Performance-controllable liquid cooling supercharging device
By designing a liquid-cooled turbocharger with controllable performance, and using temperature regulation pipelines and electronically controlled valves to regulate the coolant temperature, the problem of limited compressor efficiency was solved, the engine's overall operating efficiency was optimized, and the engine's economy and power were improved.
Patent Information
- Application Number
- CN202423285963.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-30
- Publication Date
- 2025-12-16
- Estimated Expiration
- 2034-12-30
AI Technical Summary
The current compressor efficiency range is limited by the compressor's geometric dimensions and cannot take into account the operating efficiency of the engine under all operating conditions.
Design a controllable liquid-cooled booster device that adjusts the temperature of the coolant entering the cooling channel through temperature regulation pipelines, including heating and cooling pipelines. The coolant temperature is controlled by heat exchangers and coolers, and precise temperature regulation is achieved by combining electronically controlled valves and check valves.
It optimizes compressor efficiency under different engine operating conditions, takes into account the operating efficiency of the engine under all operating conditions, reduces compressor outlet temperature, reduces or eliminates the need for intercooler, and improves engine economy and power.
Smart Images
Figure CN223676375U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model relates to the technical field of supercharging, specifically relates to a liquid cooling supercharging device with controllable performance. BACKGROUND
[0002] The traditional turbocharger is a kind of mechanical device that uses the exhaust gas energy of engine to further supercharge, it uses the exhaust gas energy of engine to drive the turbine in the turbine box to rotate, and the turbine drives the coaxial compressor impeller to work, and the electronic supercharger is to use the high-speed motor to drive the coaxial compressor impeller to work. Fresh air enters the compressor through the air filter, and the compressor impeller rotates to compress fresh air to achieve the effect of supercharging. Therefore, whether the traditional turbocharger or the electronic supercharger can increase the air quantity in the cylinder of the engine with the same displacement, optimize the combustion process and improve the working efficiency of the engine.
[0003] In the working process of the supercharger, with the increase of the rotating speed and pressure ratio of the compressor, a large amount of heat loss will be generated in the gas compression, which causes the temperature of the gas at the outlet of the compressor to rise. Generally, the temperature of the gas at the outlet of the compressor is about 50 DEG C when the engine is in low-speed working condition, and the temperature of the gas at the outlet of the compressor often exceeds 100 DEG C when the engine is in rated working condition. On the one hand, the temperature of the gas at the outlet of the compressor will affect the combustion of the engine, and even may cause the engine knock and other phenomena, so it is necessary to set a intercooler at the rear end of the compressor, and the temperature of the gas at the outlet of the compressor is cooled by the cooling liquid or air cooling, and then enters the cylinder of the engine for combustion. On the other hand, the temperature of the gas at the outlet of the compressor is a key parameter of the performance of the compressor, and is closely related to the efficiency of the compressor, and finally affects the overall economy of the engine.
[0004] The performance of the compressor is sensitive to the temperature of the gas, and the traditional compressor performance is as follows Figure 1 As described above, the working range of the compressor is mainly composed of the left dashed line surge line, the upper end maximum rotating speed line and the right end dashed line choke line, and the equivalent efficiency circle is the efficiency range of the compressor. In view of the economy and the working characteristics of the engine, the maximum efficiency of the compressor is often designed at the normal working condition in the existing traditional turbocharging technology or electronic supercharger, and the efficiency at other working conditions cannot be considered, that is, the range of the efficiency circle of the compressor is limited by the geometric size of the compressor (that is, the range of the efficiency circle of the compressor is small due to the geometric size constraint of the compressor), and the operating efficiency of the engine cannot be considered.
[0005] In view of the above, a liquid cooling supercharging device with controllable performance is needed to solve the problems in the prior art. INVENTION CONTENTS
[0006] The utility model aims at providing a controllable performance's liquid cooling pressure device, it aims at solving the problem that the range of existing compressor efficiency circle is limited by compressor geometric size constraint, cannot take into account the operation efficiency of engine full working condition, specific technical scheme is as follows:
[0007] A controllable performance's liquid cooling pressure device, including compressor, delivery main pipeline, backflow main pipeline and temperature regulation pipeline, be equipped with cooling flow channel for with the gasway in compressor gas carries out heat exchange on the compressor, cooling flow channel connects delivery main pipeline and backflow main pipeline, be equipped with temperature regulation pipeline between delivery main pipeline and backflow main pipeline, temperature regulation pipeline is used for adjusting the temperature of cooling liquid into cooling flow channel.
[0008] In the above technical scheme, preferably, the temperature regulation pipeline comprises a heating pipeline and a cooling pipeline;
[0009] A heat exchanger is provided on the heating pipeline, and the heat exchanger is used for heat exchange between the heating pipeline and an engine thermal management circulation loop to heat the cooling liquid;
[0010] A cooler is provided on the cooling pipeline, and the cooler is used to cool the cooling liquid;
[0011] The temperature of the cooling liquid into the cooling flow channel is adjusted by the operation of the heat exchanger or the cooler.
[0012] In the above technical scheme, preferably, the heating pipeline and the cooling pipeline are connected in series between the delivery main pipeline and the backflow main pipeline;
[0013] The heating pipeline comprises a bypass branch one, an electric control valve one and a heating branch, the heat exchanger is arranged on the heating branch, the bypass branch one and the heating branch are connected to the electric control valve one, and the proportion of the cooling liquid entering the bypass branch one and the heating branch is distributed by the electric control valve one;
[0014] The cooling pipeline comprises a bypass branch two, an electric control valve two and a cooling branch, the cooler is arranged on the cooling branch, the bypass branch two and the cooling branch are connected to the electric control valve two, and the proportion of the cooling liquid entering the bypass branch two and the cooling branch is distributed by the electric control valve two.
[0015] In the above technical scheme, preferably, the temperature adjusting pipeline further comprises a bypass branch three, the bypass branch three, the temperature increasing pipeline and the temperature decreasing pipeline are arranged in parallel between the conveying main pipeline and the return main pipeline, the bypass branch three is connected with the return main pipeline through an electric control valve four, the temperature increasing pipeline and the temperature decreasing pipeline are connected with an electric control valve three at the end of the return main pipeline, the bypass branch three controls the shunt proportion of the cooling liquid in the return main pipeline through the electric control valve four, and the cooling liquid in the return main pipeline is controlled to enter the temperature increasing pipeline or the temperature decreasing pipeline through the electric control valve three.
[0016] In the above technical scheme, preferably, the temperature increasing pipeline, the temperature decreasing pipeline and the bypass branch three are each provided with a one-way valve at one end close to the conveying main pipeline.
[0017] In the above technical scheme, preferably, the conveying main pipeline or the return main pipeline is provided with a conveying pump.
[0018] In the above technical scheme, preferably, the upper end surface of the compressor is provided with a cooling liquid outlet connected with the cooling flow channel, and the lower end surface is provided with a cooling liquid inlet connected with the cooling flow channel; the conveying main pipeline is connected with the cooling liquid inlet, and the return main pipeline is connected with the cooling liquid outlet.
[0019] In the above technical scheme, preferably, the conveying main pipeline or the return main pipeline is provided with a pressure relief valve.
[0020] In the above technical scheme, preferably, the conveying main pipeline or the return main pipeline is provided with a cooling liquid supplementing port.
[0021] The technical scheme of the utility model has the following beneficial effects:
[0022] The controllable liquid-cooled supercharging device can change the temperature of the gas at the outlet of the compressor by adjusting the temperature of the cooling liquid in the cooling flow channel, thereby affecting the efficiency of the compressor, and the running efficiency of the engine under all working conditions can be considered, the economic efficiency and the power performance of the engine under high speed are improved under the premise of ensuring the low speed performance of the engine, and the problem that the existing compressor cannot consider the running efficiency of the engine under all working conditions is overcome.
[0023] The controllable liquid-cooled supercharging device can reduce the temperature at the outlet of the compressor, effectively reduce the demand for the intercooler of the engine, and even can cancel the intercooler, and the effect of optimizing the matching system of the engine is achieved.
[0024] In addition to the purposes, characteristics and advantages described above, the utility model has other purposes, characteristics and advantages. BRIEF DESCRIPTION OF DRAWINGS
[0025] The accompanying drawings, which form a part of this application, are intended to provide further understanding of the present application and are incorporated herein in their entirety. The schematic embodiments of the present application and their descriptions serve to explain the present application and do not constitute an improper limitation on the present application. In the drawings:
[0026] Figure 1 is a performance diagram of an existing compressor;
[0027] Figure 2 is a cross-sectional view of a compressor air passage in Embodiment 1;
[0028] Figure 3 is a schematic diagram of a controllable performance liquid-cooled supercharging device in Embodiment 1;
[0029] Figure 4a is a schematic diagram of the position of a compressor operating point in a performance diagram when the coolant temperature is 30-40℃ in Embodiment 1;
[0030] Figure 4b is a schematic diagram of the position of a compressor operating point in a performance diagram when the coolant temperature is 50-60℃ in Embodiment 1;
[0031] Figure 5 is a schematic diagram of a controllable performance liquid-cooled supercharging device in Embodiment 2;
[0032] Wherein, 1, compressor, 1.1, air passage, 1.2, cooling flow passage, 1.3, exhaust port, 1.4, coolant outlet, 1.5, coolant inlet, 2, delivery main pipeline, 3, return main pipeline, 4, delivery pump, 5, heating pipeline, 5.1, heat exchanger, 5.2, bypass branch one, 5.3, electric control valve one, 5.4, heating branch, 6, cooling pipeline, 6.1, cooler, 6.2, bypass branch two, 6.3, electric control valve two, 6.4, cooling branch, 7, engine thermal management circulating loop, 8, pressure relief valve, 9, electric control valve three, 10, one-way valve, 11, bypass branch three, 12, electric control valve four. DETAILED DESCRIPTION
[0033] In order to facilitate the understanding of the present application, the present application will be described more fully below, and a preferred embodiment of the present application will be given. However, the present application can be realized in many different forms, and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the disclosure of the present application more thorough and comprehensive.
[0034] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which the present application belongs. The terms used in the specification of the present application herein are only for the purpose of describing specific embodiments and are not intended to limit the present application.
[0035] Embodiment 1:
[0036] Referring to Figure 2 and Figure 3 , the embodiment provides a liquid cooling supercharging device with controllable performance, which comprises a compressor 1, a delivery main pipeline 2, a return main pipeline 3 and a temperature adjusting pipeline, the compressor 1 is provided with a cooling flow channel 1.2 for heat exchange with gas in a gas channel 1.1 of the compressor 1 (i.e. cooling the gas in the gas channel), the cooling flow channel 1.2 is connected with the delivery main pipeline 2 and the return main pipeline 3, and the temperature adjusting pipeline is arranged between the delivery main pipeline 2 and the return main pipeline 3 and is used for adjusting the temperature of the cooling liquid entering the cooling flow channel 1.2.
[0037] Specifically, the cooling flow channel 1.2 is arranged at the outer periphery of the gas channel 1.1, the cooling flow channel 1.2 is consistent with the gas channel 1.1 in the direction, and the temperature of the cooling liquid entering the cooling flow channel 1.2 is changed through the temperature adjusting pipeline, so that the temperature of the gas at the exhaust port 1.3 of the gas channel 1.1 is changed (i.e. the cooling amplitude of the cooling liquid to the gas in the gas channel is adjusted through the temperature adjusting pipeline).
[0038] As shown in Figure 2 , the upper end surface of the compressor 1 is provided with a cooling liquid outlet 1.4 communicating with the cooling flow channel 1.2, and the lower end surface is provided with a cooling liquid inlet 1.5 communicating with the cooling flow channel 1.2, the cooling liquid outlet 1.4 is arranged above the cooling liquid inlet 1.5, so that the inside of the cooling flow channel 1.2 can be filled with cooling liquid, and the cooling effect of the gas in the gas channel 1.1 is improved; further, the delivery main pipeline 2 is connected with the cooling liquid inlet 1.5, and the return main pipeline 3 is connected with the cooling liquid outlet 1.4.
[0039] Further, the temperature adjusting pipeline in the embodiment comprises a temperature increasing pipeline 5 and a temperature decreasing pipeline 6; wherein the temperature increasing pipeline 5 is provided with a heat exchanger 5.1, the heat exchanger 5.1 is used for heat exchange between the temperature increasing pipeline 5 and an engine thermal management circulating loop 7, so as to increase the temperature of the cooling liquid; specifically, the temperature of the cooling water in the engine thermal management circulating loop 7 is generally 90-95℃, which is much higher than the temperature of the cooling liquid in the return main pipeline 3, so that the cooling liquid in the return main pipeline 3 can be heated through the heat exchanger 5.1.
[0040] Further, the cooling pipeline 6 is provided with a cooler 6.1, which is used to cool the coolant; preferably, the cooler 6.1 in the embodiment is a wind cooler, so as to cool the coolant in the return main pipeline 3. In some embodiments, the cooler 6.1 can also adopt other forms, such as a cooling heat exchanger, which is used to exchange heat with other cooling circuits to cool the coolant in the return main pipeline 3.
[0041] Therefore, the coolant can be heated or cooled by the heat exchanger 5.1 or the cooler 6.1, so as to adjust the temperature of the coolant entering the cooling flow channel 1.2.
[0042] Specifically, the heating pipeline 5 and the cooling pipeline 6 in the embodiment are arranged in series between the delivery main pipeline 2 and the return main pipeline 3, and the structural forms of the heating pipeline 5 and the cooling pipeline 6 are respectively as follows:
[0043] The heating pipeline 5 comprises a bypass branch 5.2, an electric control valve 5.3 and a heating branch 5.4, the heat exchanger 5.1 is arranged on the heating branch 5.4, the bypass branch 5.2 and the heating branch 5.4 are connected to the electric control valve 5.3, and the proportion of the coolant entering the bypass branch 5.2 and the heating branch 5.4 is distributed by the electric control valve 5.3; further, the proportion distribution between the bypass branch and the heating branch is realized by adjusting the opening degree of the electric control valve, and the proportion of the coolant between the bypass branch and the heating branch is a:b, wherein a+b=1, and the values of a and b are both [0, 1].
[0044] The cooling pipeline 6 comprises a bypass branch 6.2, an electric control valve 6.3 and a cooling branch 6.4, the cooler 6.1 is arranged on the cooling branch 6.4, the bypass branch 6.2 and the cooling branch 6.4 are connected to the electric control valve 6.3, and the proportion of the coolant entering the bypass branch 6.2 and the cooling branch 6.4 is distributed by the electric control valve 6.3; further, the proportion distribution between the bypass branch and the cooling branch is realized by adjusting the opening degree of the electric control valve, and the proportion of the coolant between the bypass branch and the cooling branch is c:d, wherein c+d=1, and the values of c and d are both [0, 1].
[0045] The heating pipeline 5 and the cooling pipeline 6 have two series connection modes, one is that the heating pipeline 5 and the cooling pipeline 6 are arranged in the direction from the return main pipeline 3 to the delivery main pipeline 2, and the other is that the cooling pipeline 6 and the heating pipeline 5 are arranged in the direction from the return main pipeline 3 to the delivery main pipeline 2.
[0046] For example, the heating pipeline 5 and the cooling pipeline 6 are arranged in the direction from the return main pipeline 3 to the delivery main pipeline 2. Figure 3As shown, the series connection mode of the heating pipeline 5 and the cooling pipeline 6 in the embodiment adopts the first mode, the electric control valve one 5.3 is connected with the return main pipeline 3, the bypass branch one 5.2 and the heating branch 5.4, and the proportion of the cooling liquid in the return main pipeline 3 entering the bypass branch one 5.2 and the heating branch 5.4 is controlled through the electric control valve one 5.3; through the electric control valve one 5.3, the cooling liquid can all enter the bypass branch one 5.2 or the heating branch 5.4, or part of the cooling liquid enters the bypass branch one 5.2 and the other part enters the heating branch 5.4; therefore, by adjusting the proportion of the cooling liquid entering the bypass branch one 5.2 and the heating branch 5.4, the temperature of the cooling liquid can be adjusted in the range. Further, the electric control valve two 6.3 is connected with the output end of the heating pipeline 5, the bypass branch two 6.2 and the cooling branch 6.4, and the proportion of the cooling liquid from the heating pipeline 5 entering the bypass branch two 6.2 and the cooling branch 6.4 is controlled through the electric control valve two 6.3, and similarly, the temperature of the cooling liquid can be adjusted in the range through the electric control valve two 6.3.
[0047] The control logic for realizing the heating of the cooling liquid in the embodiment is as follows: 1) the cooling liquid from the return main pipeline 3 all enters the heating branch 5.4 to be heated, and then enters the delivery main pipeline 2 through the bypass branch two 6.2, and in this control mode, the heating degree of the cooling liquid is the largest; 2) the cooling liquid from the return main pipeline 3 enters the heating branch 5.4 partially and enters the bypass branch one 5.2 with the rest, the cooling liquid in the heating branch 5.4 after being heated is mixed with the cooling liquid in the bypass branch one 5.2 which is not heated, and then enters the bypass branch two 6.2, and finally enters the delivery main pipeline 2, and in this control mode, because the cooling liquid is distributed in the heating branch 5.4 and the bypass branch one 5.2 in different proportions, the final heating degree of the cooling liquid is also different, and the more the cooling liquid enters the heating branch 5.4, the greater the final heating degree of the cooling liquid.
[0048] The control logic for realizing the cooling of the cooling liquid in the embodiment is as follows: 1) the cooling liquid from the return main pipeline 3 is delivered through the bypass branch one 5.2, and then all enters the cooling branch 6.4 before entering the delivery main pipeline 2, and in this control mode, the cooling degree of the cooling liquid is the largest; 2) the cooling liquid from the return main pipeline 3 is delivered through the bypass branch one 5.2, and then part of the cooling liquid enters the cooling branch 6.4 and the rest enters the bypass branch two 6.2, the cooling liquid in the cooling branch 6.4 after being cooled is mixed with the cooling liquid in the bypass branch two 6.2 which is not cooled, and then enters the delivery main pipeline 2, and in this control mode, because the cooling liquid is distributed in the cooling branch 6.4 and the bypass branch two 6.2 in different proportions, the final cooling degree of the cooling liquid is also different, and the more the cooling liquid enters the cooling branch 6.4, the greater the final cooling degree of the cooling liquid.
[0049] Referring to Figure 3 , the delivery main pipeline 2 or the return main pipeline 3 is provided with a delivery pump 4 for providing driving force for circulation of the cooling liquid; preferably, the delivery pump 4 is arranged on the return main pipeline 3 in the embodiment.
[0050] Referring to Figure 3 , the delivery main pipeline 2 or the return main pipeline 3 is provided with a pressure relief valve 8 for relieving pressure when overpressure occurs in the cooling liquid circulation loop of the liquid-cooled supercharger of the embodiment, thereby protecting the cooling liquid circulation loop; preferably, the pressure relief valve 8 is arranged on the delivery main pipeline 2 in the embodiment.
[0051] Preferably, the delivery main pipeline 2 or the return main pipeline 3 is provided with a cooling liquid supplement port (not shown) for supplementing the cooling liquid circulation loop of the liquid-cooled supercharger of the embodiment with cooling liquid, thereby ensuring normal operation of the cooling liquid circulation loop and cooling effect on the gas in the air passage.
[0052] Preferably, the electrically-controlled valve one 5.3 and the electrically-controlled valve two 6.3 in the embodiment are proportional control valves.
[0053] The working control logic of the liquid-cooled supercharger of the embodiment is as follows:
[0054] When the engine is in a low-speed working condition, the cooling pipeline is controlled to cool the cooling liquid to the maximum extent, the delivery pump works at full speed and full load, the temperature of the cooling liquid entering the cooling flow passage is controlled to be 30-40℃, and the working point of the compressor is located at the lower left corner of the compressor performance map, as shown in Figure 4a , and the peak efficiency is higher than that of a conventional compressor;
[0055] When the engine is in a high-speed working condition, the heating pipeline is controlled to heat the cooling liquid to the maximum extent, the delivery pump works at full speed and full load, the temperature of the cooling liquid entering the cooling flow passage is controlled to be 50-60℃, and the working point of the compressor is located at the center of the compressor performance map, as shown in Figure 4b ;
[0056] When the engine is in a medium-speed working condition or a partial load condition, the delivery pump works at full speed and full load, the bypass branch one 5.2 and the heating branch 5.4 are controlled to proportionally distribute the cooling liquid to heat the cooling liquid (non-maximum heating), or the bypass branch two 6.2 and the cooling branch 6.4 are controlled to proportionally distribute the cooling liquid to cool the cooling liquid (non-maximum cooling), thereby meeting the cooling liquid temperature requirement and finally controlling the compressor performance; wherein, when the engine is in a medium-speed working condition, the working point of the compressor is controlled to be located at the left side of the compressor performance map; and when the engine is in a partial load condition, the working point of the compressor is controlled to be located below the compressor performance map.
[0057] Embodiment 2:
[0058] The embodiment provides another liquid-cooled supercharging device with controllable performance, and the only difference between the embodiment and the embodiment 1 is that the temperature adjusting pipeline in the embodiment further comprises a bypass branch three 11, wherein the bypass branch three 11, the temperature increasing pipeline 5 and the temperature decreasing pipeline 6 are arranged in parallel between the conveying main pipeline 2 and the return main pipeline 3, as shown in the figure; the bypass branch three 11 is connected with the return main pipeline 3 through an electric control valve four 12, the temperature increasing pipeline 5 and the temperature decreasing pipeline 6 are connected with the electric control valve three 9 at the end of the return main pipeline 3, the bypass branch three 11 controls the shunt proportion of the cooling liquid in the return main pipeline 3 through the electric control valve four 12, and the cooling liquid in the return main pipeline 3 enters the temperature increasing pipeline 5 or the temperature decreasing pipeline 6 through the electric control valve three 9. Figure 5
[0059] Further, the temperature increasing pipeline 5 is provided with a heat exchanger 5.1, heat exchange is realized between the temperature increasing pipeline 5 and the engine thermal management circulating loop 7 through the heat exchanger 5.1, and the cooling liquid is heated; the temperature decreasing pipeline 6 is provided with a cooler 6.1, and the cooler 6.1 is used for realizing temperature decreasing of the cooling liquid.
[0060] The temperature increasing pipeline 5 and the temperature decreasing pipeline 6 in the embodiment do not input the cooling liquid at the same time, the proportion of the cooling liquid between the bypass branch three 11 and the temperature increasing pipeline 5 is e:f, wherein e+f=1, the values of e and f are both [0, 1], and similarly, the proportion of the cooling liquid between the bypass branch three 11 and the temperature decreasing pipeline 6 is e:k, wherein e+k=1, the values of e and k are both [0, 1].
[0061] Preferably, the electric control valve three 9 and the electric control valve four 12 in the embodiment are both selected to be proportional control valves; it should be noted that the electric control valve three 9 does not necessarily have to be selected to be a proportional control valve, for example, a two-position three-way electromagnetic valve is also possible.
[0062] Preferably, the temperature increasing pipeline 5, the temperature decreasing pipeline 6 and the bypass branch three 11 are all provided with a one-way valve 10 at one end close to the conveying main pipeline 2, the one-way valve 10 can prevent the cooling liquid from flowing back, and ensures that the cooling liquid circulating loop of the liquid-cooled supercharging device in the embodiment works normally.
[0063] The control logic for the cooling liquid temperature rise in this embodiment is: 1) the cooling liquid from the return main pipeline 3 enters the temperature rise pipeline 5 and then enters the delivery main pipeline 2, and the control mode is the maximum temperature rise of the cooling liquid; 2) the cooling liquid from the return main pipeline 3 enters the bypass branch three 11 and the temperature rise pipeline 5, and the cooling liquid from the temperature rise pipeline 5 and the cooling liquid from the bypass branch three 11 enter the delivery main pipeline 2, and the control mode is different in the proportion of the cooling liquid from the bypass branch three 11, so the temperature rise of the cooling liquid is different, and the more the cooling liquid from the temperature rise pipeline 5, the greater the temperature rise of the cooling liquid.
[0064] The control logic for the cooling liquid temperature rise in this embodiment is: 1) the cooling liquid from the return main pipeline 3 enters the temperature rise pipeline 5 and then enters the delivery main pipeline 2, and the control mode is the maximum temperature rise of the cooling liquid; 2) the cooling liquid from the return main pipeline 3 enters the temperature rise pipeline 5 and the temperature rise pipeline 5 and the cooling liquid from the bypass branch three 11 enter the delivery main pipeline 2, and the control mode is different in the proportion of the cooling liquid from the bypass branch three 11, so the temperature rise of the cooling liquid is different, and the more the cooling liquid from the temperature rise pipeline 5, the greater the temperature rise of the cooling liquid.
[0065] The working control logic of the liquid-cooled supercharging device in this embodiment is:
[0066] When the engine is in a low-speed working condition, the temperature rise pipeline 5 controls the cooling liquid to the maximum temperature rise, and the delivery pump works at full speed and full load, and the temperature of the cooling liquid entering the cooling flow passage is controlled at 30-40℃, and at this time the working point of the compressor is located at the lower left corner of the compressor performance map, and the peak efficiency is higher than that of the traditional compressor;
[0067] When the engine is in a high-speed working condition, the temperature rise pipeline 5 controls the cooling liquid to the maximum temperature rise, and the delivery pump works at full speed and full load, and the temperature of the cooling liquid entering the cooling flow passage is controlled at 50-60℃, and at this time the working point of the compressor is located at the center position of the compressor performance map;
[0068] When the engine is in the medium speed working condition or the partial load, the delivery pump works in the full speed and full load, the bypass branch three 11 and the temperature increasing pipeline 5 are controlled to proportionally distribute the coolant to realize the temperature increasing of the coolant (non-maximum temperature increasing), or the bypass branch three 11 and the temperature decreasing pipeline 6 are controlled to proportionally distribute the coolant to realize the temperature decreasing of the coolant (non-maximum temperature decreasing), so as to meet the coolant temperature requirement and finally control the compressor performance; wherein: when the engine is in the medium speed working condition, the compressor working point is located at the left side position of the compressor performance diagram; when the engine is in the partial load, the compressor working point is located at the lower position of the compressor performance diagram.
[0069] The preferred embodiments of the utility model are described above only, and are not used to limit the utility model, for the person skilled in the art, the utility model can have various changes and changes. Any modification, equivalent replacement, improvement etc. that is made within the spirit and principle of the utility model should be included in the protection scope of the utility model.
Claims
1. A liquid-cooled supercharging device with controllable performance, characterized in that, The temperature adjusting pipeline comprises a temperature raising pipeline (5) and a temperature lowering pipeline (6). The temperature raising pipeline (5) is provided with a heat exchanger (5.1), and the heat exchanger (5.1) is used for heat exchange between the temperature raising pipeline (5) and an engine thermal management circulating loop (7), so that the coolant is raised in temperature. The temperature lowering pipeline (6) is provided with a cooler (6.1), and the cooler (6.1) is used for lowering the temperature of the coolant. The temperature of the coolant entering the cooling flow channel (1.2) is adjusted through the work of the heat exchanger (5.1) or the cooler (6.1). The temperature raising pipeline (5) and the temperature lowering pipeline (6) are arranged in series between the delivery main pipeline (2) and the return main pipeline (3).
2. The liquid-cooled supercharging device of controllable performance according to claim 1, characterized in that, The temperature raising pipeline (5) comprises a bypass branch one (5.2), an electric control valve one (5.3) and a temperature raising branch (5.4), the heat exchanger (5.1) is arranged on the temperature raising branch (5.4), the bypass branch one (5.2) and the temperature raising branch (5.4) are connected with the electric control valve one (5.3), and the proportion of the coolant entering the bypass branch one (5.2) and the temperature raising branch (5.4) is distributed through the electric control valve one (5.3). The temperature lowering pipeline (6) comprises a bypass branch two (6.2), an electric control valve two (6.3) and a temperature lowering branch (6.4), the cooler (6.1) is arranged on the temperature lowering branch (6.4), the bypass branch two (6.2) and the temperature lowering branch (6.4) are connected with the electric control valve two (6.3), and the proportion of the coolant entering the bypass branch two (6.2) and the temperature lowering branch (6.4) is distributed through the electric control valve two (6.3). The temperature adjusting pipeline further comprises a bypass branch three (11), the bypass branch three (11), the temperature raising pipeline (5) and the temperature lowering pipeline (6) are arranged in parallel between the delivery main pipeline (2) and the return main pipeline (3), the bypass branch three (11) is connected with the return main pipeline (3) through an electric control valve four (12), the temperature raising pipeline (5) and the temperature lowering pipeline (6) are connected with an electric control valve three (9) at the end of the return main pipeline (3), the shunt proportion of the coolant in the return main pipeline (3) by the bypass branch three (11) is controlled through the electric control valve four (12), and the coolant in the return main pipeline (3) is controlled to enter the temperature raising pipeline (5) or the temperature lowering pipeline (6) through the electric control valve three (9).
3. The liquid-cooled energy performance controllable supercharging device according to claim 1, characterized in that, The temperature raising pipeline (5), the temperature lowering pipeline (6) and the bypass branch three (11) are each provided with a one-way valve (10) at one end close to the delivery main pipeline (2).
4. The liquid-cooled supercharging device of controllable performance according to claim 3, characterized in that, 5. The liquid-cooled supercharging device according to any one of claims 1 to 4, wherein The delivery main pipeline (2) or the return main pipeline (3) is provided with a delivery pump (4).
6. The liquid-cooled supercharging device of controllable performance according to any one of claims 1-4, characterized in that, The upper end surface of the compressor (1) is provided with a cooling liquid outlet (1.4) communicating with the cooling flow channel (1.2), and the lower end surface is provided with a cooling liquid inlet (1.5) communicating with the cooling flow channel (1.2); the delivery main pipeline (2) is connected to the cooling liquid inlet (1.5), and the return main pipeline (3) is connected to the cooling liquid outlet (1.4).
7. The liquid-cooled energy recuperation device of any of claims 1-4, wherein, The delivery main pipeline (2) or the return main pipeline (3) is provided with a pressure relief valve (8).
8. The liquid-cooled energy recuperation device of any of claims 1-4, wherein, The delivery main pipeline (2) or the return main pipeline (3) is provided with a cooling liquid supplement port.