CN210685682U

CN210685682U - Stop-and-stop door closer

Info

Publication number: CN210685682U
Application number: CN201920825546.9U
Authority: CN
Inventors: 朱力克; 聂飞
Original assignee: Suzhou Fuerda Technology Co ltd
Current assignee: Suzhou Fuerda Technology Co ltd
Priority date: 2019-06-03
Filing date: 2019-06-03
Publication date: 2020-06-05
Anticipated expiration: 2029-06-03

Abstract

The utility model relates to a stop and decide formula door closer, it includes: the main shell is internally provided with an inner cavity; the piston is arranged in the inner cavity and is connected with a connecting mechanism linked with the opening and closing of the door; a main spring that accumulates door closing energy by the travel of the piston when the door is opened; a first flow path in which a check valve is provided for controlling a flow of a fluid on a front side in a piston traveling direction to a rear side in the piston traveling direction; and when the thrust overcomes the abutting force to move the gate closing valve away from the abutting position, the second flow path communicates the front side and the rear side of the piston in the advancing direction. The door can be easily closed.

Description

Stop-and-stop door closer

Technical Field

The utility model relates to a door closer especially relates to a stop and decide formula door closer.

Background

In windows or doors of buildings such as houses, apartments, and business buildings, a door closer is sometimes used, and the door closer has a spring for storing energy, and the spring stores energy when the door is opened; after the external force is released, the spring releases the accumulated energy, thereby achieving the purpose of automatically closing the door.

There is a need for a door closer that can stop a door and maintain the door in an open state after the door is opened.

Chinese patent publication No. CN 102191899 a discloses a "door closer" of which the embodiment shown in fig. 6 to 9 is capable of stopping a door at any one of open positions, which closes the door with a closing force applied to the door by a human hand, but has disadvantages: in the state shown in fig. 8, when a person applies a door closing force to the door, the right-side oil pressure applied to the check valve 40 is significantly increased, so that the pushing force of the piston rod 38A that can push the check valve 40 is increased, or in short, a large and rapid force is required to close the door.

Chinese patent publication No. CN 87214794U discloses a "delayed automatic door closer with positioning function", which can stop the door at a large angle, but it also has a disadvantage that a large force is required to close the door: when the door closing force is applied to the door to make the oil pressure be greater than the tension of the spring 4, the oil flows back to the oil chamber 5 through the end face of the rubber ring of the valve body 10 in the valve body group, but the spring 4 is a main door closing spring, and a large force is needed to overcome the spring 4 to conduct the valve body 10.

Improvements are therefore needed.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a stop-and-go door closer can close the door more easily.

In order to achieve the above purpose, the utility model adopts the technical scheme that:

the utility model provides a stop and decide formula door closer, it includes:

a main housing having an inner cavity therein;

the piston is arranged in the inner cavity and is connected with a connecting mechanism linked with the opening and closing of the door;

a main spring that accumulates door closing energy by the travel of the piston when the door is opened;

a first flow path in which a check valve for controlling a flow of fluid on a front side in a piston traveling direction to a rear side in the piston traveling direction is provided;

a second flow path in which an associated gate valve is provided, the second flow path being for communicating front and rear sides of the piston in the traveling direction, and maintaining a fluid pressure difference between the front and rear sides of the piston in the traveling direction when the gate is stopped at any opening position within a set movable range to thereby maintain a stopped state of the piston; and releasing the gate closing valve by using the pressure difference in the fluid in which the gate closing valve is positioned.

Because of the application of the technical scheme, compared with the prior art, the utility model has the following advantages:

the utility model discloses a stop and decide formula door closer when the door is in the stop and decide state, promotes to close the door and makes the fluid pressure difference increase of preceding, the rear side of piston advancing direction, and the pressure differential increase in the fluid of closing the door valve is located, removes the shut-off valve through the pressure differential in the fluid of closing the door valve, and the shut-off valve can not increase the trend of closing because of the pressure differential increase in the fluid of closing the door valve to can more easily remove the shut-off valve, make to close the door more light.

The utility model also provides a stop-and-stop door closer, it includes:

a main housing having an inner cavity therein;

the second flow path is provided with a related gate valve, the second flow path is used for communicating the front side and the rear side of the piston in the advancing direction, the second flow path is blocked by using the resisting force borne by the gate valve, and when the gate is stopped at any opening position in a set movable range, the fluid pressure difference between the front side and the rear side of the piston in the advancing direction is kept, so that the stopping state of the piston is maintained; and forming a thrust force by utilizing the pressure difference in the fluid in which the gate closing valve is positioned, and releasing the gate closing valve when the thrust force overcomes the abutting force.

the utility model discloses a stop and decide formula door closer when the door is in the stop and decide state, thereby it makes the pressure differential increase thrust in the fluid that the door closing valve was located to promote to close the door, and the door begins to close when thrust overcomes the tightening force, and the tightening force can not increase because of the pressure differential increase in the fluid that the door closing valve was located, consequently can easily close the door.

The utility model also provides an optimization scheme:

preferably, the piston is provided with a rack, and a pinion is engaged with the rack and connected to the coupling mechanism.

Optimally, the resisting force is not generated by the main spring.

Preferably, the abutment force is generated by an elastic member.

Optimally, the abutment force is adjustably set.

Preferably, the piston further comprises a third flow path which is blocked when the piston travels to the set position, and the third flow path is used for connecting the front side and the rear side of the travel direction of the piston.

Further, a positioning opening is provided at a front end of the third flow path with respect to a forward traveling direction of the piston, and the piston blocks the positioning opening to block the third flow path when the piston travels to the set position.

Further, when the piston travels to the moment of blocking the positioning opening, the door is opened at an angle of 75-85 degrees.

Further, the set position extends continuously in the piston travel direction by a certain length.

Further, the third flow path and the second flow path have a portion that overlaps.

Furthermore, the rear end of the third flow path relative to the forward advancing direction of the piston is provided with at least one communication port distributed in the front and the rear.

Drawings

Some specific embodiments of the present invention will be described in detail hereinafter, by way of illustration and not by way of limitation, with reference to the accompanying drawings. The same reference numbers in the drawings identify the same or similar elements or components. Those skilled in the art will appreciate that the drawings are not necessarily drawn to scale. In the drawings:

fig. 1 is a schematic view of a stop-and-close door closer according to embodiment 1 of the present invention mounted on a door and a doorframe;

FIG. 2 is a cross-sectional view of the door closer of the embodiment of FIG. 1, with the door in a closed position;

FIG. 3 is a cross-sectional view of the door closer of the embodiment of FIG. 1, with the door opening;

FIG. 4 is a cross-sectional view of the door closer of the embodiment of FIG. 1, with the door closing;

FIG. 5 is a cross-sectional view of the door closer of the embodiment of FIG. 1 with the door resting in an open position;

FIG. 6 is a cross-sectional view of the door closer of the embodiment of FIG. 1 with the door manually closed and the door closing from a rest position;

fig. 7 is a door closer of the stop type according to embodiment 2 of the present invention, in which a releasing unit for releasing the gate valve is additionally provided on the basis of embodiment 1;

fig. 8 is another state diagram of fig. 7, in which the door closing valve is released by the release unit;

fig. 9 is a sectional view of a door closer according to embodiment 3 of the present invention, in which a release unit is added to the embodiment 1, and the release unit releases the second flow path in another manner;

FIG. 10 is another state diagram of FIG. 9, in which the releasing unit releases the action of the second flow path by conducting the fourth flow path;

fig. 11 is a cross-sectional view of a park type door closer according to embodiment 4 of the present invention, with a second flow path provided in the piston;

FIG. 12 is an enlarged schematic view of the left end wall of the piston of FIG. 11;

FIG. 13 is a schematic view of a gate closing valve and its adjacent components in a further embodiment, the gate closing valve blocking the second flow path but not being continuously biased;

FIG. 14 is a schematic view of the conversion of a door closer to have a time delay door closing function;

wherein the reference numerals are as follows:

1. a door closer;

2. a main housing;

3. a coupling mechanism;

4. a first arm;

5. a second arm;

6. a second valve chamber;

7. an inner cavity;

8. a piston;

9. a main spring;

10. a pinion gear;

11. a gear shaft;

12. a one-way valve;

13. a first flow path;

14. a first valve chamber;

15. a second flow path;

16. closing the gate valve;

17. a small spring;

18. a rack;

19. a third flow path;

20. positioning the opening;

21. a communication port;

22. a release unit;

23. a push rod;

24. a conductive coil;

25. a fourth flow path;

26. a first chamber;

27. a second chamber;

28. an adjusting block;

A. a door;

B. a door frame opening;

C. a door frame.

Detailed Description

The technical solution of the present invention will be described clearly and completely with reference to the accompanying drawings, and obviously, the described embodiments are some, but not all embodiments of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

Furthermore, the technical features mentioned in the different embodiments of the invention described below can be combined with each other as long as they do not conflict with each other.

Example 1

As shown in fig. 1, the door closer 1 is installed on a door a provided at a door frame opening B and hinged to a side of the door frame C and the door frame C. The main housing 2 of the door closer 1 is mounted on the door a and the coupling mechanism 3 is attached to the upper head of the door frame C. The coupling mechanism 3 comprises a first arm 4 and a second arm 5. One end of the second arm 5 is hinged with the upper head of the door frame C, the other end of the second arm 5 is hinged with one end of the first arm 4, and the other end of the first arm 4 is hinged with the main shell 2.

As shown in fig. 2, actually, the other end of the first arm 4 is fixed to the gear shaft 11.

As shown in fig. 2, the door closer 1 includes a main housing 2, an inner cavity 7 is disposed in the main housing 2, and a piston 8 is slidably disposed in the inner cavity 7. The inner cavity 7 is filled with fluid, the fluid is hydraulic oil, and the fluid can also be inert gas in other technical schemes. The inner cavity 7 is in a sealed state, so that hydraulic oil is not lost.

The side wall of the piston 8 is provided with a rack 18, a pinion 10 is meshed with the rack 18, a gear shaft 11 is integrally arranged on the pinion 10, and the gear shaft 11 is fixed with the first arm 4 (see figure 1), namely, the pinion 10 is linked with the door through the linking mechanism 3.

A first flow passage 13 is provided in the left end wall of the piston 8, and the left and right ends of the first flow passage 13 are connected to the left and right sides of the left end wall of the piston 8. A first valve chamber 14 is provided in the first flow path 13, and a check valve 12 is provided in the first valve chamber 14, and the check valve 12 controls the flow of the hydraulic oil only from the right side to the left side of the left end wall of the piston 8. The first flow path 13 may not be provided in the piston 8, and the first flow path 13 mainly functions to communicate the fluid in the front and rear side chambers 7 in the traveling direction (traveling to the right side) of the piston 8, and therefore, the first flow path 13 may be provided in the main casing 2 or formed between the piston 8 and the inner wall of the main casing 2.

A main spring 9 is arranged between the left end wall of the piston 8 and the right side wall of the main shell 2, and two ends of the main spring 9 are not connected with the piston 8 and the inner wall of the main shell 2, but compressed and tightly propped between the left end wall of the piston 8 and the right side wall of the main shell 2.

The main casing 2 is also provided with a second flow path 15, and the second flow path 15 is used for communicating the front and rear inner chambers 7 of the piston 8 when the piston 8 travels (travels to the right). The second flow path 15 is provided with a second valve chamber 6, and the second valve chamber 6 is provided with a gate valve 16. The gate valve 16 is continuously urged against the left end opening of the second valve chamber 6 by the small spring 17, thereby blocking the second flow path 15. The gate valve 16 is in a continuously closed state, that is, the second flow path 15 is in a continuously blocked state.

In this case, the resisting force applied to the closing valve 16 is generated by an elastic member, i.e. a small spring 17, but in other embodiments, the resisting force may be formed in other manners, for example, the resisting force is formed by the gravity of the closing valve 16 itself, and the closing valve 16 may be placed on the opening of the second flow path 15 facing the inner cavity 7, or a weight member may be applied to the closing valve 16 to increase the resisting force applied to the closing valve 16.

In other solutions, the closing valve 16 may not bear the resisting force when blocking the second flow path 15, for example, as shown in fig. 13, the closing valve 16 is naturally blocked when being placed in the second flow path 15, and after the pushing force generated by the pressure difference of the closing valve 16 moves to the right for a short distance, the closing valve contacts with the small spring 17 and is subjected to the resisting force generated by the compression of the small spring 17, so that the beneficial effect is that the small spring 17 is not continuously pressed when the door is in the closed state, and the service life is prolonged.

As shown in fig. 2, a third flow path 19 is further provided in the main casing 2, and the third flow path 19 communicates with the front and rear side cavities 7 of the piston 8 when the piston 8 travels (travels rightward).

The third flow path 19 has a positioning opening 20 at the right end, and the left and right positions of the positioning opening 20 are set in advance.

The second flow path 15 and the third flow path 19 have a portion overlapping each other, and the door closer is made more compact. The flow path overlapping portion passes through the pinion 10 to lubricate the pinion 10.

Three communication ports 21 are provided at the left end of the overlapping portion of the second flow path 15 and the third flow path 19, and the three communication ports 21 are distributed in the left-right direction (distributed in the front-rear direction of travel of the piston 8) to vary the opening and closing speed.

As shown in fig. 3, the door is opened manually. The door acts on the gear shaft 11 through the first arm 4 in the coupling mechanism 3 (see fig. 1), the gear shaft 11 drives the pinion 10 to rotate clockwise, the pinion 10 drives the rack 18 engaged with the pinion 10 to move rightward, and the piston 8 moves rightward. At this time, the check valve 12 is in an open state, and the hydraulic oil flows from the first chamber 26 on the front side in the traveling direction of the piston 8 into the second chamber 27 on the rear side in the traveling direction of the piston 8 through the first flow path 13. When the piston 8 advances, the main spring 9 is continuously compressed to accumulate the door-closing energy.

As shown in fig. 3, when the piston 8 moves rightward, the positioning opening 20 of the third flow path 19 is not covered yet. When the door opening power is removed, the accumulated door closing energy of the main spring 9 is released to apply a leftward force to the piston 8, as shown in fig. 4. The check valve 12 blocks the first flow path 13, and the hydraulic oil in the first chamber 26 flows to the second chamber 27 through the third flow path 19. The piston 8 backs up to the left to the initial position (corresponding to the fully closed state of the door) which causes the door to close slowly due to the restriction of the third flow path 19.

As shown in fig. 5, when the piston 8 moves rightward when the door is opened, the positioning opening 20 of the third flow path 19 is blocked, and the third flow path 19 is blocked. When the door opening power is removed, the door closing energy accumulated by the main spring 9 has a release tendency to apply a leftward acting force to the piston 8, the check valve 12 blocks the first flow path 13, the first chamber 26 is not communicated with the second chamber 27, negative pressure is formed in the first chamber 26, positive pressure is formed in the second chamber 27, and the rightward acting force formed by the pressure difference between the first chamber 26 and the second chamber 27 acting on the piston 8 is opposite to the leftward acting force of the main spring 9 on the piston 8 to keep the piston 8 stationary, so that the door is kept in a stopped state. And the rightward force of the piston 8 by the pressure difference is greater than the leftward force of the piston 8 by the main spring 9 to counter the interference of a slight external force such as wind force with the door.

As shown in fig. 6, the pressure difference between the first chamber 26 and the second chamber 27 forms a rightward thrust to the gate valve 16 through the second flow path 15, the thrust being in opposition to the leftward biasing force of the small spring 17 to the gate valve 16. When a door closing force is applied to the door, the pressure difference between the first chamber 26 and the second chamber 27 is further increased, the rightward thrust formed by the pressure difference acting on the closing valve 16 is further increased until the thrust overcomes the abutting force of the small spring 17 on the closing valve 16 to move the closing valve 16 away from the abutting position (the closing valve 16 moves rightward), the second flow path 15 is communicated to form a passage, the second flow path 15 communicates the first chamber 26 with the second chamber 27, and hydraulic oil in the second chamber 27 flows to the first chamber 26 through the second flow path 15 by the pressure difference. The piston 8 is reversed to the left and the door is closed.

When the piston 8 backs up to the left to unblock the positioning opening 20, as shown in the state of fig. 4, the closing door valve 16 blocks the second flow path 15 again, if the closing door power is removed, the hydraulic oil flows from the second chamber 27 to the first chamber 26 through the third flow path 19, the piston 8 moves slowly to the left under the pushing action of the main spring 9, and the door is closed slowly.

In this case, the main casing 2 is fitted with an adjustment block 28, and the small spring 17 is held in abutment between the adjustment block 28 and the door closing valve 16. The left and right positions of the regulating block 28 are adjustable, for example, the regulating block 28 is screwed in the main shell 2, so that the force of the small spring 17 against the gate valve 16 is adjustable, namely, the force of the small spring 17 against the gate valve 16 is adjustable. This allows the necessary closing force to be adjusted after the door has been stopped. And further can also convert the door closer into a door closer with automatic time delay door closing function: as shown in fig. 14, the tightening force of the small spring 17 against the door closing valve 16 is further reduced (the adjusting block 28 is further moved to the right), when the piston 8 moves to the rightmost end after the door is opened (the door is opened to the maximum amplitude), the door opening power is removed, and the door closing power is not applied, so that the compressed main spring 9 generates a leftward acting force on the piston 8, the rightward pushing force formed by the pressure difference in the fluid of the door closing valve 16 on the door closing valve 16 overcomes the tightening force of the small spring 17, the door closing valve 16 is slightly moved to the right, the hydraulic oil flows from the left side to the right side of the door closing valve 16 at a slight flow rate, and the door is slowly closed. The tightening force of the small spring 17 is adjusted so that the flow through the shut-off valve 16 is small enough that the piston 8 reverses from the rightmost position to the left to unblock the positioning opening 20 for a sufficient time so that the door closes slowly enough for an automatic delayed closing effect.

The left and right positions of the positioning opening 20 are set, when the piston 8 moves rightwards to the moment of shielding the positioning opening 20, the opening angle of the door is 75-85 degrees correspondingly, the door can be stopped after the door opening power is removed, and the piston 8 continues to move rightwards to any position and stops the door. The door can therefore be substantially stopped in the range of greater than 75 deg. -85 deg. -90 deg.. The angular range in which the door can be stopped is adjusted by adjusting the left-right position of the positioning opening 20.

If the position of the piston 8 when the piston 8 blocks the positioning opening 20 is referred to as a set position, the set position extends for a certain length in the traveling direction of the piston 8 in this example, and after the piston 8 travels to the moment of blocking the positioning opening 20, the positioning opening 20 is always in the blocking state when the piston 8 continues to travel. The door can be stopped at any opening position within the set movable range. The set range is a range between the position at which the door is opened at the moment the piston 8 travels to block the positioning opening 20 until the door is fully opened.

In other embodiments, the third flow path 19 may not be provided, and the door may be stopped at any position where the door is opened.

Example 2

As shown in example 2 of fig. 7, a removal unit 22 is added to example 1, and the same portions as those of example 1 are denoted by the same reference numerals. The release unit 22 is for releasing the gate valve 16.

The releasing unit 22 includes a push rod 23 and a power member, i.e., a conductive coil 24, for pushing the push rod 23. The push rod 23 is magnetic and is disposed in the conductive coil 24. When the conductive coil 24 is energized, the magnetic field generated by the conductive coil 24 acts on the push rod 23 to push the push rod 23 forward to press the small spring 17 so as to apply a continuous abutting force to the gate valve 16. The door closer functions in this case in the same manner as in embodiment 1.

When the electrically conductive coil 24 is de-energized, as shown in fig. 8, the magnetic field of the electrically conductive coil 24 is released, and the push rod 23 releases the urging force against the closing door valve 16, so that the closing door valve 16 is moved rightward by the rightward thrust due to the pressure difference in the second flow path 15, and the closing door valve 16 is deactivated, that is, the closing door valve 16 is released. At this time, the door is released from the stationary state, and the door is slowly closed. By de-energizing the conductive coil 24, the door can be closed without the use of a human hand to close the door. And the conductive coil 24 may be de-energized at any time as desired to perform control to close the door at any time.

The small spring 17 between the closing gate valve 16 and the front end of the push rod 23 plays a certain role in buffering and protecting the closing gate valve 16. When the push rod 23 retracts, the pressing action of the small spring 17 on the gate valve 16 is released.

The current and voltage in the conductive coil 24 can be adjusted, the force of the push rod 23 abutting against the small spring 17 is adjusted, and the door closing force or the automatic delay door closing function required after the door is stopped can be adjusted by adjusting the left and right positions of the adjusting block 28 in the embodiment 1.

Example 3

As in embodiment 3 shown in fig. 9, the removal unit 22 is also provided, and the same portions as those in embodiment 1 are denoted by the same reference numerals. Unlike embodiment 2, the release unit 22 does not directly act on the gate valve 16, but acts on the additional fourth flow path 25, and the additional fourth flow path 25 is matched with the release unit 22.

The fourth flow path 25 is provided in the main casing 2 and connects the front and rear chambers 7 in the traveling direction of the piston 8. The releasing unit 22 includes a push rod 23 and a power member, i.e., a conductive coil 24, for pushing the push rod 23. The push rod 23 is magnetic and is disposed in the conductive coil 24. When the conductive coil 24 is energized, the magnetic field generated by the conductive coil 24 acts on the push rod 23 to advance the push rod 23 into the fourth flow path 25, and the fourth flow path 25 is blocked. The door closer functions in this case in the same manner as in embodiment 1.

When the conductive coil 24 is de-energized, as shown in fig. 10, the magnetic field of the conductive coil 24 is released, and the push rod 23 is pushed backward by the acting force formed by the pressure difference in the fourth flow path 25, so that the fourth flow path 25 is conducted, and the function of the second flow path 15 is released, that is, the function of the second flow path 15 and the function of controlling the hydraulic oil flow by the door-closing valve 16 in the second flow path 15 are released. At this time, the door is released from the stationary state, and the door is slowly closed. By de-energizing the conductive coil 24, the door can be closed without the use of a human hand to close the door. And the conductive coil 24 may be de-energized at any time as desired to perform control to close the door at any time.

Example 4

As shown in fig. 11, embodiment 4 is different from embodiment 1 mainly in the position of the second flow path 15. The second flow path 15 is provided in the main casing 2 in embodiment 1, and the second flow path 15 is provided in the piston 8 in this embodiment, as shown in detail in fig. 12. The resulting benefit is that the door closing valve 16 is able to receive the pressure differential change across the second flow path 15 more quickly, and thus more quickly respond to the door closing action.

The above embodiments are only for illustrating the technical concept and features of the present invention, and the purpose thereof is to enable those skilled in the art to understand the contents of the present invention and to implement the present invention, so as not to limit the protection scope of the present invention, and all equivalent changes or modifications made according to the spirit of the present invention should be covered by the protection scope of the present invention.

Claims

1. A stop-and-go door closer, comprising:

the device comprises a main shell (2), wherein an inner cavity (7) is arranged in the main shell (2);

the piston (8), the said piston (8) is set up in the said cavity (7), the said piston (8) is connected to the linkage mechanism (3) linked with opening and shutting of the door;

a main spring (9), wherein the main spring (9) accumulates door closing energy by the travel of the piston (8) when the door is opened;

a first flow path (13), wherein a one-way valve (12) is arranged in the first flow path (13), and the one-way valve (12) is used for controlling the fluid on the front side of the piston (8) in the advancing direction to flow to the rear side of the piston (8) in the advancing direction;

a second flow path (15), a related gate valve (16) is arranged in the second flow path (15), the second flow path (15) is used for communicating the front side and the rear side of the advancing direction of the piston (8), the second flow path (15) is blocked by the resisting force applied by the gate valve (16), and when the gate is stopped at any opening position in a set moving range, the fluid pressure difference of the front side and the rear side of the advancing direction of the piston (8) is kept, so that the stopping state of the piston (8) is maintained; the pressure difference in the fluid in which the shut-off valve (16) is located is used to form a thrust force, and the shut-off valve (16) is released when the thrust force overcomes the abutting force.

2. The stop-and-go door closer of claim 1, wherein: the piston (8) is provided with a rack (18), a pinion (10) is meshed with the rack (18), and the pinion (10) is connected to the connecting mechanism (3).

3. The stop-and-go door closer of claim 1, wherein: the resisting force is not generated by the main spring (9).

4. The stop-and-go door closer of claim 1, wherein: the abutting force is generated by deformation of the elastic member.

5. The stop-and-go door closer of claim 1, wherein: the abutting force is adjustable.

6. The stop-and-go door closer of claim 1, wherein: it also comprises a third flow path (19), the third flow path (19) being blocked when the piston (8) travels to a set position, the third flow path (19) being used to connect the front and rear sides of the direction of travel of the piston (8).

7. The stop-and-go door closer of claim 6, wherein: the third flow path (19) is provided with a positioning opening (20) at the front end in the forward travel direction of the piston (8), and the piston (8) blocks the positioning opening (20) and blocks the third flow path (19) when the piston (8) travels to the set position.

8. The stop-and-go door closer of claim 7, wherein: when the piston (8) moves to the moment of shielding the positioning opening (20), the opening angle of the door is 75-85 degrees correspondingly.

9. The stop-and-go door closer of claim 6, wherein: the set position extends continuously over a certain length in the direction of travel of the piston (8).

10. The stop-and-go door closer of claim 6, wherein: the third channel (19) and the second channel (15) have a portion that overlaps.