A large sliding pressure and wide load compressed gas energy storage turbine system and its operation method

Abstract

The present invention discloses a large sliding pressure wide load compressed gas energy storage turbine system and its operation method, including a high pressure cylinder, a medium pressure cylinder, a low pressure cylinder, a first air intake pipe and a parallel branch; one end of the first air intake pipe is connected to a first heater, and the other end is connected to the air intake port of the high pressure cylinder; the high and medium pressure cylinder exhaust pipes are respectively provided with a second and a third heater; a check valve is provided on the high pressure cylinder exhaust pipe between the high pressure cylinder exhaust port and the second heater; the first air intake pipe is connected with a first and a second branch in parallel, the first branch is connected to the high pressure cylinder at one end away from the first air intake pipe, the second branch is connected to the high pressure cylinder exhaust pipe at one end away from the first air intake pipe, the parallel branch is connected to the medium pressure cylinder exhaust pipe at one end, and the other end is connected to the high pressure cylinder exhaust pipe between the check valve and the high pressure cylinder exhaust port, and a parallel switching valve is provided on the parallel branch. The present invention takes into account high efficiency, wide load, fast and flexible peak and frequency regulation capabilities and large over-generation capabilities.

Description

Technical Field

[0001] The present invention belongs to the technical field of turbine power generation, and in particular relates to a large sliding pressure and wide load compressed gas energy storage turbine system and an operation method thereof. Background Art

[0002] For compressed gas energy storage projects with a large sliding pressure range and turbine systems of some other power generation projects with similar characteristics, the following characteristics are usually required: During the overall operation, the main gas pressure has a large sliding pressure range (e.g., the sliding pressure range is 10MPa~3MPa, and the sliding pressure variation range is as high as 70%), full load rate requirements in the entire operation section, and high economic requirements for the turbine system. At the same time, this type of turbine system often needs to take into account the wide load, efficient and flexible operation capabilities of conventional thermal power projects, and has peak and frequency regulation operation requirements. It usually needs to have a long-term stable operation of 20%-100% load within the large sliding pressure operation range of the entire process and have a certain load over-generation capacity. Due to the need to have the above-mentioned multiple characteristics, the overall structural layout and operation method of this type of turbine system must meet a high degree of operational flexibility.

[0003] The present invention provides a large sliding pressure and wide load compressed gas energy storage turbine system and its operation method which meet the requirements of higher operational flexibility, have a large load rate over-generation capacity, take into account high efficiency, wide load, fast and flexible peak-shaving and frequency regulation capabilities, and have a large over-generation capacity. Summary of the invention

[0004] The purpose of the present invention is to provide a large sliding pressure wide load compressed gas energy storage turbine system and its operation method with a large load rate over-generation capacity, taking into account high efficiency, wide load, fast and flexible peak-shaving and frequency regulation capabilities, and large over-generation capacity in view of the deficiencies in the prior art; the present invention can meet the 100% full load rate requirement in the entire operating section when the main gas pressure continues to decrease at the large sliding pressure operating boundary, and at the same time has high economy; in addition, it can achieve wide load efficient and flexible operation within the conventional 20%-100% load rate range in the entire operating section, and has fast and flexible peak-shaving and frequency regulation operation capabilities.

[0005] The technical purpose of the present invention is achieved by the following technical solutions: A large sliding pressure and wide load compressed gas energy storage turbine system comprises a high pressure cylinder, a medium pressure cylinder, a low pressure cylinder, a first air intake pipe and a parallel branch; one end of the first air intake pipe is connected to a first heater, and the other end thereof is connected to the air intake port of the high pressure cylinder; the exhaust port of the high pressure cylinder is connected to the air intake port of the medium pressure cylinder through the high pressure cylinder exhaust pipe, and the exhaust port of the medium pressure cylinder is connected to the air intake port of the low pressure cylinder through the medium pressure cylinder exhaust pipe; the exhaust port of the low pressure cylinder discharges exhaust gas to the outside through the low pressure cylinder exhaust pipe; the high pressure cylinder exhaust pipe and the medium pressure cylinder exhaust pipe are respectively provided with There are a second heater and a third heater; a check valve is provided on the high-pressure cylinder exhaust pipe between the exhaust port of the high-pressure cylinder and the second heater; a first branch and a second branch are connected in parallel on the first intake pipe, the first branch is connected to the high-pressure cylinder at one end away from the first intake pipe, the second branch is connected to the high-pressure cylinder exhaust pipe at one end away from the first intake pipe, one end of the parallel branch is connected to the medium-pressure cylinder exhaust pipe, and the other end is connected to the high-pressure cylinder exhaust pipe between the check valve and the exhaust port of the high-pressure cylinder, and a parallel switching valve is provided on the parallel branch.

[0006] Furthermore, a high-pressure main air regulating valve is provided at one end of the first air intake pipeline close to the air intake port of the high-pressure cylinder, and a first air supply valve and a second air supply valve are provided on the first branch and the second branch, respectively; The high-pressure main air regulating valve and the first air supply valve are in sequential valve regulation mode, and the total valve position instruction is used as the main control quantity to control the regulating load rate; the second air supply valve indirectly controls the regulating load rate in a joint control manner during the entire operation process.

[0007] The present invention also discloses an operation method of a large sliding pressure and wide load compressed gas energy storage turbine system, comprising the following steps: S1. According to the main gas pressure, it is set to P0-P1-P2-P3-P4 from high to low; S2.P0-P1 stage: when the design main gas pressure is P1; at this time, the high-pressure main gas regulating valve controls the regulating load; S3.P1-P2 stage: At this time, the main gas pressure is less than the designed main gas pressure. At this time, the high-pressure main gas regulating valve is fully opened, and the first air supply valve is used to control the load. S4.P2-P3 stage: At this time, the high-pressure main gas regulating valve is fully opened, the first air supply valve is fully opened, and the second air supply valve and the main valve position instruction are connected by the logic of joint control to execute the effect of opening wide; S5. P3 stage: When the main gas pressure reaches P3, the opening of the second air supply valve reaches a certain opening, at which time the enthalpy drop section of the stage before the air supply point is shortened, and the high-pressure cylinder exhaust is switched from the original medium-pressure cylinder inlet to the medium-pressure cylinder exhaust position, so that the high-pressure cylinder and the medium-pressure cylinder are switched from the original series structure to the parallel structure; S6.P3-P4 stage: the second air supply valve is set to manual mode, that is, a separate control signal is given to the second air supply valve to allow the second air supply valve to open continuously at a certain rate; the total valve position command controls the load, and the second air supply valve is jointly controlled to feedback the load rate; S7.P4 stage: When the main gas pressure is P4, it is necessary to control the load to stop; at this time, the parallel switching valve is open, and the high and medium pressure cylinders are operating in parallel mode; reduce the set load target, and the joint control logic links the second air supply valve to close until shutdown or reverse power phase adjustment mode.

[0008] Furthermore, the control method also includes frequency modulation and peak regulation mode operation control: When the high and medium pressure cylinders are operated in series mode, the load rate is adjusted by the total valve position command with precise feedback. At the same time, when the total valve position command reaches the upper or lower limit, the second air supply valve is linked to open or close, so that the total valve position command falls back to a certain opening, with faster load regulation response speed and ability; When the high and medium pressure cylinders are operating in parallel mode, the load rate is adjusted by the total valve position command with precise feedback. At this time, the total valve position command is usually at a smaller command. At the same time, when the total valve position command reaches the upper or lower limit, the second air supply valve is linked to open or close, so that the total valve position command falls back to a certain opening, with faster load regulation response speed and ability.

[0009] Furthermore, when the parallel switching process is carried out, the main gas pressure P3 is used as a trigger instruction, and the switching duration is preset to a fixed duration. During this time period, the parallel switching valve is gradually fully opened and the check valve is gradually closed; the parallel switching valve is fully opened and the check valve is fully closed; the switching is completed.

[0010] Furthermore, when the parallel switching process is in progress, the main valve position instruction controls the load, and the second air supply valve jointly controls the load.

[0011] Furthermore, the second air supply valve uses the start of the action of the parallel switching valve as a trigger instruction, activating the second air supply valve to start opening continuously at a predetermined rate.

[0012] Compared with the prior art, the present invention has the following beneficial effects: 1. The present invention has a large load rate over-generation capacity, takes into account high efficiency, wide load, fast and flexible peak-shaving and frequency regulation capabilities, and has a large over-generation capacity.

[0013] 2. The steam distribution adjustment mode of the present invention is throttling + two-stage air supply + parallel air supply. Its operation method adds two-stage air supply and parallel air supply to the throttling air supply and bypass air supply of conventional thermal power. The present invention can meet the 100% full load rate requirement in the entire operation section when the main gas pressure continues to decrease at the large sliding pressure operation boundary, and has high economy; in addition, it can achieve wide load, efficient and flexible operation within the conventional 20%-100% load rate range in the entire operation section, and has fast and flexible peak-shaving and frequency-modulating operation capabilities. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 It is a schematic diagram of the structure of the present invention; Reference numerals: 1—high-pressure cylinder; 11—high-pressure cylinder exhaust pipe; 111—medium-pressure main regulating valve; 12—high-pressure main gas regulating valve; 13—check valve; 2—medium-pressure cylinder; 21—medium-pressure cylinder exhaust pipe; 211—low-pressure main air valve; 3—low-pressure cylinder; 31—low-pressure cylinder exhaust pipe; 4—first air intake pipe; 41—first branch; 411—first air supply valve; 42—second branch; 421—second air supply valve; 5—parallel branch; 51—parallel switching valve; 6—first heater; 7—second heater; 8—third heater. DETAILED DESCRIPTION

[0015] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings here can be arranged and designed in various different configurations.

[0016] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention claimed for protection, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0017] It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further defined and explained in the subsequent drawings. In addition, the terms "first", "second", etc. are only used to distinguish the description and cannot be understood as indicating or implying relative importance.

[0018] like Figure 1As shown, a large sliding pressure wide load compressed gas energy storage turbine system comprises a high pressure cylinder 1, an intermediate pressure cylinder 2, a low pressure cylinder 3, a first air intake pipe 4 and a parallel branch 5; one end of the first air intake pipe 4 is connected to a first heater 6, and the other end thereof is connected to the air intake port of the high pressure cylinder 1; the exhaust port of the high pressure cylinder 1 is connected to the air intake port of the intermediate pressure cylinder 2 through a high pressure cylinder exhaust pipe 11, and the exhaust port of the intermediate pressure cylinder 2 is connected to the air intake port of the low pressure cylinder 3 through an intermediate pressure cylinder exhaust pipe 21; the exhaust port of the low pressure cylinder 3 discharges exhaust gas to the outside through a low pressure cylinder exhaust pipe 31; the high pressure cylinder exhaust pipe 11 and the intermediate pressure cylinder exhaust pipe 21 are respectively provided with a first heater 6. The second heater 7 and the third heater 8; a check valve 13 is provided on the high-pressure cylinder exhaust pipe 11 between the exhaust port of the high-pressure cylinder 1 and the second heater 7; the first air intake pipe 4 is connected in parallel with a first branch 41 and a second branch 42, the first branch 41 is connected to the high-pressure cylinder 1 at one end away from the first air intake pipe 4, and the second branch 42 is connected to the high-pressure cylinder exhaust pipe 11 at one end away from the first air intake pipe 4, and one end of the parallel branch 5 is connected to the medium-pressure cylinder exhaust pipe 21, and the other end is connected to the high-pressure cylinder exhaust pipe 11 between the check valve 13 and the exhaust port of the high-pressure cylinder 1, and a parallel switching valve 51 is provided on the parallel branch 5.

[0019] In actual use, a medium-pressure main regulating valve 111 is provided on the high-pressure cylinder exhaust pipe 11 near the air inlet of the medium-pressure cylinder 2; a low-pressure main air valve 211 is provided on the medium-pressure cylinder exhaust pipe 21 near the air inlet of the low-pressure cylinder 3.

[0020] A high-pressure main gas regulating valve 12 is provided at one end of the first intake pipe 4 near the intake port of the high-pressure cylinder 1, and a first air supply valve 411 and a second air supply valve 421 are provided on the first branch 41 and the second branch 42 respectively; the high-pressure main gas regulating valve 12 and the first air supply valve 411 are in a sequential valve regulation mode, and the total valve position instruction is used as the main control quantity to control the load rate; the second air supply valve 421 indirectly controls the load rate in a joint control manner during the entire operation process. The adoption of this technical measure can meet the complex gas distribution regulation requirements. By controlling the high-pressure main gas regulating valve 12, the first air supply valve 411, the second air supply valve 421 and the check valve 13, it can meet the 100% full load rate requirement of the entire operation section when the main gas pressure continues to decrease at the large sliding pressure operation boundary, and at the same time has high economy. In addition, it can achieve wide load, efficient and flexible operation within the conventional 20%-100% load rate range in the entire operation section, and has fast and flexible peak-shaving and frequency-modulating operation capabilities. At the same time, unlike conventional thermal power systems, this system can have a larger load rate over-generation capacity. Therefore, the operation and control mode of this system takes into account high efficiency, wide load, fast and flexible peak and frequency regulation capabilities, and has a larger over-generation capacity.

[0021] During normal operation control, the system has a normal high and medium voltage series operation mode and a normal high and medium voltage parallel operation mode.

[0022] Among them, in normal high and medium voltage series operation mode: The high-pressure gas (main gas) comes from the gas storage device, absorbs heat and heats up after passing through the first heater 6, passes through the high-pressure main gas regulating valve 12, and enters the high-pressure cylinder 1 to expand and do work. At the same time, another part of the gas comes from the main gas, passes through the first air replenishment valve 411, and merges with the gas from the high-pressure main gas regulating valve 12 at a certain stage in the high-pressure cylinder 1. The two gases expand and do work in the remaining stages of the high-pressure cylinder 1 at the same time. The exhaust gas of the high-pressure cylinder 1 passes through the check valve 13 and enters the second heater 7. At this time, another part of the gas comes from the main gas, passes through the second air replenishment valve 421, and merges with the gas from the high-pressure cylinder exhaust pipe 11 at the inlet position of the second heater 7, and then absorbs heat and heats up in the second heater 7, passes through the medium-pressure main regulating valve 111, and enters the medium-pressure cylinder 2 to expand and do work. The exhaust gas of the medium-pressure cylinder 2 enters the third heater 8 to absorb heat and heat, passes through the low-pressure main gas valve 211, and enters the low-pressure cylinder 3 to expand and do work, and then the exhaust gas is discharged to the atmosphere through the low-pressure cylinder exhaust pipe 31.

[0023] Among them, in the normal high-pressure and medium-pressure parallel operation mode: the high-pressure gas (main gas) comes from the gas storage device, absorbs heat and heats up after passing through the first heater 6, passes through the high-pressure main gas regulating valve 12, and enters the high-pressure cylinder 1 to expand and do work. At the same time, another part of the gas comes from the main gas, passes through the first air replenishment valve 411, and merges with the gas from the high-pressure main gas regulating valve 12 at a certain stage in the high-pressure cylinder 1. The two gases expand and do work in the remaining stages of the high-pressure cylinder 1 at the same time, and the high-pressure cylinder 1 exhausts and transports to the outlet of the medium-pressure cylinder 2. In addition, another gas from the main gas absorbs heat and heats up in the second heater 7 after passing through the second air replenishment valve 421, passes through the medium-pressure main regulating valve 111, and enters the medium-pressure cylinder 2 to expand and do work. After the two gases merge at the exhaust outlet of the medium-pressure cylinder 2, they enter the third heater 8 to absorb heat and heat up, pass through the low-pressure main gas valve 211, enter the low-pressure cylinder 3 to expand and do work, and then exhaust to the atmosphere.

[0024] The difference between the above-mentioned series and parallel operation modes of the high and medium pressure cylinders 2 is that in the series scheme, the exhaust of the high pressure cylinder 1 enters the second heater 7 and the air inlet of the medium pressure cylinder 2 through the check valve 13. In the parallel scheme, the exhaust of the high pressure cylinder 1 is directly discharged to the exhaust port of the medium pressure cylinder 2 through the parallel switching valve 51. As for the inlet flow of the medium pressure cylinder 2, in the series scheme, the inlet flow of the medium pressure cylinder 2 includes the exhaust of the high pressure cylinder 1 and the flow from the second air replenishment valve 421; while in the parallel scheme, the inlet flow of the medium pressure cylinder 2 only includes the flow from the second air replenishment valve 421.

[0025] The large sliding pressure and wide load compressed gas energy storage turbine system of the present invention can realize smooth and reliable switching and control of the large sliding pressure turbine unit over the entire load process by adopting the operating method of throttling + two-stage air supply + parallel connection of high and medium pressure cylinders + joint control + setting the target rate for a certain valve at a certain stage. It has a faster load response capability and higher economy in the whole operation cycle.

[0026] Specifically, the operation method of the large sliding pressure and wide load compressed gas energy storage turbine system comprises the following steps: S1. According to the size of the main gas pressure, it is set to multiple stages from high to low. Specifically, according to the size of the main gas pressure, it is set to P0-P1-P2-P3-P4 from high to low; S2. P0-P1 stage: This stage is the conventional throttling operation mode; the design main gas pressure is P1; at this time, the high-pressure main gas regulating valve 12 is used to control the regulating load; S3. P1-P2 stage: This stage is a conventional one-stage air supply mode; at this time, the main gas pressure is less than the designed main gas pressure, and the high-pressure main gas regulating valve 12 is fully opened, and the first air supply valve 411 is used to control the load; S4.P2-P3 stage: This stage is a two-stage air supply mode; at this time, the high-pressure main air regulating valve 12 is fully opened, the first air supply valve 411 is fully opened, and the second air supply valve 421 and the main valve position instruction are connected by a logic of joint control to execute the effect of opening wide; S5. P3 stage: This stage is a parallel switching process; when the main gas pressure reaches P3, the opening of the second air supply valve 421 reaches a certain opening, at which time the enthalpy drop section of the stage before the air supply point is shortened, and the high-pressure cylinder exhaust is switched from the original medium-pressure cylinder inlet to the medium-pressure cylinder exhaust position, so that the high-pressure cylinder 1 and the medium-pressure cylinder 2 are switched from the original series structure to the parallel structure; Specifically, the parallel switching process: when the main gas pressure reaches P3, the opening of the second air replenishment valve 421 reaches a certain opening, and the enthalpy drop section of the stage before the air replenishment point is shortened, which on the one hand leads to an increase in the high-pressure exhaust temperature, and on the other hand will make the stage flow before the air replenishment point smaller, and there is a possibility of blast overheating. At this time, consider switching the exhaust of the high-pressure cylinder 1 from the original delivery to the air inlet of the medium-pressure cylinder 2 through the high-pressure cylinder exhaust pipe 11 to the exhaust port position of the medium-pressure cylinder 2 through the parallel branch 5, so that the high-pressure cylinder 1 and the medium-pressure cylinder 2 are switched from the original series structure to the parallel structure in terms of structure.

[0027] In the P3 stage: when the parallel switching process is in progress, the main gas pressure P3 is used as the trigger instruction, and the switching duration is preset to a fixed duration. During this time period, the parallel switching valve 51 is gradually fully opened and the check valve 13 is gradually closed; the parallel switching valve 51 is fully opened and the check valve 13 is fully closed; the switching is completed.

[0028] Specifically, the exhaust flow of the high-pressure cylinder 1 is divided into two different directions: one is through the high-pressure cylinder exhaust pipe 11 to the air inlet of the medium-pressure cylinder 2, and the other is through the parallel branch 5 to the exhaust port of the medium-pressure cylinder 2; and finally the flow of the high-pressure cylinder exhaust pipe 11 is reduced, and the flow of the parallel branch 5 is increased, until all the exhaust flow of the high-pressure cylinder 1 reaches the exhaust port of the medium-pressure cylinder 2, and the check valve 13 at the air inlet of the high-pressure cylinder exhaust pipe 11 to the medium-pressure cylinder 2 is closed.

[0029] Cylinder paralleling process 1, high pressure cylinder exhaust pipe 100%, parallel branch 0% Cylinder paralleling process 2: high pressure cylinder exhaust pipe 90%, parallel branch 10% Cylinder paralleling process 3: high pressure cylinder exhaust pipe 80%, parallel branch 20% … Cylinder paralleling process n-1: high pressure cylinder exhaust pipe 10%, parallel branch 90% Cylinder paralleling process n: high pressure cylinder exhaust pipe 0%, parallel branch 100% The parallel switching valve 51 is fully opened, and the check valve 13 is fully closed; the switching is completed.

[0030] When the parallel switching process is in progress, the main valve position instruction controls the load, and the second air supply valve 421 jointly controls the load.

[0031] However, considering that there are many possibilities for the flow distribution problem of the high-pressure cylinder 1 vs. the medium-pressure cylinder 2 after parallel connection, the second air supply valve 421 uses the start of action of the parallel switching valve 51 as a trigger instruction, activates the second air supply valve 421 and starts to open continuously at a predetermined rate. The use of this technical measure is beneficial to the economy of the system.

[0032] S6.P3-P4 stage: This stage is a parallel operation process; the second air supply valve 421 is set to manual mode, that is, a separate control signal is given to the second air supply valve 421, so that the second air supply valve 421 is continuously opened at a certain rate; the total valve position command controls the load, and the second air supply valve 421 is jointly controlled to feedback the load rate; S7. P4 stage: This stage is the process of sequential control to reduce load until shutdown. When the main gas pressure is P4, sequential control to reduce load until shutdown is required. At this time, the parallel switching valve 51 is open, and the high and medium pressure cylinders are operating in parallel mode. The set load target is reduced, and the joint control logic links the second air supply valve 421 to close until shutdown or reverse power phase adjustment mode.

[0033] In all operation stages of the main gas pressure P0-P1-P2-P3-P4, there may also be a frequency regulation and peak regulation mode operation process, the main purpose of which is to enable the unit to quickly increase or decrease the load to meet the requirements of the power grid. Compared with conventional thermal power turbine units, this unit has a faster load response speed and a larger load regulation capability, and the operation regulation is more flexible and efficient.

[0034] Specifically: When the high and medium pressure cylinders 2 are operated in series mode, the load rate is adjusted by the total valve position command with precise feedback. At the same time, when the total valve position command reaches the upper limit or the lower limit, the second air supply valve 421 is linked to open or close, so that the total valve position command falls back to a certain opening, which has a faster load adjustment response speed and ability; When the high and medium pressure cylinders 2 are operating in parallel mode, the load rate is adjusted by the total valve position command with precise feedback. At this time, the total valve position command is usually in a smaller command. At the same time, when the total valve position command reaches the upper limit or the lower limit, the second air supply valve 421 is linked to open or close, so that the total valve position command falls back to a certain opening, with faster load regulation response speed and ability.

[0035] Among them, when the high and medium pressure cylinders 2 operate in parallel mode, the way they respond to load changes is similar to that of the high and medium pressure cylinders 2 in series mode. The difference is that at this time, the total valve position command is usually a smaller command, so it has a faster load adjustment capability and a lower probability of triggering the linkage control logic.

[0036] The technical solutions provided by the embodiments of the present invention are introduced in detail above. Specific examples are used herein to illustrate the principles and implementation methods of the embodiments of the present invention. The description of the above embodiments is only applicable to help understand the principles of the embodiments of the present invention. At the same time, for those skilled in the art, according to the embodiments of the present invention, there will be changes in the specific implementation methods and application scopes. In summary, the content of this specification should not be understood as limiting the present invention.

Claims

1. A large sliding pressure and wide load compressed gas energy storage turbine system, characterized in that: It includes a high-pressure cylinder, a medium-pressure cylinder, a low-pressure cylinder, a first air intake pipe and a parallel branch; one end of the first air intake pipe is connected to a first heater, and the other end thereof is connected to the air intake port of the high-pressure cylinder; The exhaust port of the high-pressure cylinder is connected to the air inlet of the medium-pressure cylinder through the high-pressure cylinder exhaust pipe, and the exhaust port of the medium-pressure cylinder is connected to the air inlet of the low-pressure cylinder through the medium-pressure cylinder exhaust pipe; the exhaust port of the low-pressure cylinder discharges exhaust gas to the outside through the low-pressure cylinder exhaust pipe; the high-pressure cylinder exhaust pipe and the medium-pressure cylinder exhaust pipe are respectively provided with a second heater and a third heater; A check valve is provided on the high-pressure cylinder exhaust pipe between the exhaust port of the high-pressure cylinder and the second heater; A first branch and a second branch are connected in parallel on the first intake pipe, the first branch is connected to the high-pressure cylinder at one end away from the first intake pipe, the second branch is connected to the high-pressure cylinder exhaust pipe at one end away from the first intake pipe, one end of the parallel branch is connected to the medium-pressure cylinder exhaust pipe, and the other end is connected to the high-pressure cylinder exhaust pipe between the check valve and the exhaust port of the high-pressure cylinder, and a parallel switching valve is provided on the parallel branch.

2. The large sliding pressure and wide load compressed gas energy storage turbine system according to claim 1 is characterized in that: A high-pressure main air regulating valve is provided at one end of the first air intake pipeline close to the air intake port of the high-pressure cylinder, and a first air supply valve and a second air supply valve are provided on the first branch and the second branch respectively; The high-pressure main air regulating valve and the first air supply valve are in sequential valve regulation mode, and the total valve position instruction is used as the main control quantity to control the regulating load rate; the second air supply valve indirectly controls the regulating load rate in a joint control manner during the entire operation process.

3. An operating method of a large sliding pressure and wide load compressed gas energy storage turbine system, used to control the turbine system of any one of claims 1 or 2, characterized in that: The following steps are involved: S1. According to the main gas pressure, it is set to P0-P1-P2-P3-P4 from high to low; S2.P0-P1 stage: when the design main gas pressure is P1; at this time, the high-pressure main gas regulating valve controls the regulating load; S3.P1-P2 stage: At this time, the main gas pressure is less than the designed main gas pressure. At this time, the high-pressure main gas regulating valve is fully opened, and the first air supply valve is used to control the load. S4.P2-P3 stage: At this time, the high-pressure main gas regulating valve is fully opened, the first air supply valve is fully opened, and the second air supply valve and the main valve position instruction are connected by the logic of joint control to execute the effect of opening wide; S5. P3 stage: When the main gas pressure reaches P3, the opening of the second air supply valve reaches a certain opening, at which time the enthalpy drop section of the stage before the air supply point is shortened, and the high-pressure cylinder exhaust is switched from the original medium-pressure cylinder inlet to the medium-pressure cylinder exhaust position, so that the high-pressure cylinder and the medium-pressure cylinder are switched from the original series structure to the parallel structure; S6.P3-P4 stage: the second air supply valve is set to manual mode, that is, a separate control signal is given to the second air supply valve to allow the second air supply valve to open continuously at a certain rate; the total valve position command controls the load, and the second air supply valve is jointly controlled to feedback the load rate; S7.P4 stage: When the main gas pressure is P4, it is necessary to control the load to stop; at this time, the parallel switching valve is open, and the high and medium pressure cylinders are operating in parallel mode; reduce the set load target, and the joint control logic links the second air supply valve to close until shutdown or reverse power phase adjustment mode.

4. The method for operating the large sliding pressure and wide load compressed gas energy storage turbine system according to claim 3 is characterized in that: The operation method also includes frequency modulation and peak modulation mode operation control: When the high and medium pressure cylinders are operated in series mode, the load rate is adjusted by the total valve position command with precise feedback. At the same time, when the total valve position command reaches the upper or lower limit, the second air supply valve is linked to open or close, so that the total valve position command falls back to a certain opening, with faster load regulation response speed and ability; When the high and medium pressure cylinders are operating in parallel mode, the load rate is adjusted by the total valve position command with precise feedback. At this time, the total valve position command is usually at a smaller command. At the same time, when the total valve position command reaches the upper or lower limit, the second air supply valve is linked to open or close, so that the total valve position command falls back to a certain opening, with faster load regulation response speed and ability.

5. The method for operating the large sliding pressure and wide load compressed gas energy storage turbine system according to claim 3, characterized in that: When the parallel switching process is carried out, the main gas pressure P3 is used as the trigger instruction, and the switching duration is preset to a fixed duration. During this time period, the parallel switching valve is gradually fully opened and the check valve is gradually closed; the parallel switching valve is fully opened and the check valve is fully closed; the switching is completed.

6. The method for operating the large sliding pressure and wide load compressed gas energy storage turbine system according to claim 5, characterized in that: When the parallel switching process is in progress, the main valve position instruction controls the load, and the second air supply valve jointly controls the load.

7. The method for operating the large sliding pressure and wide load compressed gas energy storage turbine system according to claim 6, characterized in that: The second air supply valve uses the start of the action of the parallel switching valve as a trigger instruction, and activates the second air supply valve to start opening continuously at a predetermined rate.

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