Scroll compressor and pressure lead adjustment method and system thereof

Abstract

The application belongs to the technical field of compressors, and discloses a scroll compressor and a pressure lead regulation method and system thereof. The scroll compressor comprises a moving scroll, a stationary scroll, a back pressure cavity, a suction cavity, an exhaust cavity, a pressure lead channel, an exhaust channel, a first throttle valve and a second throttle valve. The exhaust cavity is connected with the back pressure cavity in sequence through the pressure lead channel, the first throttle valve and the exhaust channel. The suction cavity is connected with the back pressure cavity in sequence through the second throttle valve and the exhaust channel. The opening degree of the first throttle valve is adjustable. The application discloses an innovative scroll compressor and a pressure lead regulation method, which can effectively reduce the pressure pulsation of the working cavity in the compression process. The back pressure is actively adjusted in real time in one direction, so that the back pressure can meet the requirement of axial sealing and excessively increase the mechanical power of the compressor, which is crucial to the efficiency of the compressor.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, and specifically relates to a scroll compressor and its pressure regulation method and system. Background Technology

[0002] Scroll compressors are characterized by high efficiency, low noise, and stable operation, and are widely used in various air conditioning and heat pump systems; especially in the air conditioning systems of new energy vehicles, scroll compressors are the preferred solution. To further explain, the moving and stationary scrolls of a scroll compressor are subjected to axial gas force during compression. The back pressure in the back pressure chamber is often used to balance the axial gas force to achieve axial sealing of the compressor.

[0003] Currently, the general method for establishing back pressure in the back pressure chamber of a scroll compressor is to create a pressure tap on the base of the moving scroll, connecting the working chamber and the back pressure chamber, and using the pressure in the working chamber to establish back pressure. Existing scroll compressors using this method typically have a single pressure tap. Because the pressure tapping mechanism lacks a check valve function, this causes pressure pulsation within the working chamber where the pressure tap is located. Specifically, for CO2 new energy vehicle air conditioning systems, the cycle often operates within a transcritical range, with high operating pressure and a large pressure ratio. Due to the high operating pressure, the stability of the back pressure in the back pressure chamber is particularly important for CO2 scroll compressors. Under the high pressure and large pressure differential conditions of transcritical CO2 cycles, a single pressure tap structure will exacerbate pressure fluctuations in the working chamber, severely affecting the compressor's efficiency. Summary of the Invention

[0004] The purpose of this invention is to provide a scroll compressor and its pressure regulation method and system to solve one or more of the aforementioned technical problems. The technical solution provided by this invention discloses an innovative scroll compressor and pressure regulation method, which can effectively reduce pressure pulsation in the working chamber during the compression process; unidirectional real-time active regulation of the back pressure ensures that the back pressure meets the requirements of axial sealing without excessively increasing the compressor's mechanical power, which is crucial for ensuring compressor efficiency.

[0005] To achieve the above objectives, the present invention adopts the following technical solution:

[0006] The present invention provides a scroll compressor, comprising: a moving scroll, a stationary scroll, a back pressure chamber, an intake chamber, and an exhaust chamber; and further comprising: a pressure-inducing passage, an exhaust passage, a first throttle valve, and a second throttle valve;

[0007] The exhaust chamber is connected to the back pressure chamber via the pressure channel, the first throttle valve, and the exhaust channel in sequence; the intake chamber is connected to the back pressure chamber via the second throttle valve and the exhaust channel in sequence; the opening of the first throttle valve is adjustable.

[0008] A further improvement of the present invention is that the second throttle valve is set to a fixed opening.

[0009] A further improvement of the present invention is that both the first throttle valve and the second throttle valve are one-way solenoid valves.

[0010] A further improvement of the present invention is that the scroll compressor is used in the air conditioning system of new energy vehicles.

[0011] The present invention provides a pressure regulation method for a scroll compressor, comprising the following steps:

[0012] Obtain the exhaust pressure value;

[0013] Based on the obtained exhaust pressure value, the instantaneous minimum back pressure value is calculated.

[0014] The opening of the first throttle valve is optimized to make the back pressure value close to the instantaneous minimum back pressure value. During the process of the back pressure value approaching the instantaneous minimum back pressure value, the isentropic efficiency of the scroll compressor is optimized. The back pressure value corresponding to the maximum value of the isentropic efficiency is the actual optimal back pressure value. The opening of the first throttle valve at this time is taken as the optimal opening to achieve pressure regulation.

[0015] A further improvement of the present invention is that the calculation expression for the instantaneous minimum back pressure value is,

[0016]

[0017] In the formula, P min F represents the instantaneous minimum back pressure value. a For axial gas force, M t For the overturning moment, D b A b These are the outer edge diameter and back surface area of ​​the moving scroll, respectively.

[0018] The expression for calculating the axial gas force is as follows:

[0019]

[0020] In the formula, P suc Where ρ is the intake pressure, P is the involute pitch, A1 is the area of ​​the axial gas force in the central compression chamber, N is the number of involute coils, θ is the principal axis rotation angle, and ρ is the involute coil angle. i Let be the compression ratio of the i-th compression chamber.

[0021] A further improvement of the present invention is that, in the process of optimizing the opening of the first throttle valve so that the back pressure value is close to the instantaneous minimum back pressure value; during the process of the back pressure value approaching the instantaneous minimum back pressure value, the isentropic efficiency of the scroll compressor is optimized, and the back pressure value corresponding to the maximum value of the isentropic efficiency is the actual optimal back pressure value. The step of achieving pressure regulation by taking the opening of the first throttle valve at this time as the optimal opening includes:

[0022] Read the initial value and calculate the isentropic efficiency η. is-0 The initial values ​​include the suction temperature T of the scroll compressor. suc-0 Inhalation pressure P suc-0 Exhaust temperature T dis-0 Exhaust pressure P dis-0 ;

[0023] Using Δd as the gradient, increase the opening of the first one-way solenoid valve and read the intake temperature T. suc-1 Inhalation pressure P suc-1 Exhaust temperature T dis-1 Exhaust pressure P dis-1 Calculate the isentropic efficiency η is-1 The change in isentropic efficiency is Δη1, where Δη1 = η is-1 -η is-0 ;

[0024] If Δη1 = 0, then record the back pressure value at this time as the optimal back pressure value; if Δη1 < 0, then decrease the opening of the first one-way solenoid valve with Δd as the gradient, and repeatedly read the intake temperature T. suc-j Inhalation pressure P suc-j Exhaust temperature T dis-j Exhaust pressure P dis-j Calculate the isentropic efficiency η is-j The change in isentropic efficiency is Δη j ,Δη j =η is-j -η is-j-1 until Δη j Record the back pressure value at this point until it equals 0, which is the optimal back pressure value. If Δη1 > 0, increase the opening of the first one-way solenoid valve with Δd as the gradient, and repeatedly read the intake temperature T. suc-j Inhalation pressure P suc-j Exhaust temperature T dis-j Exhaust pressure P dis-j Calculate the isentropic efficiency η is-j The change in isentropic efficiency is Δη j ,Δη j =η is-j -η is-j-1 until Δη jThe back pressure is recorded as the optimal back pressure value until it reaches 0.

[0025] The present invention provides a pressure regulating system for a scroll compressor, comprising:

[0026] The data acquisition module is used to acquire exhaust pressure values;

[0027] The calculation module is used to calculate the instantaneous minimum back pressure value based on the acquired exhaust pressure value;

[0028] The optimization adjustment module is used to optimize the opening of the first throttle valve so that the back pressure value is close to the instantaneous minimum back pressure value. During the process of the back pressure value approaching the instantaneous minimum back pressure value, the isentropic efficiency of the scroll compressor is optimized. The back pressure value corresponding to the maximum value of the isentropic efficiency is the actual optimal back pressure value. The opening of the first throttle valve at this time is taken as the optimal opening to achieve pressure regulation.

[0029] A further improvement of the present invention is that the calculation expression for the instantaneous minimum back pressure value is,

[0030]

[0031] In the formula, P min P is the instantaneous minimum back pressure value. a For axial gas force, M t For the overturning moment, D b A b These are the outer edge diameter and back surface area of ​​the moving scroll, respectively.

[0032] The expression for calculating the axial gas force is as follows:

[0033]

[0034] In the formula, P suc Where ρ is the intake pressure, P is the involute pitch, A1 is the area of ​​the axial gas force in the central compression chamber, N is the number of involute coils, θ is the principal axis rotation angle, and ρ is the involute coil angle. i Let be the compression ratio of the i-th compression chamber.

[0035] A further improvement of the present invention is that the optimization adjustment module performs optimization adjustment of the opening of the first throttle valve so that the back pressure value is close to the instantaneous minimum back pressure value; during the process of the back pressure value approaching the instantaneous minimum back pressure value, the isentropic efficiency of the scroll compressor is optimized, and the back pressure value corresponding to the maximum value of the isentropic efficiency is the actual optimal back pressure value. The step of pressure regulation is achieved by taking the opening of the first throttle valve at this time as the optimal opening.

[0036] Read the initial value and calculate the isentropic efficiency η. is-0 The initial values ​​include the suction temperature T of the scroll compressor. suc-0 Inhalation pressure P suc-0 Exhaust temperature T dis-0 Exhaust pressure P dis-0 ;

[0037] Using Δd as the gradient, increase the opening of the first one-way solenoid valve and read the intake temperature T. suc-1 Inhalation pressure P suc-1 Exhaust temperature T dis-1 Exhaust pressure P dis-1 Calculate the isentropic efficiency η is-1 The change in isentropic efficiency is Δη1, where Δη1 = η is-1 -η is-0 ;

[0038] If Δη1 = 0, then record the back pressure value at this time as the optimal back pressure value; if Δη1 < 0, then decrease the opening of the first one-way solenoid valve with Δd as the gradient, and repeatedly read the intake temperature T. suc-j Inhalation pressure P suc-j Exhaust temperature T dis-j Exhaust pressure P dis-j Calculate the isentropic efficiency η is-j The change in isentropic efficiency is Δη j ,Δη j =η is-j -η is-j-1 until Δη j Record the back pressure value at this point until it equals 0, which is the optimal back pressure value. If Δη1 > 0, increase the opening of the first one-way solenoid valve with Δd as the gradient, and repeatedly read the intake temperature T. suc-j Inhalation pressure P suc-j Exhaust temperature T dis-j Exhaust pressure P dis-j Calculate the isentropic efficiency η is-j The change in isentropic efficiency is Δη j ,Δη j =η is-j -η is-j-1 until Δη j The back pressure is recorded as the optimal back pressure value until it reaches 0.

[0039] Compared with the prior art, the present invention has the following beneficial effects:

[0040] In existing technologies, for scroll compressors (exemplary, particularly scroll compressors used in CO2 new energy vehicle air conditioning systems), when axial sealing is achieved by introducing a back pressure chamber structure, the working chamber pressure is affected and pressure fluctuations occur. The back pressure, due to pressure pulsation and the inability to control it in real time, causes inconsistent contact between the moving and stationary scrolls of the compressor, thus severely affecting compressor efficiency. In view of the above, this invention specifically discloses a scroll compressor that adopts a pressure-drawing method directly from the exhaust chamber to the back pressure chamber. By adding a throttling valve with a check valve function (specifically, the inventive technical means of this invention is to add a pressure-drawing channel and a first throttling valve between the exhaust chamber and the back pressure chamber, and an exhaust channel and a second throttling valve between the back pressure chamber and the intake chamber; the opening of the first throttling valve is used to adjust the size of the pressure-drawing connection diameter, thereby precisely controlling the back pressure), real-time control of the back pressure can be achieved. In summary, the technical solution disclosed in this invention not only avoids the influence of back pressure on the working chamber pressure during the back pressure establishment process, but also realizes real-time control of back pressure according to the compressor's operating conditions. In the process of adjusting the back pressure to approach the minimum back pressure, the isentropic efficiency of the compressor is optimized in real time to ensure that the compressor is in the optimal efficiency state under any operating condition.

[0041] Further illustratively, the invention includes a first throttle valve for throttling the high-pressure working gas drawn from the exhaust chamber through the pressure channel to the back pressure chamber, and the opening of the throttle valve can be adjusted in real time. A second throttle valve is used to throttle the high-pressure working gas drawn from the back pressure chamber through the exhaust channel to the intake chamber, and this throttle valve has a fixed opening.

[0042] In the method of this invention, the back pressure can be actively adjusted in real time, which can ensure that the compressor always operates at the optimal performance with the highest isentropic efficiency. Attached Figure Description

[0043] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art are briefly introduced below; obviously, the drawings described below are some embodiments of the present invention, and those skilled in the art can obtain other drawings based on these drawings without creative effort.

[0044] Figure 1 This is a scroll compressor provided in an embodiment of the present invention;

[0045] Figure 2 This is a simplified PID logic flow diagram for active pressure regulation in an embodiment of the present invention;

[0046] The accompanying figure labels explain...

[0047] 1. First throttle valve; 2. Second throttle valve; 3. Moving scroll; 4. Stationary scroll; 5. Back pressure chamber; 6. Intake chamber; 7. Exhaust chamber; 8. Pressure channel; 9. Exhaust channel. Detailed Implementation

[0048] To enable those skilled in the art to better understand the present invention, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort should fall within the scope of protection of the present invention.

[0049] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this invention are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of the invention described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover a non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0050] The present invention will now be described in further detail with reference to the accompanying drawings:

[0051] Please see Figure 1 The present invention provides a scroll compressor comprising: a first throttle valve 1, a second throttle valve 2, a moving scroll 3, a stationary scroll 4, a back pressure chamber 5, an intake chamber 6, an exhaust chamber 7, a pressure-inducing passage 8, and an exhaust passage 9.

[0052] The exhaust chamber 7 is connected to the back pressure chamber 5 via the pressure channel 8, the first throttle valve 1, and the exhaust channel 9 in sequence; the intake chamber 6 is connected to the back pressure chamber 5 via the second throttle valve 2 and the exhaust channel 9 in sequence; the opening of the first throttle valve 1 is adjustable; more preferably, the second throttle valve 2 is set to a fixed opening.

[0053] In the technical solution provided by this embodiment of the invention, the pressure tapping method is unidirectional pressure tapping of the back pressure chamber without opening a pressure tapping hole; a pressure tapping channel 8 and a first throttle valve 1 are added between the exhaust chamber 7 and the back pressure chamber 5, and an exhaust channel 9 and a second throttle valve 2 are added between the back pressure chamber 5 and the intake chamber 6; the opening degree of the first throttle valve 1 is used to adjust the size of the pressure tapping connection diameter, thereby accurately controlling the back pressure; in addition, the second throttle valve 2 can be set to a fixed opening degree (the second throttle valve 2 does not participate in the active adjustment function, but is used for pressure relief when the back pressure chamber pressure is too high, and can be understood as an outlet channel of the back pressure chamber 5; if it is set to an adjustable opening degree, it will increase the processing and design cost and is not necessary).

[0054] The embodiments of the present invention are further explained in detail.

[0055] The moving scroll 3 is a scroll that remains in motion throughout the operation of the scroll compressor. It is driven by the rotation of the main shaft to perform translational motion and is used to mesh with the stationary scroll 4 to form a closed working chamber of the compressor and compress the working gas.

[0056] The stationary scroll 4 is a scroll that remains stationary during the operation of the scroll compressor. It is used to mesh with the moving scroll 3 to form a closed working chamber of the compressor and compress the working gas.

[0057] The back pressure chamber 5 is a closed cavity formed by the moving scroll 3 and the bearing seat, which is used to provide axial back pressure to the moving scroll 3, balance the gas force, and make the moving scroll 3 be in an appropriate stress state.

[0058] The suction chamber 6 refers to the chamber in which the compressor draws in low-pressure working fluid;

[0059] The exhaust chamber 7 refers to the chamber of the compressor used to discharge the high-pressure working gas compressed by the working chamber.

[0060] In this embodiment of the invention, the first throttle valve 1 is used to throttle the high-pressure working gas drawn from the exhaust chamber 7 through the pressure channel 8 into the back pressure chamber 5, and the opening degree of the throttle valve can be adjusted in real time. Further, by reading real-time operating parameters, based on PID negative feedback regulation and automatic optimization control, the opening degree of the throttle valve is adjusted in real time to achieve the goal of keeping the back pressure chamber pressure at the optimal back pressure value and the compressor's isentropic efficiency at its maximum value.

[0061] In this embodiment of the invention, the second throttle valve 2 is used to throttle the high-pressure working gas drawn from the back pressure chamber 5 through the exhaust channel 9 into the intake chamber 6, and the throttle valve has a fixed opening.

[0062] In specific and exemplary embodiments of the present invention, both the first throttle valve 1 and the second throttle valve 2 can be one-way solenoid valves.

[0063] The scroll compressor provided in this invention can be used in the air conditioning systems of new energy vehicles. Further illustratively, for CO2 new energy vehicle air conditioning systems, the cycle often operates within a transcritical range, with high operating pressure and a large pressure ratio. Due to the high operating pressure, the stability of the back pressure in the back pressure chamber is particularly important for CO2 scroll compressors. However, under the high pressure and large pressure difference conditions of transcritical CO2 cycles, a single pressure-inlet structure exacerbates pressure fluctuations in the working chamber, severely affecting compressor efficiency. The pressure-inlet method introduced in this invention can effectively reduce pressure pulsation in the working chamber during compression, and provides unidirectional real-time active adjustment of the back pressure. This ensures that the back pressure meets the requirements of axial sealing without excessively increasing the compressor's mechanical power, which is crucial for ensuring compressor efficiency.

[0064] This invention provides a pressure regulation method for a scroll compressor, comprising the following steps:

[0065] S1: Obtain the real-time exhaust pressure value P dis ;

[0066] S2: The exhaust pressure value P obtained in step S1 dis The instantaneous minimum back pressure value P is calculated. min ;

[0067] S3: Optimize the opening of the first throttle valve 1 so that the real-time back pressure value is close to the instantaneous minimum back pressure value P. min During the process, the isentropic efficiency of the compressor is optimized in real time. When the isentropic efficiency reaches its maximum value, the corresponding back pressure is the actual optimal back pressure value. At this time, the opening degree of the first throttle valve 1 is determined to be the optimal opening degree, and the pressure regulation is completed.

[0068] The pressure regulation method provided in this embodiment of the invention achieves real-time control of back pressure by adding a throttling valve with a check valve function. This not only avoids the influence of the back pressure build-up process on the working chamber pressure, but also enables real-time negative feedback regulation of back pressure according to the compressor's operating conditions, ensuring that the compressor always operates at its optimal performance with the highest isentropic efficiency under any operating conditions.

[0069] Please see Figure 2 To further explain, during the adjustment process, the compressor's suction temperature, suction pressure, discharge temperature, and discharge pressure are collected in real time to calculate the compressor's back pressure and isentropic efficiency. The real-time back pressure serves as the input for negative feedback PID control, with the output being the opening degree of the first single-phase throttle valve. The real-time isentropic efficiency serves as the input for real-time optimization. As the back pressure approaches the minimum back pressure, the compressor's isentropic efficiency is optimized in real time. When the isentropic efficiency reaches its maximum value, the corresponding back pressure is the actual optimal back pressure value.

[0070] In step 2 of this embodiment of the invention, the magnitude of the back pressure is determined by the real-time force condition of the moving scroll, with the minimum back pressure reference value (P) being... min Typically, it is based on back pressure and axial gas force (F). a ) and overturning moment (M t The calculation expression is as follows:

[0071]

[0072] In the formula, D b and A b These are the outer edge diameter and back surface area of ​​the moving scroll, respectively.

[0073] The calculation method for axial gas force is as follows:

[0074]

[0075] In the formula, P suc Where ρ is the intake pressure, P is the involute pitch, A1 is the area of ​​the axial gas force in the central compression chamber, N is the number of involute coils, θ is the principal axis rotation angle, and ρ is the involute coil angle. i Let be the compression ratio of the i-th compression chamber.

[0076] Explanation of the principle of this invention: As can be seen from the above calculations, the axial gas force is pulsating, so the pressure regulation is pulsating regulation; the function of the minimum back pressure value is to limit the range of isentropic efficiency optimization, ensuring that the isentropic efficiency sought is the maximum value rather than the maximum value.

[0077] Please see Figure 2 In this embodiment of the invention, the back pressure regulation is a two-layer control combining real-time negative feedback PID control and automatic optimization control; wherein,

[0078] The negative feedback PID control is the lowest-level control. The controller's input is the real-time back pressure, and its output is the opening degree of the first one-way solenoid valve. The target reference value in the early stage of control is the calculated instantaneous minimum back pressure value, and the target reference value in the later stage of control is the back pressure value obtained through automatic optimization. The overshoot σ of the back pressure during the adjustment process... P Satisfy: σ P ≤σ max , where σ max The back pressure is determined by the compressor's maximum leakage. Explaining this, the early stage of control refers to calculating the real-time back pressure using real-time data acquisition and then controlling the opening of the first throttle valve through PID negative feedback to achieve the minimum back pressure value. Its function is to limit the range of isentropic efficiency optimization in the later stage of control, ensuring that the optimal isentropic efficiency value is found to be the maximum value, not the extreme value. The later stage of control refers to automatically optimizing and controlling the compressor's isentropic efficiency to reach the maximum isentropic efficiency.

[0079] In this embodiment of the invention, the steps of the automatic optimization process are as follows:

[0080] S1: Read the initial value, compressor suction temperature T suc-0 Inhalation pressure P suc-0 Exhaust temperature T dis-0 Exhaust pressure P dis-0 Calculate the isentropic efficiency η is-0 ;

[0081] S2: Using Δd as the gradient, increase the opening of the first one-way solenoid valve and read the intake temperature T. suc-1 Inhalation pressure P suc-1 Exhaust temperature T dis-1 Exhaust pressure P dis-1 Calculate the isentropic efficiency η is-1 The change in isentropic efficiency is Δη1, which satisfies: Δη1=η is-1 -η is-0 .

[0082] If Δη1 = 0, then record the back pressure P at this time. b This is the optimal back pressure value.

[0083] If Δη1 < 0, then decrease the opening of the first one-way solenoid valve with Δd as the gradient, and repeatedly read the intake temperature T. suc-j Inhalation pressure P suc-j Exhaust temperature T dis-j Exhaust pressure P dis-j Calculate the isentropic efficiency η is-j The change in isentropic efficiency is Δη j Satisfying: Δη j =η is-j -η is-j-1 Until Δη j Record the back pressure P at the point where the pressure equals 0. b This is the optimal back pressure value.

[0084] If Δη1 > 0, then increase the opening of the first one-way solenoid valve with Δd as the gradient, and repeatedly read the intake temperature T. suc-j Inhalation pressure P suc-j Exhaust temperature T dis-j Exhaust pressure P dis-j Calculate the isentropic efficiency η is-j The change in isentropic efficiency is Δη j Satisfying: Δη j =η is-j -η is-j-1 Until Δη j Record the back pressure P at the point where the pressure equals 0. bThis is the optimal back pressure value.

[0085] In summary, there are currently two main methods for establishing back pressure in scroll compressors: one is to place the pressure tap in the high-pressure chamber on the back of the stationary scroll, using the pressure in the high-pressure chamber to establish back pressure; the other is to place the pressure tap on the base of the moving scroll, connecting the working chamber and the back pressure chamber, using the pressure in the working chamber to establish back pressure. Scroll compressors using the first method generally have a more complex structure and require a separate oil return channel for the working chamber. Existing scroll compressors using the second method typically have a single pressure tap. Because the pressure tapping mechanism lacks a check valve, this causes pressure pulsation within the working chamber where the pressure tap is located. Furthermore, it cannot be actively adjusted, making it impossible to guarantee the optimal back pressure under all operating conditions. Especially under the high-pressure, high-pressure-differential conditions involved in transcritical CO2 cycles, this exacerbates pressure fluctuations in the working chamber, severely impacting the compressor's efficiency and reliability.

[0086] The inventive point of this invention lies in its belonging to the field of compressor technology, specifically relating to scroll compressors for air conditioning in new energy vehicles. It discloses an active pressure-inducing design and its pressure-inducing adjustment method for a scroll compressor used in air conditioning of new energy vehicles. The pressure-inducing method involves unidirectional pressure in the back pressure chamber without opening a pressure-inducing hole. A pressure-inducing channel and a first one-way solenoid valve are added between the exhaust chamber and the back pressure chamber. An exhaust channel and a second one-way solenoid valve are added between the back pressure chamber and the intake chamber. The opening degree of the first one-way solenoid valve is used to adjust the size of the pressure-inducing connection diameter, thereby precisely controlling the back pressure. The second one-way solenoid valve has a fixed opening degree. The pressure-inducing adjustment steps are as follows: first, read the real-time exhaust pressure value P. dis Then calculate the instantaneous minimum back pressure value P. min Finally, the opening of the first one-way solenoid valve is adjusted so that the back pressure gradually approaches the minimum back pressure reference value. During this process, the isentropic efficiency of the compressor is optimized in real time. The back pressure corresponding to the maximum isentropic efficiency is the actual optimal back pressure value. This invention is applied to the active pressure regulation of scroll compressors, improving compressor efficiency. This invention employs an active, adjustable one-way pressure regulation method combining an added pressure channel and a solenoid valve. It has a check valve function, which can prevent pressure fluctuations in the working chamber and allows for real-time negative feedback regulation of the back pressure, ensuring that the compressor always operates at its optimal performance with maximum isentropic efficiency. The active pressure regulation design and method for scroll compressors provided in this invention can actively regulate the back pressure of scroll compressors in new energy vehicle air conditioning systems in real time, ensuring compressor efficiency.

[0087] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that modifications or equivalent substitutions can still be made to the specific implementation of the present invention. Any modifications or equivalent substitutions that do not depart from the spirit and scope of the present invention should be covered within the scope of protection of the claims of the present invention.

Claims

1. A pressure regulation method for a scroll compressor, characterized in that, The scroll compressor includes: a moving scroll (3), a stationary scroll (4), a back pressure chamber (5), an intake chamber (6), and an exhaust chamber (7), and further includes: a pressure-inducing channel (8), an exhaust channel (9), a first throttle valve (1), and a second throttle valve (2); wherein, the exhaust chamber (7) is connected to the back pressure chamber (5) in sequence via the pressure-inducing channel (8), the first throttle valve (1), and the exhaust channel (9); the intake chamber (6) is connected to the back pressure chamber (5) in sequence via the second throttle valve (2) and the exhaust channel (9); the opening degree of the first throttle valve (1) is adjustable; The pressure adjustment method includes the following steps: Obtain the exhaust pressure value; Based on the obtained exhaust pressure value, the instantaneous minimum back pressure value is calculated. The opening of the first throttle valve is optimized to make the back pressure value close to the instantaneous minimum back pressure value. During the process of the back pressure value approaching the instantaneous minimum back pressure value, the isentropic efficiency of the scroll compressor is optimized. The back pressure value corresponding to the maximum value of the isentropic efficiency is the actual optimal back pressure value. The opening of the first throttle valve at this time is taken as the optimal opening to achieve pressure regulation. It also includes: reading initial values ​​and calculating isentropic efficiency. The initial values ​​include the suction temperature of the scroll compressor. Inhalation pressure Exhaust temperature Exhaust pressure ;by To determine the gradient, increase the opening of the first throttle valve and read the intake temperature. Inhalation pressure Exhaust temperature Exhaust pressure Calculate isentropic efficiency The change in isentropic efficiency is , ; like If so, record the back pressure value at this time as the optimal back pressure value; if Then To achieve the gradient, reduce the opening of the first throttle valve and repeatedly read the intake temperature. Inhalation pressure Exhaust temperature Exhaust pressure Calculate isentropic efficiency The change in isentropic efficiency is , until Record the current back pressure value as the optimal back pressure value; if Then To achieve the gradient, increase the opening of the first throttle valve and repeatedly read the intake temperature. Inhalation pressure Exhaust temperature Exhaust pressure Calculate isentropic efficiency The change in isentropic efficiency is , until Record the back pressure value at this point as the optimal back pressure value.

2. The pressure regulation method for a scroll compressor according to claim 1, characterized in that, The expression for calculating the instantaneous minimum back pressure value is as follows: ； In the formula, This represents the instantaneous minimum back pressure value. For axial gas force, For overturning moment, These are the outer edge diameter and back surface area of ​​the moving scroll, respectively. The expression for calculating the axial gas force is as follows: ； In the formula, Inhalation pressure, For involute pitch, The area of ​​the central compression chamber where the axial gas force acts is... For the number of involute coils, Main axis rotation angle, Let be the compression ratio of the i-th compression chamber.

3. The pressure regulation method for a scroll compressor according to claim 1, characterized in that, In the scroll compressor, the second throttle valve (2) is set to a fixed opening.

4. The pressure regulation method for a scroll compressor according to claim 3, characterized in that, In the scroll compressor, the second throttle valve (2) is a one-way solenoid valve.

5. A pressure regulating system for a scroll compressor, characterized in that, The scroll compressor includes: a moving scroll (3), a stationary scroll (4), a back pressure chamber (5), an intake chamber (6), and an exhaust chamber (7), and further includes: a pressure-inducing channel (8), an exhaust channel (9), a first throttle valve (1), and a second throttle valve (2); wherein, the exhaust chamber (7) is connected to the back pressure chamber (5) in sequence via the pressure-inducing channel (8), the first throttle valve (1), and the exhaust channel (9); the intake chamber (6) is connected to the back pressure chamber (5) in sequence via the second throttle valve (2) and the exhaust channel (9); the opening degree of the first throttle valve (1) is adjustable; The pressure regulation system includes: The data acquisition module is used to acquire exhaust pressure values; The calculation module is used to calculate the instantaneous minimum back pressure value based on the acquired exhaust pressure value; The optimization adjustment module is used to optimize the opening of the first throttle valve so that the back pressure value is close to the instantaneous minimum back pressure value. During the process of the back pressure value approaching the instantaneous minimum back pressure value, the isentropic efficiency of the scroll compressor is optimized. The back pressure value corresponding to the maximum isentropic efficiency is the actual optimal back pressure value. The opening of the first throttle valve at this point is taken as the optimal opening to achieve pressure regulation. The module also includes: reading the initial value and calculating the isentropic efficiency. The initial values ​​include the suction temperature of the scroll compressor. Inhalation pressure Exhaust temperature Exhaust pressure ; by To determine the gradient, increase the opening of the first throttle valve and read the intake temperature. Inhalation pressure Exhaust temperature Exhaust pressure Calculate isentropic efficiency The change in isentropic efficiency is , ; like If so, record the back pressure value at this time as the optimal back pressure value; if Then To achieve the gradient, reduce the opening of the first throttle valve and repeatedly read the intake temperature. Inhalation pressure Exhaust temperature Exhaust pressure Calculate isentropic efficiency The change in isentropic efficiency is , until Record the current back pressure value as the optimal back pressure value; if Then To achieve the gradient, increase the opening of the first throttle valve and repeatedly read the intake temperature. Inhalation pressure Exhaust temperature Exhaust pressure Calculate isentropic efficiency The change in isentropic efficiency is , until Record the back pressure value at this point as the optimal back pressure value.

6. The pressure regulating system for a scroll compressor according to claim 5, characterized in that, The expression for calculating the instantaneous minimum back pressure value is as follows: ； In the formula, This represents the instantaneous minimum back pressure value. For axial gas force, For overturning moment, These are the outer edge diameter and back surface area of ​​the moving scroll, respectively. The expression for calculating the axial gas force is as follows: ； In the formula, Inhalation pressure, For involute pitch, The area of ​​the central compression chamber where the axial gas force acts is... For the number of involute coils, Main axis rotation angle, Let be the compression ratio of the i-th compression chamber.

7. The pressure regulating system for a scroll compressor according to claim 5, characterized in that, In the scroll compressor, the second throttle valve (2) is set to a fixed opening.

8. The pressure regulating system for a scroll compressor according to claim 7, characterized in that, In the scroll compressor, the second throttle valve (2) is a one-way solenoid valve.

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