram showing an outline of still another temperature harmonization system according to the fifth embodiment of the present invention. FIG. 12 is a schematic view showing an outline of the vehicle according to the fifth embodiment of the present invention. FIG. 13 is a schematic view showing an outline of another vehicle according to the fifth embodiment of the present invention. FIG. 14 is a cross-sectional view showing a temperature harmonizing unit of a comparative example.

Hereinafter, the present invention will be described with reference to the drawings and tables. The present invention is not limited to the following embodiments. In addition, the notation in the figure does not limit the top and bottom of the actual installation. In the following, the flow (air flow) of the air discharged from the blower 100 will be referred to as a discharge flow. In addition, the display of the white arrow drawn in the drawing schematically shows the mode of the air flow (air flow) and the discharge flow.

(Embodiment 1)
FIG. 1A is a cross-sectional view showing a temperature harmonizing unit 10 according to the first embodiment of the present invention. FIG. 1B is a perspective view showing the temperature adjustment unit 10 of the first embodiment of the present invention. FIG. 2 is a perspective view showing an example of common parts in the temperature adjustment unit 10 according to the first embodiment of the present invention. The temperature control unit 10 is exteriorized by the housing 300. The components described below are housed inside the housing 300. The blower 100, which is a centrifugal blower element, includes an impeller 110 (centrifugal fan) including a plurality of moving blades 111, a substantially disk-shaped impeller disk 112 connecting the moving blades 111, and a rotation shaft and a substantial portion of the impeller 110. In parallel with each other, the distance from the rotation axis increases as the distance from the rotation axis increases toward the discharge hole 123 with respect to the rotation direction of the impeller. It is composed of a fan case 120 comprising the above. The impeller 110 is connected and fixed to the motor 200, which is a rotational drive source, via a shaft 210. The motor 200, which is a rotational drive source, includes a shaft 210.

When the motor 200, which is a rotational drive source, is rotationally driven, the impeller 110 is rotated, and the air flowing in from the intake hole 122 of the fan case 120 and being energized by the moving blades 111 is substantially perpendicular to the rotation axis. It is discharged in the direction. The discharge flow is redirected in the anti-suction direction of the rotating shaft by the side wall of the fan case 120 having an air flow guiding shape. The shape of the inner wall of the side wall is preferably a gentle curved surface so as not to obstruct the flow of airflow. The flow of the airflow flowing out from the discharge hole 123 of the fan case 120 is communicated with the intake side chamber 311a in contact with the temperature matching target 350. The air stored in the intake side chamber 311a is almost uniformly sent to the temperature matching target 350 to cool or heat parts such as a battery pack. In some cases, the electronic device unit 320 for controlling the temperature harmonizing target 350 is sibling in the temperature harmonizing target 350 space. The region facing the suction portion of the blower 100 is isolated from the intake side chamber 311a. The isolation wall 311 is separate from the fan case 120 and may be installed so that leakage does not occur between the fan case 120 and the isolation wall 311. The isolation wall 311 and the fan case 120 are integrally configured. Is also good.

The impeller 110 includes a rotation shaft of the motor 200, which is a rotation drive source, in a central portion, and is arranged on a surface perpendicular to the rotation axis in a substantially disk-shaped impeller disk 112 and one side of the impeller disk 112. Includes a plurality of rotor blades 111 erected on the side of the intake hole of the above. The impeller 110 includes a shroud 114. The mode of the shroud 114 is an annular plate body that covers each end of the moving blade 111 of the impeller 110 on the intake hole side.

The shape of the shroud 114 is funnel-shaped, morning glory-shaped or trumpet-shaped with a hole in the center. The shroud 114 has a configuration in which the wide mouth side of the shroud 114 faces the impeller disk 112 side and the narrowed mouth side of the shroud 114 faces the intake hole side. The outer peripheral end of the impeller disk 112 is provided with an inclined portion 113 that inclines in the air supply direction in order to reduce the blowing resistance against the flow of the air flow. In the present embodiment, the shape is such that priority is given to the efficiency of the blower, but a flat shroud is sufficiently effective, and for the sake of simplification of the manufacturing process, the function as a blower even if the shroud is omitted. Will fulfill.

Conventionally, when blowing air to a temperature-adjusted object, a method of arranging a blowing mechanism in the vicinity of a heating element has been adopted. However, as in the present embodiment, in an electric device in which a large number of heating elements are densely arranged with a large object to be temperature-controlled with respect to the housing, the ventilation resistance, that is, the pressure loss becomes high. Therefore, when the occupied volume of the temperature-adjusted object with respect to the housing is large, chamber regions are provided on the inflow surface and the outflow surface of the temperature-adjusted object, and the air is blown to the temperature-adjusted object substantially uniformly. The intake side chamber and the exhaust side chamber are often suppressed to the minimum area due to the miniaturization of electrical equipment. On the other hand, since the ventilation resistance of the housing is high, the ventilation mechanism is required to have a high output, and the ventilation mechanism naturally becomes large, and it is difficult to accommodate the ventilation mechanism in the housing. Therefore, in many cases, a blower mechanism is installed outside the housing, and the discharge hole of the blower and the inflow port of the housing are connected by a duct or the like to form a flow path. In this case, it is also difficult to miniaturize the electrical equipment including the temperature adjustment target and the temperature adjustment system.

On the other hand, the temperature adjustment unit 10 of the present embodiment adopts a centrifugal blower element having a high static pressure, so that sufficient cooling air can be ventilated even if the intake side chamber 311a and the exhaust side chamber 311b have a flat shape. can. The blower 100, which is a centrifugal blower element, may be provided with either or both of the intake side chamber 311a and the exhaust side chamber 311b. FIG. 1A shows a mode in which the blower 100, which is a centrifugal blower element, is installed on the intake side chamber 311a side.

Further, in the air conditioner of the present embodiment, the physique or the shape of details of the impeller 110 can be adjusted within a certain range without increasing the size of the housing 300. The air conditioner of the present embodiment can optimize the efficiency of the blower 100. Therefore, the air volume of the cooling air can be adjusted. In addition, some or all of the parts and parts in the housing, the exterior parts covering a part or all of the parts in the housing, the fan case, the drive source exterior covering the rotary drive source, and the like. It can be integrated and configured as a shared component 500. As a result, the shape of the flow path becomes smooth, and leakage flow and turbulent flow loss due to steps are suppressed.

FIG. 2 shows an example of the above-mentioned common component 500. When a plurality of intake chambers 501 are arranged for the blower 100 which is a centrifugal blower element, a branch duct portion 502 for branching the discharge flow of the blower is provided. In this case, the centrifugal blower element includes, in addition to the blower 100, a branch duct portion 502 that connects the blower 100 and each intake chamber 501. As shown in FIG. 2, in the present embodiment, the common component 500 that integrates the support of the housing, the cover of other components, the fan case, and the branch duct portion is used. The integrated shared component 500 smoothes the shape of the flow path and suppresses leakage flow and turbulent flow loss due to steps.

By including the temperature-adjusted object and the ventilation mechanism, the electric device can be miniaturized. As a result, when this electric device is mounted on a vehicle, a large interior space can be obtained. Therefore, the comfort of the passenger is improved.

The constituent members of the centrifugal blower element of the present embodiment are made of a metal or resin material, but are not particularly limited.

The material of the stator winding of the motor which is the rotational drive source is copper, copper alloy, aluminum or aluminum alloy, but is not particularly limited.

As described above, the temperature adjustment unit 10 of the present embodiment includes an impeller 110, a rotation drive source, a fan case 120, a housing 300, a branch duct portion 502, and an intake chamber 501. The impeller 110 includes a rotation shaft 112a in the center, and is located on the side of a substantially disk-shaped impeller disc 112 arranged on a plane perpendicular to the rotation shaft and an intake hole 122 on one side of the impeller disc 112. It has a plurality of moving blades 111 to be erected. The rotational drive source includes the shaft 210 and is connected to the impeller 110 via the shaft 210. The fan case 120 includes a substantially cylindrical side wall 121 formed around a rotating shaft 112a, a circular intake hole 122 centered on the rotating shaft 112a on a plane perpendicular to the rotating shaft 112a, and a rotating shaft 112a. It has a discharge hole 123 located on the side opposite to the intake hole 122 with respect to the side wall 121 in the direction along the above. The housing 300 includes an outer surface 302 to which the fan case 120 is attached, and a temperature matching target 350 is housed inside. The branch duct portion 502 branches the air flowing from the discharge hole 123.

As a result, it is possible to provide a small temperature control unit 10 capable of efficiently blowing air even to the housing 300 containing the parts arranged at high density.

Further, the inner wall surface of the fan case 120 is a side wall of the fan case 120 that changes the direction of the centrifugal wind, in which the air taken in from the intake hole 122 is output to the entire circumference in the outer peripheral direction of the impeller 110 by the rotation of the impeller 110. Includes an airflow guidance shape of 121, a directional component parallel to the rotation shaft 112a of the impeller 110, and a scroll shape in which the distance from the rotation shaft 112a increases toward the discharge hole 123 with respect to the rotation direction of the impeller 110. It may have a curved shape.

Further, the impeller 110 may include a shroud 114 which is an annular plate body which covers each end of the moving blade 111 on the intake hole 122 side.

Further, the rotary drive source may be an electric motor 200.

Further, the centrifugal blower element may include an impeller 110 and a fan case 120.

Further, the stator winding of the motor which is the rotational drive source may include copper, a copper alloy, aluminum, or an aluminum alloy.

Also, the impeller may contain at least one of metal and resin.

Further, the temperature adjustment unit 10 may include a centrifugal blower element including an impeller 110 and a fan case 120.

(Embodiment 2)
FIG. 3 is a cross-sectional view showing the temperature harmonizing unit 10 of the second embodiment of the present invention. The second embodiment has substantially the same configuration as the first embodiment. The difference is that, in the first embodiment, a part or all of the component exterior body that covers a part or all of the internal parts group of the housing 300, the drive source exterior body that covers the fan case 120 and the rotary drive source, and the like. In the second embodiment, the component exterior, the fan case 120, and the rotational drive source that cover a part or all of the internal component group of the housing 300 are integrated. The drive source exterior body that covers the vehicle is not integrated, and the component exterior body that covers a part or all of the parts inside the housing 300, the fan case 120, the drive source exterior body that covers the rotary drive source, and the like. Each part is composed of individual parts. Therefore, a gap or a step is generated in the component exterior body that covers a part or all of the parts group inside the housing 300, the drive source exterior body that covers the fan case 120 and the rotary drive source, and the connection portions of these components with each other. Therefore, the output is reduced due to leakage flow, turbulent flow, and the like. For example, in the second embodiment, since the gap 503 is provided, the air leaks indicated by the arrow 504 with the gap 503 as the flow path. As described above, the second embodiment is inferior to the first embodiment in that the output is reduced due to the leaked flow of the air supplied, the turbulent flow, and the like. However, in other respects, it is the same as that of the first embodiment, and is not inferior to that of the first embodiment.

Leakage flow, turbulent flow, etc. can be reduced by covering the gaps and steps generated in the connection portion by applying a sealing agent such as a resin filler or adding packing.

As described above, the temperature adjustment unit 10 of the present embodiment includes a drive source exterior body that covers the fan case 120 and the rotary drive source, and a component exterior body that covers at least a part of the parts group incorporated in the housing 300. May be provided. Further, the connection portion between the drive source exterior body and the component exterior body may have at least one of a gap and a step.

Further, at least one of a sealant and a packing may be provided at the connection portion between the drive source exterior body and the component exterior body.

(Embodiment 3)
FIG. 4 is a cross-sectional view showing the temperature harmonizing unit 10 according to the third embodiment of the present invention. The temperature control unit 10 of FIG. 4 shows a mode in which the fan case 120 is provided with a substantially cylindrical side wall 121 centered on a rotation axis. In the present embodiment, the discharge flow from the impeller 110 (centrifugal fan) is largely bent in the axial direction from the radial direction, and is discharged to the anti-suction side in the rotation axis direction. In such a fan case, a part of the wall portion of the housing 300 and the fan case 120 are integrated. Further, in the present embodiment, the isolation wall 311 in the first embodiment is configured to serve as a part of the wall portion of the housing 300. Therefore, according to the configuration of the present embodiment, the body size (volume) of the temperature adjustment unit 10 can be reduced.

If the dimension of the side wall 121 of the fan case 120 in the rotation axis direction is set short, the radial component of the discharge flow from the impeller increases. On the other hand, if the dimension of the side wall 121 of the fan case 120 in the rotation axis direction is set short, the amount of the discharge flow being redirected by the fan case increases, so that the axial component increases. As described above, the ratio of the axial component and the radial component of the discharge flow can be arbitrarily adjusted by the axial height of the side wall 121 of the fan case 120. With the forward fan, the static pressure does not rise with the fan alone, and the static pressure is recovered by the fan case, but with the rearward fan, the blade length is long in the radial direction, so the flow velocity difference between the inlet and outlet of the blade is large, and the fan is unique. The static pressure can be increased. Therefore, it is effective to combine it with a fan case having a substantially cylindrical side wall centered on the rotation axis of the impeller.

As described above, the inner wall surface of the fan case 120 of the present embodiment is a substantially cylindrical shape including a directional component parallel to the rotation shaft 112a of the impeller 110 and an arc shape centered on the rotation shaft 112a of the impeller 110. It may have a shape.

(Embodiment 4)
FIG. 5 is a cross-sectional view showing the temperature harmonizing unit 10 of the fourth embodiment of the present invention. The configuration of the fourth embodiment is substantially the same as the configuration of the third embodiment. The difference is that the configuration does not include a fan case from the configuration of the third embodiment. In other words, in the configuration of the third embodiment, it can be said that the dimension of the side wall 121 of the fan case 120 in the rotation axis direction is set to zero.

In the configuration of the fourth embodiment, the discharge flow from the impeller 110 directly collides with the inner wall of the housing 300. Therefore, as compared with the third embodiment, turbulence is likely to occur at the corners of the housing, and loss and noise increase. The fourth embodiment is inferior to the third embodiment in that turbulence is likely to occur at the corners of the housing 300 and the loss and noise increase. However, in other respects, it is the same as that of the third embodiment, and is not inferior to that of the third embodiment. Further, also in the fourth embodiment, the body size (volume) of the temperature adjustment unit 10 can be miniaturized as in the third embodiment.

FIG. 8A is a perspective view showing a mode when a diffuser is added to the impeller according to the first to fourth embodiments. FIG. 8B is a front perspective view showing the diffuser according to the first to fourth embodiments. FIG. 8C is a rear perspective view showing the diffuser according to the first to fourth embodiments. In each embodiment, in addition to the configuration of the impeller 110, a configuration in which a diffuser 115 is further added is adopted. The diffuser 115 is arranged between the impeller 110 and the electric motor 200 which is a rotational drive source. The diffuser 115 is provided with a substantially disk-shaped diffuser plate 116 arranged on a surface perpendicular to the rotation axis of the motor 200, and an impeller standing on the side of an intake hole on one side of the diffuser plate 116. A plurality of stationary blades 117 for rectifying the centrifugal wind discharged from the 110 are provided.

The diffuser 115 exerts an action of increasing the pressure while decelerating the output air (centrifugal air) from the impeller 110 between the blades of the stationary blades 117 of the diffuser 115, and increases the pressure of the output air from the blower. FIG. 8A shows a mode (perspective view) when the above-mentioned diffuser 115 is added to the impeller 110. Further, regarding the mode of the diffuser described above, FIG. 8B shows a front perspective view. Similarly, FIG. 8C shows a rear perspective view. Although the action of rectifying the centrifugal wind is impaired, a configuration in which only the impeller 110 is used except for the diffuser 115 may be adopted in each embodiment. For example, when the action of rectifying the centrifugal wind by the diffuser 115 is excessive, it is also useful to remove the diffuser 115 to reduce the specifications.

As described above, the temperature adjustment unit of the present embodiment decelerates the centrifugal air output from the impeller 110, and the pressure of the output air from the centrifugal blower element including the impeller 110 and the fan case 120. The diffuser 115 may be provided. Also, the diffuser 115 may contain at least one of metal and resin.

(Comparison between the present invention and a comparative example)
Here, the temperature adjustment unit 10 shown in the first embodiment of the present invention is compared with the temperature adjustment unit 1010 of the comparative example shown in FIG. The temperature control unit 1010 of the comparative example has a scroll casing 1120 which is also used in a conventional in-vehicle air conditioner.

A forward fan 400 is mounted inside the scroll casing 1120. The positive fan 400 is also called a sirocco fan. The forward fan 400 discharges the air sucked from the front to the back of FIG. 14 toward the circumferential direction of the forward fan 400. The air flow 301 discharged from the forward fan 400 flows into the discharge hole 1123 along the side wall 1121 of the scroll casing 1120.

Further, it will be described in detail.

In the scroll casing 1120 shown as a comparative example, the air discharged from the forward fan 400 is integrated in the circumferential direction. In the scroll casing 1120, the distance from the rotating shaft 1112a to the side wall 1121 gradually increases. Therefore, the air flow 301 discharged from the forward fan 400 is biased toward the outer peripheral surface 1121a side of the side wall 1121. Therefore, in order to make the air flow 301 supplied into the housing 310 uniform, it is necessary to install a rectifying mechanism 1310 such as a duct 1311 inside the housing 310.

However, in the centrifugal blower 1100 using the forward fan 400, the distance L from the center of gravity G of the centrifugal blower 1100 to the discharge hole 1123 becomes long. Therefore, when the centrifugal blower 1100 is attached to the housing 310, the temperature adjustment unit 1010 becomes unbalanced and unstable. Therefore, the temperature adjustment unit 1010 may be fixed to a surrounding member via the mounting portion 1124. In this case, the mounting portion 1124 is required to have various shape changes in order to be suitable for the environment in which the temperature adjustment unit 1010 is used.

In particular, when the rectifying mechanism 1310 is configured separately from the housing 310, it is necessary to consider the distance from the center of gravity G to the rectifying mechanism 1310. Generally, the distance from the center of gravity G to the rectifying mechanism 1310 becomes long. Therefore, the balance of the temperature control unit becomes worse.

On the other hand, as shown in FIG. 1A, according to the temperature adjustment unit 10 in the first embodiment, the air flow 301 discharged from the blower 100 can provide an air flow with less bias to the inside of the housing 300. Therefore, the temperature of the secondary battery, which is the object of temperature adjustment, can be effectively adjusted in the housing 300 without attaching the rectifying mechanism. Therefore, the temperature adjustment unit 10 in the first embodiment does not require a rectifying mechanism such as a duct. That is, the temperature adjustment unit 10 according to the first embodiment can reduce the pressure loss and the friction loss in the air flow 301, which are conventionally generated by attaching the rectifying mechanism. As a result, the temperature adjustment unit 10 in the first embodiment is obtained by improving the efficiency of the blower 100, simplifying and downsizing the structure of the temperature adjustment unit 10, and reducing the number of parts constituting the temperature adjustment unit 10. Cost reduction can be expected.

Further, the temperature harmonizing unit 10 in the first embodiment can be made smaller than the temperature harmonizing unit 1010 shown in the comparative example. In the temperature adjustment unit 1010 shown in the comparative example, a space capable of securing the diameter dimension L of the forward fan 400 is required from the housing 310 to the outside, but in the first embodiment, the volume corresponding to the above space is required. Does not need.

As described above, in the temperature adjustment unit of the present embodiment, the temperature adjustment target 350 may be a secondary battery.

Further, the temperature matching target 350 may be a power conversion device.

(Comparison between forward-looking fans and backward-looking fans)
FIG. 6A is a diagram showing the rotor blade shape (blade cross-sectional shape on the plane perpendicular to the rotation axis of the forward fan) of the impeller used for the temperature adjustment unit 1010 in the comparative example. FIG. 6B is a diagram showing the rotor blade shape (blade cross-sectional shape on the plane perpendicular to the rotation axis of the rearward fan) of the impeller 110 used in the temperature-harmonizing unit 10 in the present invention. FIG. 7A is a diagram showing an absolute outflow angle by enlarging a main part of the moving blade (blade shape of a forward fan) shown in FIG. 6A. Similarly, FIG. 7B is a diagram showing an absolute outflow angle by enlarging a main part of the moving blade (blade shape of the rearward fan) shown in FIG. 6B. The schematic drawings shown in FIGS. 7A and 7B represent a comparison of velocity triangles with absolute outflow angles at the fan blade outlets. When at least a part of the rearward fan having a convex shape in the forward direction of rotation is used, the absolute outflow angle α2 is larger than the absolute outflow angle α1 when the forward fan is used, and is close to 90 degrees. That is, since the radial component of the flow becomes large, the flow can reach a long distance, and it is possible to blow air to a temperature-harmonized object larger than the outer diameter of the fan case.

FIG. 7C is a graph showing the efficiency characteristics of the impeller used in the temperature harmonizing unit according to the embodiment of the present invention and the impeller of the comparative example. FIG. 7D is a graph showing the relationship between the flow coefficient and the pressure coefficient characteristic of the impeller used in the temperature adjustment unit according to the embodiment of the present invention and the impeller of the comparative example. FIG. 7E is a graph showing the relationship between the air volume and the air pressure of the impeller used in the temperature harmonizing unit according to the embodiment of the present invention and the impeller of the comparative example.

In general, a forward fan has a large deceleration rate of relative velocity between blades and a high secondary flow loss. Therefore, forward-facing fans are less efficient than backward-facing fans.

FIG. 7D shows the relationship between the flow coefficient and the pressure coefficient for the forward fan and the backward fan.

As shown in FIG. 7D, the forward fan has a higher work coefficient than the backward fan. However, when operated at a low flow rate, the forward fan has an unstable region 410 in which the characteristics of the forward fan change from a downward-sloping pressure coefficient to an upward-sloping pressure coefficient.

On the other hand, the backward fan has a lower work coefficient than the forward fan. However, the rearward fan does not have an unstable region in which the characteristics change like the forward fan. Therefore, the rearward fan can be used stably in the entire area. Therefore, the rearward fan can obtain a high output by rotating at high speed.

6A and 6B show the cross-sectional shapes of the moving blades on the plane perpendicular to the rotation axis 112a of the fan for the forward fan illustrated as a comparative example and the rear fan adopted in each embodiment of the present invention. 7A and 7B show a comparison of velocity triangles at the blade outlets of the forward and backward fans.

As shown in FIGS. 6A and 7A, in the forward fan, the cross-sectional shape of the moving blade 1111 in the direction intersecting the rotation shaft 112a is an arc shape that becomes concave in the direction in which the impeller disc 1112 rotates. The rotor blade 1111 is located behind the outer peripheral side end portion 1111b whose inner peripheral side end portion 1111a located on the rotating shaft 112a side is located on the anti-rotating shaft side.

When the forward fan is rotated, the outflow angle α1 of the air discharged from each rotor blade 1111 is an angle close to the tangential direction on the outer circumference of the impeller disk 1112. Therefore, when a forward fan is used, it is difficult for the air flow to reach a long distance because the component of the impeller disk 1112 in the radial direction is small.

On the other hand, as shown in FIGS. 6B and 7B, in the rearward fan, the cross-sectional shape of the moving blade 111 in the direction intersecting the rotation axis 112a is an arc shape that is convex in the direction in which the impeller disc 112 rotates. .. The rotor blade 111 is located in front of the outer peripheral side end portion 111b whose inner peripheral side end portion 111a located on the rotating shaft 112a side is located on the anti-rotating shaft side.

When the rearward fan is rotated, the absolute outflow angle α2 of the air discharged from each of the moving blades 111 is an angle greatly opened from the tangential direction on the outer circumference of the impeller disk 112. Therefore, when a rearward fan is used, the air flow has a large component toward the radial direction of the impeller disk 112, so that the air flow can reach a long distance.

As shown in FIG. 7E, the static pressure of the forward-facing fan does not increase with the fan alone. Therefore, when using a forward-facing fan, static pressure recovery by the fan case is realized by using a scroll casing or the like.

On the other hand, as shown in FIG. 6B, the rearward fan has a long moving blade 111 in the radial direction of the impeller disk 112. Therefore, when the impeller 110 rotates, the flow velocity difference of the flowing air becomes large between the inner peripheral side end 111a which is the inlet of the moving blade 111 and the outer peripheral side end 111b which is the outlet of the moving blade 111. Therefore, as shown in FIG. 7E, the backward fan can increase the static pressure by the fan itself. Therefore, if the temperature adjustment unit according to each embodiment of the present invention is used, the operating point changes from A to B as the mounting density of the temperature-adjusted object housed in the housing 300 increases.

By utilizing this characteristic, the temperature control unit in each embodiment of the present invention is miniaturized.

As described above, in the temperature adjustment unit of the present embodiment, the trailing edge of the moving blade 111 is located on the outer peripheral side of the impeller disk 112, and the leading edge of the moving blade 111 is on the central side of the rotating shaft 112a. It is located on the forward side of the impeller 110 in the rotational direction with respect to the trailing edge. As a result, the temperature adjustment unit can be miniaturized.

Further, the trailing edge of the moving blade 111 is located on the outer peripheral side of the impeller disk 112, the leading edge of the moving blade 111 is located on the center side of the rotating shaft 112a, and is located on the front side in the rotation direction of the impeller 110 with respect to the trailing edge. However, the moving blade 111 may have a convex curved surface on the front side in the rotation direction of the impeller 110. As a result, the radial component of the air flow becomes large, so that the flow can reach a long distance, and it is possible to blow air to a temperature-harmonized object larger than the outer diameter of the fan case.

(Embodiment 5)
FIG. 9 is a system configuration diagram showing an outline of the temperature harmonization system 20 according to the fifth embodiment of the present invention. FIG. 10 is a system configuration diagram showing an outline of another temperature control system 20a according to the fifth embodiment of the present invention. FIG. 11 is a system configuration diagram showing an outline of still another temperature harmonization system 20b according to the fifth embodiment of the present invention.

Further, FIG. 12 is a schematic diagram showing an outline of the vehicle 30 according to the fifth embodiment of the present invention. FIG. 13 is a schematic diagram showing an outline of another vehicle 30a according to the fifth embodiment of the present invention.

The same components as those of the temperature harmonizing unit in the first embodiment are designated by the same reference numerals, and the description thereof will be incorporated.

As shown in FIGS. 9 to 11, the temperature harmonization system according to the fifth embodiment of the present invention has the following configuration.

That is, as shown in FIG. 9, the temperature adjustment system 20 according to the fifth embodiment of the present invention includes a first temperature adjustment unit 711a, a second temperature adjustment unit 711b, and a plurality of ducts 700, 700a, 700b. It includes 700c and 700d, a switching unit 701, a rotation speed control unit 702, and a control unit 703.

As the first temperature adjustment unit 711a and the second temperature adjustment unit 711b, the temperature adjustment unit 10 described in the first embodiment can be used. FIG. 9 shows the temperature control unit described with reference to FIG. 1A in the first embodiment.

The ducts 700b and 700c, which are a part of the plurality of ducts, connect the exhaust hole 125a of the first temperature adjustment unit 711a and the intake hole 122b of the second temperature adjustment unit 711b. The intake hole 122b takes in air into the housing. The exhaust hole 125a exhausts the intake air to the outside of the housing.

Alternatively, the ducts 700 and 700a, which are a part of the plurality of ducts, connect the intake hole 122a of the first temperature adjustment unit 711a and the exhaust hole 125b of the second temperature adjustment unit 711b.

The switching unit 701 switches the state in which the ducts 700, 700a, and 700d are connected.

The rotation speed control unit 702 controls at least one of the rotation speed of the electric motor 200a of the first temperature adjustment unit 711a and the rotation speed of the electric motor 200b of the second temperature adjustment unit 711b.

The control unit 703 controls the switching unit 701 and the rotation speed control unit 702. The control unit 703 controls the air flow path or the air volume of the air flowing through the plurality of ducts 700, 700a, 700b, 700c, and 700d.

Further, as shown in FIG. 10, the temperature adjustment system 20a according to the fifth embodiment of the present invention includes a first temperature adjustment unit 720a, a second temperature adjustment unit 720b, and a plurality of ducts 700, 700e, and 700f. A switching unit 701, a rotation speed control unit 702, and a control unit 703 are provided.

As the first temperature adjusting unit 720a and the second temperature adjusting unit 720b, the temperature adjusting unit described in the first embodiment can be used. FIG. 10 shows the temperature control unit described with reference to FIG. 1A in the first embodiment.

The ducts 700 and 700e, which are a part of the plurality of ducts, connect the intake hole 122a of the first temperature adjustment unit 720a and the intake hole 122b of the second temperature adjustment unit 720b.

Alternatively, the plurality of ducts 700, 700e, and 700f may connect the exhaust hole 125a included in the first temperature adjusting unit 720a and the exhaust hole 125b included in the second temperature adjusting unit 720b.

The switching unit 701 switches the connection state of the plurality of ducts 700, 700e, and 700f.

The rotation speed control unit 702 controls at least one of the rotation speed of the electric motor 200a of the first temperature adjustment unit 720a and the rotation speed of the electric motor 200b of the second temperature adjustment unit 720b.

The control unit 703 controls the switching unit 701 and the rotation speed control unit 702. The control unit 703 controls the air flow path or the air volume of the air flowing through the plurality of ducts 700, 700e, and 700f.

Alternatively, as shown in FIG. 11, the temperature adjustment system 20b according to the fifth embodiment of the present invention includes the temperature adjustment unit 10a, the first ducts 730, 730a, and 730b, and the second ducts 730c, 730d. It includes switching units 701a and 701b, a rotation speed control unit 702, and a control unit 703.

As the temperature adjustment unit 10a, the temperature adjustment unit described in the first embodiment can be used. FIG. 11 shows the temperature control unit described with reference to FIG. 1A in the first embodiment.

The first ducts 730, 730a, and 730b allow air to flow without passing through the temperature adjustment unit 10a.

The second duct 730c allows air supplied to the temperature adjustment unit 10a to flow. The second duct 730d allows air discharged from the temperature adjustment unit 10a to flow. Air is taken in from the intake hole 122. Air is exhausted from the exhaust hole 125.

The first ducts 730, 730a, 730b and the second ducts 730c, 730d are connected to the switching portions 701a and 701b. The switching units 701a and 701b switch the air flow.

The rotation speed control unit 702 controls at least the rotation speed of the electric motor 200 included in the temperature adjustment unit 10a.

The control unit 703 controls the switching units 701a and 701b and the rotation speed control unit 702. The control unit 703 controls the flow path of air or the air volume of air flowing in the first ducts 730, 730a, and 730b and in the second ducts 730c, 730d.

FIG. 12 is a schematic diagram showing an outline of the vehicle 30 according to the fifth embodiment of the present invention. The vehicle 30 includes a power source 800, drive wheels 801, a traveling control unit 802, and a temperature adjustment system 803.

The drive wheels 801 are driven by the power supplied from the power source 800. The travel control unit 802 controls the power source 800. The temperature adjustment system 803 can utilize the temperature adjustment systems 20, 20a, and 20b described above.

Further, FIG. 13 is a schematic view showing an outline of another vehicle 30a according to the fifth embodiment of the present invention. The vehicle 30a includes a power source 800, drive wheels 801, a traveling control unit 802, and a temperature adjustment unit 804.

The drive wheels 801 are driven by the power supplied from the power source 800. The travel control unit 802 controls the power source 800. As the temperature adjustment unit 804, each temperature adjustment unit described in the first embodiment can be used.

This will be described in more detail with reference to FIGS. 12 and 13.

As shown in FIG. 12, the temperature adjustment system 803 according to the fifth embodiment of the present invention is mounted on the vehicle 30. When the temperature adjustment system 803 is mounted on the vehicle 30, if the following configuration is adopted, cooling and heating of the temperature adjustment target can be effectively performed.

That is, in the temperature adjustment system 803 according to the fifth embodiment, a plurality of temperature adjustment units according to the above-described embodiment of the present invention can be used. The temperature adjustment system 803 includes a plurality of ducts of each temperature adjustment unit that connect the intake holes and the ventilation holes. The temperature adjustment system 803 includes a switching unit that switches the amount of airflow flowing in the duct or the path for flowing the airflow.

For example, when the air temperature on the intake side is lower than room temperature, a plurality of temperature control units are connected by a duct. With this configuration, the temperature-adjusted object can be efficiently temperature-harmonized.

Further, the temperature adjustment system 803 according to the fifth embodiment has a plurality of ducts connected to the intake holes and the ventilation holes of the temperature adjustment unit. The temperature adjustment system 803 includes a switching unit that switches the amount of airflow flowing in the duct or the path for flowing the airflow.

For example, a plurality of ducts are connected to the intake holes and the ventilation holes of the temperature control unit in the present embodiment.

As shown in FIG. 11, one end of the duct 730 is connected to the outside of the vehicle, and the other end is connected to the switching portion 701a. One end of the duct 730a is connected to the switching portion 701a, and the other end is connected to the switching portion 701b. Further, one end of the duct 730c is connected to the switching portion 701a, and the other end is connected to the intake hole 122 of the temperature adjustment unit 10a. One end of the duct 730d is connected to the exhaust hole 125 of the temperature adjustment unit 10a, and the other end is connected to the switching portion 701b.

In this configuration, when the outside air temperature of the vehicle 30 is within a predetermined range, the air outside the vehicle can be directly taken into the vehicle 30 through the duct. When the outside air temperature of the vehicle 30 is out of the predetermined range, the air outside the vehicle can be taken into the vehicle 30 through the duct and the temperature adjustment unit.

That is, the temperature adjustment system 803 can switch the air to be provided to the temperature adjustment target according to the outside air temperature of the vehicle. Therefore, the temperature harmonization system 803 can realize the temperature harmonization of the object to be temperature-harmonized while realizing efficient and energy saving.

In the temperature adjustment system 803, the threshold value of the external air temperature of the vehicle for switching the duct may be appropriately set according to the purpose. Further, in the temperature adjustment system 803, the intake of air outside the vehicle for switching the duct can be switched by atmospheric pressure instead of the air temperature outside the vehicle.

Further, the description of the form shown in FIG. 13 can be incorporated by replacing the temperature harmonization system 803 of the form shown in FIG. 12 with the temperature harmonization unit 804.

In each of the above-described embodiments, the temperature adjusting device for the battery of the hybrid car has been described as an example, but the present invention is not limited to this. The temperature adjustment unit according to the embodiment of the present invention can also be applied to temperature adjustment of an engine control unit, an inverter device, an electric motor, and the like.

As described above, the temperature control unit of the present embodiment includes the control unit 703 of the centrifugal blower element at least on either the inside or the outside of the housing.

Further, the temperature adjustment unit may further have an exhaust hole 125 for exhausting the air introduced into the housing to the outside of the housing 300.

Further, in the temperature adjustment system 20 of the present embodiment, the exhaust provided by the first temperature adjustment unit 711a and the second temperature adjustment unit 711b and the first temperature adjustment unit 711a described in the first embodiment, respectively. A plurality of ducts 700, 700a, 700b, 700c, and 700d connecting the holes 125a or the intake holes 122a and the intake holes 122b or the exhaust holes 125b included in the second temperature adjustment unit 711b are provided. Further, the temperature adjustment system 20 has a switching unit 701 for switching a state in which a plurality of ducts are connected, and at least the rotation speed of the rotation drive source of the first temperature adjustment unit 711a, or the second temperature adjustment unit 711b. 702 is a rotation speed control unit that controls one of the rotation speeds of the rotation drive source. Further, the temperature adjustment system 20 includes a control unit 703 that controls the switching unit 701 and the rotation speed control unit 702 to control the flow path of air flowing through the plurality of ducts or the air volume of the air. As a result, cooling and heating of the temperature-adjusted object are effectively performed.

Further, the temperature adjustment system 20b of the present embodiment includes the temperature adjustment unit 10a described in the first embodiment, the first ducts 730, 730a, and 730b for flowing air without passing through the temperature adjustment unit 10a, and the temperature. The second ducts 730c and 730d are provided for flowing the air supplied to the harmonizing unit 10a or flowing the air discharged from the temperature harmonizing unit 10a. Further, in the temperature adjustment system 20b, the first ducts 730, 730a, 730b and the second ducts 730c, 730d are connected to each other, and the switching unit 701a for switching the air flow and the rotation of the rotation drive source of the temperature adjustment unit 10a. It includes a rotation speed control unit 702 that controls the number, and a control unit 703 that controls the switching unit 701a and the rotation speed control unit 702 to control the flow path of air flowing through a plurality of ducts or the air volume of air. .. As a result, cooling and heating of the temperature-adjusted object are effectively performed.

Further, the vehicle 30 of the present embodiment describes the power source 800, the drive wheels 801 driven by the power supplied from the power source 800, the traveling control unit 802 that controls the power source 800, and the present embodiment. The temperature adjustment system 803 of the above is provided. As a result, cooling and heating of the temperature-adjusted object are effectively performed.

Further, the vehicle 30a of the present embodiment describes the power source 800, the drive wheels 801 driven by the power supplied from the power source 800, the traveling control unit 802 that controls the power source 800, and the first embodiment. It is provided with a temperature adjustment unit 804. As a result, cooling and heating of the temperature-adjusted object are effectively performed.

The temperature control unit and temperature control system of the present invention can be miniaturized, have high output, and have high efficiency, and are useful for in-vehicle battery temperature control applications and the like. Further, mounting the temperature control unit and the temperature control system of the present invention on a vehicle can suppress excessive vibration and noise.

10 Temperature Harmony Unit 10a Temperature Harmony Unit 20 Temperature Harmony System 20a Temperature Harmony System 20b Temperature Harmony System 30 Vehicle 30a Vehicle 100 Blower 110 Impeller (Centrifugal Fan)
111 Moving blade 111a Inner peripheral end 111b Outer peripheral end 112 Imperator disk 112a Rotating shaft 113 Inclined part 114 Shroud 115 Diffuser 116 Diffuser plate 117 Static wing 120 Fan case α1 Absolute outflow angle α2 Absolute outflow angle 121 Side wall 122 Intake hole 122a Intake hole 122b Intake hole 123 Discharge hole 125 Exhaust hole 125a Exhaust hole 125b Exhaust hole 200 Electric motor 200a Electric motor 200b Electric motor 210 Shaft 300 Housing 301 Air flow 302 Outer surface 310 Housing 311 Isolation wall 311a Intake side chamber 311b Electronic equipment part 350 Temperature adjustment target 400 Forward fan 410 Unstable area 500 Common parts 501 Intake chamber 502 Branch duct part 503 Gap 504 Arrow 700 Duct 700a Duct 700b Duct 700c Duct 700d Duct 700e Duct 700f Duct 701 Switching part 701 Switching unit 702 Rotation speed control unit 703 Control unit 711a First temperature adjustment unit 711b Second temperature adjustment unit 720a First temperature adjustment unit 720b Second temperature adjustment unit 730 First duct 730a First duct 730b First 1 Duct 730c 2nd Duct 730d 2nd Duct 800 Power Source 801 Drive Wheel 802 Travel Control Unit 803 Temperature Harmony System 804 Temperature Harmony Unit 1010 Temperature Harmony Unit 1111 Moving Wing 1111a Inner Peripheral End 1111b Outer Outer End 1112 Impeller disk 1120 Scroll casing 1121 Side wall 1121a Inner peripheral surface 1123 Discharge hole 1124 Mounting part 1310 Rectification mechanism 1311 Duct

Claims (2)

A substantially disk-shaped impeller disk that includes a rotation axis in the center and is arranged on a surface perpendicular to the rotation axis.
An impeller having a plurality of moving blades erected on the side of an intake hole on one side of the impeller disk, and an impeller.
A rotational drive source that includes a shaft and is connected to the impeller via the shaft.
With a substantially cylindrical side wall formed around the axis of rotation,
A circular intake hole centered on the rotation axis on a plane perpendicular to the rotation axis,
A fan case having a discharge hole located on the side wall in a direction along the rotation axis, and a fan case.
A housing that includes an outer surface to which the fan case is attached, and a housing that houses a temperature-adjusted object inside.
A branch duct portion that branches the air flowing from the discharge hole and
A plurality of intake chambers in which the air is collected on the inflow surface of the temperature-adjusted object are provided.
The intake hole, the plurality of intake chambers, and the temperature-controlled object are separated from each other by an isolation wall.
A temperature control unit further provided with an exhaust hole for exhausting the air introduced into the housing to the outside of the housing is provided.
It has two temperature control units.
Of the respective temperature control units, one is used as the first temperature control unit and the other is used as the second temperature control unit.
A plurality of ducts connecting the exhaust hole or the intake hole of the first temperature adjusting unit and the intake hole or the exhaust hole of the second temperature adjusting unit.
A switching unit that switches the state in which the plurality of ducts are connected, and
A rotation speed control unit that controls at least one of the rotation speed of the rotation drive source of the first temperature adjustment unit and the rotation speed of the rotation drive source of the second temperature adjustment unit.
A control unit that controls the switching unit and the rotation speed control unit to control the flow path of air flowing through the plurality of ducts or the air volume of the air.
A temperature control system equipped with. Power source and
The drive wheels driven by the power supplied from the power source,
A traveling control unit that controls the power source,
A vehicle comprising the temperature adjustment system according to claim 1.

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