Radiator assembly, lubricating and cooling system, wind generating set and wind field

Abstract

The utility model provides a radiator assembly, a lubricating and cooling system, a wind generating set and a wind farm, the radiator assembly comprises a radiator and a bypass channel, the radiator comprises a fluid inflow connector, a fluid outflow connector and a radiating core body, and a radiating channel is arranged in the radiating core body; an inlet and an outlet of the heat dissipation channel are correspondingly communicated with the fluid inflow connector and the fluid outflow connector respectively. The bypass channel communicates between the fluid inflow connector and the fluid outflow connector, and the bypass channel is constructed to be capable of being conducted under the condition that the temperature is lower than a first preset temperature so that fluid can pass through the bypass channel. By additionally arranging the bypass channel which can be conducted in a low-temperature environment for the radiator, a channel required by backflow can be provided for a lubricant in a low-temperature state, heat of the lubricant flowing through the bypass channel is transferred to the heat dissipation channel by means of heat radiation, and the residual lubricant solidified in the heat dissipation channel is melted, so that the two purposes are achieved, and the heat dissipation efficiency is improved. The problem of oil trapping in related technologies is solved, and the damage risk is reduced.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the field of wind power generation, and more particularly, to a radiator assembly, a lubrication cooling system, a wind turbine generator unit and a wind farm. BACKGROUND

[0002] Wind power is gradually widely used as a clean energy. In order to control the cost, the gear box cooling technology of the wind turbine generator unit starts to change from the original water cooling technology to the direct air cooling technology, and the direct air cooling technology of the gear box will become the development trend in the future.

[0003] At the same time, with the continuous increase of the power of the onshore wind turbine generator unit, the operating environment temperature range of the unit is wider and wider, and the low temperature environment can reach below-30℃. Therefore, the application of the gear box in the low temperature environment must be solved when the direct air cooling technology of the gear box is used. Whether the gear box cooling lubrication system can reliably operate in the low temperature environment determines the power generation of the unit and the reliability of the gear box, which is crucial for the safe operation of the unit.

[0004] Specifically, in the low temperature environment, if the direct air cooling technology is used, the radiator is in the outdoor, which will cause the oil in the radiator to solidify and block the heat dissipation channel after the unit is stopped for a certain period of time. When starting again, the lubricating oil flowing into the radiator cannot flow out of the radiator in a short time, so that the system pipeline is in the "oil trapped" state, the gear box is not lubricated and cooled, and there is a risk of short-term over-temperature operation damage. CONTENT OF THE INVENTION

[0005] Therefore, how to reduce the blockage of the radiator in the low temperature environment is crucial for the safe operation of the wind turbine generator unit.

[0006] In one general aspect, there is provided a radiator assembly, comprising a radiator and a bypass channel, wherein the radiator comprises: a fluid inflow interface; a fluid outflow interface; a radiator core body, the radiator core body is provided with a heat dissipation channel, the inlet and outlet of the heat dissipation channel correspondingly communicate with the fluid inflow interface and the fluid outflow interface respectively; the bypass channel is communicated between the fluid inflow interface and the fluid outflow interface, and the bypass channel is configured to be conductive when the temperature is lower than a first preset temperature, so as to make the fluid pass through the bypass channel.

[0007] Optionally, the number of the heat dissipation channels is at least one, and the cross-sectional area of each heat dissipation channel is smaller than the cross-sectional area of the bypass channel.

[0008] Optionally, the heat sink assembly further comprises a temperature control valve connected in series between the fluid inflow interface and the inlet of the bypass channel, the temperature control valve being configured to open when the temperature is lower than a first preset temperature, so that the fluid inflow interface and the bypass channel are connected through the temperature control valve.

[0009] Optionally, the temperature control valve is further configured to increase the valve opening degree as the temperature decreases when the temperature is lower than the first preset temperature and higher than a second preset temperature, and the valve is fully opened when the temperature is lower than or equal to the second preset temperature, wherein the first preset temperature is higher than the second preset temperature.

[0010] Optionally, the heat sink assembly further comprises a pressure valve, an inlet of the pressure valve being connected to the fluid inflow interface, and a pressure relief channel being connected between an outlet of the pressure valve and the fluid outflow interface.

[0011] Optionally, the bypass channel and the pressure relief channel at least partially overlap.

[0012] Optionally, the temperature control valve and the pressure valve are integrated into an integrated structure.

[0013] Optionally, the pressure valve is provided with an axial channel and a radial channel intersecting with each other, one end of the axial channel being opened as the inlet of the pressure valve and connected to the fluid inflow interface, the radial channel penetrating through the pressure valve, one end of the radial channel being opened as the outlet of the pressure valve and connected to the bypass channel and the pressure relief channel, the other end of the radial channel being connected to the outlet of the temperature control valve; a valve core of the pressure valve is capable of reciprocating in the axial channel to open or close the pressure valve, and the valve core of the pressure valve keeps the radial channel unblocked when the pressure valve is closed, so that the outlet of the temperature control valve is connected to the bypass channel and the inlet of the pressure relief channel through the radial channel.

[0014] Optionally, the inlet of the bypass channel is configured to allow the fluid to enter from the fluid inflow interface and pass through the inlet of the heat dissipation channel to the inlet of the bypass channel when the bypass channel is connected.

[0015] Optionally, the bypass channel is arranged in the heat sink and is configured to exchange heat with the heat sink core.

[0016] Optionally, the bypass channel is arranged on one side of the heat sink core, and / or the inlet of the bypass channel is configured to allow the fluid to enter from the fluid inflow interface and pass through the inlet of the heat dissipation channel to the inlet of the bypass channel when the bypass channel is connected.

[0017] In another general aspect, there is provided a lubrication cooling system, comprising: a lubrication pump in communication with a lubricant pool, the lubrication pump for pumping lubricant to be cooled; a radiator assembly as described above in communication with an outlet of the lubrication pump.

[0018] In another general aspect, there is provided a wind turbine generator, comprising: a radiator assembly as described above; or a lubrication cooling system as described above.

[0019] Optionally, the radiator assembly is disposed outside the wind turbine generator.

[0020] In another general aspect, there is provided a wind farm, comprising a wind turbine generator as described above.

[0021] The present disclosure provides a radiator assembly, a lubrication cooling system, a wind turbine generator and a wind farm, by adding a bypass channel capable of conducting in low temperature environment to the radiator, the bypass channel can provide a channel for lubricant backflow in low temperature state, and the heat of lubricant flowing in the bypass channel is transmitted to the heat dissipation channel by heat radiation, so as to melt the remaining lubricant frozen in the heat dissipation channel, thereby solving the "stuck oil" problem in the related art and reducing the damage risk.

[0022] It should be understood that the general description above and the following detailed description are only exemplary and explanatory, and cannot limit the present disclosure. BRIEF DESCRIPTION OF DRAWINGS

[0023] The above and other objects and features of the present disclosure will become more apparent from the following description of embodiments taken in conjunction with the accompanying drawings, in which:

[0024] Figure 1 is a schematic view showing a lubrication cooling system according to an embodiment of the present disclosure;

[0025] Figure 2 is a connection relationship schematic view showing a radiator assembly according to an embodiment of the present disclosure;

[0026] Figure 3 is a longitudinal sectional view showing a radiator assembly according to an embodiment of the present disclosure;

[0027] Figure 4 is a longitudinal sectional view showing a radiator assembly according to an embodiment of the present disclosure; Figure 3 is a local enlarged view of part I;

[0028] Figure 5 is a longitudinal sectional view showing an open pressure valve and a closed temperature control valve according to an embodiment of the present disclosure; is a longitudinal sectional view showing an open pressure valve and a closed temperature control valve according to an embodiment of the present disclosure;

[0029] Figure 6 is a longitudinal sectional view showing a closed pressure valve and an open temperature control valve according to an embodiment of the present disclosure;

[0030] Figure 7 is a partial structural schematic diagram of a heat dissipation core according to an embodiment of the present disclosure;

[0031] Figure 8 is an exploded view of a heat dissipation unit according to an embodiment of the present disclosure.

[0032] Figures 1 to 8 BRIEF DESCRIPTION OF DRAWINGS

[0033] 10: heat sink assembly; 11: fluid inflow interface; 12: fluid outflow interface; 13: heat dissipation core; 131: partition; 132: fin; 133: side strip; 14: temperature control valve; 141: inlet of temperature control valve; 142: outlet of temperature control valve; 15: bypass passage; 16: pressure valve; 161: axial passage; 162: radial passage; 163: valve core; 164: through hole; 17: inflow cavity; 20: lubrication pump; 30: lubricant pool; 40: distributor; 50: distribution temperature control valve; 60: safety valve; 70: exhaust valve; 80: filter. DETAILED DESCRIPTION

[0034] The following detailed description is provided to help the reader obtain a thorough understanding of the methods, devices, and / or systems described herein. However, various changes, modifications, and equivalents of the methods, devices, and / or systems described herein will be clear to those skilled in the art after understanding the present disclosure. For example, the order of the operations described herein is merely an example, and is not limited to those set forth herein, but can be changed as will be clear to those skilled in the art after understanding the present disclosure, except for operations that must occur in a specific order. Also, the description of features known in the art can be omitted for the sake of clarity and conciseness.

[0035] The features described herein can be implemented in different forms and should not be construed as limited to the examples described herein. Rather, the examples described herein have been provided so as to merely demonstrate some of the many possible ways of implementing the methods, devices, and / or systems described herein, which will be clear to those skilled in the art after understanding the present disclosure.

[0036] As used herein, the term "and / or" includes any one of the associated listed items, as well as any combination of any two or more of the associated listed items.

[0037] Although terms such as "first", "second", and "third" can be used herein to describe various elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms. Instead, these terms are only used to distinguish one element, component, region, layer or section from another element, component, region, layer or section. Thus, terms of a first element, a first component, a first region, a first layer or a first section described in the examples herein can also be termed as a second element, a second component, a second region, a second layer or a second section without departing from the teachings of the examples.

[0038] In the description, when an element (such as a layer, a region or a substrate) is described as "on", "connected to" or "bound to" another element, the element can be directly "on", directly "connected to" or "bound to" the other element, or one or more other elements can be interposed therebetween. In contrast, when an element is described as "directly on", "directly connected to" or "directly bound to" another element, no other element can be interposed therebetween.

[0039] The terms used herein are only used to describe various examples, and are not intended to limit the disclosure. The singular form is intended to include the plural form unless the context clearly indicates otherwise. The terms "comprise", "include" and "have" indicate the presence of a stated feature, number, operation, component, element and / or combination thereof, but do not exclude the presence or addition of one or more other features, numbers, operations, components, elements and / or combinations thereof.

[0040] Unless otherwise defined, all terms used herein, including technical terms and scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which the disclosure belongs after the disclosure is understood. Unless explicitly defined herein, terms such as those defined in a general dictionary should be interpreted in accordance with their meanings consistent with the context and the disclosure, and should not be interpreted ideally or too formally.

[0041] In addition, in the description of the examples, when it is considered that a detailed description of the related structure or function known to cause confusion in the interpretation of the disclosure will be omitted, such a detailed description will be omitted.

[0042] The following will be combined Figures 1 to 8 The heat sink assembly 10, the lubrication cooling system, the wind turbine generator and the wind farm provided by the embodiments of the disclosure are introduced.

[0043] For ease of illustration, first combined Figure 1A lubrication cooling system of a wind turbine is introduced, and the radiator assembly 10 provided by the embodiments of the present disclosure can be applied in the system. The system can be, for example, a lubrication cooling system of a gearbox of a wind turbine, or an integrated lubrication cooling system of a wind turbine, or other lubrication cooling systems, and the present disclosure is not limited thereto.

[0044] As shown in Figure 1 , in the lubrication cooling system, the radiator assembly 10 realizing the basic cooling function (in the related art, only a separate radiator is provided, and the present disclosure forms a radiator assembly by adding a bypass channel 15 to the radiator) and a lubrication pump 20 are included, wherein the lubrication pump 20 communicates with a lubricant pool 30. The lubrication pump 20 is driven by a motor to operate, for pumping lubricant (for example, but not limited to, lubricating oil) in the lubricant pool 30 and pumping the lubricant to the radiator assembly 10 to realize the heat dissipation and cooling of the lubricant. The lubrication pump 20 can provide power for the flow of the lubricant in the entire system.

[0045] Regarding the lubricant pool 30, if the lubrication cooling system is a lubrication cooling system of a gearbox of a wind turbine, the lubricant pool 30 can be a lubricant pool in the gearbox. When the wind turbine is also provided with a sub-tank or a main tank independent of the gearbox, the lubricant pool 30 can also be an oil pool in the sub-tank or the main tank, and at this time, the lubricant in the lubricant pool 30 will be supplied to the gearbox to realize the lubrication and cooling of the mechanisms in the gearbox. For other lubrication cooling systems, the lubricant pool 30 can be different according to the actual situation, which will not be listed one by one here.

[0046] When there are multiple lubrication points of the lubrication object (for example, but not limited to, the gearbox), as shown in Figure 1 , a distributor 40 can also be included in the system, which communicates with the outlet of the radiator assembly 10, and the cooled lubricant flowing out of the radiator assembly 10 is distributed by the distributor 40 to different lubrication points to play a role in lubrication and cooling.

[0047] When the system starts in a low-temperature environment, the residual lubricant in the radiator will freeze and block the heat dissipation channel, which will cause the lubricant flowing into the radiator to be unable to flow out of the radiator in a short time, and the system pipeline will be in an "oil trapped" state. For this, the related art provides a solution of arranging a pressure relief channel in parallel with the heat dissipation channel in the radiator, and when the lubricant flowing into the radiator gradually increases at the inlet of the blocked heat dissipation channel, causing the oil pressure to rise and exceed the conduction pressure of the pressure relief channel, the lubricant can flow out of the pressure relief channel, playing a role in returning the lubricant. However, in this case, it is necessary to wait until the lubricant accumulates to the oil pressure exceeding the conduction pressure of the pressure relief channel, and thus there is a problem of a long starting period.

[0048] As shown in Figure 1As shown, the system may also include a distribution temperature control valve 50 (used to distribute the amount of lubricant entering the radiator assembly 10; a temperature control valve is used here as an example, but a pressure valve can also be used). In this example, the distribution temperature control valve 50 is connected in parallel with the radiator assembly 10, and the opening of the distribution temperature control valve 50 can decrease as the lubricant temperature increases within a certain temperature range. When the lubricant in the radiator solidifies and becomes blocked in a low-temperature environment, the lubrication pump 20 of the lubrication cooling system starts. Since the distribution temperature control valve 50 is in a fully open state under certain preset low-temperature conditions, the pumped lubricant flows through the channel of the distribution temperature control valve 50 and then directly back to the lubricant pool 30 or back to each lubrication point via the distributor 40.

[0049] like Figure 1 As shown, the system may also include a safety valve 60, an exhaust valve 70, and a filter 80. The safety valve 60 is located at the outlet of the lubrication pump 20, with its other end connected to the lubricant reservoir 30. When the system pressure exceeds the opening pressure of the safety valve 60, the safety valve 60 opens, releasing pressure and returning oil to the lubricant reservoir 30. The exhaust valve 70 is connected to the lubricant reservoir 30 to balance the pressure inside the lubricant reservoir 30 with the external atmospheric pressure. The filter 80 is located between the lubrication pump 20 and the distribution temperature control valve 50 to filter the lubricant flowing from the lubrication pump 20. Specifically, the filter 80 may be a double-precision filter.

[0050] In addition, the system may also include some in Figure 1 Components not shown in the diagram. For example, the outlet of lubrication pump 20 is equipped with a check valve to prevent backflow of oil and reverse rotation of lubrication pump 20 during system shutdown, which could damage the shaft seal. The inlet of lubricant tank 30 is equipped with a pressure detection device (pressure gauge or pressure sensor) to detect the lubricant pressure at the inlet. A pressure sensor can be configured at the outlet of lubrication pump 20 to detect the outlet pressure. Differential pressure sensors are installed before and after filter 80; when the differential pressure exceeds a set value, the differential pressure sensor signals to replace the filter element. A temperature sensor is installed in lubricant tank 30 to detect the lubricant temperature.

[0051] like Figure 2 As shown, one embodiment of this disclosure provides a heat sink assembly 10, which includes a heat sink and a bypass channel. The heat sink includes a fluid inlet port 11, a fluid outlet port 12, and a heat dissipation core 13. The heat dissipation core 13 has a heat dissipation channel, the inlet and outlet of which are respectively connected to the fluid inlet port 11 and the fluid outlet port 12. The bypass channel 15 connects the fluid inlet port 11 and the fluid outlet port 12. (Refer to...) Figure 2As shown, the inlet and outlet of the bypass channel 15 correspond to the fluid inflow interface 11 and the fluid outflow interface 12 respectively, and the bypass channel 15 is configured to be conductive when the temperature is lower than the first preset temperature, so as to pass the fluid (e.g. lubricant) through the bypass channel.

[0052] According to the heat sink assembly 10 of the embodiment of the present disclosure, by adding the bypass channel 15 to the heat sink, the bypass channel 15 can provide a channel for the lubricant to return in the low-temperature environment, and at the same time, the heat of the lubricant flowing through the bypass channel 15 is transmitted to the heat dissipation channel by heat radiation, so as to melt the remaining lubricant frozen in the heat dissipation channel, thereby solving the "stuck oil" problem in the related art and reducing the damage risk.

[0053] Optionally, the number of the heat dissipation channels is at least one, and the cross-sectional area of each heat dissipation channel is smaller than the cross-sectional area of the bypass channel 15, for example, the cross-sectional area of the bypass channel is tens of times of the cross-sectional area of each heat dissipation channel, which can provide a large enough flow channel for the lubricant flowing into the heat sink assembly 10 to guarantee the reliable return of the lubricant.

[0054] With the above arrangement, since the cross-sectional area of the bypass channel 15 is large, the bypass channel is not easy to be blocked even during shutdown, and can reliably return the lubricant and melt the remaining lubricant frozen in the heat dissipation channel when starting.

[0055] Specifically, the bypass channel 15 is configured to be conductive when the temperature is lower than the first preset temperature. For the case that the ambient temperature is extremely low, since the shell of the heat sink assembly 10 and the pipeline near the fluid inflow interface 11 directly contact the cold air in the environment, even if the lubricant enters the normal working stage, the lubricant will lose part of the heat due to heat conduction when entering the heat sink assembly 10, causing the temperature of the lubricant to decrease and the bypass channel 15 to be conductive. That is, the bypass channel 15 may be in a conductive state during the daily operation of the low-temperature environment.

[0056] Based on this, during the daily operation of the low-temperature environment, the bypass channel may be conductive, so that the lubricant exchanges heat through the bypass channel 15, which can appropriately reduce the heat exchange amount between the lubricant and the heat sink assembly 10, thereby reducing the risk of the heat sink assembly 10 being frozen due to excessive heat exchange in the case that the outdoor temperature is extremely low, improving the working stability of the heat sink assembly 10 in the low-temperature environment, and helping to guarantee the safe operation of the wind turbine generator set using the heat sink assembly 10 and solve the reliability of the application of the gear box and other heat dissipation components in the low-temperature environment.

[0057] In addition, the bypass channel 15 is configured to be conductive when the temperature is lower than the first preset temperature, which can be realized by means of a temperature sensing element.

[0058] In some examples, an electric temperature control valve can be used. The electric temperature control valve includes a valve body, a temperature sensing element, and a controller, which can receive the temperature detected by the temperature sensing element and control the opening of the valve body according to the detected temperature. At this time, the electric temperature control valve can be directly arranged in the radiator assembly 10 and connected in series between the fluid inflow interface 11 and the inlet of the bypass channel 15, or only the valve body and the temperature sensing element of the electric temperature control valve can be arranged in the radiator, and the controller of the electric temperature control valve can be arranged separately from the radiator assembly 10, as long as the conduction of the bypass channel 15 can be changed with temperature, which is not limited in the present disclosure.

[0059] In other examples, a temperature control valve 14 containing a temperature sensing deformation element can be used. Optionally, the radiator assembly 10 further includes the temperature control valve 14, which is connected in series between the fluid inflow interface 11 and the inlet of the bypass channel 15, i.e., the inlet 141 of the temperature control valve is connected to the fluid inflow interface 11, and the outlet 142 of the temperature control valve is connected to the inlet of the bypass channel 15. The temperature control valve 14 is configured to open when the temperature is lower than a first preset temperature, so that the fluid inflow interface 11 and the bypass channel 15 are conducted through the temperature control valve 14. By selecting the temperature control valve 14 containing the temperature sensing deformation element, the deformation characteristics of the temperature sensing deformation element can be directly used to realize the conduction of the bypass channel 15, which is simple and reliable. For example, the deformation of the temperature sensing deformation element can be the deformation caused by the expansion or compression of the temperature sensing liquid filled in the temperature control valve 14, which is a technology in the prior art and will not be described here.

[0060] It should be understood that, regardless of which of the above examples is used, by selecting an electric temperature control valve or a temperature control valve 14 that opens when the temperature is lower than a first preset temperature, the bypass channel 15 can be reliably and reliably conducted in a low temperature environment. In addition, by reasonably selecting the opening temperature of the electric temperature control valve or the temperature control valve 14, i.e., the first preset temperature, the conduction condition of the bypass channel 15 can be adjusted according to actual needs to ensure reliable start and stable operation of the radiator assembly 10 in a low temperature environment. As an example, the first preset temperature is in the range of 6°C to 30°C, for example, it can be 6°C, 15°C or 20°C.

[0061] For ease of description, the embodiments of the temperature control valve 14 will be further described below. For the embodiments using an electric temperature control valve, the same can be reasonably referred to, and will not be described again.

[0062] Further optionally, the temperature control valve 14 is further configured to increase the valve opening degree as the temperature decreases when the temperature is lower than a first preset temperature and higher than a second preset temperature, and the valve is fully opened when the temperature is lower than or equal to the second preset temperature, wherein the first preset temperature is higher than the second preset temperature. By increasing the opening degree of the temperature control valve 14 as the temperature decreases in the range from the second preset temperature to the first preset temperature, and decreasing the opening degree as the temperature increases, i.e., gradually closing the temperature control valve 14 as the lubricant temperature rebounds, the lubricant is gradually diverted to the heat dissipation channel, and the transition from the start-up stage to the normal working stage is realized. In addition, for the case of extremely low ambient temperature (e.g., lower than -30℃), as described above, the lubricant will also dissipate part of the heat by heat conduction when entering the radiator assembly 10, and if the temperature of the lubricant decreases to below the first preset temperature, the temperature control valve 14 can be partially open, thereby reducing the overall heat exchange amount of the radiator assembly 10, and the lower the ambient temperature, the greater the opening degree of the temperature control valve 14, which can adapt to the change in ambient temperature to change the heat exchange amount between the lubricant and the radiator assembly 10, effectively reducing the risk of the radiator assembly 10 being frozen in a low-temperature environment, without affecting the cooling effect, thereby ensuring the working stability and reliability of the radiator assembly 10 in a low-temperature environment.

[0063] In addition, as long as the temperature of the lubricant flowing into the temperature control valve 14 is lower than or equal to the second preset temperature, the temperature control valve 14 will be fully opened, i.e., the opening degree reaches the maximum, and a large amount of lubricant can flow through the bypass channel 15 in the start-up stage to realize the backflow of the lubricant and the melting of the remaining lubricant frozen in the heat dissipation channel, thereby reducing the risk of the radiator assembly 10 being frozen during low-temperature operation of the lubrication cooling system.

[0064] Next, an exemplary structural design of the temperature control valve 14 and the bypass channel 15 will be introduced.

[0065] In some examples, the bypass channel 15 is arranged separately from the heat dissipation core 13, for example, a pipe body is arranged as the bypass channel 15, one end of the pipe body is connected to the fluid inflow interface 11, and the other end of the pipe body is connected to the fluid outflow interface 12. By adding a new element to the original radiator structure, the change to the original radiator structure can be reduced, and the optimization cost can be reduced. At this time, the placement position of the bypass channel 15 can be adjusted arbitrarily, and can also be fixed as needed, which is not limited in the present disclosure. At this time, similar to the structure shown in Figure 3 As shown, the inlet of the bypass channel 15 is configured to allow the fluid to enter from the fluid inflow interface 11, pass through the inlet of the heat dissipation channel, and reach the inlet of the bypass channel 15 when the bypass channel 15 is open. It should be noted that the heat dissipation channel is a very small channel, Figure 3 For the sake of clear display, part of the heat dissipation core 13 is removed, Figure 3The mark 13 indicates the location of the heat sink 13, not the structure of the heat sink 13 itself. The structure of the heat sink 13 will be described separately later. This bypass channel 15 is designed so that the fluid first flows through the diversion chamber connected to the fluid inlet 11 (for a single heat sink, the inlet of the heat dissipation channel is connected to the diversion chamber, thus entering each heat dissipation channel from the diversion chamber), then flows through the inlet of the heat dissipation channel, and then flows into the bypass channel 15 on the side.

[0066] In other examples, optionally, refer to Figure 3 As shown, the bypass channel 15 is disposed in the heat sink and is configured to exchange heat with the heat sink core 13. By disposing of the bypass channel 15 in the heat sink, an integrated structure can be formed, making the heat sink assembly 10 simple in appearance and easy to install. Furthermore, the bypass channel 15 can fully contact the heat dissipation channels within the heat sink core 13, forming heat conduction, thereby improving the heat transfer efficiency between the bypass channel 15 and the heat dissipation channels based on heat radiation, which helps to accelerate the low-temperature start-up process.

[0067] In other examples, further optionally, such as Figure 3 As shown, the bypass channel 15 is located on one side of the heat sink 13, without penetrating the interior of the heat sink 13. This avoids disrupting the original structure of the heat dissipation channels within the heat sink 13, reducing the difficulty and cost of structural optimization. Specifically, the extension direction of the bypass channel 15 is generally from the fluid inflow port 11 to the fluid outflow port 12 (i.e.,...). Figure 3 (in the vertical direction). As an example, the bypass channel 15 is specifically disposed along the width direction of the heat sink core 13 (i.e., in the vertical direction). Figure 3 (in the left and right direction) rather than the thickness direction (i.e.) Figure 3 The side perpendicular to the paper plane can maintain the flatness of the overall structure of the radiator, reduce the risk of the bypass channel 15 being damaged by bumps, and achieve a consistent appearance.

[0068] In other examples, it should be understood that the positional relationship between the bypass channel 15 and the inlet of the heat dissipation channel can be referenced, as in some of the aforementioned examples. Figure 3 As shown, the inlet of the bypass channel 15 can be configured such that when the bypass channel 15 is open, the fluid enters from the fluid inlet interface 11 and passes through the inlet of the heat dissipation channel to reach the inlet of the bypass channel 15. Alternatively, when the bypass channel 15 is open, the fluid enters from the fluid inlet interface 11 and directly reaches the inlet of the bypass channel 15 without passing through the inlet of the heat dissipation channel. These are all implementations of this disclosure and fall within the protection scope of this disclosure.

[0069] In some embodiments, optionally, such as Figure 2As shown, the radiator assembly 10 also includes a pressure valve 16 and a pressure relief channel. The inlet of the pressure valve 16 is connected to the fluid inlet port 11; the pressure relief channel connects the outlet of the pressure valve 16 and the fluid outlet port 12. By providing the pressure valve 16 and the pressure relief channel, the pressure valve 16 can be opened when the system pressure is high, allowing the lubricant to flow out through the pressure relief channel, thus ensuring the safe use of the radiator assembly 10.

[0070] In some examples, the pressure relief channel and the bypass channel 15 can be two completely independent channels, for example, but not limited to, being located on opposite sides of the heat sink core 13.

[0071] In other examples, the bypass channel 15 and the pressure relief channel may optionally overlap at least partially, for example, in a Y-shape, where the channels near the outlet overlap, or in an inverted Y-shape, where the channels near the inlet overlap. Of course, they may also overlap in the middle, or any other partially overlapping structure may be used.

[0072] Optionally, such as Figure 3 As shown, the bypass channel 15 and the pressure relief channel are the same channel. This disclosure does not limit the specific overlap between the bypass channel 15 and the pressure relief channel. Both the bypass channel 15 and the pressure relief channel can serve as bypass heat dissipation channels. By making them at least partially overlap, the structure of the heat sink assembly 10 can be simplified, redundancy can be reduced, and cost control can be achieved.

[0073] Optionally, the temperature control valve 14 and the pressure valve 16 can be integrated into a single unit. By integrating the temperature control valve 14 and the pressure valve 16 into one unit, a simple and aesthetically pleasing integrated structure can be formed, which is convenient for installation.

[0074] It should be understood that regardless of the structural relationship between the pressure relief channel and the bypass channel 15, the temperature control valve 14 and the pressure valve 16 can be integrated into a single unit. Specifically, in embodiments where the inlets of the pressure relief channel and the bypass channel 15 partially overlap (including embodiments where they completely overlap), they share an inlet, which can be connected to the outlet of the integrated temperature control valve 14 and the pressure valve 16. In embodiments where the inlets of the pressure relief channel and the bypass channel 15 do not overlap (including embodiments where they are completely independent), they each have an inlet, and the two inlets can be connected to the outlet of the integrated temperature control valve 14 and the pressure valve 16 through a connection structure, such as a three-way pipe.

[0075] Alternatively, the temperature control valve 14 and the pressure valve 16 can be integrated into a single unit, such as... Figures 4 to 6 As shown, the pressure valve 16 has intersecting axial channels 161 and radial channels 162. Figure 4 and Figure 6The pressure valve 16 is shown in a closed state, in which the valve core 163 of the pressure valve 16 extends into the axial channel 161 to close the pressure valve 16, one end of the axial channel 161 is open (the right end in Figures 4 to 6 ) as the inlet of the pressure valve 16 and is in communication with the fluid inflow interface 11, the radial channel 162 passes through the pressure valve 16, one end of the radial channel 162 is open (the lower end in Figure 4 ) as the outlet of the pressure valve 16 (also the outlet of the integrated temperature control valve 14 and pressure valve 16) and is in communication with the bypass channel 15 and the pressure relief channel (it should be understood that for the embodiment in which the pressure relief channel and the part near the inlet of the bypass channel 15 overlap, it is in communication with the overlapped inlet, and for the embodiment in which the pressure relief channel and the part near the inlet of the bypass channel 15 do not overlap, it is in communication with the inlets of both, for example, through a tee pipe), the other end of the radial channel 162 is open (the upper end in Figures 4 to 6 ) and is in communication with the outlet 142 of the temperature control valve; the valve core 163 of the pressure valve 16 can reciprocate in the axial channel 161 to open or close the pressure valve 16. As an example, the part of the valve core 163 that extends into the axial channel 161 is configured as a cylinder with one end open, specifically, the open end is arranged towards the outside of the pressure valve 16 and can extend into the axial channel 161, that is, the right end in Figures 4 to 6 , the side wall of the cylinder is provided with a plurality of through holes 164, so that when the valve core 163 moves to the position where the through holes 164 are in communication with the radial channel 162 as shown in Figure 5 , the inlet (i.e., the right end opening of the axial channel 161 in Figures 4 to 6 ) and the outlet (i.e., the lower end opening of the radial channel 162 in Figures 4 to 6 ) of the pressure valve 16 are in communication through the through holes 164, thereby opening the pressure valve 16. It should be understood that Figure 5 , the pressure valve 16 is shown in a slightly open state, when the pressure at the inlet of the pressure valve 16 continues to increase, the valve core 163 will continue to move to the left under the action of the pressure, and the opening degree of the pressure valve 16 will increase.

[0076] Of course, in other examples, the end of the valve core 163 may not have an opening, requiring complete withdrawal from the axial channel 161 before the pressure valve 16 can be opened; this is also an implementation method of this disclosure. In embodiments of this disclosure, the valve core 163 of the pressure valve 16 is also configured to keep the radial channel 162 unobstructed when the pressure valve 16 is closed, so that the outlet 142 of the temperature control valve is connected via the radial channel 162 to the bypass channel 15 and the inlet of the pressure relief channel (the specific connection relationship with the bypass channel 15 and the pressure relief channel is described above and will not be repeated). By specifically utilizing the radial channel 162 within the pressure valve 16 to connect the outlet 142 of the temperature control valve to the bypass channel 15 and the inlet of the pressure relief channel, the existing structure can be fully utilized to achieve the integration of the temperature control valve 14 and the pressure valve 16, promoting the realization of an integrated design.

[0077] Next, combine Figures 4 to 6 The flow paths of temperature control valve 14 and pressure valve 16 under different open and closed states are described. For example... Figure 4 As shown, at this time, both the temperature control valve 14 and the pressure valve 16 are in the closed state. If the heat dissipation channel is not blocked, the lubricant will enter the heat dissipation channel within the heat dissipation core 13 along the direction of the dotted arrow, and will not enter the bypass channel 15 or the pressure relief channel. Figure 5 As shown, at this time, the temperature control valve 14 is in the closed state, the pressure valve 16 is in the slightly open state, and the valve core 163 passes through the elastic element (e.g., Figure 5 The spring shown in the figure, along with the valve core 163, is in an uncut state. Figure 4 and Figure 6 Similarly, the valve core 163 is connected to the valve body of the pressure valve 16. Under pressure, the valve core 163 slightly retracts from the axial channel 161 to the left, making the through hole 164 connected to the radial channel 162. Lubricant can enter from the opening at the right end of the valve core 163, then enter the radial channel 162 through the through hole 164, and finally flow out from the opening at the lower end of the radial channel 162 (i.e., the outlet of the pressure valve 16). It should be noted that... Figure 5 Only the integrated temperature control valve 14 and pressure valve 16 were shown, therefore they were not displayed. Figure 4 The middle arrow points to the dashed arrow indicating the heat dissipation channel. Figure 6 The same principle applies.

[0078] like Figure 6 As shown, at this time, the temperature control valve 14 is in the fully open state, the pressure valve 16 is in the closed state, and the valve core 163 and the elastic element are as follows. Figure 6 The radial channel 162 is not blocked, ensuring it remains unobstructed. In embodiments where the valve core 163 might block the radial channel 162, a through hole can be provided in the portion of the valve core 163 that blocks the radial channel 162. This through hole helps maintain the radial channel 162's unobstructed flow, similar to a through hole 164. Figure 6On the basis of the above, the pressure valve 16 can be further opened. When in the small opening state as shown in Figure 5 , the elastic member and the valve core 163 of the pressure valve 16 do not block the radial channel 162; as the opening of the pressure valve 16 increases, although the portion of the valve core 163 entering the radial channel 162 increases, because the valve core 163 is provided with a through hole 164 or other similar structure, the radial channel 162 can still be kept unblocked, at which time the lubricant flows in the directions of the dashed arrows as shown in Figure 5 and Figure 6 .

[0079] As an example, for the integrated structure as shown in Figures 4 to 6 , the outlets of the temperature control valve 14 and the pressure valve 16 are in series, so that the outlet of the pressure valve 16 serves as the outlet of the integrated structure, but the inlets of the temperature control valve 14 and the pressure valve 16 are arranged in parallel, at which time an inflow cavity 17 can be arranged in the integrated structure, which simultaneously communicates the inlets of the temperature control valve 14 and the pressure valve 16, and an opening is additionally arranged as the inlet of the integrated structure, which is used to communicate the aforementioned flow separation cavity in the radiator that communicates with the fluid inflow interface 11. Of course, the inflow cavity 17 can not be arranged, and the inlets of the temperature control valve 14 and the pressure valve 16 can be connected to the fluid inflow interface 11 through a connection structure such as a tee joint, which is not limited by the present disclosure.

[0080] Regarding the specific structure of the heat dissipation channel, taking a plate-fin radiator as an example, the plate-fin radiator is composed of a plurality of heat dissipation units, which are arranged in alternating directions as shown in Figure 7 , forming a heat dissipation core 13, Figure 8 , which shows an exploded view of a heat dissipation unit, which includes an upper and lower baffle 131, a fin 132 in the middle, and a left and right side strip 133, which are enclosed together to form a plurality of heat dissipation channels, Figure 8 , the hollow arrow direction therein indicates the direction of fluid (in the embodiment of the present disclosure, the fluid is lubricant) inflow. Figure 7 , the height H and the width B of the heat dissipation channel are shown, the height H of the embodiment of the present disclosure can be less than 3mm, so the cross-sectional area of the heat dissipation channel is slightly less than H 2 , which is less than 9mm 2 . The width B corresponds to the direction perpendicular to the paper in Figure 3 , which is usually close to 100mm. The width B is also the width of the bypass channel 15, and when the bypass channel 15 is arranged on one side of the heat dissipation core 13, it flows in the direction of Figure 3The bypass passage has a cross-sectional area which is much larger than that of the heat dissipation passage, so that even if there is residual lubricant and the residual lubricant solidifies at low temperature shutdown, only the flow resistance is increased, and the passage is not blocked, so that the lubricant can pass through at low temperature start-up stage; and the cross-sectional area of the bypass passage is much smaller than that of the fluid inlet interface 11, the fluid outlet interface 12 and the system pipeline, so that the heat dissipation effect can be achieved.

[0081] Next, the radiator assembly 10 of one specific embodiment of the present disclosure is introduced. The radiator assembly 10, as shown in Figures 2 to 4 The radiator assembly 10 integrates the heat dissipation core 13, the temperature control valve 14 and the pressure valve 16 in one body, and the specific integration method is described in the previous part. The first preset temperature of the temperature control valve 14 is 30°C, and the second preset temperature is 6°C. The radiator assembly 10 combines the temperature, viscosity of the lubricant and the comprehensive characteristics of the structure of the heat dissipation core 13, realizes the rapid opening of the radiator assembly 10 at low temperature working condition of-30°C, meets the rated heat dissipation requirement at high temperature working condition of 40°C, and significantly increases the adaptability of the radiator assembly 10 (the conventional radiator can only meet the requirement of opening for more than 30 minutes at-15°C working condition). The start-up process of the lubricating cooling system using the example radiator assembly at low temperature working condition is as follows:

[0082] 1. At the beginning, the temperature of the lubricant entering the radiator assembly 10 is less than 6°C, the lubricant in the heat dissipation core 13 does not flow, the pressure valve 16 is closed and blocked, and the temperature control valve 14 is always open. After the system supplies lubricant, the system pressure gradually rises and overcomes the oil passage resistance of the bypass passage 15, and the lubricant flows out from the bypass passage 15 through the temperature control valve 14. At this time, the lubricant in the bypass passage 15 is less than 6°C, but it is still higher than the temperature of the residual lubricant in the heat dissipation passage, so the lubricant flowing through the bypass passage 15 exchanges heat with the residual lubricant in the heat dissipation passage, and the residual lubricant in the heat dissipation passage gradually begins to melt.

[0083] 2. With the melting of the residual lubricant and the circulation of the lubricant in the system, the temperature of the system gradually rises, and the temperature of the lubricant entering the radiator assembly 10 also gradually rises to between 6°C and 30°C, so that the temperature control valve 14 is in a semi-open state, at this time, part of the lubricant flows through the bypass passage 15, and the other part of the lubricant flows through the heat dissipation passage, the temperature of the lubricant in the system continues to rise rapidly, so that the temperature of the lubricant of the lubricated parts reaches a reasonable range quickly, and the operation of the lubricated parts is guaranteed.

[0084] 3. When the temperature of the lubricant entering the radiator assembly 10 further increases to above 30℃, the temperature control valve 14 is fully closed, and the lubricant flows out through the radiator passage. When the resistance of the radiator passage is large and greater than the opening pressure of the pressure valve 16, the pressure valve 16 opens, and the lubricant flows through the radiator passage and the bypass passage 15 at the outlet of the pressure valve 16 under high pressure at the inlet of the pressure valve 16. As the temperature of the lubricant increases, the pressure valve 16 is closed due to the decrease of the pressure at the front end, and the lubricant flows out through the radiator passage.

[0085] As shown in FIG. 1, the radiator assembly 10 according to an embodiment of the present disclosure comprises a temperature control valve 14, a pressure valve 16, and a radiator passage 18. The temperature control valve 14 is connected to the lubricant pool 30 and is used to control the flow of the lubricant. The pressure valve 16 is connected to the temperature control valve 14 and is used to control the flow of the lubricant. The radiator passage 18 is connected to the temperature control valve 14 and the pressure valve 16 and is used to cool the lubricant. Figure 1 As shown in FIG. 1, the radiator assembly 10 according to an embodiment of the present disclosure comprises a temperature control valve 14, a pressure valve 16, and a radiator passage 18. The temperature control valve 14 is connected to the lubricant pool 30 and is used to control the flow of the lubricant. The pressure valve 16 is connected to the temperature control valve 14 and is used to control the flow of the lubricant. The radiator passage 18 is connected to the temperature control valve 14 and the pressure valve 16 and is used to cool the lubricant.

[0086] As shown in FIG. 1, the radiator assembly 10 according to an embodiment of the present disclosure comprises a temperature control valve 14, a pressure valve 16, and a radiator passage 18. The temperature control valve 14 is connected to the lubricant pool 30 and is used to control the flow of the lubricant. The pressure valve 16 is connected to the temperature control valve 14 and is used to control the flow of the lubricant. The radiator passage 18 is connected to the temperature control valve 14 and the pressure valve 16 and is used to cool the lubricant. Figure 1 As shown in FIG. 1, the radiator assembly 10 according to an embodiment of the present disclosure comprises a temperature control valve 14, a pressure valve 16, and a radiator passage 18. The temperature control valve 14 is connected to the lubricant pool 30 and is used to control the flow of the lubricant. The pressure valve 16 is connected to the temperature control valve 14 and is used to control the flow of the lubricant. The radiator passage 18 is connected to the temperature control valve 14 and the pressure valve 16 and is used to cool the lubricant.

[0087] As shown in FIG. 1, the radiator assembly 10 according to an embodiment of the present disclosure comprises a temperature control valve 14, a pressure valve 16, and a radiator passage 18. The temperature control valve 14 is connected to the lubricant pool 30 and is used to control the flow of the lubricant. The pressure valve 16 is connected to the temperature control valve 14 and is used to control the flow of the lubricant. The radiator passage 18 is connected to the temperature control valve 14 and the pressure valve 16 and is used to cool the lubricant.

[0088] The specific embodiments of the present disclosure have been described in detail, although some embodiments have been shown and described, those skilled in the art should understand that modifications and variations can be made to these embodiments without departing from the principles and spirit of the present disclosure defined by the claims and their equivalents, and these modifications and variations should also be within the protection scope of the claims of the present disclosure.

Claims

1. A heat spreader assembly (10) characterized by, The radiator assembly (10) comprises: a radiator and a bypass channel (15), wherein the radiator comprises: a fluid inflow interface (11); a fluid outflow interface (12); a radiator core (13) provided with radiator channels, the inlet and outlet of the radiator channels correspondingly communicate with the fluid inflow interface (11) and the fluid outflow interface (12) respectively; The bypass channel (15) is communicated between the fluid inflow interface (11) and the fluid outflow interface (12), and the bypass channel (15) is configured to be conductive when the temperature is lower than the first preset temperature, so that the fluid passes through the bypass channel (15).

2. The radiator assembly (10) of claim 1, wherein: The number of radiator channels is at least one, and the cross-sectional area of each radiator channel is smaller than the cross-sectional area of the bypass channel (15).

3. The radiator assembly (10) of claim 1, wherein: The radiator assembly (10) further comprises a temperature control valve (14) connected in series between the fluid inflow interface (11) and the inlet of the bypass channel (15), and the temperature control valve (14) is configured to be opened when the temperature is lower than the first preset temperature, so that the fluid inflow interface (11) and the bypass channel (15) are conductive through the temperature control valve (14).

4. The radiator assembly (10) of claim 3, wherein: The temperature control valve (14) is further configured to increase the valve opening degree as the temperature decreases when the temperature is lower than the first preset temperature and higher than a second preset temperature, and the valve is fully opened when the temperature is lower than or equal to the second preset temperature, wherein the first preset temperature is greater than the second preset temperature.

5. The heat spreader assembly (10) of claim 4, wherein, The radiator assembly (10) further comprises: a pressure valve (16) having an inlet communicated with the fluid inflow interface (11); and a pressure relief channel communicated between the outlet of the pressure valve (16) and the fluid outflow interface (12).

6. The radiator assembly (10) of claim 5, wherein: The bypass channel (15) and the pressure relief channel at least partially overlap.

7. The radiator assembly (10) of claim 5, wherein: The temperature control valve (14) and the pressure valve (16) are integrated into an integrated structure.

8. The radiator assembly (10) of claim 7, wherein: The pressure valve (16) is provided with an axial channel (161) and a radial channel (162) intersecting with each other, one end of the axial channel (161) is opened as an inlet of the pressure valve (16) and communicates with the fluid inflow interface (11), the radial channel (162) penetrates through the pressure valve (16), one end of the radial channel (162) is opened as an outlet of the pressure valve (16) and communicates with the bypass channel (15) and the pressure relief channel, the other end of the radial channel (162) is opened and communicates with the outlet (142) of the temperature control valve (14); The valve core (163) of the pressure valve (16) can reciprocate in the axial channel (161) to open or close the pressure valve (16), and the valve core (163) of the pressure valve (16) keeps the radial channel (162) unobstructed when the pressure valve (16) is closed, so that the outlet (142) of the temperature control valve (14) communicates with the inlet of the bypass channel (15) and the pressure relief channel through the radial channel (162).

9. The heat sink assembly (10) according to any one of claims 1 to 8, wherein The inlet of the bypass channel (15) is configured to allow the fluid to enter from the fluid inflow interface (11) and pass through the inlet of the heat dissipation channel to the inlet of the bypass channel (15) when the bypass channel (15) is open.

10. The heat sink assembly (10) according to any one of claims 1 to 8, wherein The bypass channel (15) is arranged in the heat sink and is configured to exchange heat with the heat sink core (13).

11. The heat sink assembly (10) according to claim 10, wherein The bypass channel (15) is arranged on one side of the heat sink core (13); and / or the inlet of the bypass channel (15) is configured to allow the fluid to enter from the fluid inflow interface (11) and pass through the inlet of the heat dissipation channel to the inlet of the bypass channel (15) when the bypass channel (15) is open.

12. A lubrication cooling system characterized by, The lubrication cooling system comprises: A lubrication pump (20) which communicates with a lubricant pool and is used to pump lubricant to be cooled; The heat sink assembly (10) according to any one of claims 1 to 11, which communicates with an outlet of the lubrication pump (20).

13. A wind power unit, characterized in that The wind turbine generator set comprises: The heat sink assembly (10) according to any one of claims 1 to 11; or The lubrication cooling system according to claim 12.

14. A wind power plant according to claim 13, characterised in that The heat sink assembly (10) is arranged outside the wind turbine generator set.

15. A wind farm, characterized in that The wind farm comprises the wind turbine generator set according to claim 13 or 14. The heat sink assembly (10) is arranged outside the wind turbine generator set.

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