Gear pump side plate, gear pump and vehicle

Abstract

The utility model relates to the technical field of vehicles, and discloses a gear pump side plate, a gear pump and a vehicle, the gear pump side plate comprises a driving gear shaft sub-side plate and a driven gear shaft sub-side plate which are connected with each other, the driving gear shaft sub-side plate is provided with a first arc-shaped balance groove, the driven gear shaft sub-side plate is provided with a second arc-shaped balance groove, and the first arc-shaped balance groove and the second arc-shaped balance groove are connected with each other. The first arc-shaped balance groove and the second arc-shaped balance groove face the same direction and are connected with each other; the end, away from the second arc-shaped balance groove, of the first arc-shaped balance groove is provided with a first damping groove with the sectional area gradually reduced, and the end, away from the first arc-shaped balance groove, of the second arc-shaped balance groove is provided with a second damping groove with the sectional area gradually reduced. By supplementing oil to the transition area, the pressure mutation delta P of the gear pump side plate transition area is reduced, the noise of the high-pressure gear oil pump is reduced, side plate abrasion is reduced, and the service life of the gear oil pump is prolonged.

Description

Technical Field

[0001] The utility model relates to the technical field, in particular to a gear pump side plate, a gear pump and a vehicle. Background Art

[0002] The gear oil pump is mainly composed of the front cover, pump body, gears, seals, bearings, rear cover, screws, etc., which are components that provide pressure oil for the hydraulic system. The side plate is a bimetallic powder metallurgy material. The oil on both sides maintains pressure balance, which determines the service life of the gear pump. Axial floating compensation means that the pressure oil balances the side plate, and the side plate and the gear end face are sealed to achieve axial floating compensation and ensure reliable axial sealing.

[0003] In the prior art, the high-pressure gear pump has a large noise and the floating side plate suffers from severe early wear. Utility Model Content

[0004] The utility model discloses a gear pump side plate, a gear pump and a vehicle, which are used for alleviating noise and wear of the gear pump.

[0005] In order to achieve the above object, the utility model provides the following technical solutions:

[0006] In a first aspect, a gear pump side plate is provided, which includes: a driving gear shaft side plate and a driven gear shaft side plate connected to each other, the driving gear shaft side plate is provided with a first arc-shaped balancing groove, the driven gear shaft side plate is provided with a second arc-shaped balancing groove, the first arc-shaped balancing groove and the second arc-shaped balancing groove are oriented in the same direction and are connected to each other; an end of the first arc-shaped balancing groove away from the second arc-shaped balancing groove is provided with a first damping groove with a gradually decreasing cross-sectional area, and an end of the second arc-shaped balancing groove away from the first arc-shaped balancing groove is provided with a second damping groove with a gradually decreasing cross-sectional area.

[0007] As described above, the cross-sectional areas of the first damping groove and the second damping groove are gradually reduced, which is beneficial to alleviating the problem of insufficient oil supply to the transition zone through the radial clearance and the end face clearance per unit time and slow pressure establishment in the transition zone. By supplying oil to the transition zone, the sudden pressure change ΔP in the transition zone of the side plate of the gear pump is reduced, the noise of the high-pressure gear oil pump is reduced, the wear of the side plate is reduced, and the service life of the gear oil pump is increased.

[0008] Optionally, the width of the first damping groove gradually decreases in a direction away from the second arc-shaped balancing groove; and the width of the second damping groove gradually decreases in a direction away from the first arc-shaped balancing groove.

[0009] Optionally, the maximum width of the first damping groove is smaller than the width of the first arc-shaped balancing groove; the maximum width of the second damping groove is smaller than the width of the second arc-shaped balancing groove.

[0010] Optionally, the minimum width of the first damping groove is zero; the minimum width of the second damping groove is zero.

[0011] Optionally, the cross-section of the first damping groove is an isosceles triangle; the cross-section of the second damping groove is an isosceles triangle.

[0012] Optionally, the cross-section of the first damping groove is an equilateral triangle; the cross-section of the second damping groove is an equilateral triangle.

[0013] Optionally, the depth of the first damping groove gradually decreases in a direction away from the second arc-shaped balancing groove; and the depth of the second damping groove gradually decreases in a direction away from the first arc-shaped balancing groove.

[0014] Optionally, the angle between the bottom edge of the first damping groove and the surface of the side plate of the driving gear shaft is less than 20 degrees; the angle between the bottom edge of the second damping groove and the surface of the side plate of the driven gear shaft is less than 20 degrees.

[0015] In a second aspect, a gear pump is provided, which includes a driving gear shaft, a driven gear shaft and a gear pump side plate described in any of the above technical solutions, wherein the driving gear shaft and the driven gear shaft are engaged through gears, the driving gear shaft sub-side plate is located at the gear end face of the driving gear shaft, and the opening of the first arc-shaped balancing groove faces the gear end face of the driving gear shaft, the driven gear shaft sub-side plate is located at the gear end face of the driven gear shaft, and the opening of the second arc-shaped balancing groove faces the gear end face of the driven gear shaft.

[0016] The advantages of the gear pump and the gear pump side plate described above over the prior art are the same and will not be described in detail here.

[0017] In a third aspect, a vehicle is provided, comprising the gear pump described in the above technical solution.

[0018] The advantages of the vehicle and the above-mentioned gear pump over the prior art are the same and will not be described in detail here. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 A schematic diagram of the structure of a gear pump side plate provided in an embodiment of the present application;

[0020] Figure 2 for Figure 1 A partial schematic diagram of the structure shown;

[0021] Figure 3 express Figure 2 Sectional view at the middle BB;

[0022] Figure 4 express Figure 2 Sectional view at AA;

[0023] Figure 5 express Figure 1 The schematic diagram of the gear pump side plate shown is in cooperation with the driving gear and the driven gear;

[0024] Figure 6 for Figure 5 Schematic diagram of the local structure;

[0025] Figure 7 for Figure 1 Theoretical calculation curve of pressure in the middle transition zone;

[0026] Figure 8 for Figure 1 The pressure curves in the transition zone before and after structural optimization are shown. DETAILED DESCRIPTION

[0027] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments in the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0028] The high-pressure gear pump adopts floating side plate type axial clearance automatic compensation technology. Two meshing gears are supported in front and rear rolling bearings, and the gear pump side plate can float axially in the housing. When the high-pressure gear pump is working, the high-pressure oil in the pressure oil chamber is led to the outer end face of the gear pump side plate through the oil hole on the gear pump side plate, and acts on the closed oil chamber formed by the ear-shaped sealing ring to form a clamping force. This force presses the gear pump side plate to the gear end face, and its size is proportional to the reverse thrust of the internal flow field on the side plate. At the same time, the lines of action of the clamping force and the reverse thrust coincide, which can avoid the side plate tilting and premature wear due to the force generated.

[0029] refer to Figure 1 and Figure 2 The gear pump side plate provided in the embodiment of the present application includes: a driving gear shaft side plate 10 and a driven gear shaft side plate 20 connected to each other, the driving gear shaft side plate 10 is provided with a first arc-shaped balancing groove K1, and the driven gear shaft side plate 20 is provided with a second arc-shaped balancing groove K2, the first arc-shaped balancing groove K1 and the second arc-shaped balancing groove K2 are oriented in the same direction and are connected to each other; a first damping groove M1 with a gradually decreasing cross-sectional area is provided at one end of the first arc-shaped balancing groove K1 away from the second arc-shaped balancing groove K2, and a second damping groove M2 with a gradually decreasing cross-sectional area is provided at one end of the second arc-shaped balancing groove K2 away from the first arc-shaped balancing groove K1.

[0030] As described above, the cross-sectional areas of the first damping groove M1 and the second damping groove M2 are gradually reduced, which is beneficial to alleviating the problem of insufficient oil replenishment to the transition zone through the radial clearance and the end face clearance per unit time and slow pressure establishment in the transition zone. By replenishing oil to the transition zone, the sudden pressure change ΔP in the transition zone of the side plate of the gear pump is reduced, the noise of the high-pressure gear oil pump is reduced, the wear of the side plate is reduced, and the service life of the gear oil pump is increased.

[0031] In a specific embodiment, along the direction away from the second arc-shaped balancing groove K2, the width of the first damping groove M1 gradually decreases, thereby, the cross-sectional area of ​​the first damping groove M1 gradually decreases, so that the pressure mutation ΔP in the transition zone is alleviated; along the direction away from the first arc-shaped balancing groove K1, the width of the second damping groove M2 gradually decreases, thereby, the cross-sectional area of ​​the second damping groove M2 gradually decreases, so that the pressure mutation ΔP in the transition zone is alleviated.

[0032] In a specific embodiment, the maximum width L of the first damping groove M1 is smaller than the width of the first arc-shaped balancing groove K1 to ensure volumetric efficiency and avoid a sudden decrease in the oil outlet flow rate; the maximum width of the second damping groove M2 is smaller than the width of the second arc-shaped balancing groove K2 to ensure volumetric efficiency and avoid a sudden decrease in the oil outlet flow rate.

[0033] In a specific embodiment, the minimum width of the first damping groove M1 is zero to achieve zero cross-sectional area and prevent a sudden pressure change at the end of the first damping groove M1; the minimum width of the second damping groove M2 is zero to achieve zero cross-sectional area and prevent a sudden pressure change at the end of the second damping groove M2.

[0034] refer to Figure 3 In a specific embodiment, the cross section of the first damping groove M1 is an isosceles triangle for easy cutting; the cross section of the second damping groove M2 is an isosceles triangle for easy cutting. For example, the cross section of the first damping groove M1 is an equilateral triangle; the cross section of the second damping groove M2 is an equilateral triangle, which can also better prevent the pressure mutation ΔP. Figure 3 In FIG. 8 , Lx represents the width of the first damping groove M1 at the corresponding position.

[0035] refer to Figure 4 In a specific embodiment, the depth of the first damping groove M1 gradually decreases in the direction away from the second arc-shaped balance groove K2, so that the cross-sectional area of ​​the first damping groove M1 gradually decreases, so that the pressure mutation ΔP in the transition zone is alleviated; the depth of the second damping groove M2 gradually decreases in the direction away from the first arc-shaped balance groove K1, so that the cross-sectional area of ​​the second damping groove M2 gradually decreases, so that the pressure mutation ΔP in the transition zone is alleviated. Figure 4 Medium R i xθ represents the length of the first damping groove M1.

[0036] In a specific embodiment, the bottom edge and both side edges of the first damping groove M1 can be straight lines, and the angle between the bottom edge of the first damping groove M1 and the surface of the driving gear shaft side plate 10 is less than 20 degrees, for example, it can be 10 degrees, 12 degrees, 14 degrees, 16 degrees, 17 degrees and 18 degrees, etc., to prevent the depth of the first damping groove M1 from suddenly becoming shallower due to the angle being too large, so that there is still a sudden pressure change in the transition zone; the angle between the bottom edge of the second damping groove M2 and the surface of the driven gear shaft side plate 20 is less than 20 degrees, for example, it can be 10 degrees, 12 degrees, 14 degrees, 16 degrees, 17 degrees and 18 degrees, etc., to prevent the depth of the second damping groove M2 from suddenly becoming shallower due to the angle being too large, so that there is still a sudden pressure change in the transition zone.

[0037] refer to Figure 5 and Figure 6 Since the gear pump uses the method of expanding the high-pressure area to balance the radial force, the transition area is reduced to only one tooth recess, that is, a two-tooth sealing structure is adopted. Therefore, the change in the pressure in the transition area is mainly related to the difference in flow into and out of the tooth recess. Among them, the tooth A and tooth B in the transition area of ​​the driving gear 11 are two sealing teeth, and the oil pressure P in the tooth recess between the two teeth of tooth A and tooth B is the transition area pressure, P S is the pressure in the high pressure area, and P0 is the oil inlet pressure. The first damping groove M1 and the second damping groove M2 are both V-type damping grooves, and the structural parameters of the V-type damping groove mainly include: the damping groove wrap angle θ and the side length L of the equilateral triangle triangular groove. After the side plate structure is optimized, since a V-type damping groove structure is added at the end of the radial force balance groove, in addition to the original flow Q3, flow Q4 and flow Q5, the flow Q6 flowing from the high pressure to the transition zone is increased through the V-type damping groove.

[0038] refer to Figure 7 , the analysis of the pressure change in the transition zone of the gear pump shows that the change in the pressure in the transition zone is mainly related to the gear structure, the axial radial clearance value and the pressure in the high-pressure zone. Since the working conditions and gear structure parameters of the gear pump are known, the pressure in the transition zone is calculated through the differential equation of the pressure in the transition zone. The analysis of the side plate structure of the gear pump shows that when the gear angle is 0.0≤φ≤0.52rad, the pressure value of the tooth recess in the transition zone can be obtained by the differential equation; when the gear angle φ>0.52rad, the tooth recess in the transition zone is connected to the radial force balance groove and enters the high-pressure zone, and the pressure of the oil in the tooth recess rises to 18.314MPa in a short time; therefore, the pressure of the tooth recess when it transitions from the transition zone to the high-pressure zone suddenly changes to ΔP=Ps-P=10.43Mpa.

[0039] The sudden change in pressure when the tooth recess transitions from the transition zone to the high-pressure zone is as high as 10.43MPa, which is extremely harmful to the gear pump and the side plate. Excessive sudden change in pressure not only causes high noise when the gear pump is working, but also causes problems such as high-frequency vibration of the side plate and cavitation in the transition zone, destroying the formation of the oil film in the transition zone of the side plate and accelerating the early wear of the side plate.

[0040] The test measured that the average pressure in the high-pressure area at the end of the balance tank is Ps≈18.09MPa, and when φ=0.52rad, the average pressure in the transition zone is P≈8.36MPa. The experimental data is consistent with the theoretical calculation results in the previous part, which fully verifies the correctness of the established mathematical model of transition zone pressure.

[0041] Through the above analysis, it can be known that the main reason for the excessive pressure mutation ΔP in the transition zone is that the amount of oil replenished to the transition zone through the radial clearance and the end face clearance in unit time is insufficient, and the pressure in the transition zone is slowly established. To solve this problem, the side plate structure needs to be changed, and a damping groove structure is added at the end of the radial force balance groove, that is, the driving gear shaft side plate 10 is provided with a first arc balance groove K1, and the driven gear shaft side plate 20 is provided with a second arc balance groove K2 to replenish oil to the transition zone.

[0042] The gear pump side plate provided in the embodiment of the present application minimizes the pressure mutation when the transition zone transitions to the high-pressure zone while ensuring the force balance and torque balance of the gear pump side plate, as well as the volumetric efficiency and mechanical efficiency of the gear pump.

[0043] refer to Figure 8 Before optimization, that is, when the damping groove is opened, when φ=0.52rad, the gear pump transition zone tooth recess is connected with the radial force balance groove, and the pressure mutation when the transition zone transitions to the high-pressure zone is ΔP=Ps-P=10.43MPa. After optimization, the pressure mutation is ΔP=Ps-P=3.67MPa.

[0044] Based on the same inventive concept, the embodiment of the present application also provides a gear pump, which includes a driving gear shaft, a driven gear shaft and a gear pump side plate provided in the above embodiment, wherein the driving gear shaft and the driven gear shaft are meshed through gears, the driving gear shaft sub-side plate 10 is located at the gear end face of the driving gear shaft, and the opening of the first arc-shaped balance groove K1 faces the gear end face of the driving gear shaft, the driven gear shaft sub-side plate 20 is located at the gear end face of the driven gear shaft, and the opening of the second arc-shaped balance groove K2 faces the gear end face of the driven gear shaft. The beneficial effects of the gear pump can refer to the effect analysis of the gear pump in the previous text.

[0045] Based on the same inventive concept, an embodiment of the present application also provides a vehicle, which includes a gear pump of the above technical solution, and its beneficial effects can be referred to the above analysis of the effects of the gear pump side plate.

[0046] Obviously, those skilled in the art can make various changes and modifications to the embodiments of the present invention without departing from the spirit and scope of the present invention. Thus, if these modifications and variations of the present invention fall within the scope of the claims of the present invention and their equivalents, the present invention is also intended to include these modifications and variations.

Claims

1. A gear pump side plate, characterized in that: include: A driving gear shaft sub-side plate and a driven gear shaft sub-side plate connected to each other, the driving gear shaft sub-side plate is provided with a first arc-shaped balancing groove, the driven gear shaft sub-side plate is provided with a second arc-shaped balancing groove, the first arc-shaped balancing groove and the second arc-shaped balancing groove face the same direction and are connected to each other; A first damping groove with a gradually decreasing cross-sectional area is provided at one end of the first arc-shaped balancing groove away from the second arc-shaped balancing groove, and a second damping groove with a gradually decreasing cross-sectional area is provided at one end of the second arc-shaped balancing groove away from the first arc-shaped balancing groove.

2. The gear pump side plate according to claim 1, characterized in that: Along the direction away from the second arc-shaped balancing groove, the width of the first damping groove gradually decreases; The width of the second damping groove gradually decreases in a direction away from the first arc-shaped balancing groove.

3. The gear pump side plate according to claim 2, characterized in that: The maximum width of the first damping groove is smaller than the width of the first arc-shaped balancing groove; The maximum width of the second damping groove is smaller than the width of the second arc-shaped balancing groove.

4. The gear pump side plate according to claim 2, characterized in that: The minimum width of the first damping groove is zero; The minimum width of the second damping groove is zero.

5. The gear pump side plate according to claim 1, characterized in that: The cross section of the first damping groove is an isosceles triangle; The cross section of the second damping groove is an isosceles triangle.

6. The gear pump side plate according to claim 5, characterized in that: The cross section of the first damping groove is an equilateral triangle; The cross section of the second damping groove is an equilateral triangle.

7. The gear pump side plate according to claim 1, characterized in that: The depth of the first damping groove gradually decreases in a direction away from the second arc-shaped balancing groove; The depth of the second damping groove gradually decreases in a direction away from the first arc-shaped balancing groove.

8. The gear pump side plate according to claim 7, characterized in that: The included angle between the bottom edge of the first damping groove and the surface of the side plate of the driving gear shaft is less than 20 degrees; The included angle between the bottom edge of the second damping groove and the surface of the side plate of the driven gear shaft is less than 20 degrees.

9. A gear pump, characterized in that: include: A driving gear shaft, a driven gear shaft and a gear pump side plate as described in any one of claims 1 to 8, wherein the driving gear shaft and the driven gear shaft are meshed through gears, the driving gear shaft sub-side plate is located at the gear end face of the driving gear shaft, and the opening of the first arc-shaped balancing groove faces the gear end face of the driving gear shaft, the driven gear shaft sub-side plate is located at the gear end face of the driven gear shaft, and the opening of the second arc-shaped balancing groove faces the gear end face of the driven gear shaft.

10. A vehicle, characterized in that: Including the gear pump described in claim 9.

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