WO2023185010A1

WO2023185010A1 - Hydraulic retarder

Info

Publication number: WO2023185010A1
Application number: PCT/CN2022/132943
Authority: WO
Inventors: 李天维; 王天斌; 曾探; 陆锁; 李培智; 向福冲
Original assignee: 贵阳丽天苍泰科技有限公司
Priority date: 2022-03-31
Filing date: 2022-11-18
Publication date: 2023-10-05
Also published as: CN114704564A

Abstract

A hydraulic retarder, comprising a rotor member (20), an input shaft (30), and a stator member (10) having a first chamber (a) and a first channel (b). The first chamber (a) is provided around the first channel (b), and the first chamber (a) and the first channel (b) match the rotor member (20) so as to form a working chamber (A) between the stator member (10) and the rotor member (20). The input shaft (30) passes through the rotor member (20) and the stator member (10), and a second chamber (e) and a second channel (d) are formed between the input shaft (30) and the stator member (10), wherein the second chamber (e) is used for accommodating an oil seal (40), and the end of the first channel (b) away from the rotor member (20) is communicated with the first chamber (a), and the end thereof close to the rotor member (20) is communicated with the second chamber (e) by means of the second channel (d). When the hydraulic retarder works, a working medium in the working chamber can be ejected, due to the effect of a centripetal force, to the rotor member at a high speed from one side of the stator member under the guidance of the first channel, thereby reducing pressure borne by the oil seal and ensuring the sealing performance of the oil seal.

Description

A hydraulic retarder

Technical field

The invention relates to the field of automobile technology, and in particular to a hydraulic retarder.

Background technique

As an auxiliary braking device for rolling stock, hydraulic retarder is widely used in heavy-duty vehicles such as urban buses, heavy trucks, military vehicles, and large buses. It can provide assistance to vehicles during high-speed driving or downhill periods. braking torque to reduce the number of times the brake pads are used, thereby greatly improving the overall safety of the vehicle.

A hydraulic retarder usually includes a working chamber, a pair of rotors and stators that cooperate with each other to form the working chamber, a power input shaft linked to the rotor, bearings arranged between the power input shaft, the stator and other non-moving parts; at the same time , in order to prevent the leakage of the working medium, an oil seal will also be installed at the connection between the power input shaft and the working chamber. When the hydraulic retarder is working, due to factors such as the limited pressure-bearing capacity of the oil seal and the high pressure of the working chamber, the oil seal is easily damaged due to excessive pressure, and further causes problems such as leakage of the working medium due to reduced sealing performance.

technical problem

The main technical problem solved by the present invention is to provide a hydraulic retarder, which reduces the pressure of the oil seal by diverting the working medium in the working chamber to improve the reliability of the retarder.

Technical solutions

In one embodiment, a hydraulic retarder is provided, including:

rotor parts;

The stator part faces each other with the rotor part, the side of the stator part facing the rotor part has a first cavity and a first cavity, the first cavity is arranged around the first cavity, the first One end of the cavity away from the rotor component is connected to the first chamber; the first chamber and the first cavity cooperate with the rotor component to form a working chamber for accommodating the working medium between the rotor component and the stator component; as well as

The input shaft is arranged through the rotor member and the stator member. The rotor member is fixed to the input shaft. A second cavity and a second cavity are formed between the stator member and the input shaft; the second cavity The chamber is located on the side of the stator component facing away from the rotor component to accommodate the oil seal; one end of the second cavity is connected to the second cavity, and the other end of the second cavity is adjacent to the first cavity and is adjacent to the rotor component. connected at one end.

In one embodiment, an ejection part is further included, and the ejection part is arranged between the rotor part and the stator part in a manner that the input shaft is nested; wherein:

The ejection member and the stator member maintain a first preset distance in the radial direction of the input shaft to form an ejection channel between them that is connected to one end of the first cavity adjacent to the rotor member, and the ejection channel Used to eject the working medium in the first cavity toward the rotor member;

The ejection member and the stator member maintain a second preset distance in the axial direction of the input shaft to form a decompression channel connecting the first cavity and the second cavity therebetween.

In one embodiment, the first cavity channel has a main body section and a nozzle section, and the main body section communicates with the injection channel and the decompression channel through the nozzle section; wherein, the main body section and the injection channel are in the radial direction of the input shaft. The minimum dimensions are greater than or equal to the maximum dimension of the nozzle segment in the radial direction of the input shaft.

In one embodiment, the size of the injection channel in the radial direction of the input shaft gradually increases from one end adjacent to the nozzle section to one end adjacent to the rotor member; and/or

The size of the nozzle section in the radial direction of the input shaft gradually decreases from an end adjacent to the main body section to an end adjacent to the injection channel.

In one embodiment, at least one first annular groove structure is provided in the second cavity, and the first annular groove structure is arranged around the input shaft.

In one embodiment, the input shaft includes:

The shaft body part is arranged through the rotor part and the stator part, and the rotor part is fixed to the shaft body part; and

A bearing sleeve is sleeved and fixed on the shaft body part. The bearing sleeve is arranged at a corresponding matching position between the shaft body part and the stator part to form a second cavity and a second cavity between the bearing sleeve and the stator part. Chamber, the first annular groove structure is provided in the bearing sleeve.

In one embodiment, the stator component includes:

The stator faces the rotor part, the stator has an engagement sleeve hole and a drainage hole, the engagement sleeve hole is arranged through the stator in the axial direction of the input shaft, and the first chamber is arranged in the stator around the engagement sleeve hole. Facing the side of the rotor component, the drainage hole extends from an end of the joint sleeve hole away from the rotor component to the first chamber; and

The joint member is fixed to the side of the stator member facing away from the rotor member, and one end of the joint member facing the rotor member is inserted into the joint sleeve hole to form a first cavity between the joint member and the stator member; The input shaft is disposed through the joint to form a second channel and a second chamber between the input shaft and the joint.

In one embodiment, the stator includes a stator impeller and a plurality of stator blades, and the joint sleeve holes are arranged through the stator impeller along the axial direction of the input shaft; the plurality of stator blades are spacedly arranged around the joint sleeve holes facing the stator impeller. One side of the rotor component is formed with the stator impeller to form a first chamber, and the drainage hole is provided from an end of the joint sleeve hole away from the rotor component to the root of the stator blade.

In one embodiment, a second annular groove structure is provided in the joint sleeve hole. The second annular groove structure is provided around the input shaft at an end of the joint sleeve hole away from the rotor component. The drainage hole is formed from the second annular groove structure. Penetrates to the root of the stator blades.

In one embodiment, the joint includes:

A bearing seat is fixedly provided on the side of the stator facing away from the rotor; and

A sealing pressure ring is arranged through the joint sleeve hole. The edge of the end of the sealing pressure ring away from the rotor is fixed between the bearing seat and the stator to form a first cavity between the sealing pressure ring and the stator. ;

The input shaft is arranged through the sealing pressure ring and the bearing seat to form a second cavity between the input shaft and the sealing pressure ring, and a second cavity is formed between the input shaft, the sealing pressure ring and the bearing seat. room.

beneficial effects

The hydraulic retarder according to the above embodiment includes a rotor component, an input shaft and a stator component having a first chamber and a first cavity channel; the first chamber is arranged around the first cavity channel, and both cooperate with the rotor component , to form a working cavity between the stator part and the rotor part; the input shaft is arranged through the rotor part and the stator part, and a second chamber and a second cavity are formed between the input shaft and the stator part; wherein, the second cavity The chamber is used to accommodate the oil seal. One end of the first cavity away from the rotor component is connected to the first chamber, and one end adjacent to the rotor component is connected to the second chamber through the second cavity. When the retarder is working, due to the centripetal force, the working medium in the working chamber can be directed from the side of the stator to the rotor at high speed under the guidance of the first cavity. According to Bernoulli's principle, because the first cavity and the third cavity A local high-pressure area is formed near the junction of the two chambers, causing the second chamber and the second chamber to naturally form a low-pressure chamber, thereby reducing the pressure on the oil seal and ensuring the sealing performance of the oil seal.

Description of drawings

Figure 1 is an axial partial sectional schematic diagram of a hydraulic retarder according to an embodiment.

Figure 2 is a partially enlarged schematic diagram of the V area in Figure 1.

Figure 3 is an identification diagram of the components of the hydraulic retarder in Figure 1.

Figure 4 is a schematic diagram of the overall structure of a stator in a hydraulic retarder according to an embodiment.

Figure 5 is a schematic partial circumferential cross-sectional view of a stator in a hydraulic retarder according to an embodiment.

In the picture:

10. Stator part; 11. Stator; 11a, joint sleeve hole; 11b, stator impeller; 11c, stator blade; 11d, second ring groove structure; 12. joint part; 12a, bearing seat; 12b, sealing pressure ring; 13 , sealing ring;

20. Rotor part; 30. Input shaft; 31. Shaft body part; 32. Bearing sleeve; 40. Oil seal; 50. Ejector part;

A. Working chamber; a, first chamber; b, first cavity; b1, main body section; b2, nozzle section; c, drainage hole; d, second cavity; d1, first ring groove structure; e , the second chamber; f, ejection channel; g, decompression channel.

Embodiments of the invention

Similar elements in different embodiments use associated similar element numbers. In the following embodiments, many details are described in order to make the present application better understood. However, those skilled in the art can readily recognize that some of the features may be omitted in different situations, or may be replaced by other elements, materials, and methods. In some cases, some operations related to the present application are not shown or described in the specification. This is to avoid the core part of the present application being overwhelmed by excessive descriptions. For those skilled in the art, it is difficult to describe these in detail. The relevant operations are not necessary, and they can fully understand the relevant operations based on the descriptions in the instructions and general technical knowledge in the field.

Additionally, the features, operations, or characteristics described in the specification may be combined in any suitable manner to form various embodiments. At the same time, each step or action in the method description can also be sequentially exchanged or adjusted in a manner that is obvious to those skilled in the art. Therefore, the various sequences in the description and drawings are only for clearly describing a certain embodiment, and do not imply a necessary sequence, unless otherwise stated that a certain sequence must be followed.

The serial numbers assigned to components in this article, such as "first", "second", etc., are only used to distinguish the described objects and do not have any sequential or technical meaning. The terms "connection" and "connection" mentioned in this application include direct and indirect connections (connections) unless otherwise specified.

This application provides a hydraulic retarder, which uses a first cavity provided in the working chamber of the retarder, and a second cavity that connects the part for installing the oil seal in the retarder with the first cavity. , an injection decompression channel can be formed in the retarder for draining the working medium and decompressing oil seals and other components. When the retarder is working, due to the centripetal force, the working medium in the working chamber can be directed from the stator side to the rotor at high speed under the drainage of the first chamber, so that the working medium can be connected at the junction of the first chamber and the second chamber. A local high-pressure area is formed nearby. According to Bernoulli's principle, the kinetic energy of the working medium in the local high-pressure area increases and the static pressure decreases. This will cause the second cavity and the oil seal installation part to naturally form a low-pressure area due to the pressure reduction. chamber; in this way, the pressure of the oil seal can be effectively reduced by utilizing the high and low pressure difference effect.

Referring to FIGS. 1 to 5 , an embodiment provides a hydraulic retarder, including a stator member 10 , a rotor member 20 , an input shaft 30 , an oil seal 40 and other components as needed, such as for accommodating The retarder box encapsulates the stator part 10, the rotor part 20 and other components, and the bearings used to establish a relatively rotatable connection relationship between the input shaft 30, the retarder box and the stator part 10, etc.

Referring to FIGS. 1 and 3 , the input shaft 30 is arranged sequentially through the rotor member 20 and the stator member 10 . The stator member 10 and the rotor member 20 face each other along the axial direction of the input shaft 30 and are arranged to cooperate with each other. 10 and the rotor part 20 are enclosed to form a working chamber A for accommodating the working medium (such as lubricating oil, antifreeze liquid and other liquid media that play a damping role); among them, the rotor part 20 and the input shaft 30 are fixed, and the stator part 10 is rotatably connected to the input shaft 30 through bearings and other components, so that the rotor member 20 can rotate relative to the stator member 10 driven by the input shaft 30, thereby driving the working medium to move along the blade direction of the rotor member 20 to move the working medium It is thrown towards the stator part 10; and the stator part 10 will produce a reaction force on the working medium, causing the working medium to flow out of the stator part 10 and then in turn impact the rotor part 20; in this way, a resistance moment to the rotor part 20 can be formed, hindering the rotor. The member 20 rotates, and finally realizes the deceleration and braking effect on the input shaft 30 and the action device connected thereto (such as a gearbox).

In one embodiment, please refer to FIGS. 1 to 5 , the stator component 10 includes a stator 11 and a joint component 12 ; wherein, the stator 11 and the rotor component 20 face each other and are arranged in cooperation with each other, and are arranged penetratingly along the axis line of the stator 11 It is used for the input shaft 30 and other components to penetrate the joint sleeve hole 11a of the stator 11, and the structural space on the side of the stator 11 facing the rotor member 20 can be used to form a semi-open structure distributed around the outer circumference of the joint sleeve hole 11a. The cavity space is, for convenience of description, defined as the first chamber a. The joint member 12 is arranged on the side of the stator 11 facing away from the rotor member 20 and is fixed to the stator 11 . By arranging bearings and other components between the joint member 12 and the input shaft 30 , a relative position can be established between the stator 11 and the input shaft 30 . Rotating connections.

The central area of the side of the joint member 12 facing the rotor member 20 or the stator 11 extends to a certain length toward the side where the rotor member 20 is located, and maintains a certain structural gap with the inner circumferential surface of the joint sleeve hole 11a in the radial direction of the input shaft 30 is inserted into the joint sleeve hole 11a, thereby forming a semi-open cavity structure between the joint member 12 and the stator 11. For the convenience of description, this cavity structure is defined as the first cavity b; since the second cavity A cavity a is distributed around the joint sleeve hole 11a. In other words, it is equivalent to the first cavity a being distributed around the outer peripheral side of the first cavity b. Based on the limitation of the structural relationship, the first cavity a is distributed around the outer circumferential side of the first cavity b. The end of the cavity b adjacent to the rotor member 20 is in communication with the first chamber a; at the same time, a first end of the stator 11 located at the end of the first cavity b away from the rotor member 20 (or an end adjacent to the joint member 12 ) is provided. The drainage hole c that communicates with the first chamber a is the cavity b. After the rotor part 20 and the stator part 10 are combined, the first chamber a, the first cavity b, the drainage hole c and the structural space on the side of the rotor part 20 facing the stator part 10 can be used to collectively form a working chamber A. .

In other embodiments, the stator component 10 can also be configured as an integral structure, such as omitting the joint component 12 and directly constructing a structure similar to or identical to that of the joint component 12 on the stator 11 .

Referring to FIGS. 1 to 3 , the input shaft 30 is arranged through the joint member 12 in a radial direction with a certain structural gap between the input shaft 30 and the joint member 12 , so as to form an axially sequential distribution and mutual relationship between the two. The second cavity d and the second chamber e are connected; wherein, the second cavity d is adjacent to one end of the rotor member 20, and can be formed by means of the structural gap formed between the rotor member 20 (or the input shaft 30) and the joint member 12 It is connected with the first cavity b; and the second cavity e can be used to provide a structural assembly space for the oil seal 40, so as to use the oil seal 40 to seal and isolate the working chamber A from other structural spaces inside the retarder.

When the retarder is operating, the working medium in the first chamber a will be injected into the first cavity b at high speed through the drainage hole c due to the centripetal force, and will eventually be injected along the first cavity b to the rotor member 20, thereby A local high-pressure area can be formed near the junction and communication position of the first cavity b and the second cavity d. Due to the connection between the second cavity d and the second cavity e and the junction position, the second cavity d and the second cavity e are connected to the junction position. The second chamber e naturally forms a low-pressure zone chamber, thereby reducing the pressure on the oil seal 40 installed in the second chamber e, which not only ensures the sealing performance of the oil seal 40, but also prevents the oil seal 40 from being damaged due to Being damaged due to excessive pressure will help extend the life of the oil seal 40 and improve the reliability of the retarder. It should be noted that the dotted lines with arrows in Figures 1, 2 and 3 represent the paths (or directions) along which the working medium is ejected or diverted.

In the specific application of the retarder, transmission oil can be considered as the lubricating medium for its internal bearings, oil seals and other components, so that the working medium of the retarder does not need to bear the role of lubrication. This will help extend the replacement cycle of the working medium and improve the efficiency of the retarder. The reliability of the retarder; however, during specific implementation, due to the high pressure of the working chamber A of the retarder, the oil seal 40 often cannot perform a good sealing effect; therefore, with the help of the solution provided by the embodiment of the present application, through Draining the working medium in the working chamber A and using the high and low pressure differences to reduce the pressure on the oil seal 40 can make it highly feasible or feasible to lubricate the retarder with transmission oil.

Referring to Figures 1 and 3, an embodiment provides a hydraulic retarder, which also includes an ejection member 50. The overall outline of the ejection member 50 is generally annular or sleeve-shaped, and is sleeved The input shaft 30 is arranged between the stator member 10 and the rotor member 20 and is fixed to the rotor member 20 or the input shaft 30; surface) maintains a first preset distance in the radial direction of the input shaft 30, so as to form an ejection channel f between the ejection member 50 and the stator member 10, and the ejection channel f is used to connect the first cavity b and the working cavity While the main part of A (specifically, the space part formed by the cooperation between the first chamber a and the rotor member 20) is connected, the working medium sprayed from the first cavity b can also be guided, so that this part of the working medium can The injection member 20 is injected from the central area of the rotor member 20 into the rotor member 20; at the same time, the injection member 50 and the stator member 10 (specifically, the axial end surface of the extended portion of the joint member 12) maintain a second predetermined position in the axial direction of the input shaft 30. The distance is set so as to form a decompression channel g between the ejection member 50 and the stator member 10, so that the second cavity channel d can communicate with the first cavity channel b and the ejection channel f by means of the decompression channel g, so that the working medium automatically When the first cavity b is ejected and injected into the injection channel f to form a local high-pressure area, the decompression channel g, the second cavity d and the second chamber e are enclosed to form a low-pressure area chamber.

It should be noted that the “first preset distance” and the “second preset distance” may be constant distance values, such as the distance between the outer peripheral surface of the ejection member 50 and the inner peripheral surface of the joint sleeve hole 11a, along the The axial direction of the input shaft 30 remains constant or is arranged at equal intervals. The "first preset distance" and the "second preset distance" can also be numerical ranges, such as the outer peripheral surface of the ejection member 50 and the inner surface of the joint sleeve hole 11a. The spacing between the peripheral surfaces changes continuously or is unequal along the axial direction of the input shaft 30 .

In one embodiment, please refer to Figure 2 in conjunction with Figures 1 and 3. The first cavity b has a main body section b1 and a nozzle section b2 that are sequentially distributed (or divided and formed) along the exit direction of the working medium; wherein, the main body section b1 One end is connected to the first chamber a through the drainage hole c, and the other end is connected to the injection channel f and the decompression channel g through the nozzle segment b2; the maximum size of the nozzle segment b2 in the radial direction of the input shaft 30 is set to be less than or is equal to the minimum size of the main body section b1 in the radial direction of the input shaft 30, and the minimum size of the injection channel f in the radial direction of the input shaft 30 is set to be greater than or equal to the maximum size of the nozzle section b2 on the input shaft 30; thereby utilizing The size difference between the nozzle section b2, the main body section b1 and the injection channel f can be configured to form a nozzle structure at one end of the first cavity b adjacent to the rotor member 20. The working pressure, centripetal force and nozzle section b2 in the working chamber A Under the combined effect of multiple factors, when the working medium passes through the nozzle section b2, it turns into a high-speed liquid medium and is sprayed into the injection channel f. This can form a local high-pressure zone and a low-pressure zone chamber with a more significant pressure difference. Enhance the pressure reducing effect of oil seal 40.

It should be noted that the "size" mentioned above can be understood as the width of the relevant channel or cavity in the radial direction of the input shaft 30 , and based on the change in size, the "first preset spacing" mentioned above can be understood is the numerical range. Among them, in terms of the size difference between the ejection channel f and the nozzle section b2, during specific implementation, the outer diameter of the ejection member 50 can be set to be smaller than the extended portion of the joint member 12 (specifically, the nozzle section b2 is formed). The outer diameter of the corresponding part), so that the minimum size of the injection channel f is larger than the maximum size of the nozzle section b2.

In one embodiment, please refer to FIG. 2 in conjunction with FIGS. 1 and 3 . The size of the injection channel f in the radial direction of the input shaft 30 gradually increases from one end adjacent to the nozzle section b2 to an end adjacent to the rotor member 20 . On the one hand, It is beneficial to smoothly inject the working medium to the rotor member 20. On the other hand, it is equivalent to forming a flare or bell mouth structure on the outlet side of the nozzle section b2, so that the pressure of the high-speed ejected working medium is reduced and the dynamic pressure is increased. The static pressure becomes lower, thereby creating conditions for the formation of a low-pressure zone chamber; during specific implementation, the outer peripheral surface of the ejection member 50 (that is, the surface facing the side of the rotor member 20 along the radial direction of the input shaft 30) can be set to It has a conical surface structure, with the top end of the cone of the ejection member 50 facing the rotor member 20 and the bottom end of the cone facing the joint member 12; in other words, viewed from the radial direction of the input shaft 30, the outer peripheral surface of the ejection member 50 is smooth. Bevel structure or arc structure.

In some embodiments, in order to enhance the speed of the working medium ejected from the nozzle section b2 to facilitate the formation of a local high-pressure area, the size of the nozzle section b2 in the radial direction of the input shaft 30 is directed from one end adjacent to the main body section b1 to the adjacent One end of the channel f gradually decreases, which is equivalent to configuring the port portion of the first cavity b to form a shrinking structure.

In one embodiment, please refer to Figures 4 and 5. The stator 11 can be structurally configured with reference to the stator of an existing retarder. Specifically, the stator 11 includes a stator impeller 11b and a plurality of stator blades 11c; wherein, the stator impeller 11b and the rotor member 20 are arranged facing each other. The stator impeller 11b can be connected to the input shaft 30 by means of the joint 12 and bearings. The joint sleeve 11a is provided through the stator impeller 11b along the axial direction of the input shaft 30, and the plurality of stator blades 11c Then, the stator blades 11c can be fixedly arranged or formed on the stator impeller 11b in a manner that is obliquely distributed along the circumferential direction relative to the stator impeller 11b. , so the intersection between the stator blade 11c and the stator impeller 11b can be understood as the root of the stator blade 11c.

In this embodiment, the drainage hole c is provided from the root of the stator blade 11c through the stator impeller 11b to the joint sleeve hole 11a (or the first cavity b). In specific implementation, the drainage hole c can be formed from the root of each or part of the stator blade 11c. One or more drainage holes c are provided to form a plurality of drainage holes c distributed around the first cavity b at one end of the first cavity b away from the rotor member 20; at the same time, the first chamber a is equivalent to the stator blade 11c The space, or the first chamber a, is formed by the stator impeller 11b and the stator blades 11c. Since the drainage hole c is located at the root of the stator blade 11c, it can effectively guide the working medium into the first cavity b in combination with the movement form caused by the centripetal force of the working medium, so that the working medium can be injected to the rotor at high speed through the first cavity b. 20, and a local high-pressure area is formed near the junction and communication between the first cavity b and the second cavity d.

In one embodiment, please refer to Figures 4 and 5. A second annular groove structure 11d is provided on the peripheral wall of the coupling sleeve hole 11a. The second annular groove 11d is distributed around the input shaft 30 in the coupling sleeve hole 11a or the first cavity. The channel b is away from one end of the rotor member 20, and the port of the drainage hole c located on the side of the joint sleeve hole 11a is provided in the second ring groove structure 11d, so that the cooperation between the second ring groove structure 11d and the joint member 12 can be used to expand the The volume of the end of the first cavity b away from the rotor member 20 in the radial direction of the input shaft 30 enables the working medium in the first chamber a to be smoothly drained into the first cavity b through the drainage hole c, and from there. ejected from the first cavity b.

In one embodiment, please refer to Figures 1 and 3, the joint member 12 includes a bearing seat 12a and a sealing pressure ring 12b; wherein, the bearing seat 12a is fixedly disposed on a side of the stator 11 (specifically, the stator impeller 11b) facing away from the rotor member 20. side; the sealing pressure ring 12b is inserted into the joint sleeve hole 11a. The edge of the end of the sealing pressure ring 12b away from the rotor member 20 extends along the radial direction of the input shaft 30 and is fixed between the bearing seat 12a and the stator 11; On the one hand, by maintaining a certain distance between the sealing pressure ring 12b and the joint sleeve hole 11a (such as the first preset distance mentioned above), a first cavity b is constructed between the two; on the other hand, using The sealing pressure ring 12b seals the structural gap between the bearing seat 12a and the stator 11 (specifically, the stator impeller 11b) to ensure that the working medium will not affect the injection of the working medium due to leakage from between the bearing seat 12a and the stator 11 Effect: During specific implementation, the sealing ring 13 can be provided between the adjacent sealing pressure ring 12b, the stator 11 and the bearing seat 12a.

Correspondingly, the input shaft 30 includes a shaft body part 31 and a bearing sleeve 32; wherein, the shaft body part 31 is arranged through the rotor member 20, the ejection member 50, the sealing pressure ring 12b and the bearing seat 12a; the bearing sleeve 32 is nested and It is fixed on the shaft body 31 and is located at a position that matches the sealing pressure ring 12b and the bearing seat 12a; by keeping the bearing sleeve 32, the sealing pressure ring 12b and the bearing seat 12a at a certain distance in the radial direction of the input shaft 30 ( As mentioned above (the second preset distance), a second cavity d can be formed between the sealing pressure ring 12b and the bearing sleeve 32, and a second cavity d can be formed between the sealing pressure ring 12b, the bearing seat 12a and the bearing sleeve 32. second chamber e; on the other hand, the cooperation between the bearing seat 12a and the bearing sleeve 32 can also provide a structural assembly space for the bearing disposed between the stator member 10 and the input shaft 30.

In other embodiments, the input shaft 30 may also adopt an integrated structure, such as omitting the sleeve part 32, or the sleeve part 32 and the shaft body part 31 may be integrally formed; of course, the joint 12 may also adopt an integrated structure; This is helpful to reduce the number of parts arranged in the retarder to meet different application requirements.

In one embodiment, please refer to FIG. 2 , a first annular groove structure d1 arranged around the input shaft 30 is provided in the second cavity d. The first annular groove structure d1 may be one channel or multiple channels; such as When multiple first annular groove structures d1 are provided in the second cavity d, the multiple first annular groove structures d1 can be arranged at intervals along the axial direction of the input shaft 30 , or can be interconnected with each other at the same time; thus, with the help of the first The annular groove structure d1 can be constructed to form a labyrinth groove structure in the second chamber d, which is beneficial to reducing the pressure in the second chamber e or reducing the pressure experienced by the oil seal 40 . During specific implementation, the first annular groove structure d1 may be provided on the outer peripheral surface of the bearing sleeve 32 .

The above specific examples are used to illustrate the present invention, which are only used to help understand the present invention and are not intended to limit the present invention. For those skilled in the technical field to which the present invention belongs, several simple deductions, modifications or substitutions can be made based on the ideas of the present invention.

Claims

A hydraulic retarder is characterized by including:

rotor parts;

The stator part faces each other with the rotor part, the side of the stator part facing the rotor part has a first cavity and a first cavity, the first cavity is arranged around the first cavity, the first One end of the cavity away from the rotor component is connected to the first chamber; the first chamber and the first cavity cooperate with the rotor component to form a working chamber for accommodating the working medium between the rotor component and the stator component; as well as

The input shaft is arranged through the rotor member and the stator member. The rotor member is fixed to the input shaft. A second cavity and a second cavity are formed between the stator member and the input shaft; the second cavity The chamber is located on the side of the stator component facing away from the rotor component to accommodate the oil seal; one end of the second cavity is connected to the second cavity, and the other end of the second cavity is adjacent to the first cavity and is adjacent to the rotor component. connected at one end.
such as rights Require 1 The hydraulic retarder is characterized in that it also includes an ejection part, and the ejection part is arranged between the rotor part and the stator part in a manner that the input shaft is nested; wherein:

The ejection member and the stator member maintain a first preset distance in the radial direction of the input shaft to form an ejection channel between them that is connected to one end of the first cavity adjacent to the rotor member, and the ejection channel Used to eject the working medium in the first cavity toward the rotor member;

The ejection member and the stator member maintain a second preset distance in the axial direction of the input shaft to form a decompression channel connecting the first cavity and the second cavity therebetween.
such as rights Require 2 The hydraulic retarder is characterized in that the first cavity channel has a main body section and a nozzle section, and the main body section communicates with the injection channel and the decompression channel through the nozzle section; wherein, the main body section and the injection channel are The minimum size of the injection channel in the radial direction of the input shaft is greater than or equal to the maximum size of the nozzle segment in the radial direction of the input shaft.
such as rights Require 3 The hydraulic retarder is characterized in that the size of the injection channel in the radial direction of the input shaft gradually increases from one end adjacent to the nozzle section to one end adjacent to the rotor member; and / or

The size of the nozzle section in the radial direction of the input shaft gradually decreases from an end adjacent to the main body section to an end adjacent to the injection channel.
such as rights Require 1 The hydraulic retarder is characterized in that at least one first annular groove structure is provided in the second cavity, and the first annular groove structure is arranged around the input shaft.
such as rights Require 5 The hydraulic retarder is characterized in that the input shaft includes:

The shaft body part is arranged through the rotor part and the stator part, and the rotor part is fixed to the shaft body part; and

A bearing sleeve is sleeved and fixed on the shaft body part. The bearing sleeve is arranged at a corresponding matching position between the shaft body part and the stator part to form a second cavity and a second cavity between the bearing sleeve and the stator part. Chamber, the first annular groove structure is provided in the bearing sleeve.
such as rights Require 1-6 The hydraulic retarder according to any one of the above, wherein the stator component includes:

The stator faces the rotor part, the stator has an engagement sleeve hole and a drainage hole, the engagement sleeve hole is arranged through the stator in the axial direction of the input shaft, and the first chamber is arranged in the stator around the engagement sleeve hole. Facing the side of the rotor component, the drainage hole extends from an end of the joint sleeve hole away from the rotor component to the first chamber; and

The joint member is fixed to the side of the stator member facing away from the rotor member, and one end of the joint member facing the rotor member is inserted into the joint sleeve hole to form a first cavity between the joint member and the stator member; The input shaft is disposed through the joint to form a second channel and a second chamber between the input shaft and the joint.
such as rights Require 7 The hydraulic retarder is characterized in that the stator includes a stator impeller and a plurality of stator blades, the joint sleeve hole is arranged through the stator impeller along the axial direction of the input shaft; the plurality of stator blades surround the joint sleeve The holes are spacedly arranged on the side of the stator impeller facing the rotor component to form a first chamber enclosed with the stator impeller. The drainage holes are provided from an end of the joint sleeve hole away from the rotor component and penetrate to the root of the stator blade.
such as rights Require 8 The hydraulic retarder is characterized in that a second annular groove structure is provided in the joint sleeve hole, and the second annular groove structure is arranged around the input shaft at an end of the joint sleeve hole away from the rotor member, and the flow diversion The hole penetrates from the second annular groove structure to the root of the stator blade.
such as rights Require 7 The hydraulic retarder is characterized in that the joint includes:

A bearing seat is fixedly provided on the side of the stator facing away from the rotor; and

A sealing pressure ring is arranged through the joint sleeve hole. The edge of the end of the sealing pressure ring away from the rotor is fixed between the bearing seat and the stator to form a first cavity between the sealing pressure ring and the stator. ;

The input shaft is arranged through the sealing pressure ring and the bearing seat to form a second cavity between the input shaft and the sealing pressure ring, and a second cavity is formed between the input shaft, the sealing pressure ring and the bearing seat. room.