CN111336221A - Transmission with hydraulic oil way structure - Google Patents

Transmission with hydraulic oil way structure Download PDF

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Publication number
CN111336221A
CN111336221A CN201910616390.8A CN201910616390A CN111336221A CN 111336221 A CN111336221 A CN 111336221A CN 201910616390 A CN201910616390 A CN 201910616390A CN 111336221 A CN111336221 A CN 111336221A
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CN
China
Prior art keywords
oil
clutch
shaft
double
input
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201910616390.8A
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Chinese (zh)
Inventor
罗天生
薛天宝
罗南昌
雷作钊
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujian Zhongwei Power Technology Co Ltd
Original Assignee
Fujian Zhongwei Power Technology Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fujian Zhongwei Power Technology Co Ltd filed Critical Fujian Zhongwei Power Technology Co Ltd
Priority to CN201910616390.8A priority Critical patent/CN111336221A/en
Publication of CN111336221A publication Critical patent/CN111336221A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/091—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft
    • F16H3/0915—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft with coaxial input and output shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H3/097—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts the input and output shafts being aligned on the same axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0811—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts using unsynchronised clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

Abstract

The invention discloses a transmission with a hydraulic oil circuit structure, which comprises an input shaft, an output shaft, an intermediate shaft, a switching type double clutch, a shell and an oil circuit structure, wherein the oil circuit structure comprises a shell oil circuit, a shaft oil circuit and a clutch oil circuit. The transmission controls shifting of gears by a shift-type double clutch so that power can be output via an input shaft, an intermediate shaft, and an output shaft, or through the input shaft and the output shaft. And the switching type double clutch conveys hydraulic oil through the shell oil path, the shaft oil path and the clutch oil path, and then carries out clutch operation on the switching type double clutch. The oil way structure runs in a state of being filled with hydraulic oil when in use, so that the oil pressure balance in the piston cavity of the switching type double clutch can be broken only by adjusting a small amount of hydraulic oil, then the switching type double clutch is driven to carry out mutual exclusion clutch operation, and the effect of waiting for the clutch to be switched when zero time is long is achieved.

Description

Transmission with hydraulic oil way structure
Technical Field
The invention relates to the field of transmissions, in particular to a transmission with a hydraulic oil way structure.
Background
The clutch is positioned in a flywheel shell between the engine and the gearbox, the clutch assembly is fixed on the rear plane of the flywheel by screws, and the output shaft of the clutch is the input shaft of the gearbox. The engine and the gearbox are temporarily separated and gradually engaged by controlling the clutch so as to cut off or transmit the power input by the engine to the transmission. However, the existing clutches have a relatively long reaction time when the clutch is disengaged, and the consumption of kinetic energy is increased.
Disclosure of Invention
Therefore, it is necessary to provide an oil path structure of a clutch of a transmission, which is used for solving the problem that the conventional clutch needs a long time for on/off operation.
In order to achieve the above object, the inventor provides a transmission with a hydraulic oil path structure, which comprises an input shaft, an output shaft, an intermediate shaft, a switching type double clutch, a shell and an oil path structure; the central line of the input shaft and the central line of the output shaft are arranged in a collinear way, the input end of the input shaft and the output end of the output shaft respectively penetrate through two opposite side walls of the shell and are arranged on the shell, the input shaft is in transmission connection with the input end of the intermediate shaft, the output end of the intermediate shaft is in transmission connection with the output shaft, and the central line of the intermediate shaft is arranged in the shell in parallel with the central line of the input shaft; the switching type double clutch is arranged on the input shaft or the output shaft, the switching type double clutch is positioned between two adjacent gear pairs on the input shaft and/or the output shaft, and the switching type double clutch is used for controlling the gear pairs on two sides of the switching type double clutch to perform mutual exclusion clutch operation; the oil circuit structure comprises a shell oil circuit, a shaft oil circuit and a clutch oil circuit, wherein the shell oil circuit is arranged in the shell, the shaft oil circuit is arranged in the input shaft or the output shaft, one branch of the shell oil circuit is communicated with a first oil conveying circuit of the shaft oil circuit, and the other branch of the shell oil circuit is communicated with a second oil conveying circuit of the shaft oil circuit; the clutch oil circuit is arranged in the cavity of the switching type double clutch, and a first delivery oil circuit of the shaft oil circuit is communicated with a first oil guide channel of the clutch oil circuit; and a second oil delivery way of the shaft oil way is communicated with a second oil guide way of the clutch oil way.
Furthermore, the casing oil path is a double-hole conveying oil path, an oil inlet of the double-hole conveying oil path is arranged on the outer side face of the casing, and an oil outlet of the double-hole conveying oil path is arranged on the inner face of the shaft hole of the casing input shaft.
Further, the clutch oil path comprises a first oil guide passage and a second oil guide passage; the first oil guide channel is arranged between one side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch, and the second oil guide channel is arranged between the other side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch.
Further, the switching double clutch comprises a first clutch piece, a second clutch piece and a piston unit; the piston unit comprises a double-end piston body and a cavity, the cross section of the double-end piston body is I-shaped, one end of the double-end piston body is arranged in the cavity, the other end of the double-end piston body is positioned outside the cavity, the oil outlet of the first oil guide channel is arranged on one side of the cavity, and the oil outlet of the second oil guide channel is arranged on the other side of the cavity; the first clutch block comprises a first friction plate group, the second clutch block comprises a second friction plate group, the first friction plate group is located on one side of the other end of the double-end piston body, the second friction plate group is located on the other side of the other end of the double-end piston body, the first clutch block and the second clutch block are respectively arranged on gear pairs on two sides, and the double-end piston body is used for driving one of the first friction plate group or the second friction plate group to be combined and the other to be separated.
Further, a sealing ring is arranged on the input shaft on the two sides of each oil inlet of the shaft oil path.
Further, the sealing ring is an opening sealing ring.
Further, the intermediate shaft is provided with a plurality of intermediate shafts, and the plurality of intermediate shafts are arranged in the shell in a circumferential array on the central axis of the input shaft.
Further, the input shaft is provided with a first input gear, the output shaft is provided with a first output gear, and the switching clutch is provided on the input shaft or the output shaft between the first input gear and the first output gear.
Further, the intermediate shaft is provided with a second input gear and a second output gear, the first input gear and the second input gear are arranged in a meshed mode, and the first output gear and the second output gear are arranged in a meshed mode.
Different from the prior art, the transmission of the technical scheme controls the gear shifting through the switching type double clutch, so that the power can be output through the input shaft, the intermediate shaft and the output shaft, or directly output through the input shaft and the output shaft. And the switching type double clutch conveys hydraulic oil through the shell oil path, the shaft oil path and the clutch oil path, and then carries out clutch operation on the switching type double clutch. The oil way structure runs in a state of being filled with hydraulic oil when in use, so that the oil pressure balance in the piston cavity of the switching type double clutch can be broken only by adjusting a small amount of hydraulic oil, then the switching type double clutch is driven to carry out mutual exclusion clutch operation, and the effect of waiting for the clutch to be switched when zero time is long is achieved.
Drawings
FIG. 1 is a cross-sectional view of a transmission having a hydraulic fluid circuit configuration according to an embodiment;
FIG. 2 is a block diagram of a transmission having a hydraulic circuit configuration according to an exemplary embodiment;
FIG. 3 is a partial schematic illustration of a transmission having a hydraulic circuit configuration according to an exemplary embodiment;
description of reference numerals:
10. an input shaft; 11. a first input gear;
20. an output shaft; 12. a first output gear;
30. an intermediate shaft; 31. a second input gear; 32. a second output gear;
40. a switching type double clutch;
41. a first clutch block; 411. a first friction plate set;
42. a second clutch block; 412. a second friction plate set;
43. a piston unit;
431. a double-ended piston body; 432. a cavity;
50. a housing;
60. an oil path structure; 61. a housing oil passage; 62. a shaft oil passage; 63. a clutch oil path;
631. a first oil guide passage; 632. a second oil guide passage;
621. a first delivery oil path; 622. a second delivery oil path; 623. a seal ring;
Detailed Description
To explain technical contents, structural features, and objects and effects of the technical solutions in detail, the following detailed description is given with reference to the accompanying drawings in conjunction with the embodiments.
Referring to fig. 1, 2 and 3, the present embodiment provides a transmission with a hydraulic oil circuit structure, which includes an input shaft 10, an output shaft 20, an intermediate shaft 30, a switching dual clutch 40, a housing 50 and an oil circuit structure 60. The axle head of input shaft can establish through the bearing housing in this embodiment with the terminal surface dead eye of output shaft, and then reaches the effect of the central line collineation of input shaft and output shaft, and the input of input shaft and the output of output shaft then run through the relative both sides wall of casing respectively and install on the casing, the input of input shaft and jackshaft is connected in the transmission, the output and the output shaft transmission of jackshaft are connected, the central line of jackshaft is on a parallel with the central line setting of input shaft in the casing.
The input shaft is provided with a first input gear 11, the output shaft is provided with a first output gear 21, and the intermediate shaft is provided with a second input gear 31 and a second output gear 32. The first input gear and the second input gear are meshed with each other to form a first gear pair, and the first output gear and the second output gear are meshed with each other to form a second gear pair.
The switching type double clutch is arranged on an input shaft or an output shaft between the first input gear and the first output gear, and mutually exclusive clutch operation is carried out on the first gear pair and the second gear pair. When the mutual exclusion is that the first gear pair is in a closed state, the second gear pair is in an open state; conversely, when the second gear pair is in the engaged state, the first gear pair is in the disengaged state. Therefore, two different routes of power transmission modes can be carried out on the first gear pair and the second gear pair through the switching type double clutch.
Specifically, taking the example that the switching type double clutch is arranged on the input shaft, the first route is as follows: the power of the input shaft can be directly transmitted to the output shaft through the second gear pair; the corresponding second route is: the input shaft transmits power to the intermediate shaft through the first gear pair and then transmits the power to the output shaft through the second gear pair, and the effect of changing two gears is achieved.
The switching type double clutch in the embodiment comprises a first clutch block 41, a second clutch block 42 and a piston unit 43, wherein the piston unit comprises a double-end piston body 431 and a cavity 432, the cross section of the double-end piston body is I-shaped, and the structure of the double-end piston body is formed by combining three ring bodies, so that the double-end piston body is arranged in the cavity and is controlled to move in the cavity by inputting hydraulic oil, and then the clutch operation that one end of the switching type double clutch is in a closed state and the other end of the switching type double clutch is in a separated state is.
In this embodiment, the oil path structure includes a housing oil path 61, a shaft oil path 62, and a clutch oil path 63, the housing oil path is a dual-hole oil path, the dual-hole oil path has two mutually independent oil paths, the clutch oil path includes a first oil guide channel 631 and a second oil guide channel 632, the shaft oil path includes a first oil path 621 and a second oil path 622, and the shaft oil path may be disposed on the input shaft or the output shaft to form an input shaft oil path or an output shaft oil path. Specifically, hydraulic oil is injected into one side of the cavity through the first oil guide passage, and meanwhile hydraulic oil is also injected into the other side of the cavity through the second oil guide passage, so that the pressures of the two ends of the double-end piston body in the cavity are the same, the double-end piston body is kept balanced in the cavity, and an initial preparation state is achieved.
In this embodiment, the switching double clutches are mounted on the input shaft, so that only two oil ducts are needed to convey hydraulic oil respectively, the number of the oil ducts to be formed can be calculated by twice the number of the switching double clutches, and mutually exclusive clutch control can be performed on the switching double clutches independently. When the switching type double clutch is subjected to clutch operation, hydraulic oil is input into a cavity of the switching type double clutch through the shell oil path, the shaft oil path and the clutch oil path, and then the hydraulic oil is conveyed.
Specifically, the shaft oil passage is provided in the input shaft as an example. The double-hole oil conveying path is provided with two oil paths, so that hydraulic oil is conveyed to the input shaft through the double-hole oil conveying path, the shaft oil path is respectively conveyed through the first oil conveying path and the second oil conveying path and is respectively communicated and connected with the two oil paths of the double-hole oil conveying path, the clutch oil path is communicated and connected with the first oil conveying path through the first oil guide path, the second oil guide path is communicated and connected with the second oil conveying path, the hydraulic oil is respectively conveyed to the two sides of the cavity, and the purpose of conveying the hydraulic oil into the switching type double clutch through the shell is achieved.
Two annular oil inlet grooves are formed in the connecting position of the double-hole oil conveying path and the shaft oil path and on the input shaft at the connecting position, two sides of each oil inlet groove are sealed through a sealing ring, namely the sealing ring is positioned between the shell and the input shaft for sealing, and each double-hole oil conveying path is provided with one oil inlet groove for conducting connection. And between the input shaft and the inner hole of the switching type double clutch, the input shaft is connected in an interference fit manner, and meanwhile, an annular oil outlet groove is adopted, so that the shaft oil path is respectively communicated with the first oil guide channel and the second oil guide channel, and then the hydraulic oil is respectively conveyed to two sides of the cavity, and the purpose of controlling the double-head piston body to move in the cavity through the oil pressure of the hydraulic oil is achieved.
In this embodiment, the first clutch block is connected to the first input gear of the input shaft, and the second clutch block is connected to the first output gear, so that the first switching dual clutch can perform mutually exclusive clutch control on the first gear pair of the input shaft and the second gear pair of the output shaft. In this embodiment, for example, the first oil guiding passage pushes the double-end piston body to move toward the first output gear after oil enters, and the second oil guiding passage pushes the double-end piston body to move toward the first input gear after oil enters.
And hydraulic oil pumps can be used for conveying the hydraulic oil in the oil tank to different pipelines in the oil circuit in the transmission. For example, when the first gear pair needs to be in the closed state, the hydraulic oil is conveyed through the routes of one oil passage of the first dual-hole conveying oil passage, the first conveying oil passage of the shaft oil passage and the second oil guide passage, so that the double-end piston body of the first switching type double clutch moves towards the first gear pair. The first friction plate group is pushed by the double-end piston body to perform combined friction, and power is transmitted to the first input gear from the input shaft through the first clutch block, so that the first gear pair is in a combined state, namely the first input gear is meshed with the second input gear, and the power is transmitted to the intermediate shaft from the input shaft. And at the moment, the switching type double clutch and the second gear pair are in an off state.
Similarly, when the second gear pair is in a closed state, the hydraulic oil is conveyed through the other oil duct of the double-hole conveying oil duct, the second conveying oil duct of the shaft oil duct and the route of the first oil guide duct, so that the double-end piston body of the first switching type double clutch moves towards the second gear pair. The second friction plate group is pushed by the double-end piston body to perform combination friction, and power is transmitted to the first output gear from the input shaft through the second clutch block, so that the second gear pair is in a combined state, namely the first output gear is meshed with the second output gear, and the power is directly transmitted to the output shaft from the input shaft. At this time, the switching type double clutch and the first gear pair are in a separated state.
In this embodiment, for example, the shaft oil passage is provided on the input shaft, and the seal ring 623 is provided on the input shaft on both sides of each oil inlet of the shaft oil passage. Namely, a sealing ring is arranged on both sides of the oil inlet of the first oil conveying path and the oil inlet of the second oil conveying path. If the first oil conveying path and the second oil conveying path are arranged on the input shaft side by side, the sealing ring, the oil inlet of the first oil conveying path, the sealing ring, the oil inlet of the second oil conveying path and the sealing ring can be arranged on the input shaft in sequence. The sealed connection between the shell oil way and the input oil way is achieved, and the leakage of hydraulic oil is avoided. And on the input shaft section of the oil outlet of the first oil conveying path and the oil outlet of the second oil conveying path, the input shaft section can be matched with the inner hole of the clutch in an interference fit mode, so that the oil leakage condition between the shaft oil path and the first clutch oil path can be avoided, and the oil mixing condition between the oil conveying pipelines can be avoided. The sealing ring in the embodiment can be an opening sealing ring, has the characteristic of high wear resistance, can ensure the service life of the input shaft or the output shaft, and reduces the maintenance cost of the transmission.
In this embodiment, the oil path structure of the transmission is filled with hydraulic oil, so that the hydraulic oil in the cavity is unbalanced only after the hydraulic oil is injected into the cavity again, and the double-end piston body is driven to move in the cavity, and the first or second friction plate set is driven to be frictionally combined through the double-end piston body, so as to achieve the clutch effect. The preparation time for driving the double-head piston body to move is zero, the effect of waiting for clutch switching when the time is zero is achieved, and the waiting time of the clutch structure during clutch switching is shortened.
In this embodiment, the first friction plate set 411 and the second friction plate set 421 have the same structure, and the components thereof may be a friction plate and a steel plate or a friction plate and a friction plate, which are described in this embodiment by taking a friction plate and a steel plate as an example. Installing a friction plate on the clutch block, and installing a steel sheet on the outer side surface of the cavity; on the contrary, the friction plate can be arranged on the outer side surface of the cavity, the steel sheet is arranged on the clutch block, and then the mutual contact friction effect between the friction plate and the steel sheet is formed, so that the gear connected to the other end of the clutch block is subjected to clutch operation.
In the present embodiment, the number of the intermediate shafts is plural, and may be two, three, or four, and so on. The multiple intermediate shafts are circumferentially arrayed on the central axis of the input shaft or the output shaft, for example, the two intermediate shafts can be respectively arranged at the upper and lower positions of the input shaft and the output shaft, the multiple intermediate shafts have the same structure, and are provided with gears with the same tooth number and the same tooth width. Therefore, the loads of the input shaft and the output shaft can be distributed through the plurality of intermediate shafts, and the bending strength of the input shaft, the intermediate shafts and the output shaft is enhanced, so that the bearing capacity of the input shaft and the output shaft is improved, and the purpose of improving the loads is achieved.
It should be noted that, although the above embodiments have been described herein, the invention is not limited thereto. Therefore, based on the innovative concepts of the present invention, the technical solutions of the present invention can be directly or indirectly applied to other related technical fields by making changes and modifications to the embodiments described herein, or by using equivalent structures or equivalent processes performed in the content of the present specification and the attached drawings, which are included in the scope of the present invention.

Claims (9)

1. A kind of speed change gear with hydraulic oil circuit structure, characterized by that: the switching type double-clutch transmission comprises an input shaft, an output shaft, an intermediate shaft, a switching type double clutch, a shell and an oil way structure;
the central line of the input shaft and the central line of the output shaft are arranged in a collinear way, the input end of the input shaft and the output end of the output shaft respectively penetrate through two opposite side walls of the shell and are arranged on the shell, the input shaft is in transmission connection with the input end of the intermediate shaft, the output end of the intermediate shaft is in transmission connection with the output shaft, and the central line of the intermediate shaft is arranged in the shell in parallel with the central line of the input shaft;
the switching type double clutch is arranged on the input shaft or the output shaft, the switching type double clutch is positioned between two adjacent gear pairs on the input shaft and/or the output shaft, and the switching type double clutch is used for controlling the gear pairs on two sides of the switching type double clutch to perform mutual exclusion clutch operation;
the oil circuit structure comprises a shell oil circuit, a shaft oil circuit and a clutch oil circuit, wherein the shell oil circuit is arranged in the shell, the shaft oil circuit is arranged in the input shaft or the output shaft, one branch of the shell oil circuit is communicated with a first oil conveying circuit of the shaft oil circuit, and the other branch of the shell oil circuit is communicated with a second oil conveying circuit of the shaft oil circuit; the clutch oil circuit is arranged in the cavity of the switching type double clutch, and a first delivery oil circuit of the shaft oil circuit is communicated with a first oil guide channel of the clutch oil circuit; and a second oil delivery way of the shaft oil way is communicated with a second oil guide way of the clutch oil way.
2. The transmission having a hydraulic oil path structure according to claim 1, wherein the housing oil path is a double-hole delivery oil path, an oil inlet of the double-hole delivery oil path is provided on an outer side surface of the housing, and an oil outlet of the double-hole delivery oil path is provided on an inner surface of a shaft hole of the housing input shaft.
3. The transmission having a hydraulic oil path structure according to claim 2, characterized in that the clutch oil path includes a first oil guide passage and a second oil guide passage;
the first oil guide channel is arranged between one side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch, and the second oil guide channel is arranged between the other side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch.
4. The transmission having a hydraulic oil path structure according to claim 3, wherein the switching double clutch includes a first clutch block, a second clutch block, and a piston unit;
the piston unit comprises a double-end piston body and a cavity, the cross section of the double-end piston body is I-shaped, one end of the double-end piston body is arranged in the cavity, the other end of the double-end piston body is positioned outside the cavity, the oil outlet of the first oil guide channel is arranged on one side of the cavity, and the oil outlet of the second oil guide channel is arranged on the other side of the cavity;
the first clutch block comprises a first friction plate group, the second clutch block comprises a second friction plate group, the first friction plate group is located on one side of the other end of the double-end piston body, the second friction plate group is located on the other side of the other end of the double-end piston body, the first clutch block and the second clutch block are respectively arranged on gear pairs on two sides, and the double-end piston body is used for driving one of the first friction plate group or the second friction plate group to be combined and the other to be separated.
5. The transmission having a hydraulic oil passage structure according to claim 1, wherein a seal ring is provided on the input shaft on both sides of each oil inlet of the shaft oil passage.
6. The transmission having a hydraulic oil passage structure according to claim 1, wherein the seal ring is a split seal ring.
7. The transmission having a hydraulic oil circuit structure according to claim 1, wherein a plurality of the intermediate shafts are provided, and a plurality of the intermediate shafts are provided in a circumferential array on a central axis of the input shaft in the housing.
8. The transmission having a hydraulic oil passage structure according to claim 1, characterized in that the input shaft is provided with a first input gear, the output shaft is provided with a first output gear, and the switching clutch is provided on the input shaft or the output shaft between the first input gear and the first output gear.
9. The transmission having a hydraulic oil circuit structure according to claim 8, wherein the counter shaft is provided with a second input gear and a second output gear, the first input gear and the second input gear are disposed in mesh with each other, and the first output gear and the second output gear are disposed in mesh with each other.
CN201910616390.8A 2019-07-09 2019-07-09 Transmission with hydraulic oil way structure Pending CN111336221A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201910616390.8A CN111336221A (en) 2019-07-09 2019-07-09 Transmission with hydraulic oil way structure

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113606296A (en) * 2021-08-04 2021-11-05 朱丽鹏 Overload slow-changing type starting connection device for large-scale rotating shaft
WO2022083839A1 (en) * 2020-10-22 2022-04-28 Udviklingsselskabet Af 1. Juli 2020 Aps Clutch system for faster gearing process with constant torque transmission

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022083839A1 (en) * 2020-10-22 2022-04-28 Udviklingsselskabet Af 1. Juli 2020 Aps Clutch system for faster gearing process with constant torque transmission
CN113606296A (en) * 2021-08-04 2021-11-05 朱丽鹏 Overload slow-changing type starting connection device for large-scale rotating shaft

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