CN212250173U - Hydraulic tappet - Google Patents
Hydraulic tappet Download PDFInfo
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- CN212250173U CN212250173U CN202020926259.XU CN202020926259U CN212250173U CN 212250173 U CN212250173 U CN 212250173U CN 202020926259 U CN202020926259 U CN 202020926259U CN 212250173 U CN212250173 U CN 212250173U
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- pressure relief
- tappet
- valve
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- 239000003921 oil Substances 0.000 claims abstract description 57
- 238000007789 sealing Methods 0.000 claims abstract description 34
- 239000010705 motor oil Substances 0.000 claims abstract description 21
- 230000009471 action Effects 0.000 claims abstract description 12
- 230000002093 peripheral effect Effects 0.000 claims abstract description 8
- 230000005540 biological transmission Effects 0.000 claims description 3
- 238000002360 preparation method Methods 0.000 claims 1
- 230000007246 mechanism Effects 0.000 description 9
- 238000000034 method Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000010721 machine oil Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 230000008602 contraction Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
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Abstract
The utility model discloses a hydraulic tappet, include: one end of a tappet body is provided with an oil inlet and the other end is open, a plunger of the tappet body extends into the tappet body from the open end of the tappet body and forms a hydraulic cavity with the tappet body, the inner side of the oil inlet is provided with a one-way valve which can communicate an engine oil path with the hydraulic cavity under the action of engine oil pressure, and a return spring is arranged in the hydraulic cavity; the outer peripheral surface of the plunger is in sliding sealing fit with the inner peripheral surface of the tappet body, the plunger is provided with a pressure relief channel communicated with the hydraulic cavity, a pressure relief valve core and a pressure relief spring are arranged in the pressure relief channel, the pressure relief valve core is ejected away from a sealing conical surface by the pressure relief spring to form an oil leakage gap when not under the action of valve opening pressure, and the pressure relief valve core overcomes the elasticity of the pressure relief spring and is in contact with the sealing conical surface to realize sealing when under the action of the valve opening pressure. When the cam works and the valve is opened, the relative position of the tappet body and the plunger cannot be changed, and the performance of the engine is ensured.
Description
Technical Field
The utility model relates to an engine valve actuating mechanism technical field especially relates to a hydraulic tappet.
Background
The function of the lifter in the engine valve train is to transmit the thrust of the camshaft to the push rod (or valve stem) and to take up the lateral forces exerted by the camshaft as it rotates. The tappet is provided with an adjusting screw at the top thereof for adjusting the valve clearance. The reserved valve clearance can solve the problem that the valve is not closed tightly due to thermal expansion, but due to the existence of the valve clearance, the valve mechanism can cause impact and generate noise during working. In order to solve the contradiction, some engines adopt a hydraulic tappet.
As shown in fig. 1 and 2, a known hydraulic tappet is mounted at one end of a rocker arm 30, a tappet body 42A is fixedly connected with the rocker arm and is communicated with an oil path through an oil port 421A, and an oil drainage gap 46A is formed between an outer circumferential surface of the tappet body 42A and an inner circumferential surface of a plunger 41A.
When the engine valve 60 is at the closing moment (the cam 10 does not rotate to the working surface), engine oil supplies oil to the hydraulic cavity 43A through the oil inlet 421A and the check valve 44A, and slowly drains oil through the oil drainage gap 46A; the plunger 41A moves downwards relative to the tappet body 42A under the combined action of the oil pressure and the return spring 45A, presses the valve 60 to eliminate the valve clearance, but the valve 60 still closes under the condition of not overcoming the elastic force of the valve spring 50.
When the engine works at the moment that the valve 60 is opened (the cam 10 rotates to a working surface), the cam 10 pushes the tappet body 42A to move through the push rod 20 and the rocker arm 30, the oil pressure of the hydraulic cavity 43A is increased, the check valve 44A is closed, the plunger 41A is pushed to descend, and the plunger 41A pushes the valve 60 to be opened. In the process that the plunger 41A moves downwards, because the oil pressure in the hydraulic cavity 43A is very high, a part of oil is drained from the high-pressure oil through the oil drainage gap 46A, and after the valve opening process is finished, the check valve 44A is opened to supplement the oil for the hydraulic cavity 43A. The above actions are repeatedly cycled. The working length of the hydraulic tappet is continuously and automatically adjusted through leakage and supplement of hydraulic oil in the hydraulic cavity, so that the valve actuating mechanism keeps normal work, no gap exists in the valve adjusting mechanism, and impact and noise between parts are reduced.
However, the above-described hydraulic tappet has the following problems:
1) the requirement on oil drainage gaps is high, and the processing difficulty is high;
2) due to the existence of the oil drainage gap, when the cam works and the valve is opened, the tappet body and the plunger move relatively, the opening stroke of the valve is influenced, and particularly when the speed of an engine changes, oil drainage amounts at different rotating speeds are different, so that the relative movement amounts of the tappet body and the plunger are different, and the performance of the engine is influenced. On a large engine, the influence is more obvious because the valve opening force is larger.
SUMMERY OF THE UTILITY MODEL
The above-mentioned not enough to prior art, the utility model provides a hydraulic tappet to solve when cam work, valve are opened, there is relative movement tappet body and plunger, influences the valve and opens the problem of stroke.
In order to solve the technical problem, the utility model discloses a technical scheme is:
a hydraulic tappet comprising: the oil inlet is formed in one end of the tappet body, the other end of the tappet body is open, the plunger extends into the tappet body from the open end of the tappet body and forms a hydraulic cavity with the tappet body, a one-way valve capable of communicating an engine oil path with the hydraulic cavity under the action of engine oil pressure is arranged on the inner side of the oil inlet, and a return spring used for enabling the plunger to return relative to the tappet body after the valve opening pressure is eliminated is arranged in the hydraulic cavity; the outer peripheral surface of the plunger is in sliding fit with the inner peripheral surface of the tappet body, the fit clearance of the plunger ensures smooth sliding and sealing of the plunger, the plunger is provided with a pressure relief channel communicated with the hydraulic cavity, the pressure relief channel is provided with a sealing conical surface, a pressure relief valve core and a pressure relief spring are arranged in the pressure relief channel, the pressure relief valve core is jacked away from the sealing conical surface by the pressure relief spring to form an oil leakage clearance when not acted by the valve opening pressure, and the pressure relief valve core overcomes the elasticity of the pressure relief spring and is in contact with the sealing conical surface to realize sealing of the hydraulic cavity when acted by the valve opening pressure.
Wherein, the pressure relief valve core comprises a valve ball.
The pressure relief spring is arranged in a pressure relief channel communicated with the small end of the sealing conical surface and is abutted between the pressure relief valve core and one step surface of the pressure relief channel.
The hydraulic pressure cavity is internally and movably provided with a spring seat, the spring seat is provided with a through hole, the through hole is communicated with the hydraulic pressure cavity and the pressure relief channel, and the return spring is arranged in the spring seat.
And one end of the spring seat is abutted against the other end of the plunger under the action of the return spring, and a gap is reserved between the other end of the spring seat and the corresponding end surface of the tappet body.
The check valve comprises a check valve core, a limiting spring and a check valve seat, a sealing conical surface is arranged on the inner side of the oil inlet, the limiting spring is arranged in the check valve seat, the check valve seat is mounted on a tappet body of the hydraulic cavity, and the limiting spring enables the check valve core to abut against the sealing conical surface of the oil inlet.
The return spring is clamped between the one-way valve seat and the spring seat.
Wherein, the pressure relief passage is communicated with the oil pan.
The hydraulic tappet is arranged on any transmission part between a cam of an engine valve mechanism and a valve, and an oil inlet of the tappet body is communicated with an engine oil path of an engine.
The hydraulic tappet is arranged on a rocker arm of the engine valve mechanism, and the oil inlet is communicated with an engine oil path arranged on the rocker arm.
The utility model adopts the above technical scheme after, the technological effect who reaches is:
when the cam does not work, because the hydraulic plunger is not acted by the opening pressure of the valve at the moment, the pressure relief valve core is ejected away from the sealing conical surface of the pressure relief channel by the pressure relief spring, engine oil enters the hydraulic cavity through the oil inlet and the one-way valve, and slowly leaks through a gap between the pressure relief valve core and the sealing conical surface, at the moment, under the combined action of the engine oil pressure and the return spring, the tappet body and the plunger of the hydraulic tappet are respectively (directly or indirectly) close to the cam and the valve, and the valve gap is eliminated. When the cam works, the engine oil pressure of the hydraulic cavity rises, the pressure relief valve core overcomes the elasticity of the pressure relief spring, the hydraulic cavity becomes a closed cavity, no matter how the engine speed changes, the relative position of the tappet body and the plunger cannot change, and the performance of the engine is ensured.
Because the utility model discloses a can form the oil leak clearance between pressure release case and the sealed conical surface, do not have the during operation at the cam, the machine oil of engine can get into hydraulic pressure chamber through oil inlet and check valve to slowly leak through this oil leak clearance, therefore the utility model discloses the working length of hydraulic tappet both can be extended, also can shorten, the thermal expansion clearance that can the automatic compensation valve mechanism part. Compared with the traditional hydraulic tappet, when the cam works, the working length of the hydraulic tappet is almost unchanged (only slightly shortened at the initial stage of the cam work, and the shortening amount is controllable), and the valve opening stroke is more accurate.
The utility model discloses a hydraulic tappet can install on any one drive disk assembly between the valve to the cam of engine valve mechanism, and the preferred setting is on the rocking arm.
Drawings
FIG. 1 is a reference view of a known hydraulic tappet in use;
FIG. 2 is a cross-sectional structural view of the hydraulic tappet of FIG. 1;
FIG. 3 is a cross-sectional view of an embodiment of a hydraulic tappet of the present invention;
in the figure: 10-cam, 20-push rod, 30-rocker arm, 40A-hydraulic tappet, 41A-plunger, 42A-tappet body, 421A-oil inlet, 43A-hydraulic cavity, 44A-one-way valve, 45A-return spring, 46A-oil drainage clearance, 40B-hydraulic tappet, 41B-plunger, 411B-oil drainage hole, 42B-tappet body, 421B-oil inlet, 43B-hydraulic cavity, 44B-one-way valve, 45B-return spring, 46B-sealing conical surface, 47B-valve core pressure relief, 48B-pressure relief spring, 49B-spring seat, 491B-through hole, 50-valve spring, 60-valve, 70-oil pan and S-clearance.
Detailed Description
The present invention will be further explained with reference to the drawings and examples.
As shown in fig. 3 and with reference to fig. 1, a hydraulic tappet 40B is provided on a rocker arm of an engine valve train (see the position of the rocker arm 30 in fig. 1). An oil inlet 421B is formed in one end of the tappet body 42B, the other end of the tappet body is open, the plunger 41B extends from the open end of the tappet body 42B and forms a hydraulic cavity 43B with the tappet body 42B, the oil inlet 421B is communicated with an engine oil path (not shown) arranged on the rocker arm 30, a check valve 44B is arranged on the inner side of the oil inlet 421B, and the engine oil path and the hydraulic cavity 43B can be communicated through the check valve 44B under the action of engine oil pressure. The one-way valve 44B has a specific structure including a one-way valve spool 442B, a limit spring 443B and a one-way valve seat 441B, wherein a sealing conical surface is disposed on an inner side of the oil inlet 421B, the limit spring 443B is disposed in the one-way valve seat 441B, the one-way valve seat 441B is provided with an oil through hole and is mounted on a tappet body 42B of the hydraulic cavity, and the limit spring 443B abuts against the one-way valve spool 442B against the sealing conical surface of the oil inlet 421. Check valve spool 442B is preferably a valve ball, such as a steel ball.
A return spring 45B for returning the plunger 41B with respect to the tappet body 42B after the valve-opening pressure is removed is provided in the hydraulic chamber 43B. A spring seat 49B is movably arranged in the hydraulic cavity 43B, a through hole 491B is formed in the spring seat 49B, the through hole 491B is communicated with the hydraulic cavity 43B and the pressure relief channel 411B, and a return spring 45B is arranged in the spring seat 49B and is clamped between the one-way valve seat 441B and the spring seat 45B. Under the action of the elastic force of the return spring 45B, one end of the spring seat 49B abuts against the other end of the plunger 41B and has a gap S with the corresponding end surface of the tappet body 42B. The clearance S is designed to be an appropriate value (can refer to the size of the cold-state valve clearance of the traditional engine), and when the engine oil pressure is not built up when the engine is in a starting state, the normal work of the valve mechanism is ensured.
The outer peripheral surface of the plunger 41B is slidably fitted to the inner peripheral surface of the tappet body 42B, and the fitting clearance ensures smooth sliding and sealing of the plunger, so that oil does not leak therefrom. The plunger 41B is opened with a relief passage 411B communicating with the hydraulic pressure chamber 43B, and the relief passage 411B communicates with the oil pan 70. The pressure relief channel 411B is provided with a sealing conical surface 46B, a pressure relief valve core 47B and a pressure relief spring 48B are arranged in the pressure relief channel 411B, and preferably, the pressure relief valve core 47B comprises a valve ball, such as a steel ball. The elasticity of the pressure relief spring 48B should ensure that the pressure relief valve element 47B can still be disengaged from the sealing conical surface 46B to form an oil leakage gap when the engine oil of the engine reaches a maximum value, and the pressure relief valve element 47B can rapidly seal the sealing conical surface 46B when the cam working hydraulic chamber 43B forms a high pressure. The relief spring 48B is provided in a relief passage 411B communicating with the small end of the sealing tapered surface 46B, and abuts between the relief valve element 47B and a step surface of the relief passage. When the valve opening pressure is not acted, the pressure relief valve core 47B is ejected away from the sealing conical surface 46B by the pressure relief spring 48B; when acted upon by the valve opening pressure, the relief valve spool 47B overcomes the elastic force of the relief spring 48B and contacts the sealing tapered surface 46B to seal the hydraulic chamber 43B.
The working principle and the achieved technical effects of the embodiment are as follows:
when the cam 10 does not work (the cam 10 does not rotate to the working surface), because the hydraulic tappet is not acted by the valve opening pressure at the moment, the pressure relief valve core 47B is jacked away from the sealing conical surface 46B of the pressure relief channel by the pressure relief spring 48B to form an oil leakage gap, engine oil enters the hydraulic cavity 43B through the oil inlet 421B and the one-way valve 44B and slowly leaks through the gap between the pressure relief valve core 47B and the sealing conical surface 46B, at the moment, under the combined action of the engine oil pressure and the return spring 45B, the tappet body 42B and the plunger 41B of the hydraulic tappet are respectively (directly or indirectly) close to the cam 10 and the valve 60, the valve gap is eliminated, and the telescopic automatic compensation parts are influenced by expansion caused by heat and contraction caused by cold. When cam work (cam 10 rotated to the working face), hydraulic pressure chamber 43B machine oil pressure rose, and pressure relief valve core 47B overcomes pressure relief spring 48B's elasticity, and hydraulic pressure chamber 43B becomes confined chamber, shortens for traditional hydraulic tappet (working length), no matter how engine speed changes, the utility model discloses a tappet body 42B can not change with plunger 41B's relative position, has guaranteed the performance of engine.
In the present embodiment, the hydraulic tappet 40B is provided on a rocker arm, but the position of the hydraulic tappet 40B is not limited thereto, and it may be provided on any transmission member from a cam to a valve of an engine valve train.
The present invention is not limited to the above embodiments, and all improvements based on the concept, principle, structure and method of the present invention will fall within the protection scope of the present invention.
Claims (10)
1. A hydraulic tappet comprising:
the oil inlet is formed in one end of the tappet body, the other end of the tappet body is open, the plunger extends into the tappet body from the open end of the tappet body and forms a hydraulic cavity with the tappet body, a one-way valve capable of communicating an engine oil path with the hydraulic cavity under the action of engine oil pressure is arranged on the inner side of the oil inlet, and a return spring used for enabling the plunger to return relative to the tappet body after the valve opening pressure is eliminated is arranged in the hydraulic cavity; it is characterized in that the preparation method is characterized in that,
the outer peripheral surface of the plunger piston is in sliding sealing fit with the inner peripheral surface of the tappet body;
the plunger is provided with a pressure relief channel communicated with the hydraulic cavity, the pressure relief channel is provided with a sealing conical surface, a pressure relief valve core and a pressure relief spring are arranged in the pressure relief channel, the pressure relief valve core is jacked away from the sealing conical surface to form an oil leakage gap when not acted by the valve opening pressure, and the pressure relief valve core overcomes the elasticity of the pressure relief spring and contacts with the sealing conical surface to realize the sealing of the hydraulic cavity when acted by the valve opening pressure.
2. The hydraulic lifter of claim 1, wherein the pressure relief valve spool includes a valve ball.
3. The hydraulic tappet of claim 1, wherein the relief spring is disposed in a relief passage communicating with the small end of the sealing cone and abuts between the relief spool and a step surface of the relief passage.
4. The hydraulic tappet of claim 1, wherein a spring seat is movably disposed in the hydraulic chamber, the spring seat is provided with a through hole, the through hole communicates the hydraulic chamber and the pressure relief passage, and the return spring is disposed in the spring seat.
5. The hydraulic tappet of claim 4, wherein the spring seat is biased against the plunger at one end and is spaced from a corresponding end surface of the tappet body at an opposite end by the return spring.
6. The hydraulic tappet according to claim 5, wherein the check valve comprises a check valve core, a limiting spring and a check valve seat, a sealing conical surface is arranged on the inner side of the oil inlet, the limiting spring is arranged in the check valve seat, the check valve seat is mounted on a tappet body of the hydraulic cavity, and the limiting spring enables the check valve core to abut against the sealing conical surface of the oil inlet.
7. The hydraulic tappet of claim 6, wherein the return spring is sandwiched between the one-way valve seat and the spring seat.
8. The hydraulic lifter of claim 1, wherein the pressure relief passage communicates with an oil sump.
9. The hydraulic tappet of claim 1, wherein the hydraulic tappet is disposed on any one of transmission components from a cam to a valve of an engine valve train, and an oil inlet of the tappet body is communicated with an oil path of engine oil.
10. The hydraulic tappet of claim 9, wherein the hydraulic tappet is disposed on a rocker arm of the engine valve train, and the oil inlet is in communication with an engine oil gallery disposed on the rocker arm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020926259.XU CN212250173U (en) | 2020-05-26 | 2020-05-26 | Hydraulic tappet |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020926259.XU CN212250173U (en) | 2020-05-26 | 2020-05-26 | Hydraulic tappet |
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| Publication Number | Publication Date |
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| CN212250173U true CN212250173U (en) | 2020-12-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202020926259.XU Active CN212250173U (en) | 2020-05-26 | 2020-05-26 | Hydraulic tappet |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111472859A (en) * | 2020-05-26 | 2020-07-31 | 潍坊力创电子科技有限公司 | Hydraulic tappet |
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2020
- 2020-05-26 CN CN202020926259.XU patent/CN212250173U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111472859A (en) * | 2020-05-26 | 2020-07-31 | 潍坊力创电子科技有限公司 | Hydraulic tappet |
| CN111472859B (en) * | 2020-05-26 | 2024-05-03 | 潍坊力创电子科技有限公司 | Hydraulic tappet |
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