A liquid-cooled supercharging device with controllable performance

Abstract

The present invention provides a liquid-cooled supercharging device with controllable performance, comprising a compressor, a delivery main line, a return main line and a temperature regulating line, wherein the compressor is provided with a cooling channel for heat exchange with the gas in the airway of the compressor, the cooling channel connects the delivery main line and the return main line, a temperature regulating line is provided between the delivery main line and the return main line, and the temperature regulating line is used to adjust the temperature of the coolant entering the cooling channel. The liquid-cooled supercharging device with controllable performance of the present invention can change the temperature of the compressor outlet gas by adjusting the temperature of the coolant entering the cooling channel, thereby affecting the efficiency of the compressor, and can take into account the operating efficiency of the engine under all working conditions. Under the premise of ensuring the low-speed performance of the engine, the economy and power of the engine at medium and high speeds are improved by controlling the temperature, thereby overcoming the problem that the existing compressor cannot take into account the operating efficiency of the engine under all working conditions.

Description

Technical Field

[0001] The invention relates to the technical field of supercharging, and in particular to a liquid-cooled supercharging device with controllable performance. Background Art

[0002] A traditional turbocharger is a mechanical device that uses the energy of the exhaust gas discharged by the engine to further boost the pressure. It uses the exhaust gas energy of the engine to drive the turbine in the turbine box to rotate, and the turbine drives the coaxial compressor impeller to work. The electronic supercharger uses a 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 the fresh air to achieve the boosting effect. Therefore, both traditional turbochargers and electronic superchargers can increase the amount of air in the cylinder of the same displacement engine, optimize the combustion process, and improve the engine's working efficiency.

[0003] During the operation of the supercharger, as the speed and pressure ratio of the compressor increase, gas compression will generate a large amount of heat loss, resulting in an increase in the temperature of the compressor outlet gas; generally, the compressor outlet temperature is around 50°C when the engine is operating at low speed, and the compressor outlet temperature is often over 100°C when the engine is operating at rated conditions. On the one hand, the compressor outlet temperature will affect the combustion of the engine and may even cause phenomena such as engine knocking. Therefore, it is necessary to set an intercooler at the rear end of the compressor to cool the compressor outlet gas temperature through coolant or air cooling before entering the engine cylinder for combustion; on the other hand, the compressor outlet gas temperature is a key parameter of the compressor performance, which is closely related to the efficiency of the compressor and ultimately affects the overall economy of the engine.

[0004] The performance of the compressor is sensitive to the temperature of the gas. Figure 1 As mentioned above, the working range of the compressor is mainly composed of the left dashed surge line, the upper maximum speed line and the right dashed blockage line, where the equal efficiency circle is the efficiency range of the compressor. In the existing traditional turbocharging technology or electronic supercharger, the maximum efficiency of the compressor is often designed under common working conditions for economic considerations and the working characteristics of the engine, and the efficiency of other working conditions is often not taken into account, that is, the range of the compressor efficiency circle is limited by the geometric size constraints of the compressor (that is, the geometric size constraints of the compressor lead to a smaller range of the compressor efficiency circle), and the operating efficiency of the engine under all working conditions cannot be taken into account.

[0005] In summary, there is an urgent need for a liquid-cooled supercharging device with controllable performance to solve the problems existing in the prior art. Summary of the invention

[0006] The present invention aims to provide a liquid-cooled supercharging device with controllable performance, aiming to solve the problem that the range of the existing compressor efficiency circle is limited by the geometric size constraints of the compressor and cannot take into account the operating efficiency of the engine under all working conditions. The specific technical solution is as follows:

[0007] A liquid-cooled supercharging device with controllable performance comprises a compressor, a main delivery line, a return line and a temperature regulating pipeline. The compressor is provided with a cooling channel for heat exchange with gas in the airway of the compressor. The cooling channel connects the main delivery line and the return line. A temperature regulating pipeline is provided between the main delivery line and the return line. The temperature regulating pipeline is used to adjust the temperature of the coolant entering the cooling channel.

[0008] Preferably, in the above technical solution, the temperature regulating pipeline includes a heating pipeline and a cooling pipeline;

[0009] The heating pipeline is provided with a heat exchanger, and the heat exchanger is used for heat exchange between the heating pipeline and the engine thermal management circulation loop to achieve heating of the coolant;

[0010] The cooling pipeline is provided with a cooler, and the cooler is used to cool the coolant;

[0011] The temperature of the coolant entering the cooling channel is adjusted by working with a heat exchanger or a cooler.

[0012] Preferably, in the above technical solution, the heating pipeline and the cooling pipeline are arranged in series between the main delivery pipeline and the main return pipeline;

[0013] The temperature-raising pipeline includes a bypass branch 1, an electric control valve 1 and a temperature-raising branch. The heat exchanger is arranged on the temperature-raising branch. Both the bypass branch 1 and the temperature-raising branch are connected to the electric control valve 1. The electric control valve 1 distributes the ratio of coolant entering the bypass branch 1 and the temperature-raising branch.

[0014] The cooling pipeline includes a bypass branch 2, an electric control valve 2 and a cooling branch. The cooler is arranged on the cooling branch. The bypass branch 2 and the cooling branch are both connected to the electric control valve 2. The electric control valve 2 distributes the ratio of coolant entering the bypass branch 2 and the cooling branch.

[0015] Preferably in the above technical scheme, the temperature regulating pipeline also includes a bypass branch three, and the bypass branch three, the heating pipeline and the cooling pipeline are arranged in parallel between the delivery main pipeline and the return main pipeline; the bypass branch three is connected to the return main pipeline through an electric control valve four, and the heating pipeline and the cooling pipeline are connected in parallel to the electric control valve three at the end of the return main pipeline, and the diversion ratio of the coolant in the return main pipeline by the bypass branch three is controlled by the electric control valve four, and the coolant in the return main pipeline is controlled by the electric control valve three to enter the heating pipeline or the cooling pipeline.

[0016] Preferably in the above technical solution, the heating pipeline, the cooling pipeline and the bypass branch are all provided with a one-way valve at one end close to the main delivery pipeline.

[0017] Preferably in the above technical solution, a delivery pump is provided on the delivery main line or the return main line.

[0018] Preferably in the above technical solution, the upper end face of the compressor is provided with a coolant outlet connected to the cooling channel, and the lower end face thereof is provided with a coolant inlet connected to the cooling channel; the delivery main line is connected to the coolant inlet, and the return main line is connected to the coolant outlet.

[0019] Preferably in the above technical solution, a pressure relief valve is provided on the main delivery line or the return line.

[0020] Preferably in the above technical solution, a coolant replenishing port is provided on the main delivery line or the return main line.

[0021] The application of the technical solution of the present invention has the following beneficial effects:

[0022] The controllable performance liquid-cooled supercharging device of the present invention can change the compressor outlet gas temperature by adjusting the temperature of the coolant entering the cooling channel, thereby affecting the efficiency of the compressor, and can take into account the operating efficiency of the engine under all working conditions. Under the premise of ensuring the low-speed performance of the engine, the economy and power of the engine at medium and high speeds are improved by controlling the temperature, thus overcoming the problem that the existing compressor cannot take into account the operating efficiency of the engine under all working conditions.

[0023] The controllable performance liquid-cooled supercharging device of the present invention can reduce the compressor outlet temperature, effectively reduce the demand for the engine intercooler, and can even eliminate the intercooler, thereby achieving the effect of optimizing the engine supporting system.

[0024] In addition to the above-described purposes, features and advantages, the present invention has other purposes, features and advantages. The present invention will be further described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The drawings constituting a part of this application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0026] Figure 1 It is a performance diagram of an existing compressor;

[0027] Figure 2 is a cross-sectional view of the air duct of the compressor in Example 1;

[0028] Figure 3 is a schematic diagram of a liquid-cooled supercharging device with controllable performance in Example 1;

[0029] Figure 4aIt is a schematic diagram of the position of the compressor operating point in the performance diagram when the coolant temperature is 30-40° C. in Example 1;

[0030] Figure 4b It is a schematic diagram of the position of the compressor operating point in the performance diagram when the coolant temperature is 50-60° C. in Example 1;

[0031] Figure 5 is a schematic diagram of a liquid-cooled supercharging device with controllable performance in Example 2;

[0032] Among them, 1. compressor, 1.1. air duct, 1.2. cooling flow channel, 1.3. exhaust port, 1.4. coolant outlet, 1.5. coolant inlet, 2. delivery main line, 3. return main line, 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 cycle, 8. pressure relief valve, 9. electric control valve three, 10. check valve, 11. bypass branch three, 12. electric control valve four. DETAILED DESCRIPTION

[0033] In order to facilitate the understanding of the present invention, the present invention will be described more comprehensively below, and preferred embodiments of the present invention are provided. However, the present invention can be implemented 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 understanding of the disclosure of the present invention more thorough and comprehensive.

[0034] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art of the present invention. The terms used in the specification of the present invention herein are only for the purpose of describing specific embodiments and are not intended to limit the present invention.

[0035] Embodiment 1:

[0036] See also Figure 2 and Figure 3 The present embodiment provides a liquid-cooled supercharging device with controllable performance, comprising a compressor 1, a delivery main line 2, a return main line 3 and a temperature regulating pipeline. The compressor 1 is provided with a cooling channel 1.2 for performing heat exchange with the gas in the air duct 1.1 of the compressor 1 (i.e., cooling the gas in the air duct). The cooling channel 1.2 connects the delivery main line 2 and the return main line 3. A temperature regulating pipeline is provided between the delivery main line 2 and the return main line 3. The temperature regulating pipeline is used to adjust the temperature of the coolant entering the cooling channel 1.2.

[0037] Specifically, the cooling channel 1.2 is arranged on the periphery of the air channel 1.1, and the direction of the cooling channel 1.2 is consistent with the direction of the air channel 1.1. The temperature of the coolant entering the cooling channel 1.2 is changed by a temperature regulating pipeline, so as to achieve the effect of changing the gas temperature at the exhaust port 1.3 of the air channel 1.1 (that is, the cooling amplitude of the coolant on the gas in the air channel is adjusted by the temperature regulating pipeline).

[0038] like Figure 2 As shown, the upper end surface of the compressor 1 is provided with a coolant outlet 1.4 connected to the cooling channel 1.2, and the lower end surface is provided with a coolant inlet 1.5 connected to the cooling channel 1.2. The coolant outlet 1.4 is arranged above the coolant inlet 1.5 to ensure that the interior of the cooling channel 1.2 can be filled with coolant, thereby improving the effect of cooling the gas in the air channel 1.1; further, the delivery main line 2 is connected to the coolant inlet 1.5, and the return main line 3 is connected to the coolant outlet 1.4.

[0039] Furthermore, the temperature regulating pipeline in this embodiment includes a heating pipeline 5 and a cooling pipeline 6; wherein, a heat exchanger 5.1 is provided on the heating pipeline 5, and the heat exchanger 5.1 is used for heat exchange between the heating pipeline 5 and the engine thermal management circulation loop 7 to achieve heating of the coolant; specifically, under normal circumstances, the cooling water temperature in the engine thermal management circulation loop 7 is 90°C to 95°C, which is much higher than the temperature of the coolant in the return main pipeline 3, so the coolant in the return main pipeline 3 can be heated by the heat exchanger 5.1.

[0040] Furthermore, the cooling pipeline 6 is provided with a cooler 6.1, and the cooler 6.1 is used to cool the coolant; preferably, the cooler 6.1 in this embodiment is an air cooler, so as to cool the coolant in the return main pipeline 3. In some embodiments, the cooler 6.1 may also be in other forms, such as a cooling heat exchanger, and the cooling heat exchanger is heat-exchanged with other cooling circuits to cool the coolant from the return main pipeline 3.

[0041] Therefore, by operating the heat exchanger 5.1 or the cooler 6.1, the temperature of the coolant can be increased or decreased, thereby adjusting the temperature of the coolant entering the cooling channel 1.2.

[0042] Specifically, in this embodiment, the heating pipeline 5 and the cooling pipeline 6 are arranged in series between the delivery main pipeline 2 and the return main pipeline 3, and the structures of the heating pipeline 5 and the cooling pipeline 6 are respectively:

[0043] The temperature-raising pipeline 5 comprises a bypass branch 5.2, an electric-controlled valve 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 5.2 and the temperature-raising branch 5.4 are both connected to the electric-controlled valve 5.3, and the electric-controlled valve 5.3 is used to distribute the ratio of the coolant entering the bypass branch 5.2 and the temperature-raising branch 5.4; further, the proportional distribution between the bypass branch 1 and the temperature-raising branch is achieved by adjusting the opening of the electric-controlled valve 1, and the ratio of the coolant between the bypass branch 1 and the temperature-raising branch is a:b, wherein a+b=1, and the values ​​of a and b are both [0, 1].

[0044] The cooling pipeline 6 includes 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 both connected to the electric control valve 6.3. The electric control valve 6.3 distributes the ratio of the coolant entering the bypass branch 6.2 and the cooling branch 6.4. Furthermore, the proportional distribution between the bypass branch 6.2 and the cooling branch is achieved by adjusting the opening of the electric control valve 2. The ratio of the coolant between the bypass branch 2 and the cooling branch is c:d, wherein c+d=1, and the values ​​of c and d are both [0, 1].

[0045] Among them, there are two ways to connect the heating pipeline 5 and the cooling pipeline 6 in series. The first is to arrange the heating pipeline 5 and the cooling pipeline 6 in sequence from the return main line 3 to the delivery main line 2. The second is to arrange the cooling pipeline 6 and the heating pipeline 5 in sequence from the return main line 3 to the delivery main line 2.

[0046] like Figure 3 As shown, in this embodiment, the first type of serial connection method of the heating pipeline 5 and the cooling pipeline 6 is adopted, and the electric control valve 5.3 connects the return main pipeline 3, the bypass branch 5.2 and the heating branch 5.4. The electric control valve 5.3 controls the ratio of the coolant in the return main pipeline 3 entering the bypass branch 5.2 and the heating branch 5.4; the electric control valve 5.3 can be used to achieve that all the coolant enters the bypass branch 5.2 or the heating branch 5.4, and it can also be achieved that a part of the coolant enters the bypass branch 5.2 and the other part enters the heating branch 5.4; therefore, by adjusting the ratio of the coolant entering the bypass branch 5.2 and the heating branch 5.4, the temperature of the coolant can be adjusted within a certain range. Furthermore, the electric control valve 6.3 is connected to the output end of the heating pipeline 5, the bypass branch 6.2 and the cooling branch 6.4, and the electric control valve 6.3 controls the ratio of the coolant from the heating pipeline 5 entering the bypass branch 6.2 and the cooling branch 6.4. Similarly, the temperature of the coolant can be adjusted within a range through the electric control valve 6.3.

[0047] The control logic for achieving the temperature increase of the coolant in this embodiment is: 1) all the coolant from the return main line 3 enters the temperature increase branch 5.4 for temperature increase, and then enters the delivery main line 2 through the bypass branch 2 6.2. Under this control mode, the degree of temperature increase of the coolant is the greatest; 2) part of the coolant from the return main line 3 enters the temperature increase branch 5.4, and the remaining part enters the bypass branch 1 5.2. The heated coolant in the temperature increase branch 5.4 is mixed with the unheated coolant in the bypass branch 1 5.2 and enters the bypass branch 2 6.2 together, and finally enters the delivery main line 2. Under this control mode, since the ratio of coolant allocated to the temperature increase branch 5.4 and the bypass branch 1 5.2 is different, the degree of temperature increase of the coolant is also different. The more coolant enters the temperature increase branch 5.4, the greater the degree of temperature increase of the coolant is.

[0048] The control logic for cooling the coolant in this embodiment is as follows: 1) the coolant from the return main line 3 is transported through the bypass branch 1 5.2, and then all enters the cooling branch 6.4 before entering the delivery main line 2. Under this control mode, the degree of cooling of the coolant is the greatest; 2) the coolant from the return main line 3 is transported through the bypass branch 1 5.2, and then a part of it enters the cooling branch 6.4, and the remaining part enters the bypass branch 2 6.2. The coolant after cooling in the cooling branch 6.4 is mixed with the coolant not cooled in the bypass branch 2 6.2 and enters the delivery main line 2 together. Under this control mode, since the cooling liquid ratios allocated to the cooling branch 6.4 and the bypass branch 2 6.2 are different, the degree of cooling of the coolant is also different. The more coolant enters the cooling branch 6.4, the greater the degree of cooling of the coolant is.

[0049] See also Figure 3 A delivery pump 4 is provided on the delivery main line 2 or the return main line 3, and the delivery pump 4 is used to provide a driving force for the circulation of the coolant; preferably, in this embodiment, the delivery pump 4 is arranged on the return main line 3.

[0050] See also Figure 3 A pressure relief valve 8 is provided on the delivery main line 2 or the return main line 3. When overpressure occurs in the coolant circulation loop of the liquid-cooled booster device of this embodiment, pressure relief can be provided through the pressure relief valve 8 to protect the coolant circulation loop. Preferably, in this embodiment, the pressure relief valve 8 is provided on the delivery main line 2.

[0051] Preferably, a coolant replenishing port (not shown) is provided on the delivery main line 2 or the return main line 3, and the coolant replenishing port is used to replenish the coolant of the coolant circulation loop of the liquid-cooled booster device of this embodiment, thereby ensuring the normal operation of the coolant circulation loop and the cooling effect on the gas in the airway.

[0052] Preferably, the electric control valve 1 5.3 and the electric control valve 2 6.3 in this embodiment are both proportional control valves.

[0053] The working control logic of the liquid cooling and boosting device of this embodiment is:

[0054] When the engine is in low speed condition, the cooling pipeline is controlled to cool the coolant to the maximum extent, the delivery pump works at full speed and full load, and the coolant temperature entering the cooling channel is controlled at 30-40℃. At this time, the compressor operating point is located in the lower left corner of the compressor performance diagram, such as Figure 4a As shown, the peak efficiency is higher than that of the traditional compressor;

[0055] When the engine is in high-speed operation, the temperature-raising pipeline is controlled to raise the temperature of the coolant to the maximum extent, the delivery pump works at full speed and full load, and the temperature of the coolant entering the cooling channel is controlled at 50-60°C. At this time, the compressor operating point is located at the center of the compressor performance diagram, such as Figure 4b As shown;

[0056] When the engine is in medium speed condition or partial load, the delivery pump works at full speed and full load, and the bypass branch 1 5.2 and the heating branch 5.4 are controlled to distribute the coolant in proportion to achieve the heating of the coolant (not the maximum heating), or the bypass branch 2 6.2 and the cooling branch 6.4 are controlled to distribute the coolant in proportion to achieve the cooling of the coolant (not the maximum cooling), so as to meet the coolant temperature demand and finally control the compressor performance; wherein: when the engine is in medium speed condition, the compressor operating point is controlled to be located at the left side of the compressor performance diagram; when the engine is in partial load, the compressor operating point is controlled to be located at the bottom of the compressor performance diagram.

[0057] Embodiment 2:

[0058] This embodiment provides another liquid-cooled boosting device with controllable performance, which is different from the embodiment 1 only in that: the temperature regulating pipeline in this embodiment also includes a bypass branch 3 11, wherein the bypass branch 3 11, the heating pipeline 5 and the cooling pipeline 6 are arranged in parallel between the delivery main pipeline 2 and the return main pipeline 3, such as Figure 5 As shown; the bypass branch three 11 is connected to the return main line 3 through the electric control valve four 12, the heating line 5 and the cooling line 6 are connected in parallel to the electric control valve three 9 at the end of the return main line 3, the electric control valve four 12 controls the diversion ratio of the bypass branch three 11 to the coolant in the return main line 3, and the electric control valve three 9 controls the coolant in the return main line 3 to enter the heating line 5 or the cooling line 6.

[0059] Furthermore, the heating pipeline 5 is provided with a heat exchanger 5.1, through which the heating pipeline 5 and the engine thermal management circulation loop 7 can exchange heat to heat the coolant; the cooling pipeline 6 is provided with a cooler 6.1, and the cooler 6.1 is used to cool the coolant.

[0060] In this embodiment, the heating pipeline 5 and the cooling pipeline 6 will not input coolant at the same time. The coolant ratio between the bypass branch three 11 and the heating pipeline 5 is e:f, where e+f=1, and the values ​​of e and f are both [0, 1]. Similarly, the coolant ratio between the bypass branch three 11 and the cooling pipeline 6 is e:k, where e+k=1, and 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 this embodiment are both proportional control valves; it should be noted that the electric control valve three 9 does not necessarily have to be a proportional control valve, for example, a two-position three-way solenoid valve is also acceptable.

[0062] Preferably, the heating pipeline 5, the cooling pipeline 6 and the bypass branch 11 are all provided with a one-way valve 10 at one end close to the main delivery pipeline 2. The one-way valve 10 can prevent the coolant from flowing back, thereby ensuring the normal operation of the coolant circulation circuit of the liquid-cooled booster device of this embodiment.

[0063] The control logic for achieving the cooling liquid heating in this embodiment is: 1) all the cooling liquid from the return main line 3 enters the heating line 5, and then enters the delivery main line 2. Under this control mode, the degree of cooling liquid heating is the greatest; 2) part of the cooling liquid from the return main line 3 enters the bypass branch line 3 11, and the other part enters the heating line 5. The heated cooling liquid in the heating line 5 is mixed with the unheated cooling liquid in the bypass branch line 3 11 and enters the delivery main line 2 together. Under this control mode, due to the different proportions of the cooling liquid diverted by the bypass branch line 3 11, the degree of cooling liquid heating is ultimately different. The more cooling liquid enters the heating line 5, the greater the degree of cooling liquid heating is ultimately.

[0064] The control logic for achieving cooling of the coolant in this embodiment is: 1) all the coolant from the return main line 3 enters the cooling line 6, and then enters the delivery main line 2. Under this control mode, the degree of cooling of the coolant is the greatest; 2) part of the coolant from the return main line 3 enters the bypass branch three 11, and the other part enters the cooling line 6. The cooled coolant in the cooling line 6 is mixed with the uncooled coolant in the bypass branch three 11 and enters the delivery main line 2 together. Under this control mode, due to the different proportions of the coolant diverted by the bypass branch three 11, the degree of cooling of the coolant is ultimately different. The more coolant enters the cooling line 6, the greater the degree of cooling of the coolant is ultimately.

[0065] The working control logic of the liquid cooling and boosting device of this embodiment is:

[0066] When the engine is in low-speed operation, the cooling pipe 6 is controlled to cool the coolant to the maximum extent, the delivery pump works at full speed and full load, and the temperature of the coolant entering the cooling channel is controlled at 30-40°C. At this time, the compressor operating point is located in the lower left corner of the compressor performance diagram, and the peak efficiency is higher than that of the traditional compressor;

[0067] When the engine is in high-speed operation, the temperature-raising pipeline 5 is controlled to raise the temperature of the coolant to the maximum extent, the delivery pump works at full speed and full load, and the temperature of the coolant entering the cooling channel is controlled at 50-60°C. At this time, the compressor operating point is located at the center of the compressor performance diagram;

[0068] When the engine is in medium speed condition or partial load, the delivery pump works at full speed and full load, and the bypass branch 3 11 and the heating pipeline 5 are controlled to distribute the coolant in proportion to achieve the heating of the coolant (not the maximum heating), or the bypass branch 3 11 and the cooling pipeline 6 are controlled to distribute the coolant in proportion to achieve the cooling of the coolant (not the maximum cooling), so as to meet the coolant temperature demand and finally control the compressor performance; wherein: when the engine is in medium speed condition, the compressor operating point is controlled to be located at the left position of the compressor performance diagram; when the engine is in partial load, the compressor operating point is controlled to be located at the bottom position of the compressor performance diagram.

[0069] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A liquid-cooled booster device with controllable performance, characterized in that: The invention comprises a compressor (1), a main delivery line (2), a return line (3) and a temperature regulating pipeline. The compressor (1) is provided with a cooling channel (1.2) for performing heat exchange with gas in an air channel (1.1) of the compressor (1). The cooling channel (1.2) is connected to the main delivery line (2) and the return line (3). A temperature regulating pipeline is provided between the main delivery line (2) and the return line (3). The temperature regulating pipeline is used to adjust the temperature of the coolant entering the cooling channel (1.2).

2. The liquid-cooled supercharging device with controllable performance according to claim 1, characterized in that: The temperature regulating pipeline comprises a heating pipeline (5) and a cooling 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 the engine thermal management circulation loop (7), so as to raise the temperature of the coolant; The cooling pipeline (6) is provided with a cooler (6.1), and the cooler (6.1) is used to cool the cooling liquid; The temperature of the coolant entering the cooling channel (1.2) is adjusted by operating the heat exchanger (5.1) or the cooler (6.1).

3. The liquid-cooled supercharging device with controllable performance according to claim 2, characterized in that: The temperature-increasing pipeline (5) and the temperature-reducing pipeline (6) are arranged in series between the main delivery pipeline (2) and the main return pipeline (3); The temperature-raising pipeline (5) comprises a bypass branch (5.2), an electric control valve (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 (5.2) and the temperature-raising branch (5.4) are both connected to the electric control valve (5.3); and the proportion of coolant entering the bypass branch (5.2) and the temperature-raising branch (5.4) is distributed through the electric control valve (5.3); 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 both connected to the electric control valve (6.3); and the proportion of coolant entering the bypass branch (6.2) and the cooling branch (6.4) is distributed by the electric control valve (6.3).

4. The liquid-cooled supercharging device with controllable performance according to claim 2, characterized in that: The temperature regulating pipeline also includes a bypass branch three (11), wherein the bypass branch three (11), the heating pipeline (5) and the cooling 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 to the return main pipeline (3) through an electric control valve four (12), and the heating pipeline (5) and the cooling pipeline (6) are connected in parallel to the electric control valve three (9) at the end of the return main pipeline (3), and the bypass branch three (11) is controlled by the electric control valve four (12) to control the diversion ratio of the cooling liquid in the return main pipeline (3), and the cooling liquid in the return main pipeline (3) is controlled by the electric control valve three (9) to enter the heating pipeline (5) or the cooling pipeline (6).

5. The liquid-cooled supercharging device with controllable performance according to claim 4, characterized in that: The temperature-increasing pipeline (5), the temperature-reducing pipeline (6) and the bypass branch line 3 (11) are all provided with a one-way valve (10) at one end close to the main conveying pipeline (2).

6. The liquid-cooled supercharging device with controllable performance according to any one of claims 1 to 5, characterized in that: A delivery pump (4) is provided on the delivery main line (2) or the return main line (3).

7. The liquid-cooled supercharging device with controllable performance according to any one of claims 1 to 5, characterized in that: The upper end surface of the compressor (1) is provided with a coolant outlet (1.4) connected to the cooling channel (1.2), and the lower end surface is provided with a coolant inlet (1.5) connected to the cooling channel (1.2); the main delivery line (2) is connected to the coolant inlet (1.5), and the return main line (3) is connected to the coolant outlet (1.4).

8. The liquid-cooled supercharging device with controllable performance according to any one of claims 1 to 5, characterized in that: The main delivery line (2) or the main return line (3) is provided with a pressure relief valve (8).

9. The liquid-cooled supercharging device with controllable performance according to any one of claims 1 to 5, characterized in that: The main delivery line (2) or the main return line (3) is provided with a coolant replenishing port.

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