CN106640778A - Slide piece pressure energy exchanger with matched design between slide pieces and molding lines - Google Patents

Abstract

The invention discloses a sliding vane type pressure energy exchanger designed to match the sliding vane and the molded line. The rotor divides the inner cavity into two chambers, a fluid A chamber and a fluid B chamber, and the fluid A side and the fluid B side are The cylinder profile is symmetrical to each other, and is formed by connecting the sealing section I, the inlet section, the middle section, the outlet section and the sealing section II in sequence. The cylinder profile and the number of slides are designed to match. The product of the angle spanned by the middle section of the molded line is 2π, which can reduce the energy loss caused by the rapid depressurization of the liquid caused by the increase of the space between the two adjacent slides, and avoid the failure of the equipment caused by the compression of the liquid. Stable operation or damage to the normal structure of the equipment ensures the stable and efficient operation of the equipment. Its structure is simple and easy to implement, and it has strong operability.

Description

A sliding vane type pressure energy exchanger designed to match the sliding vane and profile

【Technical field】

The invention belongs to the technical field of residual pressure recovery, and relates to a sliding vane type pressure energy exchanger, in particular to a sliding vane type pressure energy exchanger designed to match the sliding vane and the profile.

【Background technique】

There are a large number of high-pressure fluids that can recover excess pressure in energy and chemical systems. The pressure energy can be transferred to the low-pressure fluid to be pressurized through the pressure energy exchanger, so as to realize the recovery and reuse of excess pressure energy, and significantly reduce the energy consumption and cost of industrial systems. , effectively solve the waste of residual pressure energy.

The existing Chinese patent CN102865259A discloses a pressure exchanger, which uses high-pressure fluid to directly contact and pressurize low-pressure fluid, and uses the tangential impact force of high and low-pressure water flow as the power to rotate the rotor. The clearance fit of the cover controls leakage. The device has a small single-machine processing capacity, a relatively complex structure, high processing and installation precision requirements, and a large mixing phenomenon between fluids.

The existing US Patent No. 745702 discloses an energy recovery device, which is composed of a stator, a rotor, and a sliding vane. The process of pressurizing one fluid to another fluid is realized through the device. However, the single shape of the cylinder makes the cylinder and the rotor in line contact at the minimum diameter of the cylinder (considering the width of the cylinder), and the leakage is difficult to control, resulting in low volumetric efficiency. At the same time, the volume of the cavity between two adjacent slides first increases and then decreases when passing through the long diameter. When the space increases, the liquid in the cavity decreases rapidly, and even cavitation occurs, resulting in fluid energy loss. loss; when the space is reduced, because the liquid is approximately incompressible fluid, it will affect the stable operation of the equipment or damage the normal structure of the equipment.

【Content of invention】

In order to overcome the defects in the above-mentioned prior art, the object of the present invention is to provide a sliding vane pressure energy exchanger with a reasonable structural design and strong operability, which is designed to match the sliding vane and the profile line, so as to effectively reduce the pressure energy transmission. The energy loss in the process ensures the stable and efficient operation of the equipment.

The present invention is realized through the following technical solutions:

A sliding vane type pressure energy exchanger designed to match the sliding vane and the profile, including a cylinder, a rotor and a sliding vane, the rotor is placed in the inner cavity of the cylinder, the rotor adopts a circular profile, and the cylinder adopts a quasi-elliptical shape line, the rotor divides the inner cavity into two chambers, the fluid A chamber and the fluid B chamber. There is a chute on the rotor in the radial direction, and a sliding piece is arranged in the chute. The cylinder body on the fluid A side and the fluid B side The profiles are symmetrical to each other and are all connected in turn by the sealing section I, the inlet section, the middle section, the outlet section and the sealing section II. The product of the number of slides and the angle spanned by the middle section is 2π; The flow section and the outflow section are respectively connected with the high-pressure inlet of fluid A and the low-pressure outlet of fluid A, and the inflow section and the outflow section of the fluid B side are respectively connected with the low-pressure inlet of fluid B and the high-pressure outlet of fluid B.

Further, the sealing section I and the sealing section II of the cylinder body molding line are the same, the inlet section and the outlet section have the same molding line, and the cylinder body molding line is continuous in three stages and has a smooth transition.

Further, the sealing section I and the sealing section II of the profile of the cylinder body are circular profiles.

Further, the inlet section and the outlet section of the profile line of the cylinder body are polynomial curves of the seventh degree.

Further, the middle section of the profile line of the cylinder body is a simple harmonic profile line.

Further, at the sealing section I and the sealing section II, there is a small gap between the rotor and the inner wall of the cylinder.

Further, the polar diameter function of the cylinder profile for:

in, is the azimuth variable; θ ₀ , θ ₁ , θ ₂ and θ ₃ are the azimuth angles; R ₁ is the short radius of the cylinder profile; R ₂ is the long radius of the cylinder profile; a ₀ ~ a ₁₅ are the equations above The coefficients of the equation to be found must meet the following conditions:

ρ ₁ is the function of the sealing section I, ρ ₂ is the function of the inflow section, ρ ₃ is the function of the middle section, ρ ₄ is the function of the outflow section, and ρ ₅ is the function of the sealing section II.

Compared with the prior art, the present invention has the following beneficial technical effects:

In the sliding vane type pressure energy exchanger of the matching design of the sliding vane and the profile disclosed in the present invention, the rotor divides the inner cavity into two chambers, the fluid A chamber and the fluid B chamber, and the cylinder body on the fluid A side and the fluid B side The profiles are symmetrical to each other and are all connected in turn by the sealing section I, inlet section, middle section, outlet section and sealing section II. The product of the angle spanned by the middle section is 2π, which can reduce the energy loss caused by the rapid depressurization of the liquid caused by the increase of the space between the two adjacent slides, and avoid the unstable operation of the equipment caused by the compression of the liquid Or destroy the normal structure of the equipment. Structural matching optimization design is carried out on the mold line of the cylinder cavity and the number of slides to ensure the stable and efficient operation of the equipment. Its structure is simple and easy to realize, and it has strong operability.

Furthermore, the sealing section I and sealing section II of the cylinder profile are the same, the inlet section and the outlet section have the same profile, the cylinder profile is continuous in three stages, and the profile transition is smooth, so that the force condition of the sliding vane Good, reduce the sudden force when the slider slides, and reduce the motion impact and noise of the slider during operation.

Further, at the sealing section I and sealing section II, a small gap is set between the rotor and the inner wall of the cylinder. This design is beneficial to control the amount of the gap, prolong the length of the leakage channel between the two fluids, and effectively inhibit the mixing process between the two fluids. .

【Description of drawings】

Fig. 1-1 is the radial sectional view of the three-sliding-vane pressure energy exchanger designed to match the sliding vanes and profile lines of the present invention;

Fig. 1-2 is the radial sectional view of the four-sliding vane pressure energy exchanger of the present invention that is designed to match the sliding vanes and the profile;

Fig. 2 is the schematic diagram of the cylinder profile of the sliding vane type pressure energy exchanger designed to match the sliding vane and the profile of the present invention;

Among them, 1 is the high-pressure outlet of fluid B; 2 is the chute; 3 is the sliding plate; 4 is the chamber of fluid B; 5 is the low-pressure inlet of fluid B; 6 is the low-pressure outlet of fluid A; 7 is the chamber of fluid A; 8 is the rotor 9 is the cylinder body; 10 is the fluid A high pressure inlet; 11 is the sealing section I; 12 is the inlet section; 13 is the middle section; 14 is the outflow section; 15 is the sealing section II;

【detailed description】

The technical solutions of the present invention will be clearly and completely described below in conjunction with the embodiments. Apparently, the described embodiments are only a part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by persons of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

Referring to Figure 1-1 and Figure 1-2, the sliding vane type pressure energy exchanger designed to match the sliding vane and profile of the present invention includes a cylinder 9, a rotor 8 and a sliding vane 3, and the rotor 8 is placed in the cylinder 9 In the inner cavity, the rotor 8 adopts a circular profile, and the cylinder body 9 adopts a quasi-elliptical profile. The rotor 8 divides the inner cavity into a fluid A chamber 7 and a fluid B chamber 4. The rotor 8 is provided with a chute in the radial direction 2. A sliding piece 3 is arranged in the chute 2 .

Referring to Fig. 2, the cylinder profile lines 16 on the fluid A side and the fluid B side are symmetrical to each other, and are formed by sequentially connecting the sealing section I11, the inlet section 12, the middle section 13, the outlet section 14 and the sealing section II15. The inlet section 12 and the outlet section 14 of the fluid A side are respectively connected with the fluid A high pressure inlet 10 and the fluid A low pressure outlet 11, and the fluid B side inlet section 12 and the outlet section 14 are connected with the fluid B low pressure inlet 5 and respectively. Fluid B high pressure outlet 1 is connected.

The cylinder profile 16 is designed to match the number of slide vanes 3, and the product of the angle spanned by the middle section 13 of the cylinder profile 16 and the number of slide vanes 3 is 2π. The reason for this structural arrangement is as follows: when there is no sliding vane 3 in the middle section 13 of the chamber, such as when the sliding vane 3 of the double-sliding vane structure is located in the sealing section at both ends, the high-pressure side and the low-pressure side are directly connected in the chamber, and the fluid is similar A "short circuit" flows directly from the high side to the low side. At this time, in the fluid A chamber, the high-pressure fluid A does not realize the output of pressure energy due to direct conduction. In the fluid B chamber, fluid B flows in reverse. When there are two or more slides 3 in the middle section 13 of the fluid A side or the fluid B side, the volume of the cavity between two adjacent slides 3 will first increase and then decrease when passing through the long diameter. small. The pressure of the liquid in the cavity decreases rapidly with the increase of the space, and even cavitation occurs, resulting in the loss of fluid energy. When the space is reduced, because the liquid is approximately incompressible fluid, it will affect the stable operation of the equipment or damage the normal structure of the equipment. The angle between two adjacent slides 3 of the three-slide structure is π/3, and the azimuth angle spanned by the middle section 13 of the chamber can be designed to be about π/3, and the middle of the fluid A side and the fluid B side There is always and only one sliding vane 3 in the section 13 . For a structure with more than three slide sheets 3, there may be more than one slide sheet 3 in the middle section 13 at the same time. Similarly, when the angle spanned by the middle section 13 is π/4, the reasonable number of slides 3 is 4, and so on, the reasonable number of slides 3 should meet the conditions: the number of slides 3 is the same as that of the middle section 13 The product of the angles spanned is π/4. See Figure 1-1, the angle spanned by the middle section 13 is π/3, and the number of sliders 3 is designed to be 3; see Figure 1-2, the angle spanned by the middle section 13 is π/4, and the number of sliders 3 is designed to be 4 indivual. This structural arrangement can effectively reduce the energy loss in the process of pressure energy transmission and ensure the stable and efficient operation of the equipment.

The sealing section I11 and sealing section II15 of the cylinder profile 16 are circular profiles, the inlet section 12 and the outlet section 14 are polynomial curves of the seventh order, and the middle section 13 is a simple harmonic profile, which can ensure that the cylinder profile 16 The third order is continuous, and the transition of the cylinder profile 16 is smooth, so that the force condition of the sliding plate 3 is good when it slides, the sudden force when the sliding plate 3 slides is reduced, and the motion impact and motion noise of the sliding plate 3 during operation are reduced.

At the sealing section I11 and the sealing section II15, a small gap is set between the rotor 8 and the cylinder 9. The setting of the sealing section is beneficial to control the amount of the gap, prolong the length of the leakage channel between the two fluids, and effectively suppress the mixing process.

Pole diameter function of cylinder profile line 16 for:

in, is the azimuth variable; θ ₀ , θ ₁ , θ ₂ and θ ₃ are the azimuth angles; R ₁ is the short radius of the cylinder profile 16; R ₂ is the long radius of the cylinder profile 16; a ₀ ~ a ₁₅ are the above equations The coefficients of the equation to be found for the group satisfy the following conditions:

Specifically, R ₁ =0.0700m, R ₂ =0.0850mm, θ ₀ =5°, θ ₁ =30°, θ ₂ =150°, θ ₃ =175°, there are:

At this time, the polar diameter function of the cylinder profile 16 for:

The working principle of the sliding vane type pressure energy exchanger designed to match the sliding vane and the profile of the present invention is as follows:

The pressure energy contained in the high-pressure fluid on the fluid A side pushes the slide plate 3 to drive the rotor 8 to rotate, and the rotor 8 rotates to drive the slide plate 3 on the fluid B side, pushing the fluid in the chamber 4 of the fluid B into the high-pressure pipeline, so that the pressure energy of the high-pressure fluid A It is transmitted to the low-pressure fluid B, and the process of supercharging the high-pressure fluid A to the low-pressure fluid B is realized through the sliding vane pressure energy exchanger designed to match the sliding vane and the profile.

It should be noted that, in the sliding vane type pressure energy exchanger of the matching design of the sliding vane and the profile disclosed in the present invention, the cylinder profile is composed of the sealing section I11, the inlet section 12, the middle section 13, the outlet section 14 and the sealing section II15 are connected sequentially, and the profile lines at the inlet section 12 and the outlet section 14 are heptadic curves, which can ensure the third-order continuity of the cylinder profile line 16. Similarly, when the profiles at the inlet section 12 and the outlet section 14 are curves of degree nine, the fourth-order continuity of the cylinder profile 16 can be realized; when the profiles at the inlet section 12 and the outlet section 14 are During the eleventh curve, the five-order continuity of the cylinder profile line 16 and the like can be realized. The higher the order of profile curves at the inflow section 12 and the outflow section 14, the higher-order continuity of the profile line can be achieved, the force condition during the movement of the slide vane 3 can be improved, and the movement of the slide vane 3 can be reduced to a greater extent. Motion shock and motion noise during operation.

To sum up, in the sliding vane type pressure energy exchanger disclosed by the present invention, the matching design of the sliding vane and the profile line is designed to match the number of the profile line 16 of the cylinder body and the number of the sliding vanes 3, and the number of the sliding vanes 3 is in the middle of the profile line 16 of the cylinder body. The product of the angles spanned by the section 13 is 2π, which can reduce the energy loss caused by the rapid depressurization of the liquid in the cavity between two adjacent slides 3 due to the increase of the space, and avoid the instability of the equipment caused by the compression of the liquid Operate or destroy the normal structure of the equipment. At the same time, at the sealing section I11 and sealing section II15, a small gap is set between the rotor 8 and the inner wall of the cylinder body 9. This design is beneficial to control the amount of the gap, prolong the length of the leakage channel between the two fluids, and effectively inhibit the mixing process. The profile line 16 of the cylinder body is continuous at a high level, and the transition of the profile line is smooth, so that the force condition of the slide plate 3 is good when it slides, the sudden force of the slide plate 3 is reduced, and the movement impact and movement of the slide plate 3 during operation are reduced. noise. In the present invention, the structural matching design is carried out on the molded line 16 of the cylinder body and the quantity of the sliding vanes 3 to ensure the stable and efficient operation of the equipment. The structure is simple and easy to realize, and the operability is strong.

The above is a preferred embodiment of the present invention. Through the above description, relevant workers in the technical field can make various improvements and replacements without departing from the technical principles of the present invention. These improvements and replacements should also be regarded as protection scope of the present invention.

Claims (7)

1. The utility model provides a sliding vane formula pressure energy exchanger of sliding vane and molded lines matching design which characterized in that: the rotor (8) is arranged in an inner cavity of the cylinder body (9), the rotor (8) adopts a circular molded line, the cylinder body (9) adopts an ellipse-like molded line, the inner cavity is divided into two chambers, namely a fluid A chamber (7) and a fluid B chamber (4), by the rotor (8), a sliding groove (2) is formed in the rotor (8) along the radial direction, the sliding piece (3) is arranged in the sliding groove (2), the cylinder molded lines (16) on the fluid A side and the fluid B side are mutually symmetrical and are formed by sequentially connecting a sealing section I (11), an inflow section (12), a middle section (13), an outflow section (14) and a sealing section II (15), and the product of the number of the sliding pieces and the span angle of the middle section (13) is 2 pi; the fluid A side inflow section (12) and the fluid B side outflow section (14) are respectively communicated with the fluid A high-pressure inlet (10) and the fluid A low-pressure outlet (11), and the fluid B side inflow section (12) and the fluid B side outflow section (14) are respectively communicated with the fluid B low-pressure inlet (5) and the fluid B high-pressure outlet (1).

2. The sliding vane type pressure energy exchanger of sliding vane and molded line matching design as claimed in claim 1, wherein: the seal section I (11) and the seal section II (15) of the cylinder body molded line (16) are identical in molded line, the inflow section (12) and the outflow section (14) are identical in molded line, and the cylinder body molded line (16) is in three-step continuous and smooth transition.

3. The sliding vane type pressure energy exchanger of sliding vane and molded line matching design as claimed in claim 2, wherein: the sealing section I (11) and the sealing section II (15) of the cylinder body molded line (16) are circular molded lines.

4. The sliding vane type pressure energy exchanger of sliding vane and molded line matching design as claimed in claim 2, wherein: the inflow section (12) and the outflow section (14) of the cylinder body molded line (16) are seven-degree polynomial curves.

5. The sliding vane type pressure energy exchanger of sliding vane and molded line matching design as claimed in claim 2, wherein: the middle section (13) of the cylinder molded line (16) is a simple harmonic molded line.

6. Sliding vane type pressure energy exchanger designed with matching of sliding vane and profile according to claims 1 and 2, characterized in that at the sealing section I (11) and the sealing section II (15), a small gap is provided between the rotor (8) and the inner wall of the cylinder (9).

7. Sliding vane type pressure energy exchanger designed according to any of claims 1-5, characterized in that the polar diameter of the cylinder profile (16)Function(s)Comprises the following steps:

wherein,is an azimuth variable; theta₀、θ₁、θ₂And theta₃Is the azimuth; r₁The cylinder profile (16) is short radius; r₂Is a cylinder body molded line (16) long radius; a is₀～a₁₅The following conditions are satisfied for the equation coefficient to be solved of the equation set:

ρ₁as a function of the seal section I (11), p₂As a function of the inflow section (12), p₃As a function of the middle segment (13), p₄As a function of the outflow section (14), p₅As a function of the sealing section II (15).