CN111486142A

CN111486142A - Stamping device for gear blank

Info

Publication number: CN111486142A
Application number: CN202010511935.1A
Authority: CN
Inventors: 田文海; 李景云; 曹加川
Original assignee: Xianghe Huamei Gear Co ltd
Current assignee: Xianghe bov Auto Parts Co.,Ltd.
Priority date: 2020-06-08
Filing date: 2020-06-08
Publication date: 2020-08-04
Anticipated expiration: 2040-06-08
Also published as: CN111486142B

Abstract

The invention discloses a stamping device for gear blanks, which comprises: the hydraulic oil cylinder comprises an upper piston rod and a lower piston rod, and the lower end of the lower piston rod is used for stamping a blank; the lower piston rod comprises an upper rod section and a lower rod section, the diameter of the upper rod section is larger than that of the upper piston rod, and the diameter of the lower rod section is smaller than that of the upper rod section; wherein: the upper piston rod and the cylinder body are enclosed to form a first hydraulic cavity, the upper rod section and the cylinder body are enclosed to form a second hydraulic cavity, and the lower rod section and the piston rod are enclosed to form a third hydraulic cavity; a bidirectional hydraulic pump; the first oil port is used for being connected with the first hydraulic cavity, and the second oil port is used for being connected with the second hydraulic cavity and the third hydraulic cavity; an actuator; a hydraulic control mechanism; wherein: the hydraulic control mechanism is used for selectively supplying hydraulic oil into the first chamber, the second chamber and the third chamber so that: before the lower piston rod punches the blank and after punching is completed, hydraulic oil in the first cavity can circulate with hydraulic oil in the second cavity.

Description

Stamping device for gear blank

Technical Field

The invention relates to the technical field of gear machining, in particular to a stamping device for stamping gear blanks.

Background

In the process of manufacturing the gear, before the gear is machined, a bar-shaped blank for the gear needs to be repeatedly punched (or forged), so that the gear can obtain better physical properties after being machined.

The prior art apparatus for stamping a bar-shaped blank generally comprises a cylinder for stamping the blank and a power system for supplying oil under pressure to the cylinder to cause a piston of the cylinder to perform a stamping action on the blank, and the power system generally comprises a bidirectional pump and an actuator for driving the bidirectional pump, wherein the actuator can be a combination of a motor and a gearbox, or a combination of an engine and a gearbox. The gearbox in the actuator is connected with a bidirectional pump for driving the bidirectional pump to pump hydraulic oil into the chamber of the oil cylinder.

Specifically, the bidirectional pump has a first oil port and a second oil port for communicating with the oil cylinder; the first oil port is communicated with a first chamber above the piston of the oil cylinder, and the second oil port is communicated with a second chamber below the piston of the oil cylinder. The two-way pump rotates forwards to enable the hydraulic oil to flow out of the first oil port and be supplied into the first chamber, and the hydraulic oil in the second chamber flows back into the two-way pump through the second oil port, so that the piston drives the piston rod to move downwards and finally punches the rod-shaped blank; the two-way pump is switched from forward rotation to reverse rotation, so that the hydraulic oil flows out of the second oil port and enters the second chamber, the hydraulic oil in the first chamber flows back into the two-way pump through the first oil port, and therefore the piston drives the piston rod to move upwards and reset. It can thus be seen that both the downward and upward movement of the plunger rod's ram motion are driven by the bi-directional pump by reversing direction.

It can be understood that the operator or designer wants the downward moving speed of the piston rod before contacting the blank and the upward moving speed after punching to be as large as possible, and the downward moving speed after contacting the blank is completed at a smaller speed, which will not affect the punched effect of the blank and can improve the punching efficiency.

In the prior art, the above-mentioned motion requirements for the piston rod are achieved by:

the two-way pump with larger displacement is selected, before the piston rod contacts the blank and after the piston rod is punched, the hydraulic oil provided by the two-way pump is not limited, and then the hydraulic oil is completely supplied into the cavity of the oil cylinder to the maximum extent so that the piston obtains larger movement speed, and when the piston rod contacts the blank to be punched, the flow limiting element or structure is used for limiting the amount of the hydraulic oil supplied into the cavity by the two-way pump, and further the downward moving speed of the piston rod is limited so that the piston rod moves downward at a lower speed.

The above-described manner of obtaining the motion requirement of the piston rod has the following problems:

1. a very large displacement bi-directional pump is required, which increases the overall cost of the press.

2. The hydraulic oil is limited by the current limiting element or structure, and energy loss is increased.

3. The adoption of the flow limiting mode can cause the related hydraulic components such as the flow limiting element and the like to generate noise easily and be damaged easily.

Disclosure of Invention

In view of the above technical problems in the prior art, embodiments of the present invention provide a punching device for gear blanks.

In order to solve the technical problem, the embodiment of the invention adopts the following technical scheme:

a stamping device for gear blanks, comprising:

the hydraulic oil cylinder comprises a cylinder body, a piston arranged in the cylinder body, an upper piston rod positioned above the piston and extending out of the cylinder body, and a lower piston rod positioned below the piston and extending out of the cylinder body, wherein the lower end of the lower piston rod is used for stamping a blank; the lower piston rod comprises an upper rod section and a lower rod section, the diameter of the upper rod section is larger than that of the upper piston rod, and the diameter of the lower rod section is smaller than that of the upper rod section; wherein: the upper piston rod and the cylinder body enclose a first hydraulic cavity, the upper rod section and the cylinder body enclose a second hydraulic cavity, and the lower rod section and the piston rod enclose a third hydraulic cavity;

a bidirectional hydraulic pump having a first port and a second port; the first oil port is used for being connected with the first hydraulic cavity, and the second oil port is used for being connected with the second hydraulic cavity and the third hydraulic cavity;

an actuator for driving the bidirectional hydraulic pump;

a hydraulic control mechanism; wherein:

the hydraulic control mechanism is used for selectively supplying hydraulic oil into the first chamber, the second chamber and the third chamber so that:

before the lower piston rod punches the blank and after punching is completed, hydraulic oil in the first cavity and hydraulic oil in the second cavity can circulate.

Preferably, the hydraulic control mechanism includes:

a first one-way valve disposed on a first flow conduit between the first chamber and the second chamber, an inlet of the first one-way valve being in communication with the second chamber and an outlet of the first one-way valve being in communication with the first chamber;

a second one-way valve disposed on a second flow conduit between the first chamber and the second chamber, an inlet of the second one-way valve being in communication with the first chamber and an outlet of the second one-way valve being in communication with the second chamber;

the electromagnetic switch valve is arranged on the second flow guide pipeline and is positioned between the second one-way valve and the first chamber;

the displacement sensor is used for detecting the length of the upper piston rod extending out of the oil cylinder so as to judge whether the lower piston rod completes the stamping of the blank; wherein:

when the displacement sensor detects that the lower piston rod completes stamping of the blank, the electromagnetic switch is switched to the open state, and the bidirectional hydraulic pump rotates reversely, so that hydraulic oil flowing out of the second oil port enters the third cavity, and hydraulic oil in the first cavity flows into the second cavity.

Preferably, a third check valve and a first pressure switch valve are arranged on the first working management between the first oil port and the first chamber in parallel,

an inlet of the third one-way valve is communicated with the first oil port, and an outlet of the third one-way valve is communicated with the first chamber;

an inlet of the first pressure switch valve is communicated with the first chamber, and an outlet of the first pressure switch is communicated with the first oil port.

Preferably, a second pressure switch valve is arranged on a second working pipeline between the second oil port and the second chamber; wherein:

an inlet of the second pressure switch valve is communicated with the second chamber, and an outlet of the second pressure switch is communicated with the second oil port; wherein:

and a bypass pipeline is led out from the second working pipeline and is used for being communicated with the third chamber.

Preferably, the diameter of the lower rod section is smaller than the diameter of the upper piston rod.

Preferably, the electromagnetic switch valve is a two-position two-way electromagnetic directional valve.

Preferably, a limiting check ring is arranged above the piston and used for limiting the piston.

Preferably, overflow pipelines are led out from positions, close to a first oil port of the bidirectional hydraulic pump, on the first working pipeline and positions, close to a second oil port of the bidirectional hydraulic pump, on the second working pipeline, and overflow valves are arranged on the overflow pipelines and used for limiting the highest working hydraulic pressure of the bidirectional hydraulic pump.

Preferably, the actuator comprises a combined engine and gearbox or a combined electric machine and gearbox.

Compared with the prior art, the stamping device for the gear blank disclosed by the invention has the beneficial effects that:

according to the invention, mutual compensation of hydraulic oil between the chambers is obtained by means of the hydraulic control mechanism, so that the lower piston rod can obtain the effects of fast forward and fast backward, and the supply amount of the hydraulic oil by the bidirectional hydraulic pump is reduced, therefore, the hydraulic pump with smaller discharge capacity can be selected as the bidirectional hydraulic pump.

The summary of various implementations or examples of the technology described in this disclosure is not a comprehensive disclosure of the full scope or all features of the disclosed technology.

Drawings

In the drawings, which are not necessarily drawn to scale, like reference numerals may describe similar components in different views. Like reference numerals having letter suffixes or different letter suffixes may represent different instances of similar components. The drawings illustrate various embodiments, by way of example and not by way of limitation, and together with the description and claims, serve to explain the inventive embodiments. The same reference numbers will be used throughout the drawings to refer to the same or like parts, where appropriate. Such embodiments are illustrative, and are not intended to be exhaustive or exclusive embodiments of the present apparatus or method.

FIG. 1 is a schematic diagram of a hydraulic ram in a press apparatus for gear blanks according to an embodiment of the present invention.

Fig. 2 is a schematic view of a stamping device for gear blanks provided by an embodiment of the present invention in a first state.

Fig. 3 is a schematic view of a punching device for gear blanks provided by an embodiment of the invention in a second state.

Fig. 4 is a schematic view of a punching device for gear blanks provided by an embodiment of the invention in a second state.

Reference numerals:

10-a hydraulic oil cylinder; 11-a cylinder body; 12-a piston; 121-an upper piston rod; 122-lower piston rod; 1221-upper pole segment; 1222-a lower pole segment; 131-a first chamber; 132-a second chamber; 133-a third chamber; 21-a first diversion pipeline; 22-a second diversion line; 31-a first one-way valve; 32-a second one-way valve; 33-a two-position two-way electromagnetic directional valve; 40-a bidirectional hydraulic pump; 41-a first working line; 411-a third one-way valve; 412-a first pressure switch valve; 42-a second working line; 421-a bypass line; 422-a second pressure switch valve; 43-overflow line; 431-overflow valve; 50-an actuator; 60-a displacement sensor; 100-blank.

Detailed Description

Unless defined otherwise, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this invention belongs. The use of "first," "second," and similar terms in the present application do not denote any order, quantity, or importance, but rather the terms are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element or item listed before the word covers the element or item listed after the word and its equivalents, but does not exclude other elements or items. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.

To maintain the following description of the embodiments of the present invention clear and concise, a detailed description of known functions and known components of the invention have been omitted.

As shown in fig. 1 to 4, an embodiment of the present invention discloses a punching apparatus for a gear blank 100, including: hydraulic rams 10, bi-directional hydraulic pump 40, actuator 50 and hydraulic control mechanism.

The actuator 50 comprises a combined engine and gearbox or a combined electric motor and gearbox, and the actuator 50 is connected with an input shaft of the bidirectional hydraulic pump 40 through the gearbox for driving the bidirectional hydraulic pump 40 to operate for pumping hydraulic oil into the hydraulic oil cylinder 10.

The bidirectional hydraulic pump 40 has a first port, a second port, and an oil supply port, and when the rotor of the bidirectional hydraulic pump 40 rotates in the forward direction, hydraulic oil is pumped out from the first port at a certain pressure, and the hydraulic oil flows back through the second port, and the bidirectional hydraulic pump 40 provides the hydraulic oil to the hydraulic cylinder 10 by the hydraulic control mechanism.

The hydraulic cylinder 10 includes a cylinder 11, a piston 12, an upper piston rod 121, and a lower piston rod 122. A piston 12 is disposed in the cylinder 11, an upper piston rod 121 is positioned above the piston 12 and connected to the piston 12, and an upper end of the upper piston rod 121 protrudes out of an upper end of the cylinder 11; the lower piston rod 122 is located below the piston 12, the lower piston rod 122 includes an upper rod segment 1221 and a lower rod segment 1222 coaxially arranged, the upper rod segment 1221 is connected to the piston 12; wherein the diameter of the upper rod segment 1221 is larger than the diameter of the upper piston rod 121, and the diameter of the lower rod segment 1222 is smaller than the diameter of the upper piston rod 121. The lower end of the lower rod 1222 is used to punch a rod-shaped blank 100.

The upper piston rod 121 and the cylinder 11 define a first chamber 131, the upper rod segment 1221 of the lower piston rod 122 and the cylinder 11 define a second chamber 132, and the lower rod segment 1222 of the lower piston rod 122 and the cylinder 11 define a second chamber 133.

The hydraulic control mechanism includes: a first check valve 31, a second check valve 32, a third check valve 411, a two-position two-way electromagnetic directional valve 33, a first pressure switch valve 412, a second pressure switch valve 422 and a displacement sensor 60.

The connection mode between the bidirectional hydraulic pump 40 and the hydraulic cylinder 10 is as follows: the first port is connected to the first chamber 131 via the first working line 41, the second port is connected to the second chamber 132 via the second working line 42, a bypass line 421 leads from the second working line 42, and the bypass line 421 is used for connecting to the third chamber 133.

A first pilot line 21 and a second pilot line 22 are arranged in parallel between the first chamber 131 and the second chamber 132.

A first check valve 31 is provided on the first pilot line 21, an inlet of the first check valve 31 communicates with the second chamber 132, and an outlet of the first check valve 31 communicates with the first chamber 131. A second check valve 32 is disposed on the second pilot line 22, an inlet of the second check valve 32 communicating with the first chamber 131, and an outlet of the second check valve 32 communicating with the second chamber 132. A two-position, two-way solenoid directional valve 33 is disposed on the second pilot conduit 22 between the second check valve 32 and the second chamber 132.

The displacement sensor 60 is disposed on one side above the cylinder 11, and the displacement sensor 60 is configured to detect a length of the upper piston rod 121 extending out of the cylinder 11, and further determine whether the lower end of the lower piston rod 122 completes stamping of the blank 100, and control the two-position two-way electromagnetic directional valve 33 to switch from closed to open when the lower piston rod 122 completes stamping of the blank 100.

The third check valve 411 is provided in the first working line 41 in parallel with the first pressure switching valve 412. The outlet of the third check valve 411 is communicated with the first chamber 131, and the inlet of the third check valve 411 is communicated with the first oil port; the first pressure switch valve 412 is a pilot operated valve, an inlet of the first pressure switch valve 412 is communicated with the first chamber 131, and an outlet of the first pressure switch valve 412 is communicated with the first port.

A second pressure switch valve 422 is provided on the second working line 42, an inlet of the second pressure switch valve 422 is communicated with the second chamber 132, and an outlet of the second pressure switch is communicated with the second port.

An overflow pipeline 43 is led out from the first working pipeline 41 at a position close to the first port of the bidirectional hydraulic pump 40 and from the second working pipeline 42 at a position close to the second port of the bidirectional hydraulic pump 40, and an overflow valve 431 is arranged on each overflow pipeline 43 for limiting the highest working hydraulic pressure of the bidirectional hydraulic pump 40.

The operation of the above-described press apparatus is described as follows:

when the blank 100 needs to be punched, the actuator 50 rotates the bidirectional hydraulic pump 40 forward, so that the hydraulic oil flows out from the first oil port and flows to the first chamber 131 through the first working line 41 and the third one-way valve 411, as shown in fig. 2, the piston 12 drives the lower piston rod 122 to move down, before the lower end of the lower piston rod 122 contacts the blank 100, because the diameter of the upper rod section 1221 of the lower piston rod 122 is larger than the diameter of the upper piston rod 121, the pressure of the hydraulic oil in the second chamber 132 is slightly larger than the pressure of the hydraulic oil in the first chamber 131, and the hydraulic oil in the second chamber 132 flows into the first chamber 131, which can increase the volume increasing speed of the hydraulic oil in the first chamber 131, and further increase the downward movement speed of the piston 12 and the lower piston rod 122, so that the lower piston rod 122 contacts the blank 100 in a fast-forwarding manner, thus, during this process, the bi-directional hydraulic pump 40 does not need to provide a large amount of hydraulic oil to fast forward the lower piston rod 122.

As shown in fig. 3, after the lower end of the lower piston rod 122 contacts the blank 100, the pressure of the hydraulic oil in the first chamber 131 rises to be immediately higher than the pressure of the hydraulic oil in the second chamber 132, thereby forcing the first check valve 31 to close. Thus, downward movement of the lower piston rod 122 is provided entirely by the bi-directional hydraulic pump 40 supplying hydraulic oil into the first chamber 131.

After the displacement sensor 60 detects that the lower piston rod 122 has punched the blank 100, as shown in fig. 4, the two-position two-way electromagnetic directional valve 33 is sequentially controlled to open, so that the two-way hydraulic pump 40 rotates in the opposite direction, and thus, the hydraulic oil flows out from the second oil path and enters the third chamber 133 through the second working line 42 and the bypass line 421, so as to push the piston 12 to move upward, at this time, the pressure of the hydraulic oil in the first chamber 131 is higher than the pressure of the hydraulic oil in the second chamber 132, so as to force the second one-way valve 32 to open, so that the hydraulic oil in the first chamber 131 enters the second chamber 132, which will accelerate the upward movement of the piston 12 and reduce the load of the two-way hydraulic pump 40.

In the whole stamping process:

the first pressure switching valve 412 functions to: the hydraulic oil in the first chamber 131 is allowed to preferentially enter the second chamber 132, and the excess hydraulic oil is returned to the bidirectional hydraulic pump 40 by increasing the pressure in the second chamber 132 to force the first pressure switching valve 412 to open.

The second pressure switch has the functions of: the hydraulic oil in the second chamber 132 is allowed to preferentially enter the first chamber 131, and the excess hydraulic oil flows back to the bi-directional hydraulic pump 40 by raising the pressure in the first chamber 131 to force the second pressure switch to open.

The provision of the relief valve 431 has the advantages that: the highest pressure of the working pipeline is limited, and further, the damage of related elements due to overhigh pressure is avoided.

A limit stop ring for limiting the uppermost position of the piston 12 is also provided in the cylinder 11.

Moreover, although exemplary embodiments have been described herein, the scope of the present invention includes any and all embodiments based on the present invention with equivalent elements, modifications, omissions, combinations (e.g., of various embodiments across), adaptations or alterations. The elements of the claims are to be interpreted broadly based on the language employed in the claims and not limited to examples described in the present specification or during the prosecution of the application, which examples are to be construed as non-exclusive. It is intended, therefore, that the specification and examples be considered as exemplary only, with a true scope and spirit being indicated by the following claims and their full scope of equivalents.

The above description is intended to be illustrative and not restrictive. For example, the above-described examples (or one or more versions thereof) may be used in combination with each other. For example, other embodiments may be used by those of ordinary skill in the art upon reading the above description. In addition, in the above-described embodiments, various features may be grouped together to streamline the disclosure. This should not be interpreted as an intention that a disclosed feature not claimed is essential to any claim. Rather, inventive subject matter may lie in less than all features of a particular disclosed embodiment. Thus, the following claims are hereby incorporated into the detailed description as examples or embodiments, with each claim standing on its own as a separate embodiment, and it is contemplated that these embodiments may be combined with each other in various combinations or permutations. The scope of the invention should be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled.

The above embodiments are only exemplary embodiments of the present invention, and are not intended to limit the present invention, and the scope of the present invention is defined by the claims. Various modifications and equivalents may be made by those skilled in the art within the spirit and scope of the present invention, and such modifications and equivalents should also be considered as falling within the scope of the present invention.

Claims

1. A stamping device for gear blanks, comprising:

an actuator for driving the bidirectional hydraulic pump;

a hydraulic control mechanism; wherein:

2. The stamping apparatus for a gear blank as defined in claim 1, wherein the hydraulic control mechanism includes:

3. The stamping device for gear blank as defined in claim 2, wherein a third check valve and a first pressure switch valve are arranged in parallel on the first working management between the first oil port and the first chamber,

4. The stamping device for gear blanks as recited in claim 2, wherein a second pressure switch valve is disposed on a second working pipeline of the second oil port and the second chamber; wherein:

5. The stamping apparatus for a gear blank as defined in claim 1, wherein the diameter of the lower stem segment is smaller than the diameter of the upper piston stem.

6. The stamping device for gear blanks as recited in claim 2, wherein the solenoid switch valve is a two-position, two-way solenoid directional valve.

7. The stamping device for gear blanks as recited in claim 1, wherein a limit stop ring is disposed above the piston for limiting the piston.

8. The stamping device for gear blanks as recited in claim 1, wherein an overflow line is led out from the first working line at a position close to the first port of the bi-directional hydraulic pump and from the second working line at a position close to the second port of the bi-directional hydraulic pump, and an overflow valve is arranged on the overflow line to limit the maximum working hydraulic pressure of the bi-directional hydraulic pump.

9. A press for gear blanks as claimed in claim 1, wherein the actuator comprises a combined motor and gearbox or a combined motor and gearbox.