WO2020037556A1 - 凸轮轴相位器用转子及凸轮轴相位器 - Google Patents

凸轮轴相位器用转子及凸轮轴相位器 Download PDF

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Publication number
WO2020037556A1
WO2020037556A1 PCT/CN2018/101769 CN2018101769W WO2020037556A1 WO 2020037556 A1 WO2020037556 A1 WO 2020037556A1 CN 2018101769 W CN2018101769 W CN 2018101769W WO 2020037556 A1 WO2020037556 A1 WO 2020037556A1
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WO
WIPO (PCT)
Prior art keywords
rotor
camshaft phaser
balance
groove portion
end surface
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.)
Ceased
Application number
PCT/CN2018/101769
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English (en)
French (fr)
Inventor
王朋
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to DE112018007916.3T priority Critical patent/DE112018007916T5/de
Priority to PCT/CN2018/101769 priority patent/WO2020037556A1/zh
Priority to US17/267,087 priority patent/US20220049633A1/en
Priority to CN201880094301.1A priority patent/CN112219015A/zh
Publication of WO2020037556A1 publication Critical patent/WO2020037556A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34479—Sealing of phaser devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts

Definitions

  • the present invention relates to a rotor for a camshaft phaser and a camshaft phaser.
  • variable valve timing system is an important part of ensuring the performance of the engine. It can adjust the opening and closing of the engine's valves as needed, so that the engine can obtain the desired power output, fuel consumption and emissions.
  • variable valve timing system mainly includes a camshaft phaser and a camshaft connected to the camshaft phaser, and the camshaft is connected to a valve of the engine through a valve distributing mechanism.
  • a camshaft phaser consists of an end cover, a rotor, and a stator (the stator and the end cover are relatively fixed).
  • a plurality of oil chambers are formed inside the camshaft phaser, and oil of different pressure can be input to the multiple oil chambers to make the rotor Relative to the stator and the end cover, the camshaft is driven by the rotor to adjust the opening and closing of the valve.
  • a camshaft phaser As shown in FIGS. 1 a and 1 b, a camshaft phaser according to the related art includes a stator 10, a rotor 20, two end covers 30, 40, a seal assembly 50, and a lock assembly 60.
  • the stator 10 includes a cylindrical stator main body 101 and a plurality of (four in the drawing) stator protrusions 102 protruding radially inward from the stator main body 101.
  • a plurality of teeth 103 distributed along the circumferential direction C are formed on the radially outer portion of the stator body 101 for meshing with a transmission member such as a chain.
  • the rotor 20 is provided on the radially inner side of the stator 10 and is rotatable relative to the stator 10.
  • the rotor 20 includes a cylindrical rotor body 201 and a plurality of (four in the drawing) rotor blades 202 protruding radially outward from the rotor body 201.
  • the plurality of rotor blades 202 and the plurality of stator protrusions 102 are alternately arranged in the circumferential direction C, so that each rotor blade 202 is located between two adjacent stator protrusions 102. In this way, the space between two adjacent stator protrusions 102 is divided into two independent oil chambers A, B by the rotor blades 202 located between the two stator protrusions 102.
  • the two end covers 30 and 40 are fixed to the stator 10 from both sides in the axial direction by fixing members, so that the two end covers 30 and 40 are enclosed with the stator 10 and the rotor 20 to form the above-mentioned oil chambers A and B.
  • a seal assembly 50 is provided on the radially outer end surface of the rotor blade 202 and abuts against the stator body 101.
  • the seal assembly 50 includes a seal lip 501 and a leaf spring 502 abutting on the seal lip 501 from the radial inside for the rotor
  • the two oil chambers A, B separated by the blade 202 are isolated from each other.
  • the locking component 60 is disposed on a stator protrusion 102 and an end cover 40.
  • the locking component 60 can lock the rotation of the rotor 20 relative to the stator 10.
  • the above-mentioned locking component 60 can be released. locking.
  • the rotor 20 and the end caps 30 and 40 are in surface contact (plane-to-plane contact) in the axial direction X, and this surface contact must have a certain gap. This ensures that the rotor 20 can rotate relative to the end covers 30, 40. In addition, while ensuring that the rotor 20 can rotate relative to the end caps 30 and 40, it is also necessary to ensure the seal between the rotor 20 and the end caps 30 and 40. Therefore, on the one hand, it is necessary to control the passage of the adjacent oil chambers A and B through the rotor 20. The amount of leakage in the gap between the end caps 30 and 40 is kept at a low level, and on the other hand, it is necessary to prevent outward leakage.
  • An object of the present invention is to provide a rotor for a camshaft phaser, which can make the gap between the rotor and the end covers on both sides as balanced as possible, so that the amount of oil leakage in the oil chamber of the camshaft phaser through the gap can be reduced And the wear between the rotor and the end cap is reduced.
  • Another object of the present invention is to provide a camshaft phaser including the above-mentioned rotor for a camshaft phaser.
  • the present invention adopts the following technical solutions.
  • the present invention provides a rotor for a camshaft phaser.
  • a balance groove is formed in an axial end surface of one side of the rotor and an axial end surface of the other side of the rotor, and the balance groove and the rotor are respectively formed.
  • the peripheral edges of the rotor are spaced apart, and the rotor is further formed with a through hole penetrating the rotor in the axial direction, and a balance groove in an axial end surface of the rotor is balanced with an axial end surface of the rotor.
  • the grooves communicate with each other via the through holes.
  • the total volume of the balance grooves in the axial end surface on one side of the rotor is equal to the total volume of the balance grooves in the axial end surface on the other side of the rotor.
  • a minimum interval between the balance groove and a peripheral edge of the rotor is greater than or equal to 3 mm.
  • the rotor includes a cylindrical rotor main body and a plurality of rotor blades protruding radially outward from the rotor main body, and the balance groove includes a peripheral portion formed in the rotor main body and extending in a circumferential direction. ⁇ ⁇ ⁇ To the groove portion.
  • the circumferential groove portion extends continuously over the entire circumference in the circumferential direction.
  • the balance groove further includes a radial groove portion extending radially outward from the circumferential groove portion to the rotor blade, and the radial groove portion communicates with the circumferential groove portion.
  • the number of the through holes is multiple, and the multiple through holes are evenly distributed in the circumferential groove portion along the circumferential direction.
  • the through hole includes a through hole formed in the radial groove portion.
  • the rotor is formed by powder metallurgy.
  • the present invention also provides a camshaft phaser including the rotor for a camshaft phaser according to any one of the above technical solutions.
  • the present invention provides a rotor for a camshaft phaser and a camshaft phaser including the same.
  • the axially-side end surfaces of the rotor are respectively formed with balancing grooves communicated through through holes.
  • the gap allows the amount of oil in the oil chamber to leak through the gap to be kept low and reduces the probability of hard contact between the rotor and the end cover, thereby allowing the oil in the oil chamber of the camshaft phaser to pass through the gap
  • the amount of leakage is reduced and the wear between the rotor and the end cap is reduced.
  • the quality of the rotor is also reduced and costs are saved.
  • FIG. 1a is a schematic axial sectional view of a camshaft phaser of the prior art
  • FIG. 1b is a schematic diagram of the structure of the camshaft phaser in FIG. 1a viewed from the axial side, and the end on the axial side is omitted cover.
  • Fig. 2a is a schematic view of a rotor of a camshaft phaser according to a first embodiment of the present invention as viewed from an axial side;
  • Fig. 2b is a slave-axis of a rotor of a camshaft phaser according to a second embodiment of the present invention Schematic view from one side.
  • stator 101 stator body 102 stator protrusion 103 tooth
  • rotor 201 rotor body 202
  • rotor blade 203 balance groove 203c circumferential groove portion 203r radial groove portion 204 through hole 30, 40 end cap 50 seal assembly 501 seal lip 502 blade spring 60
  • the camshaft phaser according to the present invention has a substantially cylindrical shape as a whole.
  • the axial, radial, and circumferential directions of the present invention refer to the axial, radial, and circumferential directions of the camshaft phaser (rotor), respectively.
  • the basic structure of the camshaft phaser according to the present invention is the same as that of the prior art camshaft phaser shown in FIGS. 1a and 1b, and the difference between the two lies in the camshaft according to the present invention.
  • the rotor of the phaser is different from the structure of the rotor of the camshaft phaser of the prior art.
  • the specific structure of the rotor of the camshaft phaser according to the present invention will be mainly explained below.
  • the camshaft phaser includes a rotor 20 having a cylindrical rotor body 201 and a plurality of rotor bodies 201 projecting radially outward from the rotor body 201 (in the figure) There are four) rotor blades 202.
  • a balance groove 203 having the same shape and the same size is formed in the axial end surface of one side of the rotor 20 and the axial end surface of the other side of the rotor 20 (only the rotor 20 is shown in the figure).
  • Balance groove 203 in the axial end surface of the rotor 20 such that the total volume of the balance groove 203 in the axial end surface of the rotor 20 is equal to the total volume of the balance groove 203 in the axial end surface of the rotor 20.
  • the balance groove 203 in the axial end surface of the rotor 20 is described as an example.
  • the balance groove 203 includes a circumferential groove portion 203 c formed in the rotor body 201 and extending in the circumferential direction C, and preferably the circumferential groove The portion 203c extends continuously over the entire circumference.
  • the circumferential groove portion 203c is spaced apart from the outer and inner peripheral edges of the rotor body 201 by the same interval (corresponding to the minimum interval L), and the interval is 4 mm.
  • the balancing grooves 203 located in the axial end surface of the rotor 20 and the axial end surface of the rotor 20 are respectively formed through four circular through holes 204 penetrating the rotor 20 in the axial direction.
  • the communication enables the oil to flow between the balancing grooves 203 on both sides in the axial direction through the through hole 204.
  • the four through holes 204 are evenly distributed in the circumferential groove portion 203c along the circumferential direction C, and the openings of all the through holes 204 are located at the bottom of the circumferential groove portion 203c.
  • the thrust generated by the balance slot 203 will increase the probability that the rotor 20 is in a more balanced position, and the thrust generated by the balance slot 203 will at least increase the chance or time that the rotor 20 is in the balanced position.
  • the gap generated between the rotor 20 and the two end covers is balanced by the thrust generated in the balance groove 203, so that the leakage amount of the engine oil in the oil chamber through the gap is kept at a low level and the The probability of the occurrence of hard contact further reduces the amount of leakage of the oil in the oil chamber of the camshaft phaser through the gap and reduces the wear between the rotor and the end cover.
  • the basic structure of the rotor 20 of the camshaft phaser according to the second embodiment of the present invention is substantially the same as the basic structure of the rotor 20 of the camshaft phaser according to the first embodiment of the present invention.
  • the balance groove 203 of the rotor 20 further includes a radial groove portion 203r and the number and formation position of the through holes 204 are different.
  • the balance groove 203 further includes a radial groove portion 203r extending radially outward from the circumferential groove portion 203c to the rotor blade 202, and the radial groove portion 203r communicates with the circumferential groove portion 203c.
  • the minimum interval L between the entire balance groove 203 and the peripheral edge of the rotor 20 is the interval between the radial groove portion 203r and the peripheral edge of the root portion of the rotor blade 202, and the minimum interval L is 3 mm.
  • the rotor 20 includes not only six circular through holes 204 formed in the circumferential groove portion 203c but also two circular through holes 204 formed in the radial groove portion 203r.
  • the present invention also provides a camshaft phaser, which includes a camshaft phaser rotor 20 having the above structure.
  • the present invention is not limited thereto. In the present invention, the number and shape of the through holes 204 can be changed as needed. In addition, the position of the through hole 204 can be arbitrarily adjusted as long as it does not affect the normal operation of the oil circuit and the lock assembly in the rotor 20.
  • the balance groove 203 includes a circumferential groove portion 203c and / or a radial groove portion 203r, the present invention is not limited thereto.
  • the balance groove 203 may include groove portions of other arbitrary shapes.
  • the balance groove 203 can be formed in as many areas as possible.
  • the minimum interval L between the balance groove 203 and the peripheral edge of the rotor 20 was described in the above specific embodiments as 4 mm and 3 mm, the present invention is not limited thereto. In the present invention, it is sufficient that the minimum interval L is greater than or equal to 3 mm. In addition, the interval between the balance groove 203 and the peripheral edge of the rotor 20 is preferably uniformly distributed.
  • the rotor 20 is formed by powder metallurgy forming.
  • the mold can be adjusted for convenient implementation. No additional machining is required. Further, due to the existence of the balance groove 203 and the through hole 204, the manufacturing material of the rotor 20 is reduced, the cost is reduced, and the mass of the rotor 20 after molding is reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

一种凸轮轴相位器用转子（20）及凸轮轴相位器。该转子（20）的轴向一侧端面内和转子（20）的轴向另一侧端面内分别形成有平衡槽（203）并且平衡槽（203）与转子（20）的周缘间隔开。转子（20）还形成有沿着轴向贯通转子（20）的通孔（204）并且转子（20）的两侧的平衡槽（203）经由通孔（204）彼此连通。这样，该凸轮轴相位器用转子（20）能够平衡转子（20）与两个端盖（30、40）之间的间隙，使得将油腔（A、B）内的机油经由该间隙的泄漏量保持较低的水平并且降低转子（20）与端盖（30、40）之间的发生硬接触的概率，进而使得凸轮轴相位器的油腔（A、B）内的机油经由该间隙的泄漏量减少并且转子（20）与端盖（30、40）之间的磨损降低。另外，由于平衡槽（203）和通孔（204）的存在，还降低了转子（20）的质量且节省了成本。

Description

凸轮轴相位器用转子及凸轮轴相位器 技术领域
本发明涉及凸轮轴相位器用转子及凸轮轴相位器。
背景技术
可变气门正时系统是保证发动机性能的重要组成部分，其能够根据需要调节发动机的气门的开闭，从而使得发动机获得期望的动力输出、燃油消耗及排放。
在现有技术中，可变气门正时系统主要包括凸轮轴相位器和与凸轮轴相位器连接的凸轮轴，凸轮轴通过配气机构与发动机的气门连接。通常，凸轮轴相位器由端盖、转子和定子(定子和端盖相对固定)三者在凸轮轴相位器的内部形成多个油腔，可以向多个油腔输入不同压力的机油来使转子相对于定子和端盖转动，从而通过转子带动凸轮轴来调节气门的开闭。
如图1a和图1b所示，根据现有技术的凸轮轴相位器包括定子10、转子20、两个端盖30、40、密封组件50和锁止组件60。
具体地，定子10包括圆筒状的定子主体101以及从定子主体101朝向径向内侧突出的多个(图中为四个)定子凸起102。定子主体101的径向外侧部形成沿着周向C分布的多个齿103，用于与链条等传动部件啮合。
转子20设置于定子10的径向内侧并且能够相对于定子10转动。转子20包括圆筒状的转子主体201以及从转子主体201朝向径向外侧突出的多个(图中为四个)转子叶片202。多个转子叶片202与多个定子凸起102在周向C上交替地布置，使得每个转子叶片202均位于相邻的两个定子凸起102之间。这样，在相邻的两个定子凸起102之间的空间被位于这两个定子凸起102之间的转子叶片202分隔成两个彼此独立的油腔A、B。
两个端盖30、40通过固定件从轴向两侧固定于定子10，使得两个端盖30、40与定子10和转子20一起包围形成上述油腔A、B。
密封组件50设置于转子叶片202的径向外侧端面并且与定子主体101抵接，该密封组件50包括密封唇501和从径向内侧抵接于密封唇501的叶片弹簧502，以用于使转子叶片202分隔开的两个油腔A、B彼此隔离。
锁止组件60设置于一个定子凸起102和端盖40，锁止组件60能够锁定转子20相对于定子10的转动，当需要转子20相对于定子10转动时则能够解除锁止组件60的上述锁定。
在具有上述结构的现有技术的凸轮轴相位器中，在轴向X上转子20与端盖30、40之间为面接触(平面与平面的接触)，这种面接触必须有一定间隙，从而保证转子20能够相对于端盖30、40转动。另外，在保证转子20能够相对于端盖30、40转动的同时还需要保证转子20与端盖30、40之间的密封，从而一方面要控制相邻的油腔A、B的经由转子20与端盖30、40之间的间隙的泄漏量保持在一个较低的水平，另一方面要防止向外泄漏。
但是，在实际的工作过程中，由于各种原因(例如链条或带等产生的弯矩、凸轮轴的轴向窜动、转子的几何误差等)，转子20在大部分时间内会更靠向轴向X的两侧中的某一侧(图1a中的左侧或右侧)，从而导致转子20与端盖30之间的间隙和转子20与端盖40之间的间隙不平衡(不相等)，进而产生了如下的问题：
1.由于泄漏量与间隙的三次方成正比，当转子20与端盖30之间的间隙和转子20与端盖40之间的间隙不平衡时会导致油腔之间以及向外的泄漏量不期望地变大；
2.由于在间隙较小的那侧转子20与端盖30或者转子20与端盖40容易发生硬接触，从而容易在转子20与端盖30之间或者在转子20与端盖40之间产生大摩擦力，使得转子20与端盖30、40容易磨损。
发明内容
基于上述现有技术的缺陷而做出了本发明。本发明的目的在于提供一种凸轮轴相位器用转子，其能够使得转子与两侧端盖之间的间隙尽可能平衡，从而使得凸轮轴相位器的油腔内的机油经由该间隙的泄漏量减少并且转子与端盖之间的磨损降低。本发明的另一个发明目的在于提供包括上述凸轮轴相位器用转子的凸轮轴相位器。
为了实现上述发明目的，本发明采用如下的技术方案。
本发明提供了一种如下的凸轮轴相位器用转子，所述转子的轴向一侧端面内和所述转子的轴向另一侧端面内分别形成有平衡槽并且所述平衡槽与所述转子的周缘间隔开，所述转子还形成有沿着轴向贯通所述转子的通孔并且所述转子的轴向一侧端面内的平衡槽与所述转子的轴向另一侧端面内的平衡槽经由所述通孔彼此连通。
优选地，所述转子的轴向一侧端面内的平衡槽的总容积与所述转子的轴向另一侧端面内的平衡槽的总容积相等。
优选地，所述平衡槽与所述转子的周缘之间的最小间隔大于或等于3mm。
优选地，所述转子包括圆筒状的转子主体以及从所述转子主体朝向径向外侧突出的多个转子叶片，并且所述平衡槽包括形成于所述转子主体的沿着周向延伸的周向槽部。
优选地，所述周向槽部沿着周向在整周上连续地延伸。
优选地，所述平衡槽还包括从所述周向槽部沿着径向向外延伸到所述转子叶片的径向槽部，所述径向槽部与所述周向槽部连通。
优选地，所述通孔的数量为多个，该多个通孔沿着周向均匀地分布于所述周向槽部内。
优选地，所述通孔包括形成于所述径向槽部的通孔。
优选地，其特征在于，所述转子通过粉末冶金成型来形成。
本发明还提供了一种如下的凸轮轴相位器，所述凸轮轴相位器包括以上技术方案中任意一项技术方案所述的凸轮轴相位器用转子。
通过采用上述技术方案，本发明提供了一种凸轮轴相位器用转子及包括该转子的凸轮轴相位器，该转子的轴向两侧端面分别形成有通过通孔连通的平衡槽。这样，在转子工作的过程中，轴向两侧的平衡槽内的机油会从间隙大的那侧的平衡槽流向间隙小的那侧的平衡槽，从而平衡转子与两个端盖之间的间隙，使得将油腔内的机油经由该间隙的泄漏量保持较低的水平并且降低转子与端盖之间的发生硬接触的概率，进而使得凸轮轴相位器的油腔内的机油经由该间隙的泄漏量减少并且转子与端盖之间的磨损降低。另外，由于平衡槽和通孔的存在，还降低了转子的质量且节省了成本。
附图说明
图1a是现有技术的凸轮轴相位器的轴向剖视示意图；图1b是从轴向一侧观察的图1a中的凸轮轴相位器的结构的示意图，其省略了轴向一侧的端盖。
图2a是根据本发明的第一实施方式的凸轮轴相位器的转子的从轴向一侧观察的示意图；图2b是根据本发明的第二实施方式的凸轮轴相位器的转子的从轴向一侧观察的示意图。
附图标记说明
10定子 101定子主体 102定子凸起 103齿 20转子 201转子主体 202转子叶片 203平衡槽 203c周向槽部 203r径向槽部 204通孔 30、40端盖 50密封组件 501密封唇 502叶片弹簧 60锁止组件 A、B油腔
X轴向 C周向 L最小间隔
具体实施方式
以下将结合说明书附图对本发明的技术方案进行说明。根据本发明的凸轮轴相位器整体具有大致圆柱形状，如无特殊说明，本发明的轴向、径向和周向分别是指凸轮轴相位器(转子)的轴向、径向和周向。
具体地，根据本发明的凸轮轴相位器的基本结构与图1a和图1b中所示的现有技术的凸轮轴相位器的基本结构相同，两者的不同之处在于根据本发明的凸轮轴相位器的转子与现有技术的凸轮轴相位器的转子的结构不同。以下将主要说明根据本发明的凸轮轴相位器的转子的具体结构。
(第一实施方式)
如图2a所示，根据本发明的第一实施方式的凸轮轴相位器包括转子20，该转子20具有圆筒状的转子主体201以及从转子主体201朝向径向外侧突出的多个(图中为四个)转子叶片202。
具体地，在本实施方式中，转子20的轴向一侧端面内和转子20的轴向另一侧端面内分别形成有形状相同且尺寸相同的平衡槽203(图中仅示出了转子20的轴向一侧端面内的平衡槽203)，使得转子20的轴向一侧端面内的平衡槽203的总容积与转子20的轴向另一侧端面内的平衡槽203的总容积相等。
以位于转子20的轴向一侧端面内的平衡槽203为例进行说明，该平衡槽203包括形成于转子主体201的沿着周向C延伸的周向槽部203c、优选地该周向槽部203c在整周上连续地延伸。该周向槽部203c与转子主体201的外周缘和内周缘均间隔开相同的间隔(对应于最小间隔L)，该间隔为4mm。
在本实施方式中，分别位于转子20的轴向一侧端面内和转子20的轴向另一侧端面内的平衡槽203经由沿着轴向贯通转子20的四个圆形的通孔204彼此连通，使得机油能够经由通孔204在轴向两侧的平衡槽203之间流通。具体地，这四个通孔204沿着周向C均匀地分布于周向槽部203c内且所有通孔204 的开口均位于周向槽部203c的底部。
以上说明了根据本发明的第一实施方式的凸轮轴相位器的转子20的区别于现有技术的具体结构，以下将说明该转子20的平衡槽203和通孔204的工作原理。
在凸轮轴相位器工作过程中，油腔内的机油经由转子20与端盖之间的间隙的内泄漏总是存在的，因此机油会一直在凸轮轴相位器的内部流动。在转子20与端盖之间的间隙较大的一侧，机油在该较大间隙内流动的阻力小，从而压降小，所以油压相对另一侧的较小间隙内的机油的油压大。于是，机油会从较大间隙侧经过通孔204流向较小间隙侧，流到较小间隙的机油会在平衡槽203中产生推力，从而使得较小间隙变大，直到转子20的两侧间隙接近平衡(相等)。换句话说，由平衡槽203产生的推力会增加转子20处在更为平衡的位置的概率，由平衡槽203产生的推力至少会增加转子20处在平衡位置的机会或时间。通过在平衡槽203中产生的推力平衡了转子20与两个端盖之间的间隙，使得将油腔内的机油经由该间隙的泄漏量保持较低的水平并且降低转子与端盖之间的发生硬接触的概率，进而使得凸轮轴相位器的油腔内的机油经由该间隙的泄漏量减少并且转子与端盖之间的磨损降低。
(第二实施方式)
如图2b所示，根据本发明的第二实施方式的凸轮轴相位器的转子20的基本结构与根据本发明的第一实施方式的凸轮轴相位器的转子20的基本结构大致相同，两者之间的不同之处在于：在第二实施方式中，转子20的平衡槽203还包括径向槽部203r并且通孔204的数量和形成位置不同。
具体地，在本实施方式中，平衡槽203还包括从周向槽部203c沿着径向向外延伸到转子叶片202的径向槽部203r，径向槽部203r与周向槽部203c连通。整个平衡槽203与转子20的周缘之间的最小间隔L为径向槽部203r与转子叶片202的根部的周缘之间的间隔，该最小间隔L为3mm。
进一步地，在本实施方式中，转子20不仅包括形成于周向槽部203c的六个圆形通孔204而且还包括形成于径向槽部203r的两个圆形通孔204。
此外，第二实施方式中的平衡槽203和通孔204的工作原理与第一实施方式中的相同，在此处不进行详细地说明了。
本发明还提供了一种凸轮轴相位器，该凸轮轴相位器包括具有以上结构的凸轮轴相位器用转子20。
虽然在以上的具体实施方式中对本发明的技术方案进行了详细地阐述，但是还需要说明的是：
1.虽然在以上的具体实施方式中说明了通孔204的数量和形状，但是本发明不限于此。在本发明中，通孔204的数量和形状可以根据需要进行改变。另外，只要不影响转子20内的油路、锁止组件的正常工作，通孔204的位置可以进行任意调整。
2.虽然在以上的具体实施方式中说明了平衡槽203包括周向槽部203c和/或径向槽部203r，但是本发明不限于此。该平衡槽203可以包括其它任意形状的槽部。另外，只要该平衡槽203与转子20的周缘具有足够的间隔，该平衡槽203可以采用尽量遍及尽可能多的区域的方式形成。
3.虽然在以上的具体实施方式中说明了平衡槽203与转子20的周缘之间的最小间隔L为4mm和3mm，但是本发明不限于此。在本发明中，只要满足该最小间隔L大于或等于3mm即可。另外，平衡槽203与转子20的周缘之间的间隔优选是均等分布的。
4.优选地，转子20通过粉末冶金成型来形成。另外，在制造具有上述结构的转子20的过程中，可以对模具进行调整，方便实现。不需要额外的机加工。进一步地，由于平衡槽203和通孔204的存在，使得转子20的制造材料减少，成本降低，并且成型后的转子20的质量减小。

Claims (10)

  1. 一种凸轮轴相位器用转子，所述转子的轴向一侧端面内和所述转子的轴向另一侧端面内分别形成有平衡槽并且所述平衡槽与所述转子的周缘间隔开，所述转子还形成有沿着轴向贯通所述转子的通孔并且所述转子的轴向一侧端面内的平衡槽与所述转子的轴向另一侧端面内的平衡槽经由所述通孔彼此连通。
  2. 根据权利要求1所述的凸轮轴相位器用转子，其特征在于，所述转子的轴向一侧端面内的平衡槽的总容积与所述转子的轴向另一侧端面内的平衡槽的总容积相等。
  3. 根据权利要求1或2所述的凸轮轴相位器用端子，其特征在于，所述平衡槽与所述转子的周缘之间的最小间隔大于或等于3mm。
  4. 根据权利要求1至3中任一项所述的凸轮轴相位器用转子，其特征在于，所述转子包括圆筒状的转子主体以及从所述转子主体朝向径向外侧突出的多个转子叶片，并且
    所述平衡槽包括形成于所述转子主体的沿着周向延伸的周向槽部。
  5. 根据权利要求4所述的凸轮轴相位器用转子，其特征在于，所述周向槽部沿着周向在整周上连续地延伸。
  6. 根据权利要求4或5所述的凸轮轴相位器用转子，其特征在于，所述平衡槽还包括从所述周向槽部沿着径向向外延伸到所述转子叶片的径向槽部，所述径向槽部与所述周向槽部连通。
  7. 根据权利要求4至6所述的凸轮轴相位器用转子，其特征在于，所述通孔的数量为多个，该多个通孔沿着周向均匀地分布于所述周向槽部内。
  8. 根据权利要求6所述的凸轮轴相位器用转子，其特征在于，所述通孔包括形成于所述径向槽部的通孔。
  9. 根据权利要求1至8中任一项所述的凸轮轴相位器用转子，其特征在于，所述转子通过粉末冶金成型来形成。
  10. 一种凸轮轴相位器，所述凸轮轴相位器包括权利要求1至9中任一项所述的凸轮轴相位器用转子。
PCT/CN2018/101769 2018-08-22 2018-08-22 凸轮轴相位器用转子及凸轮轴相位器 Ceased WO2020037556A1 (zh)

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