Novel axial plunger pump vibration and noise reduction valve plate capable of resisting cylinder body overturning

Abstract

The utility model relates to the technical field of axial plunger pumps, and particularly discloses a novel axial plunger pump vibration and noise reduction valve plate capable of preventing a cylinder body from overturning. An oil absorption waist-shaped groove and an oil discharge waist-shaped groove are formed in a valve plate circular ring on the front wall of a valve plate body and located on the left side and the right side of a shaft hole respectively; an upper dead point and a lower dead point are arranged at the positions, located at the top end and the bottom end of the flow distribution circular ring, of the front wall of the flow distribution plate body, oil suction damping grooves and first damping holes are formed between the bottom ends of the oil suction kidney-shaped grooves and the lower dead points, and the oil suction damping grooves communicate with the front portions of the bottom ends of the oil suction kidney-shaped grooves. A second damping hole, a third damping hole and a fourth damping hole are sequentially formed between the top end of the oil discharge kidney-shaped groove and the top dead center from left to right, and an oil discharge damping groove communicated with the oil discharge kidney-shaped groove is formed in the position, corresponding to the second damping hole, of the front wall of the valve plate body. The rear wall of the valve plate body is provided with an arc-shaped connecting groove for communicating the rear ends of the second damping hole, the third damping hole and the fourth damping hole with the kidney-shaped oil discharging groove, and an oil discharging groove is formed in the position, corresponding to the first damping hole, of the rear wall of the valve plate body in the radial direction; and pressure and flow pulsation generated in the flow distribution process are reduced, so that vibration and noise are reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of axial piston pumps, and specifically relates to a vibration reduction and noise reduction distribution disc for a new type of axial piston pump that resists cylinder block overturning. Background Technique

[0002] As a core component of a hydraulic transmission system, the axial piston pump has the characteristics of a compact structure, a high rated pressure, a large output power, and convenient flow regulation, and is widely used in many fields such as construction machinery. However, at the same time, due to the flow distribution characteristics of the pump, during the flow distribution process, when the plunger cavity transitions from the oil suction waist-shaped groove to the oil discharge waist-shaped groove, there are closed dead volume expansion and air suction phenomena in the plunger cavity, and at the same time, flow reversal will also occur. When the plunger cavity transitions from the oil discharge waist-shaped groove to the oil suction waist-shaped groove, there are closed dead volume compression and pressure overshoot phenomena in the plunger cavity. These phenomena are one of the main reasons for the noise generation of the axial piston pump.

[0003] In the existing technical solutions, a single pre-boost damping groove, damping hole or a combination thereof is mostly used to solve the vibration and noise problems, but the ideal vibration reduction and noise reduction effect has not been achieved.

[0004] Therefore, it is necessary to optimize the structure of the distribution disc to reduce the flow and pressure pulsations, thereby reducing the vibration and noise of the axial piston pump. Content of the Utility Model

[0005] The purpose of the utility model is to provide a vibration reduction and noise reduction distribution disc for a new type of axial piston pump that resists cylinder block overturning, the structure of which can improve the cylinder block tilting problem, and at the same time can reduce the pressure and flow pulsations generated during the flow distribution process, thereby achieving vibration reduction and noise reduction.

[0006] To achieve the above purpose, the utility model provides the following technical solution: A vibration reduction and noise reduction distribution disc for a new type of axial piston pump that resists cylinder block overturning, including a distribution disc body, a shaft hole is provided in the middle of the distribution disc body, an oil suction waist-shaped groove and an oil discharge waist-shaped groove are respectively provided at positions on the front wall distribution ring of the distribution disc body on the left and right sides of the shaft hole, the upper dead point and the lower dead point are respectively provided at the top and bottom ends of the distribution ring on the front wall of the distribution disc body, an oil suction damping groove and a first damping hole are provided between the bottom end of the oil suction waist-shaped groove and the lower dead point, and the oil suction damping groove is communicated with the front part of the bottom end of the oil suction waist-shaped groove; a second damping hole, a third damping hole and a fourth damping hole are sequentially arranged in the order from left to right between the top end of the oil discharge waist-shaped groove and the upper dead point, and an oil discharge damping groove communicated with the oil discharge waist-shaped groove is provided at the position on the front wall of the distribution disc body corresponding to the second damping hole; an arc-shaped connecting groove for communicating the rear ends of the second damping hole, the third damping hole and the fourth damping hole with the oil discharge waist-shaped groove is provided on the rear wall of the distribution disc body, and an oil discharge groove extending radially is provided at the position on the rear wall of the distribution disc body corresponding to the first damping hole.

[0007] Preferably, a plurality of reinforcing ribs are provided in the inner cavity of the oil drain waist-shaped groove.

[0008] Preferably, the oil drain damping groove is a triangular groove, the oil suction damping groove is a U-shaped groove, and the size of the oil drain damping groove is larger than that of the oil suction damping groove.

[0009] Preferably, the first damping hole, the second damping hole, the third damping hole and the fourth damping hole are on the same circular arc, and the first damping hole, the second damping hole, the third damping hole and the fourth damping hole are all stepped holes with a smaller front-end hole diameter than the rear-end hole diameter.

[0010] Preferably, the included angle between the fourth damping hole and the top dead center is 0-3°, the included angle between the third damping hole and the top dead center is 8-10°, the included angle between the second damping hole and the top dead center is 20-24°, and the third damping hole and the first damping hole are symmetric about the center of the distribution plate body.

[0011] Preferably, an outer auxiliary support belt and an inner auxiliary support belt are respectively provided at positions near the outer edge and the inner edge of the front wall of the distribution plate body, and an outer sealing belt and an inner sealing belt are respectively provided on the inner sides of the outer auxiliary support belt and the inner auxiliary support belt.

[0012] Compared with the prior art, the beneficial effects of the present utility model are:

[0013] When the novel vibration reduction and noise reduction distribution plate for an axial piston pump against cylinder block overturning involved in the present utility model is in use, high-pressure oil enters the plunger cavity at the end of the oil suction period through the fourth damping hole, which plays a role in compensating the pressure in the plunger cavity, preventing the pressure in the plunger cavity from dropping below the atmospheric separation pressure, and reducing the generation of cavitation; the third damping hole compensates for the pressure reduction in the plunger cavity caused by the closed expansion of the plunger cavity, achieving a pre-boosting effect; the second damping hole is combined with the oil drain waist-shaped groove and is directly communicated with the plunger cavity, enabling the plunger cavity to be better connected with the oil drain damping groove, reducing flow reverse flow and pressure pulsation, thereby achieving vibration reduction and noise reduction; at the end of the oil drain period, high-pressure hydraulic oil flows into the oil discharge groove through the first damping hole, generating a pre-pressure reduction effect, thereby reducing the vibration caused by pressure shock; at the same time, through the above structural improvements, the pressure transition in the plunger cavity from the low-pressure oil suction area to the high-pressure oil discharge area and from the high-pressure oil discharge area to the low-pressure oil suction area is smoothed, and the hydraulic pressure moment on the cylinder block is balanced, thereby avoiding the occurrence of cylinder block overturning. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 is the front view structural schematic diagram of the whole of the present utility model;

[0015] Figure 2 is the rear view structural schematic diagram of the whole of the present utility model;

[0016] Figure 3 For the present utility modelFigure 1 Schematic diagram of the A-A sectional structure in

[0017] In the figure: 1 - distribution disc body; 1.1 - top dead center; 1.2 - bottom dead center; 1.3 - shaft hole;

[0018] 2 - oil suction waist-shaped groove;

[0019] 3 - oil discharge waist-shaped groove; 3.1 - reinforcing rib;

[0020] 4 - oil suction damping groove;

[0021] 5 - damping hole one;

[0022] 6 - oil discharge damping groove;

[0023] 7 - damping hole two;

[0024] 8 - damping hole three;

[0025] 9 - damping hole four;

[0026] 10 - oil discharge groove;

[0027] 11 - arc connecting groove;

[0028] 12 - outer auxiliary support belt;

[0029] 13 - outer sealing belt;

[0030] 14 - inner auxiliary support belt;

[0031] 15 - inner sealing belt. Specific implementation manners

[0032] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all the embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present utility model.

[0033] Please refer to Figures 1-3, the present utility model provides a technical solution: a novel anti-overturning axial piston pump vibration reduction and noise reduction valve plate, including a valve plate body 1. A shaft hole 1.3 is provided in the middle of the valve plate body 1. An oil suction waist-shaped groove 2 and an oil discharge waist-shaped groove 3 are respectively provided at positions on the front wall flow distribution ring of the valve plate body 1 on the left and right sides of the shaft hole 1.3. The widths of the two waist-shaped grooves are equal to the diameter of the plunger cavity on the cylinder block. Since the distribution of the plunger cavities corresponds to the flow distribution ring, when the cylinder block rotates, the plunger cavities continuously correspond to the oil suction waist-shaped groove 2 and the oil discharge waist-shaped groove 3, which can provide a suitable flow space for the hydraulic oil to facilitate the processes of oil suction and oil discharge.

[0034] In order to further increase the overall structural stiffness of the valve plate body 1, a plurality of reinforcing ribs 3.1 are provided in the inner cavity of the oil discharge waist-shaped groove 3.

[0035] On the front wall of the valve plate body 1, a top dead center 1.1 and a bottom dead center 1.2 are respectively provided at the top and bottom ends of the flow distribution ring. The top dead center 1.1 corresponds to the position of the plunger when the plunger cavity is filled with oil; the bottom dead center 1.2 corresponds to the situation where the plunger discharges oil through the oil discharge waist-shaped groove 3 until the plunger reaches another extreme position.

[0036] An oil suction damping groove 4 and a damping hole 5 are provided between the bottom end of the oil suction waist-shaped groove 2 and the bottom dead center 1.2. The oil suction damping groove 4 is communicated with the front part of the bottom end of the oil suction waist-shaped groove 2.

[0037] Between the top of the oil-draining waist-shaped groove 3 and the top dead center 1.1, there are damping holes II 7, damping holes III 8, and damping holes IV 9 in sequence from left to right. At the position of the front wall of the valve plate body 1 corresponding to the damping hole II 7, there is an oil-draining damping groove 6 communicating with the oil-draining waist-shaped groove 3; on the rear wall of the valve plate body 1, there is an arc-shaped connecting groove 11 connecting the rear ends of the damping holes II 7, damping holes III 8, and damping holes IV 9 with the oil-draining waist-shaped groove 3. At the position of the rear wall of the valve plate body 1 corresponding to the damping hole I 5, there is an oil-discharging groove 10 extending radially, and the oil-discharging groove 10 penetrates one side of the rear wall of the valve plate body 1. Among them, the oil-draining damping groove 6 is a pressure-boosting triangular groove, the oil-sucking damping groove 4 is a pressure-relieving U-shaped groove, and the size of the oil-draining damping groove 6 is larger than that of the oil-sucking damping groove 4, while ensuring that the pre-pressure-boosting angle is also larger than the pre-pressure-relieving angle; the damping holes I 5, damping holes II 7, damping holes III 8, and damping holes IV 9 are on the same circular arc, and the damping holes I 5, damping holes II 7, damping holes III 8, and damping holes IV 9 are all stepped holes with a smaller front-end hole diameter than the rear-end hole diameter; the included angle between the damping hole IV 9 and the top dead center 1.1 is 0 - 3°, the included angle between the damping hole III 8 and the top dead center 1.1 is 8 - 10°, the included angle between the damping hole II 7 and the top dead center 1.1 is 20 - 24°, and the damping hole III 8 and the damping hole I 5 are centrosymmetric about the center of the valve plate body 1. The damping hole III 8 is a flow reverse-injection adjustment hole, which is beneficial to better connecting the plunger cavity with the oil-draining damping groove 6, reducing flow reverse-injection and pressure pulsation, so as to achieve vibration reduction and noise reduction. When the plunger cavity approaches the oil-draining waist-shaped groove 3 from the oil-sucking waist-shaped groove 2, it is first connected to the damping hole IV 9, then connected to the damping hole III 8 and the damping hole IV 9 simultaneously, and then connected to the damping hole IV 9, the damping hole III 8, and the damping hole II 7 simultaneously.

[0038] On the front wall of the valve plate body 1, an outer auxiliary support belt 12 and an inner auxiliary support belt 14 are respectively provided near the outer edge and the inner edge. On the inner sides of the outer auxiliary support belt 12 and the inner auxiliary support belt 14, an outer sealing belt 13 and an inner sealing belt 15 are respectively provided. The structure provided can form an oil film between the cylinder block and the valve plate body 1, reduce the wear between the cylinder block and the valve plate body 1, and at the same time reduce the loss of oil leakage.

[0039] In summary, when the plunger cavity gradually detaches from the oil-sucking waist-shaped groove 2 and approaches the oil-draining waist-shaped groove 3, the plunger cavity on the cylinder block is first connected to the oil-draining waist-shaped groove 3 through the damping hole IV 9 and the arc-shaped connecting groove 11, and a small amount of high-pressure oil enters the plunger cavity through the arc-shaped connecting groove 11 and the damping hole IV 9, preventing the pressure in the plunger cavity from dropping below the atmospheric separation pressure, thereby reducing the air suction phenomenon.

[0040] When the plunger cavity is completely detached from the oil-sucking waist-shaped groove 2, the plunger cavity is connected to the damping hole IV 9 and the damping hole III 8 simultaneously, and a small amount of high-pressure hydraulic oil flows into the plunger cavity through the arc-shaped connecting groove 11, the damping hole IV 9, and the damping hole III 8, compensating for the pressure drop in the plunger cavity caused by the closed-dead expansion of the plunger cavity. At the same time, the additional high-pressure oil can play a role in pre-pressure-boosting.

[0041] When the plunger chamber starts to communicate with the oil discharge damping groove 6, the pressure in the plunger chamber begins the second pre-boost, reducing the occurrence of reverse flow of oil. At the same time, when the plunger chamber communicates with the damping hole II 7, it can make the plunger chamber communicate better with the oil discharge waist-shaped groove 3, reducing the reverse flow of oil and making the pressure in the plunger chamber rise smoothly to the pressure of the oil discharge waist-shaped groove 3, thus achieving vibration reduction and noise reduction. The pressure in the plunger chamber gradually realizes the transition from the low suction pressure to the high discharge pressure and enters the actual oil discharge stage.

[0042] When the plunger chamber gradually separates from the oil discharge waist-shaped groove 3 and approaches the oil suction waist-shaped groove 2, the plunger chamber communicates with the damping hole I 5, and a small amount of high-pressure hydraulic oil remaining in the plunger flows into the oil discharge groove 10 through the damping hole I 5, producing a pre-pressure reduction effect to compensate for the pressure overshoot generated in the plunger chamber.

[0043] When the plunger chamber starts to communicate with the oil suction damping groove 4, the high-pressure oil in the plunger chamber undergoes the second pre-pressure reduction through the damping hole I 5 and the oil suction damping groove 4. The pressure in the plunger chamber gradually realizes the transition from the high discharge pressure to the low suction pressure and enters the actual oil suction stage.

[0044] This spherical valve plate is not limited to axial piston pumps and is also applicable to other piston-type hydraulic machinery.

[0045] It should be noted that in this article, relational terms such as first and second are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the term "comprising", "including" or any other variation thereof is intended to cover non-exclusive inclusion, so that a process, method, article or device comprising a series of elements not only includes those elements, but also includes other elements not expressly listed, or elements inherent to such process, method, article or device.

[0046] Although the embodiments of the present invention have been shown and described, for those of ordinary skill in the art, it can be understood that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principle and spirit of the present invention. The scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A novel anti-cylinder overturning axial piston pump vibration reduction and noise reduction valve plate, comprising a valve plate body (1), a shaft hole (1.3) is provided in the middle of the valve plate body (1), an oil suction waist groove (2) and an oil discharge waist groove (3) are respectively provided on the valve plate ring on the front wall of the valve plate body (1) and on the left and right sides of the shaft hole (1.3), and the front wall of the valve plate body (1) is located at the top and bottom ends of the valve plate ring. The valve plate body (1) has an upper dead point (1.1) and a lower dead point (1.2), characterized in that: An oil suction damping groove (4) and a damping hole (5) are provided between the bottom end of the oil suction waist groove (2) and the bottom dead center (1.2), and the oil suction damping groove (4) is connected to the front part of the bottom end of the oil suction waist groove (2); A damping hole 2 (7), a damping hole 3 (8) and a damping hole 4 (9) are provided in sequence from left to right between the top of the oil discharge waist groove (3) and the top dead center (1.1); and an oil discharge damping groove (6) communicating with the oil discharge waist groove (3) is provided at a position corresponding to the damping hole 2 (7) on the front wall of the distribution plate body (1); The rear wall of the distribution plate body (1) is provided with an arc-shaped connecting groove (11) for connecting the rear ends of the damping hole 2 (7), the damping hole 3 (8) and the damping hole 4 (9) with the oil discharge waist groove (3), and the rear wall of the distribution plate body (1) is provided with an oil discharge groove (10) extending radially at a position corresponding to the damping hole 1 (5).

2. According to claim 1, a novel vibration-damping and noise-reducing valve plate for an axial piston pump that resists cylinder overturning is characterized by: The inner cavity of the oil-draining waist-shaped groove (3) is provided with a plurality of reinforcing ribs (3.1).

3. The novel vibration and noise reduction valve plate for axial piston pumps that resists cylinder overturning according to claim 1 is characterized by: The oil discharge damping groove (6) is a triangular groove, the oil suction damping groove (4) is a U-shaped groove, and the size of the oil discharge damping groove (6) is larger than the size of the oil suction damping groove (4).

4. According to claim 3, a novel vibration-damping and noise-reducing valve plate for an axial piston pump that resists cylinder overturning is characterized by: The damping hole 1 (5), the damping hole 2 (7), the damping hole 3 (8) and the damping hole 4 (9) are located on the same arc, and the damping hole 1 (5), the damping hole 2 (7), the damping hole 3 (8) and the damping hole 4 (9) are all stepped holes with a front end aperture smaller than a rear end aperture.

5. The novel vibration and noise reduction valve plate for axial piston pumps that resists cylinder overturning according to claim 1 is characterized by: The wrap angle between the damping hole four (9) and the upper dead point (1.1) is 0-3°, the wrap angle between the damping hole three (8) and the upper dead point (1.1) is 8-10°, the wrap angle between the damping hole two (7) and the upper dead point (1.1) is 20-24°, and the damping hole three (8) and the damping hole one (5) are symmetrical about the center of the distribution plate body (1).

6. The novel vibration and noise reduction valve plate for axial piston pumps that resists cylinder overturning according to claim 1 is characterized by: An outer auxiliary support belt (12) and an inner auxiliary support belt (14) are respectively provided at positions close to the outer edge and the inner edge of the front wall of the distribution plate body (1), and an outer sealing belt (13) and an inner sealing belt (15) are respectively provided on the inner sides of the outer auxiliary support belt (12) and the inner auxiliary support belt (14).

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